WO2001090663A1 - Systeme de chauffage et refroidissement super efficace multi-usage - Google Patents

Systeme de chauffage et refroidissement super efficace multi-usage Download PDF

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Publication number
WO2001090663A1
WO2001090663A1 PCT/AU2001/000623 AU0100623W WO0190663A1 WO 2001090663 A1 WO2001090663 A1 WO 2001090663A1 AU 0100623 W AU0100623 W AU 0100623W WO 0190663 A1 WO0190663 A1 WO 0190663A1
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WO
WIPO (PCT)
Prior art keywords
heat
cycle
phase change
vapour
heating
Prior art date
Application number
PCT/AU2001/000623
Other languages
English (en)
Inventor
T. Trinh Danh
Terry Howard Solomon
Original Assignee
Thermal Energy Accumulator Products Pty 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
Priority claimed from AUPQ7821A external-priority patent/AUPQ782100A0/en
Priority claimed from AUPQ8304A external-priority patent/AUPQ830400A0/en
Application filed by Thermal Energy Accumulator Products Pty Ltd filed Critical Thermal Energy Accumulator Products Pty Ltd
Priority to AU61894/01A priority Critical patent/AU6189401A/en
Publication of WO2001090663A1 publication Critical patent/WO2001090663A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/02—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • 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
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present invention relates generally to a Multiple-Use Super-Efficient heating and cooling system and relates particularly, though not exclusively, to a Multiple-Use Super-Efficient heating and cooling system utilising a vapour-compression cycle or a vapour-absorption cycle which exchanges heat with a phase change substance having a relatively high latent heat of fusion for improved heating and cooling production.
  • MUSE Multiple-Use Super-Efficient
  • a MUSE heating and cooling system comprising a continuous vapour-compression cycle, adapted to carry a refrigerant working fluid or other working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator, which exchanges heat with a phase change substance having a relatively high latent heat of fusion.
  • vapour-compression fluid includes but not limited to hydrochlorofluorocarbons (HCFCs) R416A, R22, hydrofluorocarbons (HFCs) Rl34a, ammonia, hydrocarbons (HCs) n-butane, isobutane, propane gas, or other blended gas.
  • HCFCs hydrochlorofluorocarbons
  • HFCs hydrofluorocarbons
  • ammonia ammonia
  • hydrocarbons (HCs) n-butane isobutane
  • propane gas or other blended gas.
  • a MUSE heating and cooling system comprising a method of storing heat energy utilising one or more phase change substances with a relatively high latent heat of fusion whereby, in use, heat from a condenser of the vapour-compression cycle can be absorbed and stored by said phase change substance so that at least a portion of that phase change substance fuses and thereafter when said portion of that phase change substance solidifies and releases latent heat.
  • phase change substances are hydrate salts, having a relatively high latent heat of fusion.
  • the one or more hydrate salts has a melting point of between 25°C to 150°C.
  • the one or more hydrate salts has a latent heat of fusion of greater than 100 kJ/kg.
  • the hydrate salt comprises a substance of sodium acetate and water.
  • a MUSE heating and cooling system for producing heating comprising: a continuous vapour-compression heat pump cycle adapted to carry a refrigerant working fluid or other working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; and a continuous fluid path adapted to carry another fluid, said path including one or more phase change substances having a relatively high latent heat of fusion and said path including one or more heat exchangers of the vapour-compression cycle having heat transfer means in heat conductive communication with each other whereby, in use, heat from a condenser of said cycle can be absorbed by one or more said phase change substances so that at least a portion of that phase change substance fuses and thereafter when said portion of that phase change substance solidifies and releases latent heat for heating production.
  • the fluid used as a heat transfer medium between the condenser of the vapour-compression cycle and phase change substance includes but not limited to water or heating oil. More typically, the fluid path further includes a pump being designed to recirculate the working fluid around said path.
  • an ambient air is used as a heat source at the evaporator of the vapour-compression heat pump cycle.
  • a MUSE heating and cooling system for producing cooling comprising: a continuous vapour-compression refrigeration cycle adapted to carry a refrigerant working fluid or other working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; and a continuous fluid path adapted to carry another fluid, said path including one or more phase change substances having a relatively high latent heat of fusion and said path including one or more heat exchangers of the vapour-compression cycle having heat transfer means in heat conductive communication with each other whereby, in use, heat removed from one or more said phase change substances by the evaporator of said cycle thus creating a refrigerating effect so that at least a portion of that phase change substance solidifies and thereafter when said portion of that phase change substance liquifies and releases latent heat of refrigerating effect for space cooling or cooling process production.
  • the one or more phase change substances has a melting point of between -60°C to 25°C.
  • the one or more phase change substance has a latent heat of fusion of greater than 100 kJ/kg.
  • the phase change substance comprises a substance of sodium chloride and water.
  • an ambient air is used as a heat sink at the condenser of the vapour-compression refrigeration cycle.
  • a MUSE heating and cooling system for producing heating and cooling comprising the steps of: a continuous vapour-compression heat pump cycle adapted to carry a refrigerant working fluid or other working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; absorbing heat, from the condenser of the vapour- compression cycle, by one or more phase change substances having a relatively high latent heat of fusion included in heat transfer means wherein at least a portion of that said one or more phase change substances fuses and thereafter when said portion of that phase change substance solidifies and releases latent heat for heating production and removing heat, by the evaporator of the vapour- compression cycle thus creating a refrigerating effect, from one or more phase change substances having a relatively high latent heat of fusion included in heat transfer means wherein at least a portion of that said one or more phase change substances solidifies and thereafter when said portion of that phase change substance liquifies
  • phase change substances with low and high melting temperatures are used at the evaporator and condenser of the vapour-compression cycle, respectively.
  • a MUSE heating and cooling system for producing heating or cooling comprising the steps of: a continuous vapour-compression heat pump or refrigeration cycle referred to as the reverse cycle adapted to carry a refrigerant working fluid or other working fluid, said cycle including at least a compressor located upstream of a condenser which is positioned upstream of an evaporator; absorbing heat, from the condenser of the vapour- compression cycle, by one or more phase change substances having a relatively high latent heat of fusion included in heat transfer means wherein at least a portion of that said one or more phase change substances fuses and thereafter when said portion of that phase change substance solidifies and releases latent heat for heating production, and extracting heat, by the evaporator of the compression cycle, from an ambient air; or removing heat, by the evaporator of the vapour- compression cycle thus creating a refrigerating effect, from one or more phase change substances having a relatively high latent heat of fusion included in heat transfer means wherein at least
  • vapour-compression cycle is a reverse cycle air conditioning unit.
  • an electronic control system is used to operate, depending on the external load requirements, the different operating modes of the vapour-compression cycle including heat pump or refrigeration cycle referred to as the reverse cycle, or heat pump-refrigeration cycle.
  • the external heating load requirements can be hot water for showers, space heating, and other heating processes. More generally, the external cooling load requirements can be space cooling, and other cooling processes .
  • a MUSE heating and cooling system for producing cooling comprising: a continuous vapour-absorption refrigeration cycle adapted to carry a refrigerant-absorbent fluid or other working fluid, said cycle including at least a heat generator located upstream of a condenser which is positioned upstream of an evaporator-absorber; and a continuous fluid path adapted to carry another fluid, said path including one or more phase change substances having a relatively high latent heat of fusion and said path including one or more heat generators of the vapour-absorption cycle having heat transfer means in fluid communication with each other whereby, in use, heat from a heat source can be absorbed by one or more said phase change substances so that at least a portion of that phase change substance fuses and thereafter when said portion of that phase change substance solidifies and releases latent heat the refrigerant-absorbent
  • vapour-absorption fluid includes but not limited to Lithium Bromide-water or ammonia-water.
  • the continuous vapour-absorption cycle fluid path further includes a pump being designed to recirculate the working fluid around said path.
  • the fluid used as a heat transfer medium between the heat source, phase change substance, and heat generator of vapour-absorption cycle includes but not limited to water or heating oil. More generally, the fluid path further includes a pump being designed to recirculate the working fluid around said path.
  • the vapour-absorption cycle is a standard vapour-absorption cycle unit.
  • the external cooling load requirements can be space cooling, and other cooling processes.
  • the external heat source input to operate the vapour-absorption cycle can be solar, diesel water radiator and exhaust waste heat, gas turbine exhaust, furnace or other low to medium temperature sources of waste heat; particularly where the heat source is intermittent and not continuous.
  • MUSE heating and cooling system can be used in static or mobile from small domestic to large industrial uses.
  • FIG. 1 is a schematic of a MUSE heating and cooling system together with a vapour-compression heat pump system
  • FIG. 2 is a schematic of another MUSE heating and cooling system together with a vapour-compression refrigeration system
  • FIG 3 is a schematic of a further MUSE heating and cooling system in conjunction with a vapour-compression heat pump-refrigeration system
  • Figure 4 is a schematic of a further MUSE heating and cooling system together with a vapour-compression reverse cycle system
  • Figure 5 is a schematic of a MUSE heating and cooling system together with a vapour-absorption system.
  • FIG. 1 to 4 there are various embodiments of a MUSE heating and cooling system 10 together with a vapour-compression system 20.
  • a MUSE heating and cooling system 10 together with a vapour-compression system 20.
  • components and assemblies of Figures 2 to 4 which generally correspond to components and assemblies of Figure 1 have been designated with the Figure numeral prefixing like components and assemblies.
  • the MUSE heating and cooling system of Figures 2, 3 and 4 have been designated as 210, 310 and 410, respectively.
  • FIG. 5 there are various embodiments of a MUSE heating and cooling system 510 together with a vapour-absorption system 520.
  • the MUSE heating and cooling system 10 and vapour- compression cycle 20 of Figure 1 include a continuous fluid path 44 and a continuous vapour-compression cycle 24, respectively.
  • both the fluid path 44 and the vapour-compression cycle 24 are adapted to carry water and refrigerant fluid, respectively.
  • the continuous fluid path or MUSE heating and cooling system 44 of this embodiment includes one or more external heating loads 40, latent heat accumulator 42 containing one or more phase change substances, circulating pump 46, and one or more heat exchangers 22 of the vapour- compression cycle being in heat transfer means adapted to be in heat conductive communication with each other.
  • the latent heat accumulator 42 includes an accumulator vessel being configured to contain one or more phase change substances in an encapsulated form (not shown) .
  • the phase change substances are hydrate salts having a relatively high latent heat of fusion.
  • the hydrate salt comprises sodium acetate and water having a melting point of approximately 58°C and a latent heat of fusion of approximately 226 kJ/kg.
  • the encapsulation of the phase change substance can be done for example, by encapsulating hydrate salt in plastic spherical balls, plastic or metal panel or by coating of the phase change substance with one or more sealing layers constructed of a phenolic epoxy resin material. It will be appreciated that the invention is not limited to the hydrate salt comprising acetate and water but rather extends to practically any phase change substance having a relatively high latent heat of fusion.
  • the latent heat accumulator 42 is a shell-tube heat exchanger construction having one or more phase change substances in an encapsulated form being placed in a solution such as water which is being located on the shell-side and having a heat transfer fluid 44 such as water being located on the tube-side.
  • the fluid path 44 can be water, or heating oil which is suitable for handling temperature in the range from 25°C to 150°C.
  • the latent heat accumulator 42 may be of a doubled-walls of shell-tube heat exchanger preferably with the heat transfer fluid 44 such as water flowing through one of the walls.
  • the latent heat accumulator 42 is in heat conductive communication with an external heating load 40 which can be hot water for showers, space heating, or other heating processes.
  • the condenser 22 of the vapour-compression cycle is a conventional plate type or tube-tube heat exchanger.
  • the heat transfer fluid 44 such as water flows trough the tube of the heat exchanger.
  • the vapour-compression cycle 20 of this example is a standard vapour-compression heat pump cycle.
  • the cycle 20 includes a condenser 22, a compressor 30, an evaporator 28, and an expansion valve 26 connected in a conventional manner.
  • the condenser 22 is typically a plate exchanger whereas the evaporator 28 is generally a fin-tube heat exchanger.
  • the compressor 30 may be driven by an electrical motor 32.
  • Figure 1 involves the following general steps: (i) A gas compression process is performed by the compressor 30 which can be driven by an electrical motor 32.
  • the compressor 30 produces heat and raises gas temperature as the refrigerant vapour is passed through the compressor 30.
  • electrical input is required to drive the motor 32;
  • the MUSE heating and cooling system 10 of Figure 1 is in heat conductive communication with one or more external heating loads 40, latent heat accumulator 42 containing one or more phase change substances, and one or more heat exchangers 22 of the vapour-compression cycle 20 being in heat transfer means adapted to be in heat conductive communication with each other.
  • a pump 46 is generally provided to recirculate the heat transfer fluid 44.
  • COP coefficient of performance
  • the COP of the standard vapour-compression refrigeration can be from two to four. That is, a COP of three means that the system efficiency is 300% whereby the system can produce a heating or cooling output three times that of the power input. This will hereinafter be generally referred to as the COP effect.
  • a significant feature of the present invention relates to utilisation of the latent heat accumulator 42 to significantly increase the COP from two to four to three to eight in the MUSE heating and cooling system such as 10. It will be appreciated that by coupling the MUSE heating and cooling system 10 to the standard vapour- compression cycle 20 that the overall system performance is enhanced by maximising the COP effect. In particular, the COP effect is to return heat to the MUSE heating and cooling system 10 which thereby at least reduces its need for external electrical power.
  • the latent heat accumulator 42 is specifically designed to store heat energy in the form of heating or cooling so that the MUSE heating and cooling system such as 10 can be operated during the period for optimum performance each day.
  • the heat pump cycle 20 of Figure 1 can be operated during a period, generally during day-time, when the ambient air temperatures are such that the COP effect can be maximised in the MUSE heating and cooling system 10.
  • a further significant feature of the present invention relates to the utilisation of the latent heat accumulator 42 in the MUSE heating and cooling system 10. If the off- peak electricity or other cheap energy is available the latent heat accumulator 42 is designed so that the MUSE heating and cooling system 10 can be operated during the off-peak period or the time the other cheap energy is available for minimising running costs thus producing great savings in electricity power consumption.
  • a yet further significant feature of the present invention relates to the use of the electronic control system 60 in the MUSE heating and cooling system 10 of Figure 1.
  • the electronic control system 60 is used to incorporate including the COP effect, ambient air temperature, and off-peak power or other cheap energy if available for maximising the system overall performance.
  • the electronic control system 60 is also used to operate, depending on the external load requirements 40, the different operating modes of the vapour-compression cycle 20.
  • the heat pump cycle 20 of Figure 1 is used in this example.
  • the latent heat accumulator 42 in the MUSE heating and cooling system 10 is critical insofar as it provides a method of storing heat from the condenser 22 of the vapour-compression cycle 20 by heat transfer means.
  • the MUSE heating and cooling system 210 and vapour- compression cycle 220 of Figure 2 is similar to that of Figure 1 except the vapour-compression cycle 220 operates in the refrigeration cycle.
  • the refrigeration cycle 220 of Figure 2 can be operated during a period, generally during nighttime, when the ambient air temperatures are such that the COP effect can be maximised in the MUSE heating and cooling system 210.
  • the MUSE heating and cooling system 210 and vapour- compression refrigeration system 220 of Figure 2 include a continuous fluid path 264 and a continuous vapour- compression cycle 224, respectively.
  • both the fluid path 264 and the vapour-compression cycle 224 are adapted to carry water and refrigerant fluid, respectively.
  • the continuous fluid path or MUSE heating and cooling system 264 of this embodiment includes one or more external cooling loads 260, latent heat accumulator 262 containing one or more phase change substances, circulating pump 266, and one or more heat exchangers 228 of the vapour-compression cycle being in heat transfer means adapted to be in heat conductive communication with each other.
  • the latent heat accumulator 262 is a shell-tube heat exchanger construction, having one or more phase change substances.
  • the phase change substances are hydrate salts having a relatively high latent heat of fusion.
  • the hydrate salt comprises sodium chloride and water having a freezing point of approximately -21°C and a latent heat of fusion of approximately 222 kJ/kg.
  • the latent heat accumulator 262 is a shell-tube heat exchanger construction with the transfer fluid 264 such as water flowing through the tube-side.
  • the latent heat accumulator 262 is in heat conductive communication with an external cooling load 260 which can be chilled water for providing space cooling, or other cooling processes.
  • the fluid path 264 can be water, or glycol which is suitable for handling temperature in the range from -60°C to 25°C.
  • the vapour-compression refrigeration cycle 220 of Figure 2 is similar to that of Figure 1 except: (i) The discharged refrigerant vapour from the compressor 230 is condensed to liquid as the gas is passed through the condenser 222. Heat is rejected from the condenser 222 to an ambient air 250 used in this example; and (ii) The liquid refrigerant vapourises, removing heat from a latent heat accumulator 262 containing one or more phase change substances, thus creating the refrigeration effect in the evaporator 228. Thereafter the latent heat accumulator 262 releases its latent heat to an external cooling load 260 via a heat exchanger such as a fan-coil unit can be used in this example (not shown) for space cooling.
  • a heat exchanger such as a fan-coil unit can be used in this example (not shown) for space cooling.
  • the MUSE heating and cooling system 310 and vapour- compression cycle 320 of Figure 3 is similar to that of Figure 1 and Figure 2 except: (i) In operation the MUSE heating and cooling system 310 utilises both heating and cooling production in the condenser 322 and evaporator 328, respectively, from the operating cycle 320; (ii) The discharged refrigerant vapour from the compressor 330 is condensed to liquid as the gas is passed through the condenser 322. Heat is rejected from the condenser 322 which can be absorbed by a latent heat accumulator 322 containing one or more phase change substances.
  • the latent heat accumulator 322 releases its latent heat to an external heating load 340 via a heat exchanger such as a coil heat exchanger can be used in this example for water heating.
  • a heat exchanger such as a coil heat exchanger can be used in this example for water heating.
  • the condenser 322 and the latent heat accumulator 322 is constructed in a common shell heat exchanger, containing one or more phase change substances with one or more coil heat exchangers within the said common shell, in heat transfer means adapted to be in direct heat conductive communication with each other; and
  • a yet another significant feature of the present invention relates to utilisation of the latent heat accumulator 322 and 328 for heating and cooling production, respectively. It will be appreciated that by coupling the MUSE heating and cooling system 10 to the manner as shown in Figure 3 that the overall system performance is enhanced by maximising heat utilisation in both heating and cooling.
  • the MUSE heating and cooling system 410 and vapour- compression cycle 420 of Figure 4 is similar to that of Figure 1, Figure -2 and Figure 3 except the vapour- compression cycle 420 operates in the heat pump or refrigeration cycle as referred to the reverse cycle.
  • the reverse cycle 420 of Figure 4 can be operated during a period, depending on the mode of operation of the cycle, when the ambient air temperatures are such that the COP effect can be maximised in the MUSE heating and cooling system 410.
  • vapour-compression reverse cycle 420 of Figure 4 is similar to that of Figure 1, Figure 2 and Figure 3 except : (i) In operation the reverse cycle 420 for the heat pump (heating) or refrigeration (cooling) of Figure
  • the latent heat accumulator 422 releases its latent heat to an external cooling load 440 via a heat exchanger for water cooling, and the vapour refrigerant condenses, rejecting heat to an ambient air 450 in the condenser 428.
  • the latent heat accumulator 422 releases its latent heat to an external load 440 for heating or cooling depending on the mode of operation of the reverse cycle 420 via a heat exchanger.
  • the latent heat accumulator 422 is arranged, in direct heat conductive communication with the vapour-compression cycle 420.
  • the MUSE heating and cooling system 510 and vapour- absorption cycle 520 of Figure 5 is similar to that of
  • the MUSE heating and cooling system 510 and vapour- absorption cycle 520 of Figure 5 include a continuous fluid path 544 and a continuous vapour-absorption refrigeration cycle 524, respectively.
  • both the fluid path 544 and the vapour-absorption refrigeration cycle 524 are adapted to carry water and refrigerant-absorbent fluid, respectively.
  • the continuous fluid path or MUSE heating and cooling system 544 of this embodiment includes one or more sources of heat 532, latent heat accumulator 542 containing one or more phase change substances, and one or more heat generators 530 of the vapour-absorption cycle being in heat transfer means in fluid communication with each other.
  • the latent heat accumulator 542 is a shell-tube heat exchanger construction having one or more phase change substances being placed in a solution such as water which is being located on the shell-side and having a heat transfer fluid 544 such as water being located on the tube-side.
  • the latent heat accumulator 542 is in heat conductive communication with a heat source 532 which can be solar, or other waste heat.
  • the vapour-absorption cycle 520 of this example is a standard vapour-absorption refrigeration cycle.
  • the cycle 520 includes an evaporator-absorber 528, a heat generator 530, a condenser 522, an absorbent pump 526, and a metering valve and a refrigerant pump (not shown) connected together in a conventional manner.
  • the evaporator-absorber 528 and heat generator 530 are typically a shell-tube heat exchanger whereas the condenser 522 is generally a plate heat exchanger.
  • the vapour-absorption cycle 520 of Figure 5 is similar to that of the vapour-compression cycle 220 of Figure 2 except: (i) The electric compressor 230 of Figure 2 is to be replaced with a heat source 532 of Figure 5; (ii) The vapour-compression cycle 220 of Figure 2 is to be replaced with a heat generator 530 and condenser 522 of the vapour-absorption cycle 520 of Figure 5.
  • the COP of the standard vapour-absorption refrigeration can be from 0.5 to 1.2.
  • Another significant feature of the present invention relates to the utilisation of the latent heat accumulator 542 in conjunction with the use of the standard vapour- absorption cycle having the COP effect in the MUSE heating and cooling system such as 510.
  • the invention has at least the following advantages: (i) the MUSE heating and cooling system and vapour- compression cycle when combined the overall system performance is enhanced by maximising the COP effect; (ii) the MUSE heating and cooling system is energy efficient and may produce carbon credits or similar advantages; (iii) the MUSE heating and cooling system, take full advantage of off-peak electricity, has low operational costs compared to existing systems; (iv) the apparatus and method maximise heat energy utilisation in producing heating and cooling; and (v) the MUSE heating and cooling system and vapour- absorption refrigeration cycle are environmentally friendly; and (vi) the apparatus and method maximise heat energy input utilisation and waste heat recovery in producing air conditioning or cooling.
  • vapour- compression or vapour-absorption cycle or system is a standard system although this is preferable.

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  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

La présente invention concerne, de manière générale, un système de chauffage et refroidissement super efficace multi-usage (10) associé à un système de compression de vapeur (20), chacun comprenant respectivement un parcours de fluide continu (44) et un cycle de compression de vapeur continu (24). Dans cet exemple, le parcours de fluide (44) et le cycle de compression de vapeur (24) sont conçus pour transporter, respectivement, de l'eau et un fluide réfrigérant. Le parcours de fluide continu ou le système de chauffage et refroidissement super efficace multi-usage (44) de cet exemple, comprennent au moins une charge de chauffage externe (40), un accumulateur de chaleur latente (42) renfermant une ou plusieurs substances à changement de phase, une pompe de circulation (46), un ou plusieurs échangeurs de chaleur (22) du cycle de compression de vapeur (20) étant placés dans des moyens de transfert de chaleur conçus pour être en communication conductrice de chaleur les uns avec les autres. Le cycle de compression de vapeur (20) de cet exemple est un cycle normalisé de pompe à chaleur de compression de vapeur. Le cycle (20) comprend un condenseur (22), un compresseur (30), un évaporateur (28) et un détendeur (26) reliés d'une manière classique. Le compresseur (30) peut être entraîné par un moteur électrique (32). Le cycle de compression de vapeur (20) d'un autre exemple est un cycle normalisé de réfrigération d'absorption de vapeur.
PCT/AU2001/000623 2000-05-26 2001-05-25 Systeme de chauffage et refroidissement super efficace multi-usage WO2001090663A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU61894/01A AU6189401A (en) 2000-05-26 2001-05-25 A multiple-use super-efficient heating and cooling system

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AUPQ7821A AUPQ782100A0 (en) 2000-05-26 2000-05-26 Sustainable air conditioning and coolroom system
AUPQ7821 2000-05-26
AUPQ8304A AUPQ830400A0 (en) 2000-06-23 2000-06-23 A multiple-use super-efficient heating and cooling system
AUPQ8304 2000-06-23

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1666814A1 (fr) * 2004-11-26 2006-06-07 LG Electronics Inc. Conditionneur d'air
EP1666815A1 (fr) * 2004-11-26 2006-06-07 LG Electronics Inc. Conditionneur d'air
WO2009063055A1 (fr) * 2007-11-15 2009-05-22 Shell Internationale Research Maatschappij B.V. Procédé et appareil permettant de refroidir un flux de traitement
WO2010034991A1 (fr) * 2008-09-23 2010-04-01 Solar Polar Limited Appareil de refroidissement
CN101435629B (zh) * 2008-12-12 2010-06-09 广东美的电器股份有限公司 一种螺杆式冷源热水机组
WO2010147560A1 (fr) * 2009-06-18 2010-12-23 Central Provident Fund Board Système de climatisation et procédé pour son utilisation
WO2012071624A1 (fr) * 2010-12-01 2012-06-07 Strathbrook Industrial Services Pty Limited Système frigorifique
WO2014065938A1 (fr) * 2012-10-25 2014-05-01 Carrier Corporation Système de réfrigération ayant une matière à changement de phase
US9032755B2 (en) 2008-09-23 2015-05-19 Solar Polar Limited Solar-absorption hybrid modular cooling apparatus
CN104697236A (zh) * 2015-02-11 2015-06-10 南京航空航天大学 基于蒸发制冷的机载发热元件的冷却系统及方法
US10753661B2 (en) 2014-09-26 2020-08-25 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
US10866002B2 (en) 2016-11-09 2020-12-15 Climate Master, Inc. Hybrid heat pump with improved dehumidification
US10871314B2 (en) 2016-07-08 2020-12-22 Climate Master, Inc. Heat pump and water heater
US10935260B2 (en) 2017-12-12 2021-03-02 Climate Master, Inc. Heat pump with dehumidification
US11506430B2 (en) 2019-07-15 2022-11-22 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater

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Cited By (24)

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EP1666814A1 (fr) * 2004-11-26 2006-06-07 LG Electronics Inc. Conditionneur d'air
EP1666815A1 (fr) * 2004-11-26 2006-06-07 LG Electronics Inc. Conditionneur d'air
CN100344916C (zh) * 2004-11-26 2007-10-24 Lg电子株式会社 空调系统
CN100351588C (zh) * 2004-11-26 2007-11-28 Lg电子株式会社 空调系统
US7343756B2 (en) 2004-11-26 2008-03-18 Lg Electronics Inc. Air conditioning system
WO2009063055A1 (fr) * 2007-11-15 2009-05-22 Shell Internationale Research Maatschappij B.V. Procédé et appareil permettant de refroidir un flux de traitement
WO2010034991A1 (fr) * 2008-09-23 2010-04-01 Solar Polar Limited Appareil de refroidissement
US9032755B2 (en) 2008-09-23 2015-05-19 Solar Polar Limited Solar-absorption hybrid modular cooling apparatus
CN101435629B (zh) * 2008-12-12 2010-06-09 广东美的电器股份有限公司 一种螺杆式冷源热水机组
WO2010147560A1 (fr) * 2009-06-18 2010-12-23 Central Provident Fund Board Système de climatisation et procédé pour son utilisation
WO2012071624A1 (fr) * 2010-12-01 2012-06-07 Strathbrook Industrial Services Pty Limited Système frigorifique
WO2014065938A1 (fr) * 2012-10-25 2014-05-01 Carrier Corporation Système de réfrigération ayant une matière à changement de phase
US11480372B2 (en) 2014-09-26 2022-10-25 Waterfurnace International Inc. Air conditioning system with vapor injection compressor
US10753661B2 (en) 2014-09-26 2020-08-25 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
US11927377B2 (en) 2014-09-26 2024-03-12 Waterfurnace International, Inc. Air conditioning system with vapor injection compressor
CN104697236A (zh) * 2015-02-11 2015-06-10 南京航空航天大学 基于蒸发制冷的机载发热元件的冷却系统及方法
US11448430B2 (en) 2016-07-08 2022-09-20 Climate Master, Inc. Heat pump and water heater
US10871314B2 (en) 2016-07-08 2020-12-22 Climate Master, Inc. Heat pump and water heater
US11435095B2 (en) 2016-11-09 2022-09-06 Climate Master, Inc. Hybrid heat pump with improved dehumidification
US10866002B2 (en) 2016-11-09 2020-12-15 Climate Master, Inc. Hybrid heat pump with improved dehumidification
US10935260B2 (en) 2017-12-12 2021-03-02 Climate Master, Inc. Heat pump with dehumidification
US11592215B2 (en) 2018-08-29 2023-02-28 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
US11953239B2 (en) 2018-08-29 2024-04-09 Waterfurnace International, Inc. Integrated demand water heating using a capacity modulated heat pump with desuperheater
US11506430B2 (en) 2019-07-15 2022-11-22 Climate Master, Inc. Air conditioning system with capacity control and controlled hot water generation

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