US20060218948A1 - Cooling and heating system - Google Patents

Cooling and heating system Download PDF

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Publication number
US20060218948A1
US20060218948A1 US11/392,772 US39277206A US2006218948A1 US 20060218948 A1 US20060218948 A1 US 20060218948A1 US 39277206 A US39277206 A US 39277206A US 2006218948 A1 US2006218948 A1 US 2006218948A1
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Prior art keywords
refrigerant
heat exchanger
indoor
cooling
tube
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US11/392,772
Inventor
Masahisa Otake
Ichiro Kamimura
Hiroshi Mukaiyama
Koji Sato
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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Assigned to SANYO ELECTRIC CO., LTD. reassignment SANYO ELECTRIC CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAMIMURA, ICHIRO, MUKAIYAMA, HIROSHI, OTAKE, MASAHISA, SATO, KOJI
Publication of US20060218948A1 publication Critical patent/US20060218948A1/en
Abandoned legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00Compression machines, plants or systems, with reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00Gas cycle refrigeration machines
    • F25B2309/06Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02791Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-off valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031Sensor arrangements
    • F25B2313/0314Temperature sensors near the indoor heat exchanger
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031Sensor arrangements
    • F25B2313/0315Temperature sensors near the outdoor heat exchanger
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00Details of evaporators; Details of condensers
    • F25B2339/04Details of condensers
    • F25B2339/047Water-cooled condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00Problems to be solved
    • F25B2500/19Calculation of parameters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/02Compressor control
    • F25B2600/025Compressor control by controlling speed
    • F25B2600/0253Compressor control by controlling speed with variable speed
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/17Control issues by controlling the pressure of the condenser
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19Pressures
    • F25B2700/193Pressures of the compressor
    • F25B2700/1931Discharge pressures
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2115Temperatures of a compressor or the drive means therefor
    • F25B2700/21152Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2117Temperatures of an evaporator
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a cooling and heating system, more particularly to a cooling and heating system which uses a refrigerant in a supercritical state and which can control cooling and heating capacity so as to maximize a coefficient of performance.
  • a cooling and heating system described in Japanese Patent Application Laid-Open No. 2004-226018 is known as a cooling and heating system in which a carbon dioxide refrigerant is used in a supercritical state.
  • the system has an outdoor unit and a plurality of indoor units, the plurality of indoor units can be operated at the same time in a cooling operation or a heating operation, and the cooling operation and the heating operation can be performed in a mixed manner.
  • the cooling operation refers to an operation to be performed in a case where a set temperature of the indoor unit is lower than an indoor temperature
  • the heating operation refers to an operation to be performed in a case where the set temperature of the indoor unit is higher than the indoor temperature.
  • an evaporation temperature or an evaporation pressure
  • a condensation temperature or a condensation pressure
  • Capacities of a heat exchanger in the indoor unit and a compressor are controlled so that a measured value of the temperature comes close to a target value (a coefficient of performance is maximized).
  • the capacity control of the heat exchanger in the outdoor unit indicates that: a plurality of heat exchangers having different sizes are connected depending on a heat balance between a cooling load and a heating load on an indoor side, the heat exchangers are provided with change valves, respectively, and the number of the heat exchangers to be operated is changed; an amount of the refrigerant to be circulated in each heat exchanger is adjusted; or a rotational speed of a blower disposed in each heat exchanger is adjusted to control the capacity so that the temperature reaches the targeted evaporation or condensation temperature.
  • An object of the present invention is to provide a cooling and heating system in which cooling and heating capacity can be controlled so as to maximize a coefficient of performance and in which a refrigerant is used in a supercritical state.
  • a cooling and heating system including: an outdoor unit including a compressor and an outdoor heat exchanger; and a plurality of indoor units including indoor heat exchangers and connected to one another by a pipe between the units, one end of the outdoor heat exchanger being selectively connected to a refrigerant discharge tube and a refrigerant suction tube of the compressor, the pipe between the units including: a high pressure tube connected to the refrigerant discharge tube; a low pressure tube connected to the refrigerant suction tube; and an intermediate pressure tube connected to the other end of the outdoor heat exchanger, one end of the indoor heat exchanger of each indoor unit being selectively connected to the high pressure tube and the low pressure tube, the other end of the indoor heat exchanger being connected to the intermediate pressure tube, the plurality of indoor units being simultaneously allowed to perform a cooling operation or a heating operation or the plurality of indoor units being allowed to perform a cooling operation and a heating operation simultaneously in
  • a cooling and heating system including: an outdoor unit including a compressor and an outdoor heat exchanger; and a plurality of indoor units including indoor heat exchangers and connected to one another by a pipe between the units, one end of the outdoor heat exchanger being selectively connected to a refrigerant discharge tube and a refrigerant suction tube of the compressor, the pipe between the units including: a high pressure tube connected to the refrigerant discharge tube; a low pressure tube connected to the refrigerant suction tube; and an intermediate pressure tube connected to the other end of the outdoor heat exchanger, one end of the indoor heat exchanger of each indoor unit being selectively connected to the high pressure tube and the low pressure tube, the other end of the indoor heat exchanger being connected to the intermediate pressure tube, the plurality of indoor units being simultaneously allowed to perform a cooling operation or a heating operation or the plurality of indoor units being allowed to perform a cooling operation and a heating operation simultaneously in a mixed manner, the cooling and heating system comprising: discharge
  • the high side pressure of the refrigeration cycle is above the critical pressure of the refrigerant during the operation of the cooling and heating system.
  • carbon dioxide is used as the refrigerant.
  • cooling and heating capacity can be controlled so as to maximize a coefficient of performance.
  • FIG. 1 is a schematic diagram showing a cooling and heating system of the present invention
  • FIG. 2 is a P-h diagram showing a refrigeration cycle of the cooling and heating system in the present invention
  • FIG. 3 is a control flowchart for determining an operation mode of an outdoor heat exchanger in the cooling and heating system of the present invention
  • FIG. 4 is a control flowchart of thermal load balance control in Embodiment 1 of the present invention.
  • FIG. 5 is a schematic diagram showing the cooling and heating system in Embodiment 1 of the present invention.
  • FIG. 6 is a control map diagram at a time when the outdoor heat exchanger is an evaporator in Embodiment 1 of the present invention.
  • FIG. 7 is a control map diagram at a time when the outdoor heat exchanger is a gas cooler in Embodiment 1 of the present invention.
  • FIG. 8 is a control flowchart of thermal load balance control in Embodiment 2 of the present invention.
  • FIG. 9 is a schematic diagram showing the cooling and heating system in Embodiment 2 of the present invention.
  • FIG. 10 is a control map diagram at a time when the outdoor heat exchanger is an evaporator in Embodiment 2 of the present invention.
  • FIG. 11 is a control map diagram at a time when the outdoor heat exchanger is a gas cooler in Embodiment 2 of the present invention.
  • FIG. 1 is a schematic diagram of a cooling and heating system of the present invention.
  • This cooling and heating system 30 includes: an out door unit 1 including outdoor heat exchangers 3 a , 3 b and outdoor expansion valves 27 a , 27 b ; an indoor unit 5 a including an indoor heat exchanger 6 a and an indoor expansion valve 18 a ; an indoor unit 5 b including an indoor heat exchanger 6 b and an indoor expansion valve 18 b ; and a hot water unit 50 including a gas cooler 41 , a hot water storage tank 43 , a circulation pump 45 , and a circulation valve 47 .
  • the out door unit 1 , the indoor units 5 a , 5 b , and the hot water unit 50 are connected to one another by inter-unit piping 10 .
  • the cooling and heating system 30 While operating the hot water unit 50 , the cooling and heating system 30 simultaneously allows the indoor units 5 a , 5 b to perform a cooling operation or a heating operation. Alternatively, the cooling operation and the heating operation can be performed in a mixed manner.
  • ends of the indoor heat exchangers 3 a , 3 b are selectively connected to a discharge tube 7 and a suction tube 8 of the compressor 2 via change valves 9 a and 9 b , and 19 a and 19 b , respectively.
  • the suction tube 8 is provided with an accumulator 4 .
  • the out door unit 1 includes an outdoor control device (not shown), and this outdoor control device controls the compressor 2 in the out door unit 1 , the outdoor expansion valves 27 a , 27 b , the change valves 9 a , 9 b , 19 a , and 19 b , and the cooling and heating system 30 .
  • the inter-unit piping 10 includes a high-pressure gas tube 11 , a low-pressure gas tube 12 , and a liquid tube 13 .
  • the high-pressure gas tube 11 is connected to the discharge tube 7
  • the low-pressure gas tube 12 is connected to the suction tube 8 .
  • the liquid tube 13 is connected to the other ends of the outdoor heat exchangers 3 a , 3 b via the outdoor expansion valves 27 a , 27 b.
  • Ends of the indoor heat exchangers 6 a , 6 b of the indoor units 5 a , 5 b are connected to the high-pressure gas tube 11 via discharge-side valves 16 a , 16 b , and connected to the low-pressure gas tube 12 via suction-side valves 17 a , 17 b .
  • the other ends of the indoor heat exchangers are connected to the liquid tube 13 via the indoor expansion valves 18 a , 18 b , respectively.
  • the indoor units 5 a , 5 b further have indoor fans 23 a , 23 b , remote controllers (not shown), and indoor control devices.
  • the indoor fans 23 a , 23 b are disposed close to the indoor heat exchangers 6 a , 6 b to send air to the indoor heat exchangers 6 a , 6 b , respectively.
  • the remote controllers are connected to the indoor units 5 a , 5 b , respectively, and output cooling or heating operation commands, stop commands or the like to the indoor control devices, respectively.
  • one end of the gas cooler 41 is connected to the high-pressure gas tube 11 , and the other end of the gas cooler 41 is connected to the liquid tube 13 via the circulation valve 47 .
  • This gas cooler 41 is connected to a water pipe 46 , and this water pipe 46 is connected to the hot water storage tank 43 via the circulation pump 45 .
  • a carbon dioxide refrigerant is introduced into the out door unit 1 , the indoor units 5 a , 5 b , the hot water unit 50 , and the inter-unit piping 10 .
  • the high side pressure of the refrigeration cycle such as the pressure in the high-pressure gas tube 11 is a supercritical pressure.
  • examples of the refrigerant include ethylene, diborane, ethane, and nitrogen oxide.
  • an outlet of the compressor 2 in a state a an outlet of the compressor 2 in a state a.
  • the refrigerant circulates through the heat exchanger (gas cooler), rejects heat, and is cooled to a state b. Moreover, the refrigerant reaches a state c owing to a pressure drop in the expansion valve (throttling device) to form a two-phase mixture of gas and liquid.
  • the heat exchanger evaporator
  • heat heat is absorbed by evaporation of a liquid phase
  • a state d is brought in an outlet of the evaporator.
  • the refrigerant flows toward the suction tube 8 of the compressor 2 .
  • a folded line is drawn between the states d and a.
  • the refrigerant discharged from the compressor 2 is introduced into the gas cooler 41 through the high-pressure gas tube 11 , this gas cooler 41 heats water passing through the water pipe 46 , and water at high temperature is stored in the hot water storage tank 43 (hot-water storage operation). Since the carbon dioxide refrigerant is used, and a high-pressure supercritical cycle is obtained, water is stored at a high temperature of about 80° C. or more in the tank. Moreover, hot water stored in this hot water storage tank 43 is sent to various hot-water facilities such as a bathroom, kitchen, and floor heating via piping (not shown).
  • the change valves 9 a , 9 b of the outdoor heat exchangers 3 a , 3 b are opened, the change valves 19 a , 19 b are closed, the discharge-side valves 16 a , 16 b are closed, and the suction-side valves 17 a , 17 b are opened. Accordingly, the refrigerant discharged from the compressor 2 successively flows to the discharge tube 7 , the change valves 9 a , 9 b , and the outdoor heat exchangers 3 a , 3 b .
  • the refrigerant exchanges heat (rejects heat) in the outdoor heat exchangers 3 a , 3 b , the refrigerant is distributed to the indoor expansion valves 18 a , 18 b of the indoor units 5 a , 5 b via the liquid tube 13 , and the pressure of the refrigerant is reduced. Moreover, the refrigerant evaporates (absorbs heat) in the indoor heat exchangers 6 a , 6 b , and flows through the suction-side valves 17 a , 17 b . The refrigerant is successively passed through the low-pressure gas tube 12 , the suction tube 8 , and the accumulator 4 , and sucked into the compressor 2 . In this manner, all of the indoor units 5 a , 5 b are simultaneously cooled by functions of the indoor heat exchangers 6 a , 6 b functioning as evaporators, respectively (cooling operation).
  • the change valves 9 a , 9 b of the outdoor heat exchangers 3 a , 3 b are closed, the change valves 19 a , 19 b are opened, the discharge-side valves 16 a , 16 b are opened, and the suction-side valves 17 a , 17 b are closed. Accordingly, the refrigerant discharged from the compressor 2 is successively passed through the discharge tube 7 and the high-pressure gas tube 11 to flow to the discharge-side valves 16 a , 16 b and the indoor heat exchangers 6 a , 6 b .
  • the refrigerant exchanges heat (rejects heat), and flows into the liquid tube 13 . Moreover, the pressure of the refrigerant is reduced by the outdoor expansion valves 27 a , 27 b .
  • the refrigerant evaporates (absorbs heat) in the outdoor heat exchangers 3 a , 3 b , and is thereafter successively passed through the change valves 9 a , 9 b , the suction tube 8 , and the accumulator 4 .
  • the refrigerant is sucked into the compressor 2 . All of the indoor units 5 a , 5 b are simultaneously heated by functions of the indoor heat exchangers 6 a , 6 b which function as gas coolers in this manner (heating operation).
  • a demanded load in each indoor unit is calculated (S 14 ), and it is judged by a total load value (S 15 ) whether the outdoor heat exchanger 3 is operated as a gas cooler or an evaporator (S 16 ).
  • the change valve 9 of the outdoor heat exchanger 3 is opened, and the change valve 19 is closed.
  • the discharge-side valve 16 a of the indoor unit 5 a and the suction-side valve 17 b of the indoor unit 5 b are closed, and the suction-side valve 17 a of the indoor unit 5 a and the discharge-side valve 16 b of the indoor unit 5 b are opened. Accordingly, the refrigerant discharged from the compressor 2 successively flows to the discharge tube 7 , the change valve 9 , the discharge-side valve 16 b of the indoor unit 5 b , the outdoor heat exchanger 3 , and the indoor heat exchanger 6 b .
  • the refrigerant After the refrigerant exchanges heat (rejects heat) in the outdoor heat exchanger 3 and the indoor heat exchanger 6 b , the refrigerant flows into the liquid tube 13 to enter the indoor expansion valve 18 a , and the pressure of the refrigerant is reduced in the valve. Moreover, the refrigerant evaporates (absorbs heat) in the indoor heat exchanger 6 a . After the refrigerant flows in the suction-side valve 17 a , the refrigerant is successively passed through the low-pressure gas tube 12 , the suction tube 8 , and the accumulator 4 , and sucked into the compressor 2 .
  • the change valve 9 of the outdoor heat exchanger 3 is closed, and the change valve 19 is opened.
  • the discharge-side valve 16 a of the indoor unit 5 a and the suction-side valve 17 b of the indoor unit 5 b are closed, and the suction-side valve 17 a of the indoor unit 5 a and the discharge-side valve 16 b of the indoor unit 5 b are opened. Accordingly, the refrigerant discharged from the compressor 2 successively flows to the discharge tube 7 , the discharge-side valve 16 b of the indoor unit 5 b , and the indoor heat exchanger 6 b .
  • the refrigerant After the refrigerant exchanges heat (rejects heat) in this indoor heat exchanger 6 b , the refrigerant passes through the liquid tube 13 , and is distributed to the outdoor expansion valve 27 and the indoor expansion valve 18 a . The pressure of the refrigerant is reduced in the valves. Moreover, the refrigerant evaporates (absorbs heat) in the outdoor heat exchanger 3 and the indoor heat exchanger 6 a . After the refrigerant flows through the change valve 19 and the suction-side valve 17 a , the refrigerant successively flows through the low-pressure gas tube 12 , the suction tube 8 , and the accumulator 4 , and is sucked into the compressor 2 .
  • the total load value may be calculated assuming that a load of the hot water unit 50 is similar to that of the heating operation of the indoor unit 5 .
  • the refrigerant circulates so that the indoor heat exchanger, the outdoor heat exchanger, and a gas cooler are mutually, so-called thermally balanced.
  • hot water can be stored (supplied) by indoor heat. Therefore, heat is remarkably effectively utilized. There is an effect of preventing a heat island phenomenon caused by heat rejection from the outdoor unit.
  • an evaporation temperature T EVA is measured (S 150 ).
  • a place to be measured differs with an operation state of a cooling and heating system 130 .
  • a temperature during phase change of the refrigerant (carbon dioxide) from a liquid to a gas is the evaporation temperature T EVA .
  • an object to be measured may be the evaporation pressure P EVA .
  • an outlet refrigerant temperature T GC of the gas cooler is measured.
  • the outlet refrigerant temperature of an indoor heat exchanger 106 a is measured as T GC (S 152 Y) by a temperature sensor T C08 .
  • the outlet refrigerant temperature of an outdoor heat exchanger 103 a is measured as T GC (S 152 N) by a temperature sensor T CO3 .
  • the outlet refrigerant temperature of the indoor heat exchanger or the outdoor heat exchanger may be replaced with a temperature of environment in a place where the heat exchanger is installed (indoor temperature or outside air temperature).
  • a target high pressure P H.OPT is set from the measured evaporation temperature T EVA and the outlet refrigerant temperature T GC of the gas cooler (S 153 ), and a high pressure P H is measured (S 154 ).
  • a pressure sensor P C01 is disposed in the vicinity of an outlet of a compressor 102 to measure the high pressure P H .
  • a control operation is determined depending on states of the measured evaporation temperature T EVA and high pressure P H with respect to a predetermined reference temperature T S and the target high pressure P H.OPT .
  • the outdoor heat exchanger 103 is operated as an evaporator (S 155 )
  • the compressor 102 and the outdoor heat exchanger 103 are controlled (S 157 , S 158 ).
  • the outdoor heat exchanger 103 is not operated as the evaporator (S 155 )
  • the compressor 102 and the outdoor heat exchanger 103 are controlled (S 157 , S 158 ).
  • an evaporation temperature T EVA is measured (S 250 ).
  • a place to be measured differs with an operation state of a cooling and heating system 230 .
  • a temperature during phase change of the refrigerant (carbon dioxide) from a liquid to a gas is the evaporation temperature T EVA .
  • an object to be measured may be the evaporation pressure P EVA .
  • an outlet refrigerant temperature T GC of the gas cooler is measured (S 252 ).
  • the outlet refrigerant temperature of an indoor heat exchanger 206 a is measured as T GC (S 252 Y) by a temperature sensor T C28 .
  • the outlet refrigerant temperature of an outdoor heat exchanger 203 a is measured as T GC (S 252 N) by a temperature sensor T C23 .
  • the outlet refrigerant temperature of the indoor heat exchanger or the outdoor heat exchanger may be replaced with a temperature of environment in a place where the heat exchanger is installed (indoor temperature or outside air temperature).
  • an optimum high pressure P H.OPT is calculated from the measured evaporation temperature T EVA and an outlet refrigerant temperature T GC of the gas cooler, and a target discharge temperature T DIS.OPT is set from the calculated optimum high pressure P H.OPT , and characteristics or a suction state of a compressor 202 (S 253 ), and a discharge temperature T DIS is measured (S 254 ).
  • a pressure sensor T C21 is disposed in the vicinity of an outlet of the compressor 202 to measure the discharge temperature T DIS .
  • a control operation is determined depending on states of the measured evaporation temperature T EVA and discharge temperature T DIS with respect to a predetermined reference temperature T S and the target discharge temperature T DIS.OPT .
  • the outdoor heat exchanger 203 is operated as an evaporator (S 255 )
  • the compressor 202 and the outdoor heat exchanger 203 are controlled (S 257 , S 258 ).
  • the outdoor heat exchanger 203 is not operated as the evaporator (S 255 )
  • a thermal load balance control map (C 3 ) shown in FIG. 11 (S 256 N) the compressor 202 and the outdoor heat exchanger 203 are controlled (S 257 , S 258 ).
  • the present invention can be utilized in not only a cooling and heating system for business in a building or the like but also a household cooling and heating system having a hot water supply system or a floor heating system.

Abstract

There is disclosed a cooling and heating system in which a refrigerant is used in a supercritical state and in which cooling and heating capacity can be controlled so as to maximize a coefficient of performance. A cooling and heating system 130 includes: an outdoor unit 101 indicating a compressor 102 and an outdoor heat exchanger 103 a; a plurality of indoor units 105 including indoor heat exchangers 106; a high pressure tube 111; a low pressure tube 112; and an intermediate tube 113. The system includes: a refrigerant pressure detection unit PC01 for measuring a pressure of the refrigerant discharged from the compressor 102; a first refrigerant temperature detection unit TC03 which measures an outlet temperature of the refrigerant in a case where the outdoor heat exchanger 103 functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the outdoor heat exchanger 103 functions as an evaporator; and a second refrigerant temperature detection unit TCO8 which measures an outlet temperature of the refrigerant in a case where the indoor heat exchanger 106 functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the indoor heat exchanger 106 functions as an evaporator.

Description

    BACKGROUND OF THE INVENTION
  • The present invention relates to a cooling and heating system, more particularly to a cooling and heating system which uses a refrigerant in a supercritical state and which can control cooling and heating capacity so as to maximize a coefficient of performance.
  • A cooling and heating system described in Japanese Patent Application Laid-Open No. 2004-226018 is known as a cooling and heating system in which a carbon dioxide refrigerant is used in a supercritical state. The system has an outdoor unit and a plurality of indoor units, the plurality of indoor units can be operated at the same time in a cooling operation or a heating operation, and the cooling operation and the heating operation can be performed in a mixed manner. Here, the cooling operation refers to an operation to be performed in a case where a set temperature of the indoor unit is lower than an indoor temperature, and the heating operation refers to an operation to be performed in a case where the set temperature of the indoor unit is higher than the indoor temperature.
  • When a fluorocarbon refrigerant is used in the cooling and heating system, an evaporation temperature (or an evaporation pressure) or a condensation temperature (or a condensation pressure) is measured to grasp a state of the refrigerant. Capacities of a heat exchanger in the indoor unit and a compressor are controlled so that a measured value of the temperature comes close to a target value (a coefficient of performance is maximized). Here, the capacity control of the heat exchanger in the outdoor unit indicates that: a plurality of heat exchangers having different sizes are connected depending on a heat balance between a cooling load and a heating load on an indoor side, the heat exchangers are provided with change valves, respectively, and the number of the heat exchangers to be operated is changed; an amount of the refrigerant to be circulated in each heat exchanger is adjusted; or a rotational speed of a blower disposed in each heat exchanger is adjusted to control the capacity so that the temperature reaches the targeted evaporation or condensation temperature.
  • On the other hand, in the cooling and heating system in which a refrigerant such as carbon dioxide is used in a supercritical state, a high pressure side has a supercritical state. Therefore, there is a problem that the condensation pressure (high pressure) cannot be uniquely obtained from the condensation temperature (this refers to a high-pressure-side temperature because condensation does not occur in actual) unlike the fluorocarbon refrigerant, and both of the condensation temperature and the condensation pressure have to be measured on the high pressure side in order to grasp the state of the refrigerant. Therefore, it has been difficult to control the capacities of the heat exchanger and the compressor so as to maximize the coefficient of performance.
  • SUMMARY OF THE INVENTION
  • An object of the present invention is to provide a cooling and heating system in which cooling and heating capacity can be controlled so as to maximize a coefficient of performance and in which a refrigerant is used in a supercritical state.
  • The present invention has been developed in order to achieve the above-described object. In a first aspect of the present invention, there is provided a cooling and heating system including: an outdoor unit including a compressor and an outdoor heat exchanger; and a plurality of indoor units including indoor heat exchangers and connected to one another by a pipe between the units, one end of the outdoor heat exchanger being selectively connected to a refrigerant discharge tube and a refrigerant suction tube of the compressor, the pipe between the units including: a high pressure tube connected to the refrigerant discharge tube; a low pressure tube connected to the refrigerant suction tube; and an intermediate pressure tube connected to the other end of the outdoor heat exchanger, one end of the indoor heat exchanger of each indoor unit being selectively connected to the high pressure tube and the low pressure tube, the other end of the indoor heat exchanger being connected to the intermediate pressure tube, the plurality of indoor units being simultaneously allowed to perform a cooling operation or a heating operation or the plurality of indoor units being allowed to perform a cooling operation and a heating operation simultaneously in a mixed manner, the cooling and heating system comprising: refrigerant pressure measurement means for measuring a pressure of the refrigerant discharged from the compressor; first refrigerant temperature measurement means which is disposed in the outdoor unit and which measures an outlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as an evaporator; and second refrigerant temperature measurement means which is disposed in the indoor unit and which measures an outlet temperature of the refrigerant in a case where the indoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the indoor heat exchanger functions as an evaporator.
  • Moreover, in a second aspect of the present invention, there is provided a cooling and heating system including: an outdoor unit including a compressor and an outdoor heat exchanger; and a plurality of indoor units including indoor heat exchangers and connected to one another by a pipe between the units, one end of the outdoor heat exchanger being selectively connected to a refrigerant discharge tube and a refrigerant suction tube of the compressor, the pipe between the units including: a high pressure tube connected to the refrigerant discharge tube; a low pressure tube connected to the refrigerant suction tube; and an intermediate pressure tube connected to the other end of the outdoor heat exchanger, one end of the indoor heat exchanger of each indoor unit being selectively connected to the high pressure tube and the low pressure tube, the other end of the indoor heat exchanger being connected to the intermediate pressure tube, the plurality of indoor units being simultaneously allowed to perform a cooling operation or a heating operation or the plurality of indoor units being allowed to perform a cooling operation and a heating operation simultaneously in a mixed manner, the cooling and heating system comprising: discharge temperature measurement means for measuring a temperature of the refrigerant discharged from the compressor; first refrigerant temperature measurement means which is disposed in the outdoor unit and which measures an outlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as an evaporator; and second refrigerant temperature measurement means which is disposed in the indoor unit and which measures an outlet temperature of the refrigerant in a case where the indoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the indoor heat exchanger functions as an evaporator.
  • Furthermore, in a third aspect of the present invention, in the cooling and heating system of the first or second aspect, the high side pressure of the refrigeration cycle is above the critical pressure of the refrigerant during the operation of the cooling and heating system. In a fourth aspect of the present invention, in the cooling and heating system of the third aspect, carbon dioxide is used as the refrigerant.
  • According to the present invention, in the cooling and heating system in which the refrigerant is used in the supercritical state, cooling and heating capacity can be controlled so as to maximize a coefficient of performance.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 is a schematic diagram showing a cooling and heating system of the present invention;
  • FIG. 2 is a P-h diagram showing a refrigeration cycle of the cooling and heating system in the present invention;
  • FIG. 3 is a control flowchart for determining an operation mode of an outdoor heat exchanger in the cooling and heating system of the present invention;
  • FIG. 4 is a control flowchart of thermal load balance control in Embodiment 1 of the present invention;
  • FIG. 5 is a schematic diagram showing the cooling and heating system in Embodiment 1 of the present invention;
  • FIG. 6 is a control map diagram at a time when the outdoor heat exchanger is an evaporator in Embodiment 1 of the present invention;
  • FIG. 7 is a control map diagram at a time when the outdoor heat exchanger is a gas cooler in Embodiment 1 of the present invention;
  • FIG. 8 is a control flowchart of thermal load balance control in Embodiment 2 of the present invention;
  • FIG. 9 is a schematic diagram showing the cooling and heating system in Embodiment 2 of the present invention;
  • FIG. 10 is a control map diagram at a time when the outdoor heat exchanger is an evaporator in Embodiment 2 of the present invention; and
  • FIG. 11 is a control map diagram at a time when the outdoor heat exchanger is a gas cooler in Embodiment 2 of the present invention.
  • DESCRIPTION OF THE PREFERRED EMBODIMENT
  • FIG. 1 is a schematic diagram of a cooling and heating system of the present invention. This cooling and heating system 30 includes: an out door unit 1 including outdoor heat exchangers 3 a, 3 b and outdoor expansion valves 27 a, 27 b; an indoor unit 5 a including an indoor heat exchanger 6 a and an indoor expansion valve 18 a; an indoor unit 5 b including an indoor heat exchanger 6 b and an indoor expansion valve 18 b; and a hot water unit 50 including a gas cooler 41, a hot water storage tank 43, a circulation pump 45, and a circulation valve 47. Moreover, the out door unit 1, the indoor units 5 a, 5 b, and the hot water unit 50 are connected to one another by inter-unit piping 10. While operating the hot water unit 50, the cooling and heating system 30 simultaneously allows the indoor units 5 a, 5 b to perform a cooling operation or a heating operation. Alternatively, the cooling operation and the heating operation can be performed in a mixed manner.
  • In the out door unit 1, ends of the indoor heat exchangers 3 a, 3 b are selectively connected to a discharge tube 7 and a suction tube 8 of the compressor 2 via change valves 9 a and 9 b, and 19 a and 19 b, respectively. The suction tube 8 is provided with an accumulator 4. The out door unit 1 includes an outdoor control device (not shown), and this outdoor control device controls the compressor 2 in the out door unit 1, the outdoor expansion valves 27 a, 27 b, the change valves 9 a, 9 b, 19 a, and 19 b, and the cooling and heating system 30. The inter-unit piping 10 includes a high-pressure gas tube 11, a low-pressure gas tube 12, and a liquid tube 13. The high-pressure gas tube 11 is connected to the discharge tube 7, and the low-pressure gas tube 12 is connected to the suction tube 8. The liquid tube 13 is connected to the other ends of the outdoor heat exchangers 3 a, 3 b via the outdoor expansion valves 27 a, 27 b.
  • Ends of the indoor heat exchangers 6 a, 6 b of the indoor units 5 a, 5 b are connected to the high-pressure gas tube 11 via discharge- side valves 16 a, 16 b, and connected to the low-pressure gas tube 12 via suction-side valves 17 a, 17 b. The other ends of the indoor heat exchangers are connected to the liquid tube 13 via the indoor expansion valves 18 a, 18 b, respectively. When one of the discharge-side valve 16 a and the suction-side valve 17 a is opened, the other valve is closed. Similarly, when one of the discharge-side valve 16 b and the suction-side valve 17 b is opened, the other valve is closed. This selectively connects the ends of the indoor heat exchangers 6 a, 6 b to the high-pressure gas tube 11 and the low-pressure gas tube 12 of the inter-unit piping 10. The indoor units 5 a, 5 b further have indoor fans 23 a, 23 b, remote controllers (not shown), and indoor control devices. The indoor fans 23 a, 23 b are disposed close to the indoor heat exchangers 6 a, 6 b to send air to the indoor heat exchangers 6 a, 6 b, respectively. The remote controllers are connected to the indoor units 5 a, 5 b, respectively, and output cooling or heating operation commands, stop commands or the like to the indoor control devices, respectively.
  • In the hot water unit 50, one end of the gas cooler 41 is connected to the high-pressure gas tube 11, and the other end of the gas cooler 41 is connected to the liquid tube 13 via the circulation valve 47. This gas cooler 41 is connected to a water pipe 46, and this water pipe 46 is connected to the hot water storage tank 43 via the circulation pump 45.
  • In the present embodiment, a carbon dioxide refrigerant is introduced into the out door unit 1, the indoor units 5 a, 5 b, the hot water unit 50, and the inter-unit piping 10. In a case where the carbon dioxide refrigerant is introduced, as shown in an enthalpy and pressure (P-h) graph, the high side pressure of the refrigeration cycle, such as the pressure in the high-pressure gas tube 11 is a supercritical pressure. As to a refrigerant for use in the trance critical refrigeration cycle, examples of the refrigerant include ethylene, diborane, ethane, and nitrogen oxide.
  • In FIG. 2, an outlet of the compressor 2 in a state a. The refrigerant circulates through the heat exchanger (gas cooler), rejects heat, and is cooled to a state b. Moreover, the refrigerant reaches a state c owing to a pressure drop in the expansion valve (throttling device) to form a two-phase mixture of gas and liquid. In the heat exchanger (evaporator), heat is absorbed by evaporation of a liquid phase, and a state d is brought in an outlet of the evaporator. Moreover, the refrigerant flows toward the suction tube 8 of the compressor 2. In the present embodiment, since a two-stage compressor is used in the compressor 2, a folded line is drawn between the states d and a.
  • Next, an operation of the cooling and heating system 30 will be described.
  • In this cooling and heating system 30, the refrigerant discharged from the compressor 2 is introduced into the gas cooler 41 through the high-pressure gas tube 11, this gas cooler 41 heats water passing through the water pipe 46, and water at high temperature is stored in the hot water storage tank 43 (hot-water storage operation). Since the carbon dioxide refrigerant is used, and a high-pressure supercritical cycle is obtained, water is stored at a high temperature of about 80° C. or more in the tank. Moreover, hot water stored in this hot water storage tank 43 is sent to various hot-water facilities such as a bathroom, kitchen, and floor heating via piping (not shown).
  • In a case where the cooling operation is simultaneously performed by all of the indoor units 5 a, 5 b, the change valves 9 a, 9 b of the outdoor heat exchangers 3 a, 3 b are opened, the change valves 19 a, 19 b are closed, the discharge- side valves 16 a, 16 b are closed, and the suction-side valves 17 a, 17 b are opened. Accordingly, the refrigerant discharged from the compressor 2 successively flows to the discharge tube 7, the change valves 9 a, 9 b, and the outdoor heat exchangers 3 a, 3 b. After the refrigerant exchanges heat (rejects heat) in the outdoor heat exchangers 3 a, 3 b, the refrigerant is distributed to the indoor expansion valves 18 a, 18 b of the indoor units 5 a, 5 b via the liquid tube 13, and the pressure of the refrigerant is reduced. Moreover, the refrigerant evaporates (absorbs heat) in the indoor heat exchangers 6 a, 6 b, and flows through the suction-side valves 17 a, 17 b. The refrigerant is successively passed through the low-pressure gas tube 12, the suction tube 8, and the accumulator 4, and sucked into the compressor 2. In this manner, all of the indoor units 5 a, 5 b are simultaneously cooled by functions of the indoor heat exchangers 6 a, 6 b functioning as evaporators, respectively (cooling operation).
  • Conversely, in a case where all of the indoor units 5 a, 5 b are simultaneously heated, the change valves 9 a, 9 b of the outdoor heat exchangers 3 a, 3 b are closed, the change valves 19 a, 19 b are opened, the discharge- side valves 16 a, 16 b are opened, and the suction-side valves 17 a, 17 b are closed. Accordingly, the refrigerant discharged from the compressor 2 is successively passed through the discharge tube 7 and the high-pressure gas tube 11 to flow to the discharge- side valves 16 a, 16 b and the indoor heat exchangers 6 a, 6 b. The refrigerant exchanges heat (rejects heat), and flows into the liquid tube 13. Moreover, the pressure of the refrigerant is reduced by the outdoor expansion valves 27 a, 27 b. The refrigerant evaporates (absorbs heat) in the outdoor heat exchangers 3 a, 3 b, and is thereafter successively passed through the change valves 9 a, 9 b, the suction tube 8, and the accumulator 4. The refrigerant is sucked into the compressor 2. All of the indoor units 5 a, 5 b are simultaneously heated by functions of the indoor heat exchangers 6 a, 6 b which function as gas coolers in this manner (heating operation).
  • Moreover, in a cooling/heating mixed operation in which, for example, the indoor unit 5 a is cooled, and simultaneously the indoor unit 5 b is heated, in accordance with a control flow (A1) of an outdoor unit operation mode shown in FIG. 3, a demanded load in each indoor unit is calculated (S14), and it is judged by a total load value (S15) whether the outdoor heat exchanger 3 is operated as a gas cooler or an evaporator (S16).
  • In a case where the outdoor heat exchanger 3 is operated as the gas cooler (S16N), the change valve 9 of the outdoor heat exchanger 3 is opened, and the change valve 19 is closed. Moreover, the discharge-side valve 16 a of the indoor unit 5 a and the suction-side valve 17 b of the indoor unit 5 b are closed, and the suction-side valve 17 a of the indoor unit 5 a and the discharge-side valve 16 b of the indoor unit 5 b are opened. Accordingly, the refrigerant discharged from the compressor 2 successively flows to the discharge tube 7, the change valve 9, the discharge-side valve 16 b of the indoor unit 5 b, the outdoor heat exchanger 3, and the indoor heat exchanger 6 b. After the refrigerant exchanges heat (rejects heat) in the outdoor heat exchanger 3 and the indoor heat exchanger 6 b, the refrigerant flows into the liquid tube 13 to enter the indoor expansion valve 18 a, and the pressure of the refrigerant is reduced in the valve. Moreover, the refrigerant evaporates (absorbs heat) in the indoor heat exchanger 6 a. After the refrigerant flows in the suction-side valve 17 a, the refrigerant is successively passed through the low-pressure gas tube 12, the suction tube 8, and the accumulator 4, and sucked into the compressor 2.
  • On the other hand, in a case where the outdoor heat exchanger 3 is operated as the evaporator (S16Y), the change valve 9 of the outdoor heat exchanger 3 is closed, and the change valve 19 is opened. Moreover, the discharge-side valve 16 a of the indoor unit 5 a and the suction-side valve 17 b of the indoor unit 5 b are closed, and the suction-side valve 17 a of the indoor unit 5 a and the discharge-side valve 16 b of the indoor unit 5 b are opened. Accordingly, the refrigerant discharged from the compressor 2 successively flows to the discharge tube 7, the discharge-side valve 16 b of the indoor unit 5 b, and the indoor heat exchanger 6 b. After the refrigerant exchanges heat (rejects heat) in this indoor heat exchanger 6 b, the refrigerant passes through the liquid tube 13, and is distributed to the outdoor expansion valve 27 and the indoor expansion valve 18 a. The pressure of the refrigerant is reduced in the valves. Moreover, the refrigerant evaporates (absorbs heat) in the outdoor heat exchanger 3 and the indoor heat exchanger 6 a. After the refrigerant flows through the change valve 19 and the suction-side valve 17 a, the refrigerant successively flows through the low-pressure gas tube 12, the suction tube 8, and the accumulator 4, and is sucked into the compressor 2.
  • Moreover, in a case where the hot water storage operation is simultaneously required, the total load value may be calculated assuming that a load of the hot water unit 50 is similar to that of the heating operation of the indoor unit 5.
  • As described above, during the cooling and heating mixed operation, or during the hot water storage operation, the refrigerant circulates so that the indoor heat exchanger, the outdoor heat exchanger, and a gas cooler are mutually, so-called thermally balanced. This makes possible an operation in which indoor heat and outdoor heat are efficiently utilized. Especially, during the mixed operation of the cooling operation by the indoor unit and the hot water storage operation, hot water can be stored (supplied) by indoor heat. Therefore, heat is remarkably effectively utilized. There is an effect of preventing a heat island phenomenon caused by heat rejection from the outdoor unit. Moreover, in a case where a supercritical cycle is set using carbon dioxide in the refrigerant, since high-pressure single-phase refrigerant vapor discharged from the compressor 2 does not condense in the high-pressure gas tube 11, unlike the Freon refrigerant, a disadvantage that the refrigerant liquefies and accumulated in the high-pressure gas tube 11 is solved. This obviates a necessity for a bypass tube or the like between the high-pressure gas tube 11 and the low-pressure gas tube 12, which has been required for recovering the accumulated refrigerant. The refrigerant can be prevented from accumulating in the high-pressure gas tube 11 without complicating any pipe structure. Furthermore, since any bypass tube or the like is not required, an electromagnetic valve used herein is not required, the control is not required, and cost is reduced.
  • There will be described hereinafter an embodiment for controlling the above-described operation of the cooling and heating system 30 so as to maximize a coefficient of performance.
  • Embodiment 1
  • In the present embodiment, there will be described an operation control by a high pressure and an evaporation temperature with reference to FIGS. 4, 5, 6, and 7.
  • First in the present embodiment, as shown in a control flow (B1) of a thermal load balance control of FIG. 4, an evaporation temperature TEVA is measured (S150). A place to be measured differs with an operation state of a cooling and heating system 130. When the state c shown in FIG. 2 advances to the state d, a temperature during phase change of the refrigerant (carbon dioxide) from a liquid to a gas is the evaporation temperature TEVA. At this time, since the evaporation temperature TEVA and an evaporation pressure PEVA are uniquely determined, an object to be measured may be the evaporation pressure PEVA.
  • Next, an outlet refrigerant temperature TGC of the gas cooler is measured. Here, if the heating operation is performed in an out door unit 105 a shown in FIG. 5 (S151), the outlet refrigerant temperature of an indoor heat exchanger 106 a is measured as TGC (S152Y) by a temperature sensor TC08. Unless the heating operation is performed in both of the out door unit 105 a and an out door unit 105 b (S151), the outlet refrigerant temperature of an outdoor heat exchanger 103 a (it is assumed that the outdoor heat exchanger 103 a is used in preference to an outdoor heat exchanger 103 b) is measured as TGC (S152N) by a temperature sensor TCO3. Here, the outlet refrigerant temperature of the indoor heat exchanger or the outdoor heat exchanger may be replaced with a temperature of environment in a place where the heat exchanger is installed (indoor temperature or outside air temperature).
  • Moreover, a target high pressure PH.OPT is set from the measured evaporation temperature TEVA and the outlet refrigerant temperature TGC of the gas cooler (S153), and a high pressure PH is measured (S154). A pressure sensor PC01 is disposed in the vicinity of an outlet of a compressor 102 to measure the high pressure PH.
  • A control operation is determined depending on states of the measured evaporation temperature TEVA and high pressure PH with respect to a predetermined reference temperature TS and the target high pressure PH.OPT. In this case, when the outdoor heat exchanger 103 is operated as an evaporator (S155), in accordance with a thermal load balance control map (B2) shown in FIG. 6 (S156Y), the compressor 102 and the outdoor heat exchanger 103 are controlled (S157, S158). When the outdoor heat exchanger 103 is not operated as the evaporator (S155), in accordance with a thermal load balance control map (B3) shown in FIG. 7 (S156N), the compressor 102 and the outdoor heat exchanger 103 are controlled (S157, S158).
  • Embodiment 2
  • In the present embodiment, there will be described an operation control by a discharge temperature and an evaporation temperature with reference to FIGS. 8, 9, 10, and 11.
  • First in the present embodiment, as shown in a control flow (C1) of a thermal load balance control of FIG. 8, an evaporation temperature TEVA is measured (S250). A place to be measured differs with an operation state of a cooling and heating system 230. When the state c shown in FIG. 2 advances to the state d, a temperature during phase change of the refrigerant (carbon dioxide) from a liquid to a gas is the evaporation temperature TEVA. At this time, since the evaporation temperature TEVA and an evaporation pressure PEVA are uniquely determined, an object to be measured may be the evaporation pressure PEVA.
  • Next, an outlet refrigerant temperature TGC of the gas cooler is measured (S252). Here, if the heating operation is performed in an indoor unit 205 a shown in FIG. 9 (S251), the outlet refrigerant temperature of an indoor heat exchanger 206 a is measured as TGC (S252Y) by a temperature sensor TC28. Unless the heating operation is performed in both of the indoor unit 205 a and an indoor unit 205 b (S251), the outlet refrigerant temperature of an outdoor heat exchanger 203 a (it is assumed that the outdoor heat exchanger 203 a is used in preference to an outdoor heat exchanger 203 b) is measured as TGC (S252N) by a temperature sensor TC23. Here, the outlet refrigerant temperature of the indoor heat exchanger or the outdoor heat exchanger may be replaced with a temperature of environment in a place where the heat exchanger is installed (indoor temperature or outside air temperature).
  • Moreover, an optimum high pressure PH.OPT is calculated from the measured evaporation temperature TEVA and an outlet refrigerant temperature TGC of the gas cooler, and a target discharge temperature TDIS.OPT is set from the calculated optimum high pressure PH.OPT, and characteristics or a suction state of a compressor 202 (S253), and a discharge temperature TDIS is measured (S254). A pressure sensor TC21 is disposed in the vicinity of an outlet of the compressor 202 to measure the discharge temperature TDIS.
  • A control operation is determined depending on states of the measured evaporation temperature TEVA and discharge temperature TDIS with respect to a predetermined reference temperature TS and the target discharge temperature TDIS.OPT. In this case, when the outdoor heat exchanger 203 is operated as an evaporator (S255), in accordance with a thermal load balance control map (C2) shown in FIG. 10 (S256Y), the compressor 202 and the outdoor heat exchanger 203 are controlled (S257, S258). When the outdoor heat exchanger 203 is not operated as the evaporator (S255), in accordance with a thermal load balance control map (C3) shown in FIG. 11 (S256N), the compressor 202 and the outdoor heat exchanger 203 are controlled (S257, S258).
  • The present invention can be utilized in not only a cooling and heating system for business in a building or the like but also a household cooling and heating system having a hot water supply system or a floor heating system.

Claims (4)

1. A cooling and heating system including: an outdoor unit including a compressor and an outdoor heat exchanger; and a plurality of indoor units including indoor heat exchangers and connected to one another by a pipe between the units, one end of the outdoor heat exchanger being selectively connected to a refrigerant discharge tube and a refrigerant suction tube of the compressor, the pipe between the units including: a high pressure tube connected to the refrigerant discharge tube; a low pressure tube connected to the refrigerant suction tube; and an intermediate pressure tube connected to the other end of the outdoor heat exchanger, one end of the indoor heat exchanger of each indoor unit being selectively connected to the high pressure tube and the low pressure tube, the other end of the indoor heat exchanger being connected to the intermediate pressure tube, the plurality of indoor units being simultaneously allowed to perform a cooling operation or a heating operation or the plurality of indoor units being allowed to perform a cooling operation and a heating operation simultaneously in a mixed manner,
the cooling and heating system comprising:
refrigerant pressure measurement means for measuring a pressure of the refrigerant discharged from the compressor;
first refrigerant temperature measurement means which is disposed in the outdoor unit and which measures an outlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as an evaporator; and
second refrigerant temperature measurement means which is disposed in the indoor unit and which measures an outlet temperature of the refrigerant in a case where the indoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the indoor heat exchanger functions as an evaporator.
2. A cooling and heating system including: an outdoor unit including a compressor and an outdoor heat exchanger; and a plurality of indoor units including indoor heat exchangers and connected to one another by a pipe between the units, one end of the outdoor heat exchanger being selectively connected to a refrigerant discharge tube and a refrigerant suction tube of the compressor, the pipe between the units including: a high pressure tube connected to the refrigerant discharge tube; a low pressure tube connected to the refrigerant suction tube; and an intermediate pressure tube connected to the other end of the outdoor heat exchanger, one end of the indoor heat exchanger of each indoor unit being selectively connected to the high pressure tube and the low pressure tube, the other end of the indoor heat exchanger being connected to the intermediate pressure tube, the plurality of indoor units being simultaneously allowed to perform a cooling operation or a heating operation or the plurality of indoor units being allowed to perform a cooling operation and a heating operation simultaneously in a mixed manner,
the cooling and heating system comprising:
discharge temperature measurement means for measuring a temperature of the refrigerant discharged from the compressor;
first refrigerant temperature measurement means which is disposed in the outdoor unit and which measures an outlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the outdoor heat exchanger functions as an evaporator; and
second refrigerant temperature measurement means which is disposed in the indoor unit and which measures an outlet temperature of the refrigerant in a case where the indoor heat exchanger functions as a gas cooler and which measures an inlet temperature of the refrigerant in a case where the indoor heat exchanger functions as an evaporator.
3. The cooling and heating system according to claim 1 or 2,
wherein the high side pressure of the refrigeration cycle is above the critical pressure of the refrigerant during the operation of the cooling and heating system.
4. The cooling and heating system according to claim 3, wherein carbon dioxide is used as the refrigerant.
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