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WO2003038342A1 - Chauffe-eau ameliore - Google Patents

Chauffe-eau ameliore Download PDF

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Publication number
WO2003038342A1
WO2003038342A1 PCT/AU2002/001444 AU0201444W WO03038342A1 WO 2003038342 A1 WO2003038342 A1 WO 2003038342A1 AU 0201444 W AU0201444 W AU 0201444W WO 03038342 A1 WO03038342 A1 WO 03038342A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
tank
heat
wall
water heater
Prior art date
Application number
PCT/AU2002/001444
Other languages
English (en)
Inventor
Steve Harmon
Ying You
Original Assignee
Quantum Energy Technologies Pty Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AUPR8658A external-priority patent/AUPR865801A0/en
Application filed by Quantum Energy Technologies Pty Limited filed Critical Quantum Energy Technologies Pty Limited
Priority to JP2003540574A priority Critical patent/JP2005507069A/ja
Priority to EP02802249A priority patent/EP1446615A4/fr
Priority to NZ532679A priority patent/NZ532679A/en
Priority to KR1020047006736A priority patent/KR100929951B1/ko
Priority to US10/494,125 priority patent/US20040237557A1/en
Priority to CA2465538A priority patent/CA2465538C/fr
Publication of WO2003038342A1 publication Critical patent/WO2003038342A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • F24H1/18—Water-storage heaters
    • F24H1/181—Construction of the tank
    • 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
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F24H4/04—Storage heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/70—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits
    • F24S10/75—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits with enlarged surfaces, e.g. with protrusions or corrugations
    • F24S10/755—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits with enlarged surfaces, e.g. with protrusions or corrugations the conduits being otherwise bent, e.g. zig-zag
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/44—Heat exchange systems

Definitions

  • This invention relates to improvements in the design and manufacture of water heaters, and more particularly the design and manufacture of heat pump water heaters.
  • Australian Patent No. 603510 discloses a water heater and a method of making a heat exchanger for a water heater wherein a tube adapted to carry a refrigerant fluid is wound around a water tank and is bonded to the wall of the water tank by a heat conductive bonding material.
  • the tube is wound around the tank under tension so as to reduce the likelihood of the heat conductive bonding material breaking during the expansion and contraction of the tube and tank during use.
  • the tank is baked in an oven to enable the bonding material to harden.
  • the bonding material performs two roles; namely to bond the coil onto the tank and to secondly improve the heat transfer performance between the tube and the tank.
  • a first aspect of the present invention provides a water heater comprising: a water tank having a wall formed from material having heat transfer properties; a cold water inlet adjacent one end of the tank; a tube adapted to carry a refrigerant fluid secured externally about said tank wall; heat-conductive material along the length of said tube with the tube and heat- conductive material in heat-conductive contact with the external surface of said wall of said tank to transfer heat from condensation of refrigerant fluid in said tube through said wall to the water contained in the tank; an evaporator positioned to be exposed to ambient conditions for absorbing heat energy from said ambient conditions, and having a passage for carrying the refrigerant fluid whereby said fluid may be heated by said ambient conditions; and a compressor connected to said passage and to said tube to circulate refrigerant fluid through said tube and to said evaporator.
  • the tube is wound around said tank.
  • the heat conductive material is substantially coextensive with the length of the tube.
  • the tube is formed from copper or a copper-based alloy.
  • the tube is mechanically fastened at one or more locations to the wall of the tank.
  • two or more tubes are wound around the tank and carry the refrigerant fluid.
  • a second aspect of the present invention provides a method of making a heat exchanger for a water heater comprising the step of attaching one end of a tube to the external surface of a metallic water tank, placing the tube around the external surface of said tank, and injecting a heat transfer sealer material between the tube and the wall of the tank.
  • the tube is wound around the external surface of the tank. More preferably, the tube is wound around the external surface of the tank under a predetermined tension.
  • the pitch of the winding of the tube around the tank varies. More particularly, the windings of the tube are more closely spaced at the bottom of the tank and the spacing between adjacent windings progressively increases towards the top of the tank.
  • the present invention alleviates the need for the curing of a bonding material at an elevated temperature. In comparison to the water heater disclosed in Australian Patent No.
  • the heat transfer material acts to enhance the heat transfer between the tube and the tank and, unlike the bonding material disclosed in the prior art, does not act to retain the tube on the wall of the water tank. According to the present invention the tube is mechanically retained on the wall of the tank.
  • Fig. 1 is a fragmentary sectional elevation of a water tank incorporating a heat exchanger suitable for use with the water heater embodying the invention
  • Fig. 1 A is an enlarged fragmentary sectional elevation of portion of the tank showing the attachment of the tube thereto;
  • Fig. 2 A is a schematic elevation of mechanism for applying the tube to the tank;
  • Fig. 2B is an enlarged schematic elevation of the tube deforming rollers shown in Fig. 2A;
  • Fig. 3 is a schematic diagram showing the layout of a solar boosted heat pump water heating system embodying the invention
  • Fig. 4 is a schematic diagram showing an arrangement for cooling the compressor used in the system of Fig. 3;
  • Fig. 5 is a schematic diagram showing one layout of the refrigerant passages in the solar collector used in the system of Fig. 3;
  • Fig. 6 is a sectional side elevation of one of the solar evaporator/collectors used in the system of Fig. 3.
  • the water tank 1 has a cylindrical wall 2, a bottom wall 3, a convex top wall 4, a cold water inlet 5 adjacent the bottom wall 3 incorporating a diffuser or diverter 6 and a hot water outlet 7 adjacent the top wall 4. While the bottom wall 3 is shown to be concave, it may be convex if desired.
  • a tube 8 carrying a refrigerant, such as refrigerant R22, is wrapped around the external surface of the tank wall 2.
  • the tube 8 is manufactured from copper or a copper-based alloy.
  • the tube 8 is preferably flattened as shown in Fig. 1 A, so that it is substantially D-shaped in cross-section, with the flattened face of the tube located against the wall of the tank.
  • a heat sealing paste 9 is located between the adjacent surfaces of the tube 8 and the wall of the tank so as to provide heat transfer therebetween.
  • the heat sealing paste is located along the entire length of the interface between the tube 8 and the tank wall 2.
  • the heat sealing paste may be intermittently located along the interface, although typically this would result in a decrease in heat transfer efficiency.
  • the tube 8 is wound around the tank 1 under tension and is mechanically secured to the tank 1 while under tension. This may be achieved in the manner shown schematically in Fig. 2 A of the drawings.
  • the tube 8 Whilst it is preferable for the tube 8 to be helically wound around the external surface of the tank wall 2, it should be noted that alternative placings of the tube 8 on the external wall of the tank may be possible.
  • the tube may be formed in a concertina manner and placed on the external wall of the tank so that the tube extends up and down the external wall of the tank.
  • such a configuration may add additional complexity to the manufacture of the system and hence be less desirable than a helical tube winding.
  • a heat transfer material 9 in the form of a paste is inserted or injected between the tube 8 and the tank wall 2.
  • the paste does not need to be cured, or if curing is required it may be cured under ambient conditions hence alleviating the need for curing at elevated temperatures in an oven or kiln.
  • a suitable heat transfer paste is "HTSP Silicone Heat Transfer Compound Plus", marketed in Australia by Electrolube. This is a silicone oil-based heat transfer paste with a thermal conductivity of approximately 3.0 W/mK.
  • Other suitable kinds of heat transfer paste such as "Bostik 1128 Heat Transfer Sealer” marketed in Australia by Bostik, may also be used.
  • the tank 1 is supported on a rotating table 20, which is rotatably driven by a motor 21 through a gear box 22 and chain drive 23.
  • a suitable length of tube 8 is fed by feed rollers 24 and deformed into the D-shape shown in Fig. 1A by deforming rollers 25.
  • the feed rollers 24 and the deforming rollers 25 form part of an assembly including a nut engaging a feed screw 26 which is rotatably driven by a motor 27 to move the assembly up the tank 1 at the required rate relative to rotation of the table 20 so that the tube 8 is wound around the tank with the required spacing between adjacent turns.
  • the deforming rollers 25 include a knurled roller 28 and a grooved support roller 29.
  • the rollers 28 and 29 are driven by gears 30, 31 which are driven at the same speed as the pinch rollers 24 to ensure that the tube 8 is fed and deformed at the same rate.
  • the pinch rollers 24 and the rollers 28 and 29 are restrained against free rotation by means of brake pads, such as those shown in Fig. 2B at 32.
  • the tension applied to the tube may be adjusted by clamping the brake pads 32 into engagement with the roller 29 and gear 30 under the influence of a spring 33 which is adjustably compressed by means of a tension nut 34.
  • the part of the tank 1 to which the tube 8 is to be fixed in cleaned and a copper flash is applied in a known manner.
  • the tube 8 is then fixed by spot welding to the bottom of the tank wall 2 and the tube 8 is then wound around the tank using the mechanism shown in Fig. 2A of the drawings.
  • the upper end thereof is fixed to the wall 2 of the tank 1 by spot welding to maintain the tube 8 under tension.
  • the tube 8 extends from the position adjacent the bottom wall 3 to an appropriate height on the tank 1 and defines a heat exchange surface S on the wall 2.
  • the lowermost turn 8 A of tube 8 is located under the cold water inlet 5, which is usually cold, and this causes sub-cooling of the refrigerant whereby it is rendered stable enough for transportation.
  • the tube 8 is connected to a solar boosted heat pump (Fig. 3 as described below) of the general type described in Australian Patent No. 509901, although it will be noted that modifications to that system have been made in the system described further below.
  • Other forms of heat pump may also be used and the heat exchange medium carried by the tube 8 may be varied as desired.
  • both the tube 8 and the tank 1 are preferably made from a similar material, or at least from materials having similar coefficients of thermal expansion.
  • the tank 1 is fabricated from steel or stainless steel whilst the tube 8 is made from copper or copper-based alloy.
  • the different rates of expansion and contraction of the materials may be compensated for by increasing the winding tension of the tube 8 in the manner described above.
  • the winding of the tube under tension ensures that the thermal bond is maintained notwithstanding the flexing of the materials caused by expansion and contraction in use.
  • the described heat exchange arrangement is eminently suitable for use with a fluid A, such as water which is likely to contain precipitatable contaminants since a major portion of the heat exchanger surface S is vertical whereby the accumulation of precipitates on the heat exchanger surface is discouraged.
  • the heat exchanger surface S is sufficiently enlarged to allow for the application of coatings, such as vitreous enamel, while still maintaining the product of heat transfer coefficient and surface area at an efficient level and minimising the temperature difference between the fluid to be heated A and the heat exchanger surface S.
  • the area of the heat exchange surface S is selected so as to give the best compromise between the following conflicting requirements: (a) The requirement that the heat exchanger surface be substantially vertical, downwardly facing or downwardly sloping as discussed above;
  • Requirement (c) minimises the irreversibility of the system of which the heat exchanger is a part which implies that the temperature at which heat is being transferred between the refrigerant B and the fluid A to be heated is as close as possible to the coldest sink temperature of fluid A.
  • the passive volume of the vessel is increased. This volume acts as a stored volume of fluid ready for delivery to the end user of the fluid A.
  • the spacing between the turns of tubing 8 and the flow rate of the refrigerant or other heat transfer fluid B must be optimised so as to give adequate fluid side surface area S, heat transfer medium side surface area T, heat transfer coefficients, heat exchanger fin efficiency and adequate passive storage if required.
  • the requirements of this optimisation is always a compromise and depends largely on the size of the system and the fluids in use.
  • the surface area S is made as large and yet as compact as possible until the benefits outlined above are negated by the increase in heat transfer temperature difference across surface S caused by the reduction in area available to transmit the desired total heat flux.
  • the spacing and sizing of the tubes on the outside face of the heat exchanger surface S is then determined by established engineering design procedures involving consideration of internal tube heat transfer, tube to wall bond conduction and fin efficiency if applicable. Reconsideration of the surface area S determined may then be necessary if the tube spacing computations reveal that further optimisation of the design is possible through some compromise with surface area S.
  • the entry and exit conduits are arranged so as not to promote mixing by stirring up the fluid A.
  • the cold conduit 5 is positioned at the bottom of the tank and the hot conduit 7 at the top of the tank.
  • the axis of the entry conduit 5 is perpendicular to the axis of stratification, hi addition a downwardly facing diffuser-deflector 6 is used at the cold water inlet 5 while an upwardly facing diffuser- deflector 6a is used at the hot water outlet 7 to further reduce mixing and stirring.
  • the heat exchanger should preferably be arranged so that the counterflow principle is embodied as this further improves heat transfer.
  • the refrigerant B flows from the top of the coiled tube 8 to the bottom.
  • a preferred solar boosted heat pump water heating system is shown schematically in Fig. 3 of the drawings and will be seen to include a heat exchange system embodying the invention in which the tank 1 and refrigerant carrying tube 8 is enclosed in a housing 10 containing insulating foam 11.
  • the compressor 12 and receiver/filter/drier 13 of the heat pump system are mounted on a refrigeration chassis 14 located on top of the tank housing 10. This arrangement avoids the need for the housing 10 to be supported at an elevated position to allow location of the compressor and receiver under the tank housing as is usual, thereby reducing construction costs.
  • the compressor 12 is preferably a rotary compressor, although other forms of refrigerant compressors may be used without materially detracting from the efficiency of the system.
  • a rotary compressor is preferred because of its relatively smooth quieter operation.
  • a rotary compressor is able to accept slugs of liquid on the suction side of the compressor whereas other types of compressors have greater difficulty accepting such slugs. These slugs may occur in a solar boosted heat pump due to the rapid variations in temperature which may be experienced as a result of changing weather conditions.
  • the compressor 12 is preferably externally insulated.
  • the compressor is cooled by bleeding refrigerant from the outlet of the condenser or receiver directly into the inlet suction line or into the "suction side" of the cylinder through a bypass line which is preferably controlled by a control valve, capillary tubing or fixed orifice (not shown).
  • a control valve capillary tubing or fixed orifice (not shown).
  • FIG. 4 of the drawings One arrangement for achieving this is shown schematically in Fig. 4 of the drawings and will be seen to comprise a cylinder 12A enclosed within an insulating casing 12B and containing a rolling piston 12C and vane 12D.
  • a liquid injection tube 12E is connected from the refrigerant liquid line to the suction line 12G into the compressor 12.
  • the system includes a thermostat control system including a thermostat T. More complex thermostat variations are possible, including: a) a variable or dual thermostat setting which depends on the level of sunlight, or b) sensing evaporation temperature when the unit is running and using this as an indication of the potential performance which in turn increases or decreases the thermostat set point.
  • the overall aim of the above described systems is to bias the system towards running during the day by making it raise the water to a higher temperature during daylight hours than during the night. Further sophistications are possible by making the set point of the thermostat a function of solar radiation and ambient air temperature although control "intelligence" is required in this case so that adequate water temperatures are reached during the winter. Similarly, biasing the system to operate primarily during a low tariff (off-peak) period is possible.
  • Each evaporator plate 15 contains a number of refrigerant passages 16 which are preferably arranged in the configuration shown in Fig. 5 of the drawings.
  • Each evaporator plate 15 is made from two sheets of metal which are bonded together, except in the regions of the passages 16, by the so-called Roll-BondTM process, which is well known in the art. Since the evaporator plates are formed from thin sheet metal, each evaporator plate is supported in an outwardly curved profile as shown in the sectional elevation of Fig. 6 of the drawings.
  • the outwardly curved profile is maintained by the positioning of a moulded insulating foam former 17 behind each plate 15, the assembly being supported by two bearers as shown in Figs. 3 and 6 of the drawings.
  • Each evaporator plate 15 is further strengthened by the formation of an angle section 18 along each longitudinal edge of the plate 15.
  • the evaporator plate arrangement described above has been found to perform well in wind tests conducted to assess its ability to withstand wind forces of the type encountered when the evaporator plate is mounted on the roof of a dwelling.
  • each evaporator plate is formed with three separate parallel refrigerant passages 16 connected at either end by a manifold 19 to which the refrigerant lines (not shown) are connected.
  • the plates 15 are, as shown in Fig. 3 of the drawings, connected in series so that the outlet manifold of the first plate is connected to the inlet manifold of the second plate and so on.
  • the first passage connected to a manifold at one end of the plate is the last passage connected to the manifold at the other end of the plate to assist in equalising the flow of refrigerant in the parallel passage 16.
  • the cross- sectional area of the manifold is reduced 2 after each junction to further assist in flow equalisation.
  • the arrangement minimises the cross-sectional area of the manifold and its junctions for a given design pressure drop across the manifold. This results in an improved burst pressure for a given refrigerant pressure drop compared with the performance of the typical "waffle” type distributor used in other "Roll Bond” evaporators.
  • the evaporator plate can be used with high evaporation pressure refrigerants such as R22 without incurring a high pressure drop across the evaporator.
  • the evaporator may be mounted at downward sloping angles, as is usually desired, as flow equalisation between passages 16 is relatively unaffected by the forces of gravity which usually cause the lowermost passage to be favoured.
  • Refrigerant fluid is delivered to the top of each plate 15 rather than to the bottom, as is usually the case, and this allows the use of less refrigerant since the plates do not need to be flooded as is the case with bottom entry.
  • An additional advantage is that positive oil return is achieved since the oil does not tend to accumulate at the bottom of the plates as it does with bottom entry.
  • Top entry of the refrigerant in combination with high velocity refrigerant circulation causes annular flow of wet fluid in the passages 16 which improves the heat transfer from the plates to the fluid. In this mode of operation refrigerant gas flows within the wet fluid annulus.
  • a liquid trap is provided prior to returning the refrigerant to the compressor suction to prevent any accumulation of liquid in the plates 15 while the system is off from flowing by gravity down into the compressor suction.
  • the trap must be sized such that oil is carried over with the refrigerant gas during operation.
  • the TX valve in the liquid line is located inside the refrigeration chassis 14 rather than at the evaporator plates 15 as is usually the case.
  • the TX valve is biased to give an appropriate superheat by setting to an appropriate superheat setting.
  • the evaporator plates are shown in the above embodiment as being mounted in a position exposed to the sun, the plates may be mounted on the outside of the housing 10, as shown in broken outline in Fig. 3, in a wrap around configuration in areas where the ambient temperature is high or where the tank is able to be mounted on a roof or in another position which is at least partly exposed to the sun.
  • the heat pump operates at least partly as an air source heat pump.

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  • Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Combustion & Propulsion (AREA)
  • Dispersion Chemistry (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Fluid Heaters (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

La présente invention concerne un chauffe-eau qui comprend un réservoir (1) d'eau possédant une paroi formée dans un matériau possédant des propriétés de transfert thermique, et une entrée (5) d'eau froide contiguë à une extrémité du réservoir. Un tuyau (8), conçu pour porter un fluide réfrigérant est fixé à l'extérieur autour de la paroi (2) du réservoir. Un matériau thermoconducteur est placé sur la longueur du tuyau, ce tuyau et ce matériau thermoconducteur étant en contact thermoconducteur avec la surface externe de la paroi du réservoir de façon à transférer la chaleur issue de la condensation du fluide réfrigérant présent dans le tube via la paroi dans l'eau contenue dans le réservoir (1). Un évaporateur (15) est positionné de façon à être exposé aux conditions ambiantes afin d'absorber l'énergie thermique de ces conditions ambiantes. L'évaporateur est pourvu d'un passage destiné à porter le fluide réfrigérant, permettant à ce fluide d'être chauffé par les conditions ambiantes. Un compresseur (12) est connecté à ce passage et au tuyau (8) de façon à faire circuler le fluide réfrigérant à travers le tube vers l'évaporateur (15).
PCT/AU2002/001444 2001-11-02 2002-10-24 Chauffe-eau ameliore WO2003038342A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2003540574A JP2005507069A (ja) 2001-11-02 2002-10-24 改良された温水器
EP02802249A EP1446615A4 (fr) 2001-11-02 2002-10-24 Chauffe-eau ameliore
NZ532679A NZ532679A (en) 2001-11-02 2002-10-24 Improved water heater
KR1020047006736A KR100929951B1 (ko) 2001-11-02 2002-10-24 개선된 워터 히터
US10/494,125 US20040237557A1 (en) 2001-11-02 2002-10-24 Improved water heater
CA2465538A CA2465538C (fr) 2001-11-02 2002-10-24 Chauffe-eau ameliore

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AUPR8658 2001-11-02
AUPR8658A AUPR865801A0 (en) 2001-11-02 2001-11-02 Improved water heater
AUPR923101 2001-11-30
AUPR9231 2001-11-30

Publications (1)

Publication Number Publication Date
WO2003038342A1 true WO2003038342A1 (fr) 2003-05-08

Family

ID=25646831

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU2002/001444 WO2003038342A1 (fr) 2001-11-02 2002-10-24 Chauffe-eau ameliore

Country Status (9)

Country Link
US (1) US20040237557A1 (fr)
EP (1) EP1446615A4 (fr)
JP (1) JP2005507069A (fr)
KR (1) KR100929951B1 (fr)
CN (1) CN1417527A (fr)
AU (2) AU2008203073A1 (fr)
CA (1) CA2465538C (fr)
NZ (1) NZ532679A (fr)
WO (1) WO2003038342A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004085927A1 (fr) * 2003-03-28 2004-10-07 Siddons Stevens Developments Pty Ltd Chauffe-eau/refroidisseur d'eau
CN100398936C (zh) * 2003-08-28 2008-07-02 上海交通大学 太阳能-空气热泵热水器
EP1933100A3 (fr) * 2006-12-05 2010-10-27 Sanyo Electric Co., Ltd. Réservoir de stockage de l'eau chaude
ES2510790A1 (es) * 2013-01-25 2014-10-21 Universidad De Las Palmas De Gran Canaria Calentador solar de agua potable
CN108204684A (zh) * 2017-12-21 2018-06-26 海宁德诺太阳能设备有限公司 一种便于组装的太阳能热水器
WO2018134126A1 (fr) * 2017-01-17 2018-07-26 Stiebel Eltron Gmbh & Co.Kg Réservoir pour le stockage d'un liquide et procédé pour la fabrication du réservoir
WO2018234786A1 (fr) * 2017-06-19 2018-12-27 Magic Thermodynamic Box Ltd Appareil de chauffage d'eau
FR3077622A1 (fr) * 2018-02-07 2019-08-09 Atlantic Industrie Appareil de chauffage thermodynamique d'une cuve

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2003901610A0 (en) * 2003-03-28 2003-05-01 Siddons Stevens Developments Pty Ltd Water heater/cooler
EP1809949B1 (fr) * 2004-11-12 2010-02-24 Zenex Technologies Limited c/o Mark Holt & Co Limited Systeme pour distribuer des fluides rechauffes
US20060213210A1 (en) * 2005-03-24 2006-09-28 Tomlinson John J Low-cost heat pump water heater
GB0522307D0 (en) * 2005-11-01 2005-12-07 Zenex Technologies Ltd A burner and heat exchanger combination, and a boiler including such a burner and heat exchanger combination
US8245949B2 (en) * 2007-07-25 2012-08-21 Grand Hotel, LLC Energy conservation system for using heat from air conditioning units to heat water supply lines
CN102027308A (zh) * 2008-05-16 2011-04-20 开利公司 具有增强的制冷剂分布的微通道热交换器
KR101547007B1 (ko) * 2009-08-27 2015-08-24 맥알리스터 테크놀로지즈 엘엘씨 주거 지원을 위한 에너지 시스템
US8385729B2 (en) 2009-09-08 2013-02-26 Rheem Manufacturing Company Heat pump water heater and associated control system
JP4707764B1 (ja) * 2010-04-13 2011-06-22 八尾乳業協同組合 温度管理を要する流動体貯蔵タンク内の汚染防止方法、およびその装置
CA2702463C (fr) * 2010-04-26 2013-07-09 Huazi Lin Chauffage d'un fluide en circulation commandee par la chaleur et reservoir de stockage et systeme connexe
CN202188657U (zh) 2010-04-26 2012-04-11 林华谘 受热液体的自驱动装置及热驱动的液体自循环系统
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US20240200875A1 (en) * 2022-12-20 2024-06-20 Blue Origin, Llc Heat exchange system with tubing applied to a complex curved surface
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2716866A (en) * 1955-09-06 Water heating systems of the heat
US4452050A (en) * 1983-03-14 1984-06-05 Heat Transfer Engineering, Inc. Energy efficient water heating device and system
GB2183817A (en) * 1985-11-12 1987-06-10 Robert Dominic Walker Heat exchange elements
AU603510B2 (en) * 1988-04-08 1990-11-15 Quantum Energy Technologies Pty Limited Water heater

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5187852A (fr) * 1974-12-24 1976-07-31 Breda Backer Rueb Maschf
GB1541577A (en) * 1976-10-06 1979-03-07 Solar Apparatus & Equipment Solar heating panels
DE3430918C1 (de) * 1984-08-22 1985-10-24 Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart Vorrichtung zum Kuehlen des Inhalts eines Gefaesses
US4918938A (en) * 1986-01-08 1990-04-24 Siddons Industries Limited Heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2716866A (en) * 1955-09-06 Water heating systems of the heat
US4452050A (en) * 1983-03-14 1984-06-05 Heat Transfer Engineering, Inc. Energy efficient water heating device and system
GB2183817A (en) * 1985-11-12 1987-06-10 Robert Dominic Walker Heat exchange elements
AU603510B2 (en) * 1988-04-08 1990-11-15 Quantum Energy Technologies Pty Limited Water heater

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004085927A1 (fr) * 2003-03-28 2004-10-07 Siddons Stevens Developments Pty Ltd Chauffe-eau/refroidisseur d'eau
CN100398936C (zh) * 2003-08-28 2008-07-02 上海交通大学 太阳能-空气热泵热水器
EP1933100A3 (fr) * 2006-12-05 2010-10-27 Sanyo Electric Co., Ltd. Réservoir de stockage de l'eau chaude
US8056825B2 (en) 2006-12-05 2011-11-15 Sanyo Electric Co., Ltd. Heating tank and hot water storage tank
ES2510790A1 (es) * 2013-01-25 2014-10-21 Universidad De Las Palmas De Gran Canaria Calentador solar de agua potable
WO2018134126A1 (fr) * 2017-01-17 2018-07-26 Stiebel Eltron Gmbh & Co.Kg Réservoir pour le stockage d'un liquide et procédé pour la fabrication du réservoir
WO2018234786A1 (fr) * 2017-06-19 2018-12-27 Magic Thermodynamic Box Ltd Appareil de chauffage d'eau
CN108204684A (zh) * 2017-12-21 2018-06-26 海宁德诺太阳能设备有限公司 一种便于组装的太阳能热水器
FR3077622A1 (fr) * 2018-02-07 2019-08-09 Atlantic Industrie Appareil de chauffage thermodynamique d'une cuve

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EP1446615A1 (fr) 2004-08-18
JP2005507069A (ja) 2005-03-10
EP1446615A4 (fr) 2005-07-20
KR20050039729A (ko) 2005-04-29
US20040237557A1 (en) 2004-12-02
KR100929951B1 (ko) 2009-12-04
CA2465538A1 (fr) 2003-05-08
NZ532679A (en) 2005-12-23
CN1417527A (zh) 2003-05-14
CA2465538C (fr) 2011-01-04
AU2008203073A1 (en) 2008-07-31
AU2010202723A1 (en) 2010-07-15

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