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WO2011071393A1 - Appareil d'échange de chaleur et système de chauffage de fluide - Google Patents

Appareil d'échange de chaleur et système de chauffage de fluide Download PDF

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Publication number
WO2011071393A1
WO2011071393A1 PCT/NZ2010/000244 NZ2010000244W WO2011071393A1 WO 2011071393 A1 WO2011071393 A1 WO 2011071393A1 NZ 2010000244 W NZ2010000244 W NZ 2010000244W WO 2011071393 A1 WO2011071393 A1 WO 2011071393A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat transfer
transfer fluid
heat exchange
heat
working fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/NZ2010/000244
Other languages
English (en)
Inventor
Rodney Mitchell Innes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Energy Saving Concepts Ltd
Original Assignee
Energy Saving Concepts Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Energy Saving Concepts Ltd filed Critical Energy Saving Concepts Ltd
Publication of WO2011071393A1 publication Critical patent/WO2011071393A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
    • F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
    • 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
    • F24H1/14—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 by tubes, e.g. bent in serpentine form
    • 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
    • F24H1/14—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 by tubes, e.g. bent in serpentine form
    • F24H1/16—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 by tubes, e.g. bent in serpentine form helically or spirally coiled
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • 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
    • F24D17/0005—Domestic hot-water supply systems using recuperation of waste heat
    • F24D17/001—Domestic hot-water supply systems using recuperation of waste heat with accumulation of heated water
    • 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
    • F24D17/0073—Arrangements for preventing the occurrence or proliferation of microorganisms in the water
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/14—Solar energy
    • 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
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/08—Storage tanks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/20—Solar thermal
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/18—Domestic hot-water supply systems using recuperated or waste heat

Definitions

  • the present invention relates to heat pumps and to heat exchange apparatus for heat pumps, and in particular, but not exclusively, to systems, apparatus and methods for heating and sterilizing water.
  • Health & Safety Regulations also govern this industry sector, with a multitude of solutions being used, including various high temperature and chemical solutions to combat bacteria growth.
  • a problem with heating the water to high temperatures to kill bacteria is that mechanical controls may be required to limit accidental hot water scalding.
  • fluid includes liquids and gases, including vapour and saturated vapour.
  • heat transfer fluid is used herein to refer to a liquid.
  • the liquid may be any liquid which is suitable for use with a heat exchanger, and in preferred embodiments is water.
  • a heat exchange apparatus for a heat pump, the heat exchange apparatus comprising a working fluid flow path having a working fluid inlet and a working fluid outlet, the working fluid flow path arranged in a heat transfer relationship with a heat transfer fluid flow path having a heat transfer fluid inlet and a heat transfer fluid outlet, the apparatus having a first heat exchange section and a second heat exchange section, the heat transfer fluid flow path and working fluid flow path extending through the first and second heat exchange sections, the apparatus further including a bypass conduit having a bypass inlet in fluid communication with the heat transfer fluid flow path in the first heat exchange section, wherein, in use a portion of the heat transfer fluid which flows through the apparatus flows through the bypass conduit, thereby bypassing the second heat exchange section.
  • the bypass conduit is substantially thermally insulated from the second heat exchange section.
  • the working fluid flow path in the second heat exchange section includes a restrictor means to restrict the flow rate of heat transfer fluid through the second heat exchange section.
  • the apparatus is configured such that, in use, the ratio of heat transfer fluid which flows through the bypass conduit to heat transfer fluid which flows through the second heat exchange section is between 5:1 and 10:1.
  • the ratio of heat transfer fluid which flows through the bypass conduit to heat transfer fluid which flows through the second heat exchange section is between 7:1.
  • the working fluid flowing through the working fluid flow path flows in counter flow to heat transfer fluid flowing through the heat transfer fluid flow path.
  • bypass conduit has an outlet which is substantially adjacent the outlet of the heat transfer fluid flow path.
  • bypass conduit outlet and the heat transfer fluid outlet converge to a single outlet.
  • the heat exchange apparatus is operable as a working fluid condenser.
  • a heat transfer fluid heating system comprising the heat exchange apparatus of the first aspect, wherein the working fluid inlet is in fluid communication with a source of working fluid vapour, and the heat transfer fluid inlet is in fluid communication with a source of heat transfer fluid.
  • the heat transfer fluid heating system comprises a heat pump.
  • a heat transfer fluid heating system comprising a working fluid circulating around a closed working fluid circuit, the working fluid circuit comprising the heat exchange apparatus of the first aspect for transferring heat from the working fluid to the heat transfer fluid, thereby condensing the working fluid, an expansion means for expanding the condensed working fluid to a saturated vapour, an evaporator for heating the saturated working fluid vapour and a compressor means for compressing the working fluid vapour before the working fluid returns to the heat exchange apparatus.
  • the working fluid circuit further comprises a subcooler heat exchange means for transferring heat from working fluid between the heat exchange apparatus and the expansion means to working fluid between the evaporator and the compressor means.
  • a heat transfer fluid heating system comprising the heat exchange apparatus of the first aspect wherein the working fluid inlet is in fluid communication with a source of working fluid vapour, and the heat transfer fluid inlet is in fluid communication with a source of heat transfer fluid, wherein the heat transfer fluid heating system further comprises sensor means for measuring a property which is indicative of a temperature of heat transfer fluid leaving the second heat exchange section, and flow rate control means for controlling a flow rate of the heat transfer fluid through the heat exchange apparatus, wherein the flow rate control means varies the flow rate of the heat transfer fluid as required to keep the temperature of the heat transfer fluid leaving the second heat exchange section above a required minimum temperature.
  • the heat transfer fluid heating system comprises a pumping means for pumping the heat transfer fluid to the heat transfer fluid inlet.
  • the pumping means is a variable flow rate pumping means.
  • the flow rate control means adjusts the flow rate of the heat transfer fluid by adjusting the flow rate of the pumping means.
  • the heat transfer fluid heating system further comprises a heat pump means which includes a working fluid liquid line, wherein the property which is indicative of a temperature of heat transfer fluid leaving the second heat transfer section comprises the temperature of the working fluid in the working fluid liquid line.
  • the heat transfer fluid heating system further comprises a heat pump means which includes a working fluid liquid line, wherein the property which is indicative of a temperature of heat transfer fluid leaving the second heat exchange section comprises the pressure of the working fluid in the working fluid liquid line. .
  • the minimum temperature is 61 °C.
  • the minimum temperature is 65°C.
  • the heat transfer fluid is water.
  • a hot water heating and storage system comprising a water circuit comprising a hot water storage tank, a pump and the heat exchange apparatus of the first aspect, wherein the working fluid inlet of the heat exchange apparatus is in fluid communication with a source of working fluid vapour, and wherein the heat transfer fluid comprises water.
  • a method of heating water comprising the steps of passing the water through the heat transfer fluid flow path of the heat transfer fluid heating system of the second, third or fourth aspects.
  • a seventh aspect of the present invention there is provided a method of reducing bacterial activity in a water stream, the method comprising the steps of passing the water through the heat transfer fluid flow path of the heat transfer fluid heating system of the second aspect wherein the water in the second heat exchange section is heated to at least 61 °C.
  • a heat transfer fluid heating system is substantially as herein described, with reference to Figures 1 , 2, 3 and 4 or Figures 1 , 2, 3 and 5.
  • the invention may also be said broadly to consist in the parts, elements and features referred to or indicated in the specification of the application, individually or collectively, in any or all combinations of two or more of said parts, elements or features, and where specific integers are mentioned herein which have known equivalents in the art to which the invention relates, such known equivalents are deemed to be incorporated herein as if individually set forth.
  • Figure 1 is a schematic diagram of a heat transfer apparatus of the present invention.
  • Figure 1A is a schematic diagram of an alternative embodiment of the heat transfer
  • Figure 2 Is a diagrammatic perspective view of a heat transfer apparatus of the present invention, with the outer housing shown in outline.
  • FIG. 3 Is an end view of the heat transfer fluid outlet fitting of the heat transfer apparatus of Figure 2.
  • Figure 4 Is a schematic diagram of a heat transfer fluid heating system of the present invention.
  • Figure 5 Is a schematic diagram of an alternative embodiment of the heat transfer fluid heating system shown in Figure 4.
  • FIG. 1 a schematic representation of the heat exchange apparatus of the present invention is generally referenced by arrow 100.
  • the apparatus 100 is typically configured as a combined desuperheater and condenser for a heat pump, but may also be used simply as a condenser or as a desuperheater, depending on the application.
  • the apparatus 100 has a heat transfer fluid flow path 1 arranged in a non-mixing heat transfer relationship with a working fluid flow path 2. Whether used as a working fluid condenser, desuperheater, or both, the apparatus 00 functions as a sterilizer for a portion of the heat transfer fluid which flows through it, as is described further below.
  • the heat transfer fluid flow path 1 has an inlet 3 and an outlet 4.
  • the working fluid flow path also has an inlet 5 and an outlet 6, which are arranged so that the working fluid flows in counter flow to the heat transfer fluid.
  • the apparatus 100 further includes a bypass conduit 7 which has at least one inlet 8 in fluid communication with the heat transfer fluid flow path 1 , between the inlet 3 and outlet 4.
  • the position of the inlet 8 divides the heat transfer apparatus 100 and the heat transfer fluid flow path 1 into a first heat exchange section 9, between the inlet 3 and bypass inlet 8, and a second heat exchange section 10 between the bypass inlet 8 and the outlet 4.
  • the bypass conduit 7 allows a portion of the heat transfer fluid which flows though the first heat exchange section 9 to bypass the second heat exchange section 10 and flow directly to the bypass outlet 11.
  • the bypass outlet 11 and heat transfer fluid flow path outlet 4 are preferably substantially adjacent, as is described hereinbelow.
  • the working fluid inlet 5 is in fluid communication with a source of working fluid vapour.
  • the heat exchange apparatus 100 is operable as a desuperheater/ condenser of a heat pump, as is described further below, and the working fluid inlet 5 receives working fluid from a compressor of the heat pump.
  • the working fluid outlet 6 is preferably in fluid communication with a pressure reduction means of the heat pump (not shown in Figure 1), for example a thermostatic valve (TXV) or a capillary tube (not shown), via a working fluid liquid line.
  • TXV thermostatic valve
  • capillary tube not shown
  • the first heat exchange section 9 preferably, provides a condenser function for the working fluid and the second heat exchange section 10 preferably provides a desuperheater function for the working fluid, as well as sterilizing a portion of the heat transfer fluid.
  • heat transfer fluid flows through the first heat exchange section 9 and receives heat from the working fluid, which is in counter flow to the heat transfer fluid, and has therefore already passed through the second heat exchange section 10.
  • the second heat exchange section 10 a portion of the heat transfer fluid flows though the heat transfer fluid flow path 1 to the outlet 4, and so receives heat from working fluid, while the remainder of the heat transfer fluid flows through the bypass conduit 7 to the bypass outlet 11 , substantially without receiving any further heat from the working fluid.
  • the proportion of heat transfer fluid which flows through the second heat exchange section 10 is controlled by a flow restriction means 12, for example an orifice or similar, which is preferably provided at or adjacent the outlet 4. Because the flow rate of heat transfer fluid through the second heat exchange section 10 is reduced, the temperature of the heat transfer fluid exiting the second heat exchange.
  • the heat transfer fluid leaves the second heat exchange section 10 at a temperature of 61 °C or more, in order to provide a reduction in bacterial activity, that is, a partial sterilisation, of the heat transfer fluid which has passed through the second heat exchange section 10.
  • the heat transfer fluid which flows through the heat transfer fluid outlet 4 is preferably combined with the heat transfer fluid which exits the bypass conduit outlet 11 , either within the apparatus ⁇ 00, or in the conduit (not shown) immediately downstream of the apparatus. However, in some embodiments the heat transfer fluid from the outlet 4 may be directed to another location or apparatus (not shown) where high temperature heat transfer fluid is required.
  • Figure 1 shows the apparatus 100 as a single, integral unit
  • the first and second heat exchange sections 9, 10 may be provided in separate housings, as shown in schematically in Figure 1 A.
  • the bypass inlet 8 may be a T junction in the conduit connecting the two discrete heat exchange units 9, 10.
  • the apparatus 100 is preferably a modification of the heat exchange apparatus described in International Patent Application No.PCT/NZ2004/000008.
  • the apparatus 100 preferably comprises a housing 13, which may be substantially cylindrical, within which a support body 14 is provided.
  • the support body 14 is also preferably substantially cylindrical.
  • One or more coils of tube 15 are wrapped tightly around the support body 14, the tube 15 providing the flow path for the working fluid between the inlet 5 and the outlet 6.
  • the tube 15 is preferably provided with one or more helical ribs, corrugations, protrusions, intrusions, tracks, or the like 16.
  • Spiral or helical tracks 17 are preferably also provided in the support body 14, in
  • the heat transfer fluid flows from the inlet 3 though the annulus between the housing 13 and the support body 14.
  • the spiral tracks 17 and helical ribs 16 ensure that the heat transfer between the working fluid in the tube 15 and the heat transfer fluid is maximised.
  • bypass inlet apertures 8 are provided in the support body 14.
  • the bypass inlet apertures 8 define the start of the second section of the heat transfer fluid flow path, and allow a portion of the heat transfer fluid to flow though the bypass conduit 7 (not shown in Figure 2), which is provided within the support body 14. The remainder of the heat transfer fluid flows through the second heat exchange section 10.
  • the bypass inlet apertures 8 are preferably between 1 ⁇ 2 to 3 ⁇ 4 of the way up the support body 14, . that is, the length of the heat transfer fluid flow path in the second heat exchange section 10 (the sterilizer section) is preferably between 50% and 100% of the length of the heat transfer fluid flow path in the first heat exchange section 9.
  • the outlet 4 of the heat transfer fluid flow path and the bypass conduit outlet 11 are preferably substantially adjacent.
  • the heat exchange apparatus 100 is provided with a common outlet fitting 18 which encompasses both the bypass conduit outlet 11 and the heat transfer fluid outlet 4.
  • the bypass conduit 7 and heat transfer flow path 1 may merge upstream of a common outlet.
  • the flow of the heat transfer fluid through the second heat exchange section 10 is preferably restricted by a suitable restriction means.
  • the heat transfer fluid outlet 4 preferably has a smaller cross-sectional area than the bypass outlet 11 , so that in use the proportion of the heat transfer fluid which flows through the bypass conduit 7 is larger than that flowing through the second heat exchange section 10.
  • the apparatus 100 is configured such that the ratio of the flow rate through the bypass conduit 7 to flow rate through the second heat exchange section 10 is between 5:1 and 10:1 , more preferably around 7:1. However, the ratio may vary outside this range as necessary to provide an optimum COP for a given application.
  • the temperature of the heat transfer fluid in the second section can be raised to a sufficiently high temperature to ensure that bacterial activity in the heat transfer fluid is reduced, so that the heat transfer fluid is partially or completely sterilised.
  • the temperature of the heat transfer fluid in the second section is raised to over 61 °C, thereby complying with regulations regarding control of Legionella bacteria.
  • the temperature of the heat transfer fluid in the second section is raised to between 65°C and 70°C.
  • the overall temperature of the heat transfer fluid may be dropped to around 55-60°C when the flow through the second heat exchange section 10 is mixed with the flow through the bypass conduit 7. In this way the temperature of the heat transfer fluid immediately downstream of the apparatus is lowered sufficiently to avoid scalding.
  • the higher flow rate of heat transfer fluid through the first heat exchange section 9 ensures that the working fluid is condensed properly and, in some embodiments, subcooled, although in other embodiments, for example as shown in Figure 5, a separate subcooler heat exchanger may be provided.
  • the working fluid in the second heat exchange section 10 remains in a vapour state rather condensing to a liquid state. This increases the volume of vapour in the heat pump system, and can have the effect of reducing the compressor discharge pressure.
  • working fluid in a typical condenser may condense (i.e, reach Saturated Condensing Temperature) around one third (1/3) of the way through the condenser
  • working fluid in the apparatus of the present invention may condense approximately two thirds (2/3) of the way through the apparatus 100.
  • a hot water heating system is generally referenced by arrow 300, and includes the heat transfer apparatus 100 which is connected to and forms part of a suitable heat pump circuit, generally referenced by arrow 400.
  • the apparatus 100 is also in fluid communication with a hot water storage tank 19.
  • the working fluid in the heat pump circuit may be R410A, or C0 2 although other suitable working fluids such as R22, R417A or R407A may be used, as well as others such as will be known to those skilled in the art.
  • the heat pump circuit 400 shown includes a TXV 20 in fluid communication with the working fluid outlet 6, an evaporator 21 and a compressor 22 which supplies the working fluid inlet 5.
  • a TXV 20 in fluid communication with the working fluid outlet 6, an evaporator 21 and a compressor 22 which supplies the working fluid inlet 5.
  • the heat pump circuit may be provided with additional components, including accumulators and the like. Other combinations of heat pump
  • a pump 23 is provided for pumping the heat transfer fluid from the bottom of the tank 19 through the heat exchange apparatus 100.
  • the pump 23 may be provided with a variable speed drive (not shown), and a control means 24, for example a computer or microprocessor based speed controller or similar, may be provided.
  • One or more sensors 25 are provided to measure a property of the heat transfer fluid, or the working fluid, which is indicative of the temperature of the water leaving the second heat exchange section 10.
  • the sensor 25 preferably measures the temperature at or adjacent the outlet 4 of the second heat exchange section 10 directly, as is shown in Figure 4, but in other embodiments the temperature may be calculated indirectly though measurement of the working fluid temperature and/or pressure at the compressor discharge or suction lines, or at the working fluid outlet.
  • control means 24 controls the flow rate of the pump 23 in order to ensure that the heat transfer fluid leaving second heat exchange section 10 is at least 61 °C, more preferably at least 65°C.
  • the control means 24 reduces the flow rate through the pump 23 if the measured variable indicates the temperature is too low, for example if the temperature of the heat transfer fluid leaving the condenser is below around 61 °C. In this way the sterilizing effect on the heat transfer fluid is maintained, overcondensing of the working fluid may be avoided and the Coefficient of Performance (COP) of the system maybe maximised.
  • COP Coefficient of Performance
  • control means may measure the ambient temperature, refrigerant discharge temperature, evaporator temperature, water tank temperature and the temperature of the water at the outlet 4. The control means may then determine the heat available from the heat pump 400 and select a suitable water pump motor speed which will result in the heat transfer fluid in the second heat exchange section being heated to at least 61 °C. Once the temperature in the water tank 19 has reached the desired value, the control means varies the flow rate through the apparatus 100 in order to maintain the temperature in the tank 19.
  • Maintaining the water in the tank 19 at this relatively low temperature minimises thermal losses within the tank.
  • the portion of the water which has travelled through the second heat exchange section 10 has been heated to around 61 °C or 65°C in order to obtain the required sterilizing effect.
  • FIG. 5 shows a hot water heating system, generally referenced by arrow 301 , which is a variation of the hot water heating system of Figure 4.
  • the modified system 301 has a modified heat pump circuit, generally referenced by arrow 401.
  • the heat pump circuit 401 is provided with a working fluid subcooler 28.
  • the subcooler 28 transfers heat from the working fluid between the heat exchange apparatus 100 and the TXV 20 to the working fluid between the evaporator 21 and the compressor 22. This has the effect of raising the pressure of the working fluid entering the compressor 22, thereby reducing the compression ratio, as well as removing excess heat from the working fluid leaving the apparatus 100 and increasing the COP of the system.
  • the subcooler 28 is particularly useful when the hot water temperature is high and the log mean temperature difference is relatively low.
  • the pressure and temperature sensors (not shown) for the expansion means or TXV are positioned downstream of the subcooler 28 and upstream of the compressor 22.
  • system of the present invention may be used with new installations or hot water cylinder refits, and used for other hot water heat
  • the invention increases the Log Mean Temperature Difference (LMTD) between entering heat transfer fluid and the entering working fluid that flow in counterflow to each other.
  • LMTD Log Mean Temperature Difference
  • the upper desuperheater section limits the heat transfer fluid flow to maintain the heat transfer fluid at a higher temperature, in conjunction with the speed controlled water pump sensor.
  • the lower condenser section maintains a higher flow rate to condense the heat transfer fluid and produce a more ideal refrigeration effect to optimise the performance and Coefficient of Performance (COP) at a wider range of extreme conditions than currently available hot water heat pumps.
  • COP Coefficient of Performance

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  • 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)
  • Geometry (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention concerne un appareil d'échange de chaleur (100, 101) pour une pompe à chaleur (400, 401), qui a un chemin (2) d'écoulement de fluide de travail agencé en relation de transfert thermique avec un chemin (1) d'écoulement de fluide de transfert thermique. L'appareil (100) a une première section (9) d'échange de chaleur et une deuxième section (10) d'échange de chaleur, le chemin (1) d'écoulement de fluide de transfert thermique et le chemin (2) d'écoulement de fluide de travail s'étendent à travers les première et deuxième sections (9, 10) d'échange de chaleur. L'appareil (100, 101) comporte en outre un conduit de dérivation (7) avec une entrée de dérivation (8) en communication fluidique avec le chemin (1) d'écoulement de fluide de transfert thermique dans la première section (9) d'échange de chaleur, et pendant l'utilisation, une partie du fluide de transfert thermique qui s'écoule à travers l'appareil (100, 101) s'écoule à travers le conduit de dérivation (7), en contournant ainsi la deuxième section d'échange de chaleur (10). Des procédés et des systèmes pour chauffer de l'eau font également l'objet de l'invention.
PCT/NZ2010/000244 2009-12-09 2010-12-06 Appareil d'échange de chaleur et système de chauffage de fluide Ceased WO2011071393A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NZ58177809 2009-12-09
NZ581778 2009-12-09

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WO2011071393A1 true WO2011071393A1 (fr) 2011-06-16

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2735835A3 (fr) * 2012-11-26 2014-11-26 TI Automotive Engineering Centre (Heidelberg) GmbH Échangeur de chaleur interne pour système de conditionnement d'air

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4730663A (en) * 1986-02-05 1988-03-15 Deutsche Gesellschaft Fur Wiederaufarbeitung Von Kernbrennstoffen Mbh Passive cooling arrangement
DE3823783C1 (en) * 1988-07-14 1989-08-24 Rheinisch-Westfaelisches Elektrizitaetswerk Ag, 4300 Essen, De Heat-pump installation, in particular for heating purposes
US6527046B1 (en) * 1999-06-02 2003-03-04 Akg Of America, Inc. Heat exchanger, particularly oil cooler
US20070068665A1 (en) * 2003-08-26 2007-03-29 Daimler Chrysler Ag Heat exchanger comprising an integrated supply and discharge
US20070289581A1 (en) * 2004-09-28 2007-12-20 T. Rad Co., Ltd. Egr Cooler
US20080008710A1 (en) * 2003-09-04 2008-01-10 Hiroyuki Aburatani Therapeutic Agent And Diagnostic Agent For Cholangiocarcinoma
US7412945B2 (en) * 2005-12-01 2008-08-19 Alstom Technology Ltd. Waste heat boiler

Patent Citations (7)

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Publication number Priority date Publication date Assignee Title
US4730663A (en) * 1986-02-05 1988-03-15 Deutsche Gesellschaft Fur Wiederaufarbeitung Von Kernbrennstoffen Mbh Passive cooling arrangement
DE3823783C1 (en) * 1988-07-14 1989-08-24 Rheinisch-Westfaelisches Elektrizitaetswerk Ag, 4300 Essen, De Heat-pump installation, in particular for heating purposes
US6527046B1 (en) * 1999-06-02 2003-03-04 Akg Of America, Inc. Heat exchanger, particularly oil cooler
US20070068665A1 (en) * 2003-08-26 2007-03-29 Daimler Chrysler Ag Heat exchanger comprising an integrated supply and discharge
US20080008710A1 (en) * 2003-09-04 2008-01-10 Hiroyuki Aburatani Therapeutic Agent And Diagnostic Agent For Cholangiocarcinoma
US20070289581A1 (en) * 2004-09-28 2007-12-20 T. Rad Co., Ltd. Egr Cooler
US7412945B2 (en) * 2005-12-01 2008-08-19 Alstom Technology Ltd. Waste heat boiler

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2735835A3 (fr) * 2012-11-26 2014-11-26 TI Automotive Engineering Centre (Heidelberg) GmbH Échangeur de chaleur interne pour système de conditionnement d'air

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