WO2001044727A1 - Water heater and water heater component construction - Google Patents
Water heater and water heater component construction Download PDFInfo
- Publication number
- WO2001044727A1 WO2001044727A1 PCT/AU1999/001106 AU9901106W WO0144727A1 WO 2001044727 A1 WO2001044727 A1 WO 2001044727A1 AU 9901106 W AU9901106 W AU 9901106W WO 0144727 A1 WO0144727 A1 WO 0144727A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- water
- water heater
- plates
- plate
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
- F24H1/12—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
- F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/10—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium
- F24H1/12—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium
- F24H1/124—Continuous-flow heaters, i.e. heaters in which heat is generated only while the water is flowing, e.g. with direct contact of the water with the heating medium in which the water is kept separate from the heating medium using fluid fuel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
- F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
- F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
- F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
- F24H1/44—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with combinations of two or more of the types covered by groups F24H1/24 - F24H1/40 , e.g. boilers having a combination of features covered by F24H1/24 - F24H1/40
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/48—Water heaters for central heating incorporating heaters for domestic water
- F24H1/52—Water heaters for central heating incorporating heaters for domestic water incorporating heat exchangers for domestic water
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/48—Water heaters for central heating incorporating heaters for domestic water
- F24H1/52—Water heaters for central heating incorporating heaters for domestic water incorporating heat exchangers for domestic water
- F24H1/526—Pipes in pipe heat exchangers for sanitary water
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
Definitions
- This present invention relates to a fired instantaneous water heaters and other instantaneous types such as combination boilers, central room heaters, commercial and industrial water heaters and water processing systems to name some others. More particularly the present invention relates to a heat exchanger and a water jacket assembly for such water heaters. The invention also relates to a method of manufacturing such a water heater. These water heaters can be used to heat not just potable water, but mixtures of water and other additives whether potable or not. Such instantaneous fired water heaters provide hot water on demand.
- Instantaneous water heaters are common in colder climates as they can be used for the dual purpose of providing hot water of approximately 80°C for central room heating as well as hot potable water at approximately 50°C for cooking and washing.
- the present invention provides a water heater heat exchanger element being formed from first and second plates joined together to form at least one channel therebetween to provide at least one liquid flow path inside of said element and a combustion heat transfer surface on the outside thereof, said element being characterised by said at least one flow path each consisting of a single path which extends across a portion of said element in one direction and across said portion in the opposite direction, in a serpentine manner.
- the flow path can extend partially or fully across the width of the element.
- the flow path when extending across the plate does so in preferably a zig zag or sinusoidal configuration. Further the serpentine manner is such that the flow path winds back over itself at least once, and preferably two to four times.
- the water flow path is preferably shaped like one of the following: generally helical; cork screw; square helical; or vortex shaped.
- the first plate can have a single continuous groove whereby when a flat second plate is joined thereto, said channel is formed.
- said first and second plates each have a series of discrete dimples therein, whereby adjacent dimples on said first plate are connected by the series of adjacent and partially overlapping dimples on said second plate.
- the flow path requires liquid flowing therein to travel along one of said dimples in said first plate having a straight line pathway then flow through an approximately 90° direction change into said second plate then through an approximately 90° direction change to flow through an adjacent dimple in said second plate in a straight line pathway through said adjacent dimple.
- the dimples can provide a straight line path after transition from said first plate to said second plate whereby the maximum length of the straight line path is in the range of two to ten times the depth or height of the dimple.
- the first and second plates each have a flared end extending away from a joining plane of said first and second plates.
- the flared ends can extend along the side edges of said plate from said leading edge to said trailing edge. Also said flared ends can extend for a distance in the direction towards the centre of said plate along said leading and trailing edges.
- the element is formed from identical plates placed back to back.
- the heat exchanger element and or plates forming said heat exchanger element have a nestable shape.
- the heat exchanger element and plates from which it is formed has or have a shape which includes a main portion and at least two arms extending away from the main portion.
- the at least two arms can extend in the one of the following directions away from the main portion: parallel to each other; diverging away from each other; converging towards each other; or produces any one of the following shapes: a Y shape, U shape, C shape, E shape H shape, V shape or any other appropriate shape.
- the arms of the form a water jacket around a combustion chamber, while the main portion forms a heat exchanger unit.
- the exchanger element can also have a shape whereby the at least two arms extend in opposite directions to each other, such as in a T shape, with the cross bar of said T shape forming an end wall of said combustion chamber.
- the element formed includes at least one dimple formation thereon whereby when two or more of such elements are positioned side by side, said dimple formations are aligned to form a header which can receive a liquid and which will direct said liquid through each of said heat exchanger elements simultaneously.
- the leading edge of the plates and or the element formed from the plates or is scalloped or curved so that most points along said leading edge have a minimum distance to the nearest channel such that said minimum distances are similar.
- the plates each have a formation to allow all plates to be nested together prior to holding or joining them together.
- the formation is preferably a flange on said first and second plates such that when placed back to back said flanges all extend in the same general direction.
- the flange is preferably at an angle to said plate.
- the flange can extend partially around the periphery of said plates or alternative a wholly around the periphery of said plates, where a combustion products path is provided.
- the heat exchanger elements can be formed from plates made from two or more plate segments which are bonded together to from a composite single plate. Such a composite single plate can have different materials in the different plate segments. The different materials can be chosen on the basis of heat resistance characteristics. If desired a series heat exchange elements can have a leading edge formed of a different material to that portion of the heat exchange element which contains said dimples or channels. The leading edges can have a shape which will help to maintain the temperature in the combustion chamber in order to promote combustion.
- Heat exchanger elements can include a by pass channel or dimple which connects an entry header to an exit header. Further if desired the water flow paths in the heat exchanger elements can cross over each other at predetermined points to enable water flowing therein to mix with, pass through, or pass over and under, each other.
- the invention also provides a water heater heat exchanger element being formed from a first plate and a second plate forming a channel therebetween to form a liquid flow path inside of said heat exchanger and a heat transfer surface on the outside of said heat exchanger element wherein the configuration of said liquid flow path and said heat transfer surface is varied across the width of said exchange element.
- the first plate can have a single continuous groove wherein when a flat second plate is joined thereto said liquid flow path is formed.
- said first and second plate each have a series of discrete dimples whereby adjacent dimples on said first plate are connected by dimples on said second plate to form said liquid flow path.
- said flow path is of a zig zag or sinusoidal configuration.
- the liquid flow path can be configured to provide at near to a leading edge thereof longer straight line sections compared with the length of straight line sections in the vicinity of a trailing edge of said element.
- the flow path is preferably a single path which travels over all or part of said element in a serpentine manner. Preferably said path extends across part or all of said element at least two.
- the path can be such that the included angle between lengths of dimples or segments of channels on said first and/or second plate in the vicinity of a leading edge is varied by comparison to the included angle in the region of a trailing edge. Also if desired the amplitude of said zig zag or sinusoidal configuration can be varied in said flow path in the vicinity of said leading edge by comparison to the amplitude of said zig zag or sinusoidal configuration in the vicinity of said trailing edge.
- the flow path can be divided into a multiple number of parallel flow paths connecting a channel across said elements in the vicinity of said trailing edge to a channel across said elements in the vicinity of said leading edge.
- the thickness of said heat exchanger is varied from said leading edge to said trailing edge.
- the depth of said dimples on said plate or plates is varied from said leading edge to said trailing edge.
- a combustion products flow path is formed between adjacent plates, said flow path, near to said leading edges being wider than at said trailing edges.
- the water heater heat exchanger element as described above has a greater than one pair of inlets and outlets so that said heat exchanger element can have more than one liquid circuit passing therethrough.
- the hottest parts of the heat exchanger element receive a first circuit, while a second circuit is heated in a cooler part of the element.
- the water heater heat exchange element can have, in addition to a series of discrete dimples, a continuous peripheral path to serve a water jacket function.
- the invention also provides a heat exchanger formed from a plurality of heat exchanger elements as described above, said elements being like oriented in said heat exchanger and placed parallel.
- the outside surfaces of dimples of said first plate of one element make contact with outside surfaces of dimples on said second plate of another element at discrete lines or points of contact.
- the discrete lines or points of contact preferably fused, soldered, brazed or otherwise connected or contacting each other, by such other means as mechanical clamping forces etc.
- the heat exchanger so formed is such that when in use, combustion products are forced around said channels and said discrete lines or points of contact forming a convoluted combustion path through said heat exchanger.
- the invention further provides a water jacket assembly for an instantaneous gas fired water heater, the assembly including plates having therein an array of dimples, said plates being placed together in pairs, the pairs of plates being arranged in parallel to form a heat exchanger, the heat exchanger being bordered by a water jacket being formed from plates having therein channels or dimples to allow water to flow through said jacket, said jacket being joined to or integral with the heat exchanger, said heat exchanger and water jacket having passages interconnecting them to allow liquid to pass between the plates, the assembly being held together to define a combustion chamber with combustion product passages and water passages within said assembly.
- the water jacket assembly includes a heat exchange element or a heat exchanger as described above
- said water jacket assembly is formed from a plurality of plates including at least a U or Y shaped plate to form a heat exchanger as described above and at least a T shape plate to form a second heat exchanger element as described above whereby each of said plurality of plates are joined back to back with like plates to form a plurality of intermediate and end heat exchange elements, said water jacket assembly being constructed by sandwiching said intermediate heat exchangers between said end heat exchangers and holding them together.
- the elements can be generally vertically oriented so that when said elements are assembled leading edges of said elements are generally aligned with the depth of said unit; or generally vertically oriented so that when said elements are assembled the leading edges of said elements are generally aligned with the width of said unit; or generally horizontally oriented.
- said elements include apertures therethrough to permit combustion products to flow between pairs of elements.
- the plates of the heat exchanger are adapted to cause turbulent flow of water through the water passages; and or are adapted to cause turbulent flow of combusted gases past the exterior; and or are such that their exterior also provides an escape path for condensate that in use collects on the external surfaces of the heat exchanger.
- the invention further provides a water heater having a heat exchanger as described above and or a water jacket assembly as described above.
- the water heater can include a storage means to receive hot water which would otherwise remain in said apparatus when a user has closed a valve preventing further hot water passing through said valve.
- the hot water in said storage means can be passed through said valve once said valve is re-opened.
- the present invention also provides a water heater system having at least two water flow paths, with both paths passing through a water/gas heat exchanger, which transfers heat from combustion products to water contained in said circuits, a first of said at least two paths including a serial connection to a radiator means and a serial connection to a water/water heat exchanger where water in said first path can transfer heat to or receive heat from water in said second path.
- a water in said first path is in a closed loop.
- the second of said at least two paths includes a cold water inlet.
- the cold water inlet can split into two water flow sub-paths, a first sub-path to deliver water to said water/water heat exchanger and a second sub-path to deliver water said water/gas heat exchanger.
- the second sub-path can merge with said first sub path for water to flow out of said system, when a valve on an outlet conduit from said system is in an open condition.
- water in said first and second sub-paths is circulated.
- the invention also provides a water jacket assembly for an instantaneous gas fired water heater, the assembly including pressed profiled plates, one plate being the inverted image of the other, said plates being placed together in pairs, the pairs of plates being arranged in a parallel to form a heat exchanger, the heat exchanger being bordered by a water jacket comprising overlapping side and end panels of copper or copper coated steel attached to the heat exchanger, the assembly being fused together to define a combustion chamber with discrete combusted gases and water passages within said assembly.
- the profiled plates of the heat exchanger are adapted to cause turbulent flow of water through the water passages, and turbulent flow of combusted gases past the exterior, the exterior also providing escape routes for condensate that in use collects on the external surfaces of the heat exchanger.
- the water jacket has a cold water inlet and a hot water outlet, at least one gas burner being positioned within the combustion chamber whereby cold water flows through the assembly to exit as hot water.
- the at least one gas burner is positioned above the heat exchanger and the heater includes a fan that mixes gas with air and forces the gas/air mixture to the burner and, as combusted gases past the heat exchanger.
- the invention also provides a method of manufacturing a water jacket assembly including making profiled heat exchanger plates, placing pairs of plates together to form a heat exchanger element, placing a plurality of heat exchanger elements together to form a sandwich, said assembly having a combustion chamber and combustion products passages and water passages within said assembly.
- Preferably two type of heat exchanger elements are formed, end elements and intermediate elements with said end elements having a different water path to said intermediate elements.
- heat exchanger plates are manufactured such that those portions not required on a blank for one plate are a part of the next successive plate stamped.
- the heat exchanger elements can be assembled as a set of parallel plates, which can be any one of the following: vertically oriented or horizontally oriented. If vertically oriented the elements can extend such that their leading edges run generally parallel to the width of the combustion or water heater into which the water jacket assembly will be installed.
- the elements can extend such that their leading edges run generally parallel to the depth of the combustion or water heater into which the water jacket assembly will be installed.
- a method of manufacturing a water jacket assembly comprising pressing profiled heat exchanger plates, side panels and end panels out of copper or copper coated steel, placing two plates together, one being the inverted image of the other to form a pair of abutting plates, placing a plurality of pairs of heat exchanger plates together to form a sandwich, attaching the side panels to the sandwich and placing the end plates on each corner so that the side and end panels overlap, holding the assembly with a jig, and placing the assembly in an oven for a predetermined time to fuse the copper surfaces together to provide an integral assembly having a combustion chamber and discrete combusted gases and water passageways within said assembly.
- an instantaneous gas fired water heater comprising a heat exchanger through which water flows to be heated by a gas fired burner, the heat exchanger having a cold water inlet and a hot water outlet, an air tight chamber positioned downstream of the hot water outlet of the heat exchanger whereby when the demand for hot water ceases, the internal pressure within the hot water system causes hot water to flow from the heat exchanger into the air chamber to reduce the temperature of the heat exchanger.
- the air chamber preferably comprises a sealed tank that initially contains only air, the internal pressure of the system causing the tank to fill when no water is being drawn off and causing the tank to empty as hot water is drawn off, the tank refilling when demand for hot water ceases.
- a water jacket assembly comprising a plurality of heat exchanger plates pressed out of metal, the plates being placed together in inverted pairs in parallel, each plate having peripheral side portions that overlap as the plates are placed together, a pair of end panels being positioned at the ends of the heat exchanger plates with overlapping edges whereby the assembly can be placed in an oven on its end so that the weight of the assembly causes the plates and panels to fuse together to define discrete water and air passageways.
- the profile of the plates and panels defines a heat exchanger surrounded by a water jacket, the water jacket defining a combustion chamber within the assembly.
- Figure 1 is a front elevation view of a water heater being one embodiment of the invention, with the front portion of its water jacket assembly removed;
- Figure 2 is a left side elevation of the heater of Figure 1 ,
- Figure 3 is a right side elevation of the heater of Figure 1 ;
- Figure 4 is an exploded perspective view of components of a water jacket assembly
- Figure 5 is a front elevation of a water jacket assembly used in the water heater of Figure 1 ;
- Figure 6 is a side elevation of the water jacket assembly of Figure 5;
- Figure 7 is a plan view of the water jacket assembly of Figure 5, with the heat exchanger 51 shown in schematic representation, for a detail of the plan view of the heat exchanger refer to figure 23;
- Figure 8 is a diagrammatic cross section through the plate 53 of Figure 9 along plane A-A;
- Figure 9 is a front elevation of the plate 53 of Figure 4;
- Figure 10 is a representation of the water flow path as viewed in front elevation formed from plates 53 and 54 of
- Figure 11 is a rear view of plate 54 of Figure 4.
- Figure 12 is a diagrammatic cross section through the plate 54 of Figure 1 1 along plane BB;
- Figure 13 is a diagrammatic cross section through heat exchangers formed from pairs of plates 53 and 54;
- Figure 14 is an enlarged view of part of the cross section of Figure 8F;
- Figure 15 is a diagrammatic perspective view of a heat exchanger assembled from elements formed from pairs of plates 53 and 54 of Figures 4, 9 and 11 with combustion products and water path ways ;
- Figure 16 is a detail view of three of the dimples of plate 54 of Figure 11 ;
- Figure 17 is an enlarged view of two whole dimples of the plate 53 of Figure 9;
- Figure 18 illustrates the dimples of Figures 16 and 17 connected together back to back;
- Figure 19 illustrates portions of plates 53 and 54 (in spaced apart relation for clarity) indicating diagrammatically the flow path of liquid through the plates and passages formed when the plates are abutted face to face;
- Figure 20 illustrates a typical combustion gas flow path over the external surface of plate 53 of Figure 9;
- Figure 21 illustrates a typical combustion gas flow path over the external surfaces of plate 54 of Figure 11 ;
- Figure 22 illustrates the drawings of Figure 20 and 21 combined showing the convoluted combustion gas flow path between adjacent contacting elements formed from plates 53 and 54;
- Figure 23 illustrates a plan view of a heat exchanger made up of plates 53 and 54 of Figure 4;
- Figure 24 is a plan view of a single dimple
- Figure 25 is a side elevation of the dimple of Figure 24;
- Figure 26 is a cross section through line BB of Figure 25;
- Figure 27 is a cross section through line CC of Figure 25;
- Figure 28 illustrates a front view of a plate of heat exchanger element being a further embodiment of the invention.
- Figure 28A illustrates an embodiment similar to that of Figure 28 except that the straight line path length is varied
- Figure 29 illustrates a front view of a plate of a heat exchanger element of another embodiment having parallel flows therethrough
- Figure 29A illustrates an embodiment similar to that of Figure 29 except that the straight line path length is varied
- Figure 30 illustrates a side view of a heat exchanger assembly of another embodiment ;
- Figure 31 is a left side elevation of an instantaneous gas fired water heater of another embodiment of the invention;
- Figure 32 is a front elevation of the heater of Figure 31 ;
- Figure 33 is a right side elevation of the heater of Figure 31 ;
- Figure 34 is a side elevation of a plate that forms part of a water jacket assembly of a further embodiment of the invention applicable to the water heater of Figures 31 to 33;
- Figure 35 is a side elevation of an end plate forming part of the water jacket assembly of Figure 35;
- Figure 36 is a side elevation of a pair of end plates of Figure 35 to illustrate flow path
- Figure 37 is an exploded perspective view showing the assembly of heat exchanger plates and end panels in the water heater of Figures 31 to 33;
- Figure 38 is a schematic cross section of stacked plates showing nesting feature;
- Figure 39 is a side elevation of an alternative form of heat exchanger plate
- Figure 40 is a diagrammatic side elevation of the liquid flow path through a channel formed by back to back dimples on a pair of plates of Figure 39 placed together;
- Figure 41 is a side elevation of a heat exchanger element plate of another embodiment
- Figure 41 A is a side elevation of an end heat exchanger element plate for use with the element formed from the plate of Figure 41 ;
- Figure 42 is a schematic circuit illustration showing use of the heat exchanger plate of Figure 41 ;
- Figure 43 is a schematic circuit illustration showing a different use of the heat exchanger plate of Figure 41 ;
- Figure 44 illustrates a front elevation of a further embodiment of the invention
- Figure 45 illustrates a side apparatus view the apparatus of Figure 44;
- Figure 46 is a sectional view through the apparatus of Figure 44 through the lines AA of Figure 45;
- Figure 47 is a front elevation of a further embodiment of the invention showing water flow path
- Figure 48 is the front elevation of Figure 47 showing combustion gasses flow path
- Figure 49A is a perspective view of five plates which are used to manufacture the water jacket assembly 50C of Figures 47 and 48;
- Figure 49B is an exploded view of the water jacket assembly plates formed form the plates of Figure 49B and as used in the embodiment of Figure 47;
- Figure 49C is a schematic water flow path through the plates of Figures 49A and 49B;
- Figure 50 illustrates an accumulator or reservoir for use with the water heater of previous drawings
- Figure 51 illustrates a schematic cross section of a part of a heat exchanger being another embodiment
- Figure 52 illustrates a heat exchanger element with a cross over path
- Figure 53 illustrates an end plate with an end plate with a bypass feature
- Figure 54 illustrates a cross section through another embodiment of a water heater having a water jacket assembly similar to that of Figures 44 to 46, but with a naturally aspirated burner system. Detailed description of the embodiments
- a domestic water heater 10 is illustrated in Figures 1 to 3, and is fuelled by gas and operates to provide an instantaneous flow of hot water.
- the water heater 10 is housed in a rectangular enclosure 11 that is designed to be mounted flush against an external wall.
- the heater needs to be coupled to a supply of gas and it is understood that the heater can be adapted to work on a variety of commercially available gases.
- the combustion of the air gas mixture forms combustion products which are vented to the atmosphere via a small aperture 12 at the front 13 of the heater.
- the heater can be installed internally with exhaust gases being vented to the atmosphere via a small flue that would extend either through the wall cavity or up through the ceiling.
- the water heater 10 has a burner 20 positioned above a water jacket assembly 50 so that heat and combustion products from the gas burner 20 pass through a heat exchanger 51 that forms part of the water jacket assembly 50 to heat up a supply of cold water that is arranged to flow through the heat exchanger to exit the heat exchanger as hot water.
- a single burner 20 will be the cheaper construction, if desired to allow the water heater 10 to cope with turn down situations, multiple burners (with appropriate controls) can be utilised so as to be able to effectively shut off parts of the burner thereby allowing optimising of the burners output depending upon needs.
- a control mechanism 32 controls the amount of gas delivered from conduit 32A and which will ultimately be burned by the burners 20.
- the amount of gas burned is dependent on the flow of water and the temperature requested, ie on demand.
- the burning capacity of the gas burners is enhanced by the provision of a blower or fan 30 that mixes gas with air before prior to arriving at the burners 20 to ensure use of the most efficient air fuel mixture.
- the fan 30 also operates to downwardly force the combustion products and hot air generated by the burners 20 in a generally vertical direction through the heat exchanger 51.
- the high efficiency of the heat exchanger 51 is such that it can produce condensation which drips down into a collection tray 71 mounted at the base of the enclosure 11.
- the condensate is directed out of the enclosure 11 by means of a discharge conduit 72 into a sewerage drain.
- the burner 20 is positioned across the top of the heater 10.
- the burner 20 is fed an air gas mixture from a mixing chamber 31 , which receives gas and air via a modulating gas valve 32 and the electrically driven fan 30, which mixes the gas with the air prior to feeding the air/gas mixture to the burner 20.
- the burner 20 is in the form of one or more ceramic plates 35 having a series of small apertures (not shown) extending therethrough. Whilst a ceramic plate burner construction is described in the embodiment of Figures 1 to 3, any burner or multiples or combinations of burners can be used, such as mesh burners, plate burners, metal screen and mesh burners, carbon fibre burners etc.
- the apertures in the burner provide a very large number of small flames that project downwardly (as a result of the air/gas mixture flow caused by fan 30) towards the water jacket assembly 50.
- the flames terminate in the combustion chamber 50A at a position that is above the leading edges 260 of the heat exchanger 51.
- the heat exchanger 51 is positioned in the lower half of the water jacket assembly 50.
- the overall height of the water heater 10 can be decreased by selecting a burner, such as a mesh burner, which will operate with a smaller flame length.
- the cold water inlet 14 extends into the base of the water jacket assembly 50 (cut away for illustration purposes) on the left hand side thereof as viewed in Figure 2, with hot water exiting the water jacket assembly 50 via conduit 15 A from the right hand side, thereof towards the top of the heat exchanger 51 at the hot water outlet 15.
- a water flow meter 90 monitors flow of water at the cold water inlet 14.
- a first temperature sensor Tl is positioned on the cold water inlet and a second temperature sensor T2 is positioned on the hot water outlet 15 from the heat exchanger 51.
- a third temperature sensor T3 is positioned on a water flow control valve 60 which is coupled both to the cold water inlet 14 and the hot water outlet 16. The supply of gas flows up conduit 32A from the base of the water heater 10 along the left thereof side to the modulating gas valve 32 and into the fan 30 as shown in Figures 1 to 3.
- the hot water outlet 16 from the water valve 60 has a first outlet 17 that is designed to provide water up to a temperature of 80°C and a second lower temperature outlet 18 that dispenses water up to a temperature of 50°C via a flow sensor 19 if the water heater 10 is to provide hot water for radiator use as well as potable water.
- Water heaters of this kind generally have safety controls to prevent scalding when water of 80°C can be produced.
- the electronic control system 80 automatically limits the maximum available temperature to 50°C.
- the combustion products generated by burner 20 pass through the heat exchanger 51 and exit the water heater 10 at the base of the heat exchanger 51 via the rectangular outlet 12 in the front face 13. These exhausted combustion products exit at a temperature that is close to the temperature of the cold water entering at inlet 14, thus the loss of the heat to the surroundings is kept to a minimum.
- the electronic control system 80 is mounted near the top of the water heater 10 as shown in Figure 1 to control operation of the heater 10.
- the water heater 10 has to be coupled to a source of gas, a source of cold water and a source of electricity.
- the water jacket assembly 50 is illustrated in detail with reference to Figures 4 to 23 and includes an external water jacket 52 that supports an internally located heat exchanger 51 that is in the form of a discrete number of pairs of rectangular plates 53, 54 (as illustrated in Figures 4 and 5) depending on the heat exchanger 51 requirements.
- the construction of the heat exchanger 51 will be discussed in more detail later.
- the water jacket assembly 50 in summary has the combustion chamber 50A, the water jacket 52 and heat exchanger 51. These components are constructed from 3 differently shaped plates. Two of a first shaped plate form the front plate 100F and rear plate 100R (see Figure 4 and the associated description). These first shaped plates are placed back to back to encase opposite sides of the assembly. Four of a second shaped plate form end plates 101 A, 101B, lOlC and 101D that, as shown in Figures 4, 5 and 6, envelop and overlap the ends and sides to define the water jacket 52.
- a plurality of pairs of a third plate defines the heat exchanger 51 , with only one pair of rectangular plates 53, 54, being illustrated for convenience and clarity of Figure 4.
- the plurality of plates 53 and 54 when mounted in spaced apart pairs constitute the heat exchanger 51.
- the sandwich of the plates which forms the heat exchanger 51 is located towards the base of the unit.
- the water jacket 52 has liquid passageways or channels that run across the bottom, then up to the top of half of the sides 200 then crosses to the other half of sides 200, then across the top of this other half, then down to the bottom.
- the water flow path begins at the bottom and flows initially in two directions to the middle of the side
- the water jacket 52 is positioned externally of the heat exchanger 51 with the gas flames from the burner 20 being produced along the centre line of the water jacket assembly 50 within the combustion chamber 50A. This feature has the effect of drawing off heat from the gas flames to reduce sideways escape of heat and also reduce the temperature of the hot gases at the heat exchanger 51.
- the cold water enters the assembly 50 from one side at the base and exits the assembly on the opposite side towards the top of the heat exchanger 51. Initially, the water moves in two directions around the sides and ends of the water jacket 52 so that water flows through the whole of the water jacket before passing into the heat exchanger 51. This reduces the likelihood of the water jacket 52 being overheated and reduces waste of hot gases.
- the assembly By manufacturing the assembly from three plates that are simply reversed and or inverted, the whole assembly can be produced from a simple stamping operation. Furthermore, in this embodiment, the assembly is manufactured from stainless steel plates coated in copper and the components are assembled together by use of a jig (not shown) so that the component plates are in abutting contact with all the abutting surfaces being copper to copper. The assembly is placed in an oven for a predetermined period at a temperature to fuse the copper to provide an integral unit in which all the components are bonded together and the water and air passageways are defined accurately with no leakages. There is thus no need for welding, soldering, or other fasteners and this fusing of the copper coating ensures satisfactory operation over a long life.
- the design of a convoluted passage for water flow is also specifically designed to encourage turbulent flow to ensure that there are no stagnant water pockets or hot spots in the heat exchanger 51 or water jacket 52.
- the external shape of the plates provides a convenient route for run-off of condensate that forms on the exterior of the heat exchanger elements.
- the water jacket assembly 50 has proved efficient and allows maximum transfer of heat from the gas flames to the water without excessive heat being lost to exhaust.
- fusing is described with respect to copper other fusing metals can be used such as nickel or the like. Instead of fusing however, any means of holding the plates together which form the water jacker 52 and heat exchanger 51 can be utilised.
- a gas pressure sensor 84 is positioned at the gas entry of the modulating gas valve 32 to sense a drop in gas pressure to reduce the output of the water heater 10 should there be a shortage of gas pressure.
- Conventional domestic gas pressures are such that if too many appliances are used at once there is often a drop in the gas pressure.
- the gas pressure sensor 84 causes the rate of flow of water to be reduced by means of valve 60 to compensate for a reduction in gas pressure so that the water heater 10 operates at the desired temperature albeit at a reduced output in terms of litres per minute.
- controller 80 can be made to decrease the flow rate of air being mixed with the gas, and or the gas by the valve 32, to form the air/gas mixture, to maintain optimum combustion.
- Another feature of the gas valve 32 and controller 80 is the use of an oxygen sensor 71 A that detects the amount of oxygen in the flue gases. If the oxygen content of the flue gas is either too high or too low, a signal is fed back to the controller 80 to change the gas flow by valve 32 to ensure an optimum mixture.
- the computerised controller 80 monitors three temperatures, namely the temperature Tl which is the temperature at the inlet of the cold water, the temperature T2 being the temperature which is at the heat exchanger outlet; and the temperature T3 which is the temperature at the hot water outlet from the water heater 10.
- the third temperature monitor T3 is adjustable by a user or service person to adjust the desired output temperature.
- the controller 80 on sensing the three temperatures can then control the rate of water flow through the water heater 10 and also the gas input through the modulated gas valve 32 and the air input by varying the speed of the fan 30.
- the controller 80 varies these parameters to ensure maximum efficiency.
- a flow sensor 90 is positioned in the cold water inlet 14.
- the flow sensor 90 provides an electrical signal which is sent to the controller 80 to control the operation of the water heater 10 in relation to demand. It will also be understood that with this flow sensor 90 can produce a signal to give a visual indication, or be processed to give a visual indication, of the rate of flow which can be displayed at the water heater 10 and/or at remote locations.
- the flow control valve 60 as illustrated in Figure 1 is provided to compensate for too much demand for hot water, or to reduce flow, or if there is a danger of the water exceeding the maximum design temperature. In these cases the valve 60 can be made to open or close as the conditions require.
- an electrically operated ignition system is (such as a spark igniter or glowing surface or HSI [hot surface ignition] or any suitable system) is utilised in the combustion chamber 50A and the control system 80 ensures that when a hot water tap is opened causing flow of water, there is first a pause to purge any combustible gases within the combustion chamber. Then depending on the ignition system used there may be a short pause during which the electrically operated ignition system activates and commences to ignite the air/gas mixture otherwise the air/gas mixture enters the combustion chamber and is ignited. In this embodiment a spark igniter is preferred as it has no lag time to operate.
- the control system can be programmed so that if this fails a predetermined number of times then the water heater 10 shuts down and a warning light comes on warning the user of the system that a service call is required.
- the water jacket 52 is made from a plurality of two types of plates.
- the first type of plate is that which makes plate 100F and 100R which has three sides, a middle side 200 forming the front and rear faces of the water jacket assembly 50 and the outer sides 201 and 202 at right angles to the side 200.
- the side 201 on the front plate 100F is located adjacent to side 202 on rear plate 100R on the left side and vice a versa on the right side of the water jacket assembly 50 as illustrated in Figures 4 and 7.
- a series of channel formations are formed in the front plate 100F and are constructed so as to have depth into the page as illustrated in Figure 4. While in the rear plate 100R (which is identical to plate 100F) the channels 204 are formed so as to have depth out of the page of the drawings.
- the channels 204 are at the front and rear of the combustion chamber 50A and define the combustion chamber 50A therebetween.
- plates 101 A, 101B, 101C and 101 D are oriented and positioned on the front and rear plates 100F and 100R so that their respective comers 205 and 206 are positioned onto front and rear plates 100F and 100R at corresponding respective corners 205R, 205L, 206L and 206R.
- the plates 101B and 101C as illustrated in Figure 4 have their channels, which are generally designated by the arrows 208, formed such that the depth of the channels away from the plate is out of the page in Figure 4.
- the plates 101A and 101 D have their channels generally designated by the arrows 208, such that the depth of these channels 208 are formed into the page.
- the channels 204 and 208 will form a sealed flow path whereby those portions of the channels 208 on all plates
- 101 A, 101B, 101C and 101 D in the top half U of the jacket 52 will form double depth channels with the channels 204 on the front and rear plates 100F and 100R.
- the double depth channels are in the vicinity of or adjacent to the combustion chamber
- a half width channel is formed between the channels 208 and the flat plate area 210 on the middle sides 200 of front and rear plates 101 F and 101R.
- Half depth channels are also formed on the left and right sides of the water jacket 52 by both the upper half U and lower half L of plates 101 A, 101B, 101C and 101 D.
- each pair of generally rectangular plates 53 and 54 are positioned in abutting contact to define a convoluted water path therebetween.
- the two plates 53 and 54 are identical.
- One plate has been inverted and placed back to back with the other so that the corners UL, LL, UR and LR on the plate 53 are placed adjacent to the respective corners LL, UL, LR and UR on the plate 54 (which is simply an inverted plate identical to plate 53).
- the expression 'back to back' in this specification and claims signifies the procedure of aligning plates, or the arrangement of aligned plates, whether identical or not, so that the concave sides of the dimples or channels formed in or on the plates are brought together to define a channel or flow path between the dimples or channels. Examples of back to back formations can be seen in figures 4, 23, 30, 37 and 38.
- the plate 53 (and likewise 54) has an array of discrete dimples 220, which have their longitudinal axis at approximately 45 degrees to the direction of flow of combustion products.
- the dimples 220 are all of similar size, width, depth and length and are angled at approximately 45° to the longitudinal axis of the plates 53 and 54.
- a channel or flow path is formed by the dimples 220 on plate 53 and dimples 220 on plate 54. Any two adjacent dimples 220 on plate 53 are interconnected by a corresponding dimple 220 on plate 54 so that water can flow from a first dimple in plate 53 along that dimple into the connecting dimple on plate 54, then along that dimple and out of plate 54 and back into plate 53 but into the next adjacent dimple to the first dimple mentioned on plate 53.
- a flow path which has a zig zag or sinusoidal configuration when viewed from the front of the heat exchanger 51. This is better illustrated with respect to Figure 16 to Figure 19.
- the dimples 220 form a channel through the both the plates 53 and 54 with the last portion of the flow path being illustrated.
- the water flows from the interior 220A" and crosses over to the interior 220A' and then into the interior of the differently shaped dimples 231 and 230 which form upper header 232 (see Figure 10).
- the combustion products travel through the passages 220B into the page of the illustration.
- This flow path (which is further described below) is repeated to make up each of the paths 242, 243, 244 and 245.
- hot combustion gases X flow downward in Figure 15 and pass over the leading edges 260 of each of the heat exchangers formed from pairs of plates 53 and 54.
- the combustion products flow through the heat exchanger 51 with a flow path as described in more detail with respect to Figures 20 to 23, until they pass over the trailing edges 261 of each of the elements formed from the plates 53 and 54. Simultaneously the water enters the heat exchanger 51 through entry 56 being on the outermost side of lower header 233. The water then flows through the paths 242, 243, 244 and 245 in each of the heat exchangers making its way via a zig zag/helical or sinusoidal/helical serpentine path up to the upper header 232 where it will exit the heat exchanger 51 by the outlet 57, which is on the same plate and heat exchanger that inlet 56 is formed on. If desired the inlet and outlet 56 and 57 can be located on opposite sides, and if the number of paths were to be varied, could even be located on opposite ends of the heat exchanger 51.
- the flow will have to change direction again by approximately 90° for the flow to travel along the dimple 220 in the plate 54 and so on creating a complex convoluted flow path which can be described as generally helical, or corkscrew, or possibly even of a square or rectangular helical shape or other three dimensional flow path.
- the dimples 220 have a length as illustrated in Figure 24 to 27 of approximately 24mm, however, the straight line path length of the dimple 220 when a water path is formed is of only approximately 15mm because after a maximum of 15mm travel, water will have to change direction when flowing in the dimple 220.
- the depth of the dimple 220 out of the plate on each plate, is approximately 3.5 to 4.5mm.
- the upper header 232 is connected to the outlet 15 of previous Figures to deliver water to the user or for the temperature to be sensed and output flow monitored.
- adjacent heat exchanger elements are assembled as illustrated in Figure 13, Figure 15 and Figure 23, a convoluted combustion gas flow path is formed over and around the external surfaces of the dimples 220 as illustrated in Figures 20 to 22.
- the fan 30 will cause combustion products to pass over the leading edge of the heat exchanger elements and if the adjacent elements are arranged such that the external extremity of the outside surface of dimple 220 contacts the extremity of the external surface of an adjacent dimple 220 (on an adjacent heat exchanger element) then combustion products will flow around respective dimples 220 as illustrated in Figure 20. If a gap were provided between adjacent heat exchangers, then combustion products would flow not only around individual elements 220 but also between dimples 220 on adjacent plates effectively flowing over as well as around the dimples 220.
- Illustrated in Figure 21 is a similar flow path over the plate 54 which helps to provide an even more complex flow path between adjacent heat exchanger elements when plate 53 on one element contacts plate 54 on an adjacent element to produce a flow path as illustrated in Figure 22, which is highly a convoluted flow path and as illustrated is the path that can be present between adjacent elements formed from plates 53 and 54.
- the water will be at the highest temperature possible.
- the plates 53 and 54 as illustrated in Figure 4 have a flared end or flange F (which is also visible in Figure 14) that serves two purposes.
- the flange F forms a double width flange on the heat exchanger element when the two plates 53 and 54 are placed back to back as illustrated in Figure 14.
- This double width flange helps to provide greater surface area through which heat can be exchanged between the heat exchanger 51 and the water jacket 52.
- the portion of the flange F which does this effectively acts like a dam or flow director which is useful to direct the flow of combustion products over the external surfaces of the dimples 220.
- FIG. 28 Illustrated in Figure 28 is a heat exchanger element 300 which is configured differently to the heat exchanger element made from plates 53 and 54 of the previous Figures.
- a lower header 233 is provided and an upper header 232 is also provided in a similar manner to that of Figures 4, 9, 10 and 11.
- the flow path segments 342, 343, 344 and 345 double back across the heat exchanger 300 in a serpentine fashion as in the previous embodiment.
- the difference between the heat exchanger element 300 of Figure 28 is that a zig zag/helical water flow path segments 342, 343, 344 and 345 provided, is such that the included angle 301 between the straight line sections or dimples 220 in path 342 is a larger angle compared to the included angle 302 in the path 243 above or the included angle 303 in the path 344, or the angle 304 in the path 345 closest to the leading edge 260.
- the included angles 301, 302 and 303 in respective passes across the heat exchanger 300 even greater efficiency can be provided ensuring that the water passing, for example, through the path 345 near to the leading edge has a longer path to travel and possibly passing through the leading edge segment at a slower rate than through the flow path segment
- FIG. 28A Illustrated in Figure 28A is a heat exchanger element 300 which is similarly configured to the embodiment as illustrated in Figure 28 and like part have been like numbered.
- the difference between the heat exchanger element 300A of Figure 28A and 300 of Figure 28 is that at the trailing edge there is provided a flow path which begins from the lower header 233 and has full depth (that is on each of the plates dimples or a channel of equal depth are formed so that when they are placed together, a flow path results of a depth equal to twice the depth of one dimple or channel ).
- the first flow path 342A is generally of a straight configuration and runs across the full width of the heat exchanger 300A. While a full depth flow path is described, it may be necessary to either vary the depth or size it appropriately to ensure that a combustion products' flow path will be formed which will not be constricted to the point of preventing the escape of combustion products.
- a zig zag/helical water flow path is provided, wherein the included angle 301 between the straight line sections is a relatively large angle compared to the included angle 302 in the row above or the included angle 303 in the row closest to the leading edge 260.
- the flow path segments 342A, 343A, 344A and 345A double back across the heat exchanger 300A in a serpentine fashion as in the previous embodiment.
- angles 301, 302 and 303 By varying the included angles 301, 302 and 303 in respective passes across the heat exchanger 300A, better efficiency can result, ensuring that the water passing, for example, through the leading edge has a longer path to travel and thereby remains in the combustion products' flow path longer than through the flow path segment 342 at the trailing edge segment. This can help the heat transfer process by producing greater mixing and turbulence such that it may cause the combustion products to condense. Further
- the angles need not be such that angles 301 > 302 >303, as circumstances may arise where a different relationship is found to be advantageous given the design criteria and conditions to be worked with.
- the effective cross-sectional area of the flow paths 342A, 343A, 344A and 345A can also be varied according to the requirements of operation of the heat exchanger. Also if desired, the amplitudes A, B and C of paths 343A, 344A and 345A might also be varied to optimise the efficiency and heat transfer.
- FIG. 29 Illustrated in Figure 29 is a heat exchanger element of a further configuration useable with the present invention.
- the heater exchanger element 400 has an upper header 232 and a lower header 233, however, in this embodiment a lower header channel 442 is provided running from lower header 233 substantially parallel to the trailing edge 261 whilst an upper header channel 445 runs back to upper header 232 in a direction substantially parallel to the leading edge 260 of the heat exchanger.
- water enters the heat exchanger element 400 from the water jacket 52 via lower header 233 and fills the lower header channel 442.
- the most efficient direction of movement of liquid in the heat exchanger element 400 is in the opposite direction and thus by the arrangement illustrated in Figure 29, water travels through the flow paths 443 from lower header channel 442 up to upper header channel 445 and out of the heat exchanger element 400 via upper header 232.
- the flow path has a constant zig zag or sinusoidal path wherein the amplitude D of the zig zag/helical flow path measured is constant as is the included angle 401 between connecting dimples on the two plates
- FIG. 29A Illustrated in Figure 29A is a heat exchanger element of a further configuration which is similar to that of Figure 29, with like parts being like numbered.
- the differences between the elements of Figures 29 and 29A is that in Figure 29A the flow path has a decreasing zig zag or sinusoidal path wherein the amplitude of the zig zag/helical flow path measured in the region D closest to the trailing edge, E in the middle and F at the leading edge are decreasing in size across the height of the heat exchanger element 400A.
- the included angle 401 and other included angles 402 and 403 are varied to minimise back pressure and/or resistance to flow through the heat exchanger 400.
- the cross sectional area of the flow path depth closest to the leading edge is generally smaller than the rest of the flow paths.
- the flow path depth can be sized so as to ensure that water passing therethrough will be sufficiently turbulent to increase the probability that thermal boundary layer mixing will occur. While the depths G, H I and J are decreasing in size in a particular direction, it may be advantageous to have the variation occur in some other pattern depending upon the requirements demanded or desired form the heat exchanger 51
- FIG. 31 to 33 Illustrated in Figure 31 to 33 is an instantaneous gas water heater similar to that of Figures 1 to 3, except that the combustion chamber 50A, water jacket 52 and heat exchanger 51 are formed in a different manner.
- Like parts between Figures 31 to 33 and 1 to 3 have been like numbered and their function and purpose need not be described further as reference can be made to earlier description.
- the water heater 10A of Figures 31 to 33 differs from the water heater 10 of Figures 1 to 3 in that a cold water bypass conduit 81 in the form of a tube directly communicates with the cold water inlet 14 and first and second water outlets 17, 18. There is a pressure drop across the heat exchanger where the pressure at the inlet 14 is greater than the pressure at outlets 17 and 18. This is a result of loss in pressure caused by the zig zag/helical flow path is tortuous or convoluted nature through the heat exchanger 51.
- Cold water bypasses the heat exchanger 51 through the bypass conduit 81 and mixes directly with hot water prior to exit 18 from the water heater 10A thereby increasing the outflow pressure. Mixing cold water with the hot water at the outlet 18 will of course mean that the outlet water temperature is decreased. This can be simply compensated by increasing the heating temperature at the gas burners 20 so that the overall effect is hot water leaving the water heater at a desired temperature but having a greater pressure.
- Flow valve 82 on the cold water bypass conduit 81 determines the amount of cold water supplied to the hot water outlets. It is understood that the greater cold water pressure, the greater will be the hot water delivery pressure at the outlet 18.
- the valve 82 can be manually adjusted by a technician at the time of installation of the water heater or during maintenance visits. Alternatively, the valve 82 can be automatically adjusted in response to fluctuating inlet water pressure measured by a sensor (not shown) at the inlet.
- the water jacket assembly 50' is constructed from a plurality of two different plates 550 of Figure 34 and 560 from Figure 35.
- the plate 550 of Figure 34 that makes up the central portion of the water jacket assembly 50' is of a generally Y shaped appearance.
- Each plate 550 includes a central body portion 551 with a pair of upwardly extending arms 552 and 553 that define a bight or space 54 therebetween.
- a series of heat exchanger elements 570 are formed (as illustrated in Figure 37 where only 3 pairs are illustrated for convenience) which form the central portion of a water jacket assembly 50'.
- the plate 560 which is of a generally T shaped appearance.
- the plate 560 differs from the plate 550 in that at the base of the T in plate 560 there are no dimples and thus no channels formed in the middle portion, unlike in the base of the Y of the plate 550. This is because this flat region on the plate 560 is adjacent the base of the Y of plate which will extract heat from the combustion products thus making the base of the T of plate 560 redundant in the heat scavenging process.
- the plates 550 and 560 have an unbroken channel 244 and 244A which runs around the outer periphery of the plates 550 and 560.
- This unbroken channel 244 and 244A forms a water jacket type flow path.
- a lower header 233 is formed with water exiting to the left side of the lower header 233 following a continuous path 244A around the left hand side outer periphery of the plate 560 to the top of plate 560.
- the flow path 245A takes the water in a downward direction until flow path 243A which takes the water in an upward direction and so on through downward path
- serpentine flow path formations in the plates 560 and 550 result in an effectiveness which is added to by the convoluted flow path of similar shape to the previously described paths of previously described embodiments.
- two plates 550 are reversed which will allow them to be pressed and fused together to form joined pairs with flow paths therethrough.
- the plates 550 are made such that the dimple portions are identical, but during the manufacturing process flanges 600 (which will be described in more detail later) are oriented in different directions (thereby making the plates no longer identical) so as to form a front and back or a left and right side plate, which will be placed back to back to form a heat exchanger element.
- the pairs of Y shaped plates 550 are arranged in a vertical orientation and in parallel to form a combustion chamber 50A between the arms of the Y shape which form the front wall 100F and the rear wall 100R of the water jacket 52.
- the water jacket assembly 50' is completed by placing two pairs of plates 560, one pair on each end of the assembly to close off the water passageways and to create end walls 100LS and 100 RS of the water jacket 52 thus forming the combustion chamber by completing the water jacket 52 therearound.
- the water jacket assembly 50' is thus defined as a block containing a rectangular combustion chamber 50A bounded by a water jacket 52 defined by the walls 100LS, 100RS, 100F and 100R formed from the arms 552 and 553 of Y shaped plates 550 and the ends by pairs of end plates 560.
- the base portion 551 of the Y shape contains a rectangular block that constitutes the heat exchanger 51.
- the Y shape in particular has the advantage that the arms of the Y are formed from those positions cut away from the base of the Y of the previous plates in the stamping or guillotining process.
- the flanges 600 can be bent so as to form an angled flange which is best illustrated in the schematic cross section of Figure 38.
- each plate 550 and 560 has a flange 600 which nest together.
- the angled flanges 600 are all oriented in the same direction irrespective of which plate is considered.
- This flange 600 provides the nesting ability of the plates 550 and 560, and thus helps to form the water jacket assembly 50' of Figure 37, with a relatively strong periphery due to the overlapping of these flanges 600.
- the angled flanges are arranged to overlap each other as the plates 550 and 560 are placed together in a sandwich.
- the angled flanges 600 have a slight taper of approximately 5 or 10 degrees so that the plates 550 and 560 can be loosely placed together in a wedged arrangement.
- the gas burners of the heater are located in the combustion chamber 50A and the interior surface can be lined with a box-like structure 610 ( Figure 37) having metal gauze 612 to isolate the comparatively cold surfaces of the heat exchanger 51 from the very hot surface of the gas burner.
- the gauze has the effect of ensuring good combustion at the gas burner which could be detrimentally affected by the cold surface of the heat exchanger 51.
- each panel 550 and 560 are preferably pressed out of stainless steel or copper coated stainless steel.
- each panel 550 and 560 can be made of composite materials so that the hotter part of the panel, namely the upper portion including the arms 520 and 530 can be made of a material, such as those stainless steels or titanium and its alloys specifically designed to resist high radiant and convectional temperatures whilst the lower main body portion 51 of the panel would be manufactured of a material that does not need to withstand particularly high temperatures such as 316 stainless steel. This feature allows efficient use of materials and reduces overall costs.
- the panel could be stamped/pressed in two halves which are then brazed or fused together. This is best illustrated with respect to Figure 47, 49A and 49B and its associated description below.
- a water jacket assembly 170 is constructed in a similar manner to the assembly described with reference to the embodiments above.
- the plates 150 are of a U shape with a rectangular base structure 151 with a pair of upstanding arms 152, 153.
- the plate 150 illustrated and the heat exchange element made therefrom form intermediate elements.
- the end plates will be similarly structured to the plates 150 except that the base 151 will have no dimples, as dimples and channels are somewhat redundant on the end plates in those regions other than the water jacket region, due to the effectiveness of the water jacket assembly formed therefrom.
- the base structure effectively defines the body of the heat exchanger whilst the arms 152, 153 define the water jacket and the periphery of the combustion chamber in the same manner as the embodiment of Figure 31 to 38.
- a cold water inlet 233 is positioned centrally at the base of the unit whilst the hot water outlet 232 is positioned also along the centre line of the top part of the rectangular heat exchanger element base structure 151.
- the combustion chamber is of rectangular configuration and houses the burner in the same manner as the embodiments described above.
- One means of reducing the likelihood of build up of scale deposits on the interior surfaces of the heat exchanger is to ensure that the water is heated evenly by preventing hot spots on the heat exchanger.
- One way to do this is to provide turbulent flow of water through the heat exchanger.
- the turbulence of the flow reduces the likelihood of scale deposits and tends to sweep particulate material out through the system. Consequently, the profile of the water passageways in the heat exchangers is sufficient to optimise the possibility of turbulence and to increase thermal boundary layer mixing which also enhances heat transfer and reduces the probability of scaling.
- Another means thought to be able to reduce the likelihood of scaling is to split the water flow path in the heat exchanger into two separate water passageways. Such a splitting of the water path circuit can be useful in combination or co bi- boilers or heaters which provide water at approximately 80°C for radiator usage which may be used in central room heating and at 50°C for potable water uses.
- FIG. 42 Such a splitting of the water flow path is illustrated in Figure 42 where a heat exchanger 51 made from plates 550A and 550B (see discussion with respect to Figure 41 and 41 A below) has two water flow paths therethrough.
- the first water flow path is labelled with numeral 701 and the second with label 703.
- the water flow path 701 is a closed loop while water flow path 703 contains an open loop.
- cold water 709 enters the flow path 703 and is divided into two conduits 711 and 713 at junction 710.
- Conduit 71 1 passes water into the heat exchanger 51 to those areas near to the trailing edge 261.
- the hot water tap is open, water will flow through conduit 713 into potable water passages 717 of a water to water heat exchanger 716.
- the heat exchanger 716 also has heating water passages 717A through it for the water in circuit 701 to heat the water in passages 717, and visa versa as will be described below.
- the water which may be heated in coil 717 passes via conduit 714 to meet up with water coming from the heat exchanger 51.
- the mixing of the two flows takes place at junction 718 so that the combined hot water can flow out of the water heater via outlet 719.
- Cold water bypasses such as those described previously with respect to other embodiments, can be included together with temperature sensing, etc to ensure that the exiting water is cooled, if necessary, to the desired output temperature and to provide the best possible flow rate of hot water.
- the water which flows through conduit 711 into the heat exchanger 51 , passes through those parts of the heat exchanger 51 heated by combustion products that are initially cooled by the water flow path 701 in the hottest parts of the heat exchanger 51.
- the closed loop water flow path 701 contains water preferably with glycol (or similar additive) for the purpose of reducing the likelihood of scaling.
- the water flow path 701 includes a series connection to a radiator 705, a pump 707 and heat exchanger 716.
- the water flow path 701 will deliver water along conduit 701B to the outer side of the heat exchanger 51.
- the heat exchanger 51 water flow path passes from the entry point up to the top of the water jacket assembly, then down the side of the combustion chamber through the water jacket, then through the hottest part of the heat exchanger 51 near to the leading edge 260, then up the other side of the water jacket and then delivers water at a desired temperature to the radiator 705, which can be used for central room heating radiator. All the time the combustion chamber is functioning, the pump 707 is circulating water through the water flow path 701.
- the water temperature After the water has passed through the radiator 705 (and the radiator is functioning) the water temperature will have dropped. The temperature of the water that exits the radiator 705 will more than likely be above the water temperature of the water in the conduit 713 passing through heat exchanger 716. If the water temperature in passages 717A is higher than water in passages 717 then water in passages 717 will be heated by water in passages 717A.
- valve 719 were to be closed however, without pump assistance, water would not circulate in water flow path 703.
- a pump 712 is provided to circulate water through the flow path 703, conduits 711 , 713 and 714 and passages 717.
- the pump 712 can be made to automatically switch on once no flow is detected in hot water outlet 719. In this way, if the temperature in 717A were less than 717, the water in the water flow path 703 (which is temporarily in a closed condition) will continue circulating and dissipating heat to the water from heat exchanger 717 into 717A. This process will keep water in a relatively hot condition, that is approximately 50°C in the closed loop.
- the circuit 701 can be used to assist in the transferral of heat to the open loop circuit 703 thereby providing water at a relatively high flow rate but also, it is expected, to be with less thermal lag than by comparison with prior art systems.
- Illustrated in Figure 43 is a circuit very similar to that illustrated in Figure 42 and like parts have been like numbered.
- the heat exchanger 51 heats the cold water in the first instance.
- the heat exchanger 51 is in a series connection with passages 717 of heat exchanger 716, which is the potable water side of heat exchanger 716.
- a bypass capability is provided by the opening and/or closing of valves 717B and/or 717C so that the bypass line 718A can connect directly from the start of conduit 713 to the hot water outlet.
- FIG 41 and 41 A illustrate the profiles of a plate 550A and 550B to construct a water jacket assembly that can be used in the Figure 42 or 43 dual circuit approach.
- the end plates 550B are of a similar construction to the plates 560 of Figure 35.
- the panel has four apertures 795, 796, 797, 798 to form 4 headers, and are arranged vertically and in line centrally of the panel.
- the lower aperture 795 is the first water heating line (equivalent to item 703A of Figure 42)
- the next aperture 796 constitutes the cold water input (equal to item 711 in Figure 42).
- the second water heating line which is the closed circuit is illustrated as the aperture 797 connects to 701B of Figure 42 and the hot water outlet aperture 798 is the third highest aperture and connects to 701 A of Figure 42.
- the plate 550A of Figure 41 only has inlets and outlets for two circuits illustrated, it will be readily understood that additional outlets and inlets can be provided on the heat exchanger plates and heat exchanger formed therefrom so that other water circuits can be connected.
- FIGs 44 to 46 Illustrated in Figures 44 to 46 is a water heater 10B similar in construction to that of Figures 31 to 33 and like parts have been like numbered and their function and purpose need not be described further as reference can be made to earlier description.
- the difference between these two embodiments is that the plates 550B and 560B even though still of a generally Y and T shape are configured and arranged so as to be parallel to the width of the water heater 10B.
- This configuration results in the use of a lesser number of actual plates albeit bigger ones but this is helpful for dimensional stability and integrity of the water jacket assembly when in use .
- the flow path through the water jacket assembly 50B is illustrated. In Figure 44 it can be seen that the two flow paths are the mirror image of each other.
- Figure 47 is a front elevation of a water heater IOC having a water jacket assembly 50C, which differs from water jacket assemblies 50A and 50B of previous Figures.
- Illustrated in Figure 49A and 49B are the five component plates and the four plates assembled from the component plates, which when paired form heat exchanger elements, which when sandwiched form water jacket assembly 50C having combustion chamber 50A, a heat exchanger and a water jacket.
- a first plate is end plate 380A which effectively forms the ends or side portions of each of the plates illustrated in Figure 49 in exploded view.
- the second plate is 380D from which plates 380B and 380E are formed by the punching of an aperture therethrough.
- the third plate is 380C.
- the burner plate 380 is made from two end plates 380A and a central plate 380B.
- the plate 380B has a central circular aperture 381 therein. As the view in Figure 49 is from the top, the underside is not visible.
- plates 380A has been joined to 380B they form a single plate which can be joined to a like plate (not illustrated) having a nesting flange similar to the flange 600 (but in the opposite direction relative to the dimple formations) such that the dimples on the surfaces of the back to back plates join together to form channels between the respective plates.
- a single heat exchanger element can be formed.
- the plate 380A can be of a different metal to the plate 380B to take account of heat resistance of the metals used if such a requirement is necessary.
- the aperture 381 through the plate 380 will form a through hole in the corresponding heat exchanger whereby this element is used as the upper most element in the water jacket assembly 50C.
- This element in use has a fan shroud 382 passing through the aperture 381 and seals therewith as illustrated in Figures 47 and 48.
- the burner 20 as illustrated in Figure 47 is attached to the shroud 382 and is of a circular type that can radiate flame 360° therearound, or alternatively the burner 20 will send flame to the left and right sides of combustion chamber 50A.
- the plates 383 which form the combustion chamber 50A are constructed in a similar manner to the plate 380 except that the plate 380B is replaced by a channel plate 380C, with each plate 383 having two of these.
- the channel plates 380C conduct water from the left end plate 380A over to the right end plate 380A on plate 383.
- a stack of pairs of plates 383 form heat exchanger elements, as indicated in Figure 47 between the top plate 380 and a separation plate 390.
- Two of the separation plates 390 form an end heat exchanger element for the combustion chamber 50A.
- This end heat exchanger element is constructed from two plates made up of end plates 380A and a central plate 380D which in the central portion thereof has a flat closed section. If desired, the plate 380D could have a series of dimples across the flat closed section for the purpose of forming a channel through the central portion of the plate 380D. However, as this would increase the number of plates required, this may have an undesirable effect of increasing the overall cost to manufacture a water jacket assembly 50C.
- the plates 392 form flue elements (so described because they provide therein a flue by which the combustion products may escape).
- the plates 392 are made from two end plates 380A and a central plate 380E, which has an aperture 381A, which is preferably larger than aperture 381 of plate 380.
- Most plates 380A have an aperture 232A, which when adjacent plates are positioned back to back to form elements and the elements are sandwiched to form the water jacket assembly 50C, will form a left and right side header 390A and 390B when all plates and elements are assembled.
- the plate 380 has its right side aperture 232A blanked off so that water will not pass through the upper most plate 380.
- the lower most plate 392 is also blanked off to prevent water passing therethrough.
- the right side header 390B is thus formed between the uppermost plate 380 and lower most plate 392.
- plate 390 is blanked on the left side thereof so as to divide the left side header 390A into an upper and lower chamber, the purpose of which will be described below.
- all but the uppermost and lowermost of the end plates 380A have two apertures 388 thereon. These apertures 388 provide a passage 388A for the combustion products to move outwardly across the heat exchangers from the centre as illustrated in Figure 48 and out to the left and right sides. All the apertures 388 together and aligned form a left and right hand side downward passage as illustrated in Figure 48 whereby the exhaust gases will move past the separation plate 390 and then begin an inwardly directed motion across the flue plates 392 passing out of the central aperture 381 A and out of the flue 38 IB which is formed at the base of the heat water jacket assembly 50C.
- Figure 47 illustrates the water flow path through the heat exchanger elements which make up the water jacket assembly 50A
- Figure 48 illustrates the hot combustion gas flow path
- the left and right headers 390 A and 390B and left and right side vertically oriented combustion paths 388A cannot be viewed easily from a single front elevation as they are located one in front of the other as Figures 49A and 49B illustrate.
- the direction of the liquid flow path is upward from the cold water supply to fill a lower portion of left side header 390A.
- header 390A Once lower portion of header 390A is pressurised water flows from the left to right, across the flue plates 392, then up into right side header 390B. From header 390B the water travels from the right hand side of the plates 383, 390 and 380 into the upper portion of left side header 390A.
- the upper portion is a separate chamber to the lower portion in the region of the flue plates 392 with the hot water exiting at exit 15 as in the previous embodiments.
- a typical water flow path such as formed in elements formed by plates 392 is schematically shown at the bottom of Figure 49.
- the shape of the path is zig-zag (and helical) as in the previously described embodiments.
- the zig- zag/helical path travels across half the depth and ultimately across the full width of the plates in a serpentine fashion.
- the difference with the heat exchangers formed by plate 383 is that the channel plate 380C has a straight line flow path straight across from the left hand side plate 380.
- the water jacket assembly 50C differs in that it is made up of 5 plates which are oriented in a generally horizontal arrangement.
- the top most plate as illustrated in Figure 37 substantially fully closed except for a circular aperture 381 in the middle thereof.
- Two such plates are placed back to back to form the upper element through which the fan shroud 382 passes and seals therewith.
- the burner 20 in this instance, is attached to the shroud 382, and is of a circular type that will radiate flame in 360 degrees therearound.
- the combustion products, under the influence of the fan travel outwardly across heat exchangers formed from plates 384 as illustrated in Figure 48.
- the plates 384 have a relatively large cavity 386 which provides the formation of the combustion chamber 50A when several elements are stacked on top of each other. The combustion products move outwardly until the downward exhaust passages 388A are reached. Then the passages
- the water flow path is illustrated in Figure 36 and flows from the left hand side of the water jacket assembly 50C to the right hand side.
- the channel or water path formed by the dimples in the plates 381 , 392, 390 and 384 has a continuous path around each element and a zig zag or sinusoidal path through the middle of the plate.
- the zig zag or sinusoidal path crosses the elements in a serpentine manner doubling back across the elements to increase the efficiency thereof.
- Illustrated in Figure 50 is a water heater having a storage vessel or accumulator 450 to receive hot water once a hot water tap has been closed.
- the accumulator 450 is of a generally circular construction but can be any appropriate shape.
- the accumulator 450 receives hot water from the water heater by suitable control systems and valves provided in the heater. This hot water, once the hot water is closed, would otherwise remain in the water jacket assemblies described above.
- the accumulator 450 is able to be used as a storage of hot water to minimise the lag time to deliver hot water to the hot water tap. In some countries this lag time has to be minimised so as to preserve water.
- the accumulator 450 has a flexible membrane 451 , whereby hot water is received in the chamber 452 on the water heater side of membrane 451 whereas the chamber 453 will have air therein or will vent to atmosphere allowing the membrane 451 to minimise the volume of chamber 453 when hot water fills chamber 452.
- the accumulator need only be of a volume sufficient to hold all the hot water in the water jacket assembly with a 10% to 15% extra volume as a safety factor.
- Illustrated in Figure 51 is a schematic representation of a heat exchanger 430 made up of elements 431 formed from plates 432 which can be like any of the previously described embodiments.
- the heat exchange 430 is made from a series of adjacent elements 431 made from plates 432 which are preferably identical but need not necessarily be so.
- the improvement in Figure 51 is the provision of a leading edge plate 433 which is joined to what would have been the leading edges 434 of elements 431.
- the joining can be by fusing, soldering, bronzing, welding or any appropriate means which provides good surface contact for heat transfer purposes between plates 433 and plates 432.
- the leading edge plates 433 are manufactured from a metal having high temperature resistance qualities such as appropriate stainless steel or titanium and/or its appropriate alloys.
- the leading edges 435 of the plates 433 are at right angles to each other.
- the leading edges 435 are angled in this way to support the combustion process preventing quenching of the heat coming from the combustion chamber which would normally tend to denigrate the combustion process.
- the shape of the leading edges of the plates 433 can be any appropriate shape to protect the plate 433 in this arrangement and to help support the combustion process.
- the leading edges 435 and plates 433 can help to reduce C0 2 emissions from the combustion chamber by helping to maintain heat therein to support the combustion process.
- Figure 52 is a heat exchanger with the flow path shown, for illustration purposes only, such as it would be if the plates were manufactured from perspex or some clear material.
- the shape of the plate is of a Y configuration similar to some of the previous embodiments and the flow path is formed in much the same way and has much the same characteristics.
- the plate of Figure 52 and the heat exchanger formed therefrom has a difference with the elements of previous embodiments in that at two points in the flow path an opportunity for crossing over is provided. These cross overs are at points 527A and 527B. In the flow path water travels from the lower header 233, out to the left and right hand sides thereof, then upwardly and back towards the centre to approach the first cross over at 527B.
- the two flows may either cross over each other; pass through each other; or generally fill the central dimples of the cross over and then from there radiate outwardly in the right and left hand direction. It is possible that the water may not actually cross over but rather may keep to the respective halves of the plate.
- the water may or may not cross over; may or may not pass over; under or through. However water will continue to flow from the central dimples of the cross over in an outward direction along the predefined paths making its way back along the leading edge into the upper header 232.
- leading edge 260 has an appropriately scalloped or shaped leading edge so that the material of the leading edge is such that along any point thereon the distance to the closest channel or dimple is roughly the same across the same of the whole leading edge. This ensures that hot spots which might otherwise have formed because of being a further distance away from the channel or dimples will not be created.
- FIG. 52 The construction and flow path illustrated in Figure 52 is thought to be advantageous in that if any one portion of the flow path were to be effected by scale, water could still flow through at least half the combustion chamber.
- Illustrated in Figure 53 is an end heat exchanger which could be utilised with the embodiment of Figure 52. Whilst there are no cross overs in this element and it is constructed in a similar manner to the plate 560 of Figure 35 (and like numbers have been used for like parts).
- a special feature of the plate of Figure 53 is that a bypass passage 529A is provided between the lower header 233 and the upper header 232. The use of such a bypass passage can be advantageous in that a lesser pressure drop can be sustained.
- Illustrated in Figure 54 is a water heater 10D which uses a water jacket assembly 50D similar to water jacket assembly
- Each of the embodiments previously described above do or can use a cold water bypass which helps to increase the pressure at the output as well as to control temperature.
- a cold water bypass which helps to increase the pressure at the output as well as to control temperature.
- the bypass can be adjustable to cope with conditions as sensed by the control unit 80 which may need to increase or decrease the flow through the bypass thereby achieving both hot water and a higher pressure at output.
- One of the features of the water heaters of the present invention is that several prior art instantaneous water heaters tend to have a serially connected water passage through the heat exchanger.
- One of the distinct advantages of the present invention is the ability to "gang up” or “connect in parallel” heat exchanger elements made up of similarly shaped plates which can result in a lower pressure drop from the inlet to the outlet of the heat exchanger in view of many parallel flows occurring simultaneously through the heat exchanger elements.
- the above description and method of manufacturing a heat exchanger, water jacket and combustion chamber assembly is such that one of the advantages is that the construction and features allow for a modular and scalable unit.
- the term scalable is used in the sense of being able to scale the size up or down according to the amount of Mega Joules utilised or required from the hot water system. For example, in a hot water system that would utilise approximately 200 Mega Joules of energy per hour, the combustion chamber/water jacket/heater exchanger assembly of Figure 37 which will have effectively two end elements and three heat exchanger elements would be of a size generally suitable for example for say 60 to 90 Mega Joules of heat throughput.
- orientation of combustion chamber and combustion gas flow path can be in any one of the following directions: upwardly; downwardly; side ways directed; directed at an angle to the horizontal and or vertical. While the above descriptions of the embodiments generally utilises identical plates to form heat exchanger elements, it will also be understood that non identical plates can be utilised. By the use of non identical plates different shaped flow paths can be produced to those described above which in the main tend to be somewhat regular and in some cases symmetrical in front elevation. However, to produce a flow path such as a saw tooth shape made up of one vertical path length connected by an angled path length, will require the use of non identical plates if dimples are to be formed on both plates. Clearly, if a flow path is formed from a plate having a continuous channel therein and is joined to a flat plate, the shape of the path of the continuous channel can be any desired shape.
- fusing is the preferred process described above to join and hold plates and adjacent plates together. This can be substituted by any joining or holding process such as suitable adhesives, mechanical clamping systems with appropriate sealing mechanisms; welding etc.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Health & Medical Sciences (AREA)
- Public Health (AREA)
- Details Of Fluid Heaters (AREA)
- Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
Abstract
Description
Claims
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP99966763A EP1285203A4 (en) | 1999-12-14 | 1999-12-14 | Water heater and water heater component construction |
AU22672/00A AU768717C (en) | 1998-06-15 | 1999-12-14 | Water heater and water heater component construction |
JP2001545781A JP2003517559A (en) | 1999-12-14 | 1999-12-14 | Water heater and water heater member structure |
PCT/AU1999/001106 WO2001044727A1 (en) | 1999-12-14 | 1999-12-14 | Water heater and water heater component construction |
CN99817081A CN1398337A (en) | 1999-12-14 | 1999-12-14 | Water heater and water heater component construction |
KR1020027007630A KR20020070992A (en) | 1999-12-14 | 1999-12-14 | Water heater and water heater component construction |
US10/166,782 US20020148415A1 (en) | 1998-06-15 | 2002-06-12 | Water heater and water heater component construction |
AU2003262471A AU2003262471A1 (en) | 1998-06-15 | 2003-11-21 | Water Heater and Water Heater Component Construction |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/AU1999/001106 WO2001044727A1 (en) | 1999-12-14 | 1999-12-14 | Water heater and water heater component construction |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/166,782 Continuation US20020148415A1 (en) | 1998-06-15 | 2002-06-12 | Water heater and water heater component construction |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001044727A1 true WO2001044727A1 (en) | 2001-06-21 |
Family
ID=3764602
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AU1999/001106 WO2001044727A1 (en) | 1998-06-15 | 1999-12-14 | Water heater and water heater component construction |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1285203A4 (en) |
JP (1) | JP2003517559A (en) |
KR (1) | KR20020070992A (en) |
CN (1) | CN1398337A (en) |
WO (1) | WO2001044727A1 (en) |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001092788A1 (en) * | 2000-06-02 | 2001-12-06 | Rheem Australia Pty Ltd | Flow path in water heater heat exchanger plates |
US6470836B1 (en) | 1998-06-15 | 2002-10-29 | Rheem Australia Pty Ltd. | Water jacket assembly |
ES2230961A1 (en) * | 2002-10-10 | 2005-05-01 | Jose Maria Vergara Uranga | Condensation boiler controlling the outlet water temperature includes two heat exchangers for condensation by counterflow of cold water |
ES2273549A1 (en) * | 2005-01-10 | 2007-05-01 | Jose Maria Vergara Uranga | Heat exchanger for condensing boiler |
US7298968B1 (en) | 2007-01-05 | 2007-11-20 | Rheem Manufacturing Company | Pumpless combination instantaneous/storage water heater system |
EP1933101A2 (en) | 2006-12-08 | 2008-06-18 | Vaillant GmbH | Heat exchanger with combustion chamber |
CN103438562A (en) * | 2013-08-29 | 2013-12-11 | 苏州赛斯德工程设备有限公司 | Gas water heater heated step by step |
US8696873B2 (en) | 2009-07-27 | 2014-04-15 | Ppm-Clean Ab | Method and plant for purification of oil-contaminated bilge and sludge water on a ship, and ship equipped with such plant |
US8768154B2 (en) | 2011-06-21 | 2014-07-01 | Daichi L Nakagawa | Fixed and selectively fixed bypass pumpless instantaneous / storage water heater system |
WO2016010500A1 (en) * | 2014-07-16 | 2016-01-21 | Zümrüt Ali | Combi boiler with heat exchanger |
CN106133456A (en) * | 2014-03-17 | 2016-11-16 | 庆东纳碧安株式会社 | The heat exchanger of condensation gas boiler |
TWI558957B (en) * | 2014-09-05 | 2016-11-21 | 台灣櫻花股份有限公司 | Gas water heater and heat exchanger thereof |
EP3128253A4 (en) * | 2014-03-17 | 2017-12-06 | Kyungdong Navien Co., Ltd. | Latent-heat exchanger for hot-water heating and condensing gas boiler including same |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101975528A (en) * | 2010-11-09 | 2011-02-16 | 美的集团有限公司 | Heat exchanger for gas water heater |
US20140123578A1 (en) * | 2011-03-01 | 2014-05-08 | President And Fellows Of Harvard College | Thermal management of transparent media |
KR101639188B1 (en) * | 2014-11-19 | 2016-07-13 | 주식회사 경동나비엔 | Boiler having check valve integrated water pipe conduit |
KR101931971B1 (en) * | 2016-02-05 | 2018-12-24 | 주식회사 경동나비엔 | Heat exchanger |
JP2018059650A (en) * | 2016-10-04 | 2018-04-12 | リンナイ株式会社 | Heat exchanger and heat source device |
CN106595056B (en) * | 2017-01-27 | 2023-01-24 | 黄婉平 | Heat exchanger applied to gas heating water heater or gas water heater |
JP7256951B2 (en) * | 2018-10-29 | 2023-04-13 | 株式会社ノーリツ | Plate heat exchanger and water heater equipped with same |
CN109654737A (en) * | 2018-12-25 | 2019-04-19 | 广东顺德大派电气有限公司 | A kind of heat exchanger with the stainless steel tube containing fin |
CN110530179B (en) * | 2019-08-12 | 2021-02-12 | 西安交通大学 | Symmetrical bubbling type plate heat transfer element |
RU203911U1 (en) * | 2020-09-29 | 2021-04-27 | Общество с ограниченной ответственностью "Эко-Спектрум" | HOT WATER GAS BOILER |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5050671A (en) * | 1989-05-12 | 1991-09-24 | Du Pont Canada Inc. | Panel heat exchangers formed from thermoplastic polymers |
WO1993018360A1 (en) * | 1992-03-12 | 1993-09-16 | John Francis Urch | Moulded baffle heat exchanger |
EP0611941A2 (en) * | 1993-02-19 | 1994-08-24 | GIANNONI S.r.l. | A plate-type heat exchanger and related plates |
WO1996041995A1 (en) * | 1995-06-13 | 1996-12-27 | Tetra Laval Holdings & Finance S.A. | Plate heat exchanger |
US5727118A (en) * | 1993-11-25 | 1998-03-10 | Vicarb | Electric boiler for heat-transfer liquid circulating in an open or closed circuit |
EP0857925A2 (en) * | 1997-02-08 | 1998-08-12 | VIESSMANN WERKE GmbH & CO. | Wall mounted burner |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE767617R (en) * | 1971-05-25 | 1971-10-18 | Defawes Ets Thomas | |
IT1210380B (en) * | 1987-05-05 | 1989-09-14 | Zanussi A Spa Industrie | DUCTED PLATE EVAPORATOR FOR REFRIGERATOR APPLIANCES. |
US5111878A (en) * | 1991-07-01 | 1992-05-12 | General Motors Corporation | U-flow heat exchanger tubing with improved fluid flow distribution |
CA2150437C (en) * | 1995-05-29 | 1999-06-08 | Alex S. Cheong | Plate heat exchanger with improved undulating passageway |
-
1999
- 1999-12-14 JP JP2001545781A patent/JP2003517559A/en active Pending
- 1999-12-14 EP EP99966763A patent/EP1285203A4/en not_active Withdrawn
- 1999-12-14 CN CN99817081A patent/CN1398337A/en active Pending
- 1999-12-14 KR KR1020027007630A patent/KR20020070992A/en not_active Application Discontinuation
- 1999-12-14 WO PCT/AU1999/001106 patent/WO2001044727A1/en not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5050671A (en) * | 1989-05-12 | 1991-09-24 | Du Pont Canada Inc. | Panel heat exchangers formed from thermoplastic polymers |
WO1993018360A1 (en) * | 1992-03-12 | 1993-09-16 | John Francis Urch | Moulded baffle heat exchanger |
EP0611941A2 (en) * | 1993-02-19 | 1994-08-24 | GIANNONI S.r.l. | A plate-type heat exchanger and related plates |
US5727118A (en) * | 1993-11-25 | 1998-03-10 | Vicarb | Electric boiler for heat-transfer liquid circulating in an open or closed circuit |
WO1996041995A1 (en) * | 1995-06-13 | 1996-12-27 | Tetra Laval Holdings & Finance S.A. | Plate heat exchanger |
EP0857925A2 (en) * | 1997-02-08 | 1998-08-12 | VIESSMANN WERKE GmbH & CO. | Wall mounted burner |
Non-Patent Citations (1)
Title |
---|
See also references of EP1285203A4 * |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6470836B1 (en) | 1998-06-15 | 2002-10-29 | Rheem Australia Pty Ltd. | Water jacket assembly |
WO2001092788A1 (en) * | 2000-06-02 | 2001-12-06 | Rheem Australia Pty Ltd | Flow path in water heater heat exchanger plates |
ES2230961A1 (en) * | 2002-10-10 | 2005-05-01 | Jose Maria Vergara Uranga | Condensation boiler controlling the outlet water temperature includes two heat exchangers for condensation by counterflow of cold water |
ES2273549A1 (en) * | 2005-01-10 | 2007-05-01 | Jose Maria Vergara Uranga | Heat exchanger for condensing boiler |
EP1933101A2 (en) | 2006-12-08 | 2008-06-18 | Vaillant GmbH | Heat exchanger with combustion chamber |
EP1933101A3 (en) * | 2006-12-08 | 2012-09-05 | Vaillant GmbH | Heat exchanger with combustion chamber |
US7298968B1 (en) | 2007-01-05 | 2007-11-20 | Rheem Manufacturing Company | Pumpless combination instantaneous/storage water heater system |
US8696873B2 (en) | 2009-07-27 | 2014-04-15 | Ppm-Clean Ab | Method and plant for purification of oil-contaminated bilge and sludge water on a ship, and ship equipped with such plant |
US8768154B2 (en) | 2011-06-21 | 2014-07-01 | Daichi L Nakagawa | Fixed and selectively fixed bypass pumpless instantaneous / storage water heater system |
CN103438562A (en) * | 2013-08-29 | 2013-12-11 | 苏州赛斯德工程设备有限公司 | Gas water heater heated step by step |
CN106133456A (en) * | 2014-03-17 | 2016-11-16 | 庆东纳碧安株式会社 | The heat exchanger of condensation gas boiler |
EP3128249A4 (en) * | 2014-03-17 | 2017-12-06 | Kyungdong Navien Co., Ltd. | Heat exchanger for condensing gas boiler |
EP3128253A4 (en) * | 2014-03-17 | 2017-12-06 | Kyungdong Navien Co., Ltd. | Latent-heat exchanger for hot-water heating and condensing gas boiler including same |
US10605484B2 (en) * | 2014-03-17 | 2020-03-31 | Kyungdong Navien Co., Ltd. | Latent-heat exchanger for hot-water heating and condensing gas boiler including same |
WO2016010500A1 (en) * | 2014-07-16 | 2016-01-21 | Zümrüt Ali | Combi boiler with heat exchanger |
TWI558957B (en) * | 2014-09-05 | 2016-11-21 | 台灣櫻花股份有限公司 | Gas water heater and heat exchanger thereof |
Also Published As
Publication number | Publication date |
---|---|
KR20020070992A (en) | 2002-09-11 |
EP1285203A4 (en) | 2006-06-21 |
EP1285203A1 (en) | 2003-02-26 |
JP2003517559A (en) | 2003-05-27 |
CN1398337A (en) | 2003-02-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1285203A1 (en) | Water heater and water heater component construction | |
US20020148415A1 (en) | Water heater and water heater component construction | |
EP1872062B1 (en) | Heat exchanger for condensing wall-mounted boilers | |
US6470836B1 (en) | Water jacket assembly | |
AU666812B2 (en) | Ultra-high efficiency on-demand water heater | |
JP3889001B2 (en) | Liquid heating system | |
EP1281919A2 (en) | High efficiency spiroidal heat exchanger for heating and/or production of sanitary hot water | |
EP0719991B1 (en) | Heat exchanger | |
AU768717C (en) | Water heater and water heater component construction | |
CN101711339B (en) | Heat exchanger | |
AU2003262471A1 (en) | Water Heater and Water Heater Component Construction | |
JP4728056B2 (en) | Hot water equipment | |
CA2469438C (en) | Finned tube water heater | |
AU2006203424A1 (en) | A Water Heater and Water Heater Component | |
WO2001092788A1 (en) | Flow path in water heater heat exchanger plates | |
AU748676B2 (en) | Water jacket assembly | |
JP2000205658A (en) | Combustion equipment | |
EP1306626B1 (en) | Equipment for water heater | |
EP0608030B1 (en) | Three-way combi-boiler | |
CA2448655A1 (en) | Hot water heater | |
AU2766102A (en) | Water jacket assembly | |
EP0751363A1 (en) | Heat exchanger | |
AU2766002A (en) | Water jacket assembly | |
CN107850340A (en) | Heat exchanger | |
CN2288370Y (en) | Gas water heater |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AL AM AT AU AZ BA BB BG BR BY CA CH CN CR CU CZ DE DK DM EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): GH GM KE LS MW SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG |
|
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 22672/00 Country of ref document: AU |
|
WWE | Wipo information: entry into national phase |
Ref document number: 10166782 Country of ref document: US |
|
ENP | Entry into the national phase |
Ref country code: JP Ref document number: 2001 545781 Kind code of ref document: A Format of ref document f/p: F |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020027007630 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 519795 Country of ref document: NZ |
|
WWE | Wipo information: entry into national phase |
Ref document number: 99817081X Country of ref document: CN |
|
WWP | Wipo information: published in national office |
Ref document number: 1020027007630 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1999966763 Country of ref document: EP |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: 8642 |
|
WWP | Wipo information: published in national office |
Ref document number: 1999966763 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 22672/00 Country of ref document: AU |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: 1020027007630 Country of ref document: KR |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: 1999966763 Country of ref document: EP |