US20110146339A1 - Air-conditioning apparatus - Google Patents

Air-conditioning apparatus Download PDF

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Publication number
US20110146339A1
US20110146339A1 US13/055,841 US200813055841A US2011146339A1 US 20110146339 A1 US20110146339 A1 US 20110146339A1 US 200813055841 A US200813055841 A US 200813055841A US 2011146339 A1 US2011146339 A1 US 2011146339A1
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United States
Prior art keywords
heat medium
heat exchanger
flow path
temperature
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US13/055,841
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English (en)
Inventor
Koji Yamashita
Hiroyuki Morimoto
Yuji Motomura
Takeshi Hatomura
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HATOMURA, TAKESHI, MORIMOTO, HIROYUKI, MOTOMURA, YUJI, YAMASHITA, KOJI
Publication of US20110146339A1 publication Critical patent/US20110146339A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger

Definitions

  • the present invention relates to an air-conditioning apparatus such as a multiple air conditioner for buildings.
  • a multiple air conditioner which is a conventional air-conditioning apparatus
  • cooling energy or heating energy is delivered indoors by circulating a refrigerant between an outdoor unit, which is a heat source apparatus installed outdoors, and an indoor unit installed indoors.
  • a refrigerant an HFC (hydrofluorocarbon) refrigerant is mainly used and the air-conditioning apparatus using a natural refrigerant such as CO2 is proposed.
  • a chiller which is another conventional air-conditioning apparatus
  • cooling energy or heating energy is generated in a heat source apparatus disposed outdoors
  • cooling energy or heating energy is transferred to a heat medium such as water and an anti-freezing liquid at a heat exchanger disposed in an outdoor unit
  • cooling operation or heating operation is performed by carrying the heat medium to a fan coil unit, a panel heater and the like, which are of an indoor unit (Refer to Patent Literature 1, for example).
  • the present invention is made to solve the above-mentioned problems and its object is to obtain an air-conditioning apparatus having an excellent energy-saving property and an anti-freezing design of the indoor unit side heat medium without circulating the refrigerant such as HFC in the indoor unit.
  • the air-conditioning apparatus comprises: at least one intermediate heat exchanger that exchanges heat between a refrigerant and a heat medium that is different from the refrigerant; a refrigeration cycle in which a compressor, a heat source side heat exchanger, at least one expansion valve, and a refrigerant side flow path of the intermediate heat exchanger are connected via piping through which the refrigerant flows; and a heat medium circulation circuit in which a heat medium side flow path of the intermediate heat exchanger, a pump, and a use side heat exchanger are connected via piping through which the heat medium flows.
  • the heat source side heat exchanger, the intermediate heat exchanger, and the use side heat exchanger are formed in separate bodies respectively and adapted to be disposed at separate locations one another.
  • a temperature sensor is installed in the heat medium circulation circuit and there is provided an anti-freezing operation mode in which when a detection temperature of the temperature sensor becomes equal to or lower than a set temperature while the compressor or the pump is stopped, anti-freezing operation of the heat medium is performed.
  • the pump of the heat medium circulation circuit corresponding to the temperature sensor that detected a temperature equal to or lower than a set temperature was made to operate and the heat medium is made to circulate using the heat medium circulation circuit, for example.
  • the air-conditioning apparatus is safe since the problem of refrigerant leakage into the room like the air-conditioning apparatus such as the multiple air conditioner for buildings doesn't occur because no HFC refrigerant is transferred into the indoor unit.
  • the water circulation path is shorter than the air-conditioning apparatus such as a chiller, enabling carrying power of the heat medium such as water to be reduced to achieve energy saving. Further, an anti-freezing operation mode is provided in which anti-freezing operation of the heat medium is performed, therefore, the air-conditioning apparatus having improved reliability can be obtained.
  • FIG. 1 is an entire configuration diagram of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 2 is another entire configuration diagram of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 3 is a circuit diagram for a refrigerant and a heat medium of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 4 is a circuit diagram showing the refrigerant and the heat medium flow at the time of cooling only operation.
  • FIG. 5 is a circuit diagram showing the refrigerant and the heat medium flow at the time of heating only operation.
  • FIG. 6 is a circuit diagram showing the refrigerant and the heat medium flow at the time of cooling-main operation.
  • FIG. 7 is a circuit diagram showing the refrigerant and the heat medium flow at the time of heating-main operation.
  • FIG. 8 is a first circuit diagram showing the refrigerant and the heat medium flow at the time of anti-freezing operation.
  • FIG. 9 is a second circuit diagram showing the refrigerant and the heat medium flow at the time of anti-freezing operation.
  • FIG. 10 is a third circuit diagram showing the refrigerant and the heat medium flow at the time of anti-freezing operation.
  • FIG. 11 is a fourth circuit diagram showing the refrigerant and the heat medium flow at the time of anti-freezing operation.
  • FIG. 12 is a fifth circuit diagram showing the refrigerant and the heat medium flow at the time of anti-freezing operation.
  • FIG. 13 is a first flow chart showing the operation of anti-freezing operation mode.
  • FIG. 14 is a second flow chart showing the operation of anti-freezing operation mode.
  • FIG. 15 is a third flow chart showing the operation of anti-freezing operation mode.
  • FIG. 16 is a fourth flow chart showing the operation of anti-freezing operation mode.
  • FIG. 17 is a fifth flow chart showing the operation of anti-freezing operation mode.
  • FIGS. 1 and 2 are an entire configuration diagram of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the air-conditioning apparatus includes a heat source apparatus (outdoor unit) 1 , an indoor unit 2 subjected to air conditioning of indoors, and a relay unit 3 that is separated from the outdoor unit 1 to be disposed in a non-air-conditioning space 8 or the like.
  • the heat source apparatus 1 and the relay unit 3 are connected by a refrigerant pipeline 4 in which a refrigerant subjected to two-phase transition or a refrigerant (a primary medium) under a supercritical state flows.
  • the relay unit 3 and the indoor unit 2 are connected by a pipeline 5 in which a heat medium (a secondary medium) such as water, brine, or anti-freezing liquid flows.
  • a heat medium such as water, brine, or anti-freezing liquid flows.
  • the relay unit 3 exchanges heat between the refrigerant transferred from the heat source apparatus 1 and the heat medium transferred from the indoor unit 2 .
  • the heat source apparatus 1 is usually disposed in an outdoor space 6 , which is an external space of structures such as building 9 .
  • the indoor unit 2 is disposed at a position capable of carrying heated or cooled air to an indoor space 7 such as a living room inside of structures such as building 9 .
  • the relay unit 3 is housed in a different housing from the heat source apparatus 1 and the indoor unit 2 , being connected to them by the refrigerant pipeline 4 and the heat medium pipeline 5 of the heat medium, and being adapted to be capable of being disposed at a different location from the outdoor space 6 and the indoor space 7 .
  • the relay unit 3 is inside the building 9 , however, being disposed in a non-air-conditioning space 8 such as under the roof, which is a different space from the indoor space 7 .
  • the relay unit 3 can be disposed in a common use space having an elevator or the like.
  • the heat source apparatus. 1 and the relay unit 3 are configured so as to be connected using two refrigerant pipelines 4 .
  • the relay unit 3 and each indoor unit 2 are connected using two heat medium pipelines 5 respectively. Connection using two pipelines facilitates the construction of the air-conditioning apparatus.
  • FIG. 2 shows a case where a plurality of relay units 3 are provided. That is, the relay unit 3 is divided into one main relay unit 3 a and two sub relay units 3 b ( 1 ) and 3 b ( 2 ) derived therefrom. Accordingly, a plurality of sub relay units 3 b can be connected with one main relay unit 3 a . In this configuration, there are three connection pipelines between the main relay unit 3 a and the sub relay units 3 b.
  • the indoor unit 2 is shown with a ceiling cassette type being an example, however, it is not limited thereto. Any type such as a ceiling-concealed type and a ceiling-suspended type will be allowable as long as heated or cooled air can be blown out into the indoor space 7 directly or through a duct or the like.
  • the heat source apparatus 1 is explained with the case of being disposed in the outdoor space 6 outside the building 9 as an example, however, it is not limited thereto.
  • the heat source apparatus 1 may be disposed in a surrounded space such as a machine room with a ventilating opening.
  • the heat source apparatus 1 may be disposed inside the building 9 to discharge exhaust heat to outside of the building 9 through an exhaust duct.
  • a water-cooled type heat source apparatus may be employed to be disposed in the building 9 .
  • the relay unit 3 may be disposed near the heat source apparatus 1 . However, when the distance from the relay unit 3 to the indoor unit 2 is too long, since the carrying power of the heat medium becomes large, the energy-saving effect is made to be weakened.
  • FIG. 3 is a circuit diagram for the refrigerant and the heat medium of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the air-conditioning apparatus as shown in FIG. 3 , has a heat source apparatus 1 , an indoor unit 2 , and a relay unit 3 .
  • the heat source apparatus 1 includes a compressor 10 , a four-way valve 11 , a heat source side heat exchanger 12 , check valves 13 a , 13 b , 13 c and 13 d , and an accumulator 17 .
  • the indoor unit 2 includes use side heat exchangers 26 a to 26 d .
  • the relay unit 3 includes a main relay unit 3 a and a sub relay unit 3 b .
  • the main relay unit 3 a includes a gas-liquid separator 14 to separate a gas phase and a liquid phase of the refrigerant and an expansion valve 16 e (an electronic expansion valve, for example).
  • the sub relay unit 3 b includes intermediate heat exchangers 15 a and 15 b , expansion valves (electronic expansion valves, for example) 16 a to 16 d , pumps 21 a and 21 b , and flow path switching valves 22 a to 22 d and 23 a to 23 d such as a three-way valve.
  • the flow path switching valves are installed at inlet side flow paths and outlet side flow paths of each use side heat exchanger 26 a to 26 d , correspondingly.
  • the flow path switching valves 22 a to 22 d switch outlet side flow paths among plurally disposed intermediate heat exchangers.
  • the flow path switching valves 23 a to 23 d switch inlet side flow paths thereof.
  • the flow path switching valves 22 a to 22 d perform the operation to switch outlet side flow paths between the intermediate heat exchangers 15 a and 15 b
  • the flow path switching valves 23 a to 23 d perform the operation to switch inlet side flow paths between the intermediate heat exchangers 15 a and 15 b.
  • stop valves 24 a to 24 d are provided, and at outlet sides of the use side heat exchangers 26 a to 26 d , flow amount adjustment valves 25 a to 25 d are provided, respectively.
  • the inlet side and the outlet side of each use side heat exchanger 26 a to 26 d are connected by bypasses 27 a to 27 d via the flow amount: adjustment valves 25 a to 25 d.
  • the sub relay unit 3 b further includes temperature sensors and pressure sensors as follows:
  • thermometers temperature sensors and pressure sensors can employ a variety of thermometers, temperature sensors, pressure gauge, and pressure sensors.
  • the compressor 10 , the four-way valve 11 , the heat source side heat exchanger 12 , the check valves 13 a , 13 b , 13 c and 13 d , the gas-liquid separator 14 , the expansion valves 16 a to 16 e , the intermediate heat exchangers 15 a and 15 b , and the accumulator 17 configure a refrigeration cycle.
  • the intermediate heat exchanger 15 a , the pump 21 a , the flow path switching valves 22 a to 22 d , the stop valves 24 a to 24 d , the use side heat exchangers 26 a to 26 d , the flow amount adjustment valves 25 a to 25 d , and the flow path switching valves 23 a to 23 d configure a heat medium circulation circuit.
  • the intermediate heat exchanger 15 b , the pump 21 b , the flow path switching valves 22 a to 22 d , the stop valves 24 a to 24 d , the use side heat exchangers 26 a to 26 d , the flow amount adjustment valves 25 a to 25 d , and the flow path switching valves 23 a to 23 d configure a heat-medium circulation circuit.
  • each of use side heat exchangers 26 a to 26 d is provided with the intermediate heat exchangers 15 a and 15 b in parallel in plural, each configuring the heat medium circulation circuit.
  • a controller 100 that controls equipment constituting thereof to make the heat source apparatus 1 perform operations as, what is called, an outdoor unit.
  • a controller 300 is provided that controls equipment constituting thereof and has means to perform operations to be mentioned later.
  • These controllers 100 and 300 are composed of such as microcomputers to be communicably connected with each other. Next, operations of each operation mode of the above air-conditioning apparatus will be explained.
  • FIG. 4 is a circuit diagram showing a refrigerant and a heat medium flow at the time of cooling only operation.
  • the refrigerant is compressed by the compressor 10 , turned into a high-temperature high-pressure gas refrigerant to enter the heat source side heat exchanger 12 via the four-way valve 11 .
  • the refrigerant is condensed and liquefied there, passes through the check valve 13 a , and flowed out of the heat source apparatus 1 to flow into the relay unit 3 via the refrigerant pipeline 4 .
  • the refrigerant enters the gas-liquid separator 14 to be guided into the intermediate heat exchanger 15 b via the expansion valves 16 e and 16 a .
  • the refrigerant is expanded by the expansion valve 16 a to turn into a low-temperature low-pressure two-phase refrigerant and the intermediate heat exchanger 15 b operates as an evaporator.
  • the refrigerant turns into a low-temperature low-pressure gas refrigerant in the intermediate heat exchanger 15 b and flows out of the relay unit 3 via the expansion valve 16 c to flow into the heat source apparatus 1 again via the refrigerant pipeline 4 .
  • the refrigerant passes through the check valve 13 d to be sucked into the compressor 10 via the four-way valve 11 and the accumulator 17 .
  • the expansion valves 16 b and 16 d have an opening-degree small enough for the refrigerant not to flow and the expansion valve 16 c is made to be a full-open state so as not to cause a pressure loss.
  • the secondary side heat medium water, anti-freezing liquid, etc.
  • the intermediate heat exchanger 15 b cooling energy of the refrigerant on the primary side is transferred to the heat medium on the secondary side, and cooled heat medium is made to flow in the secondary side piping by the pump 21 b .
  • the heat medium flowed out of the pump 21 b passes through the stop valves 24 a to 24 d via the flow path switching valves 22 a to 22 d to flow into the use side heat exchangers 26 a to 26 d and the flow amount adjustment valves 25 a to 25 d .
  • the air-conditioning load required indoors can be covered by controlling the flow amount of the heat medium passing through the use side heat exchangers 26 a to 26 d so that a difference between the detection temperatures of the third temperature sensors 33 a to 33 d and the fourth temperature sensors 34 a to 34 d is maintained at a predetermined target value by the controller 300 . It will be the same in the case of heating only operation, cooling-main operation, and heating-main operation.
  • FIG. 5 is a circuit diagram showing a refrigerant and a heat medium flows at the time of heating only operation.
  • the refrigerant is compressed by the compressor 10 , turns into a high-temperature high-pressure gas refrigerant, passes through the check valve 13 b via the four-way valve 11 , and flows out of the heat source apparatus 1 via the check valve 13 b to flow into the relay unit 3 via the refrigerant pipeline 4 .
  • the refrigerant is guided into the intermediate heat exchanger 15 a through the gas-liquid separator 14 , condensed and liquefied in the intermediate heat exchanger 15 a to flow out of the relay unit 3 through the expansion valves 16 d and 16 b .
  • the refrigerant is expanded by the expansion valve 16 b , turned into a low-temperature low-pressure two-phase refrigerant, and flows into the heat source apparatus 1 again through the refrigerant pipeline 4 .
  • the refrigerant is guided into the heat source side heat exchanger 12 through the check valve 13 c and the heat source side heat exchanger 12 operates as an evaporator.
  • the refrigerant turns into a low-temperature low-pressure gas refrigerant there to be sucked into the compressor 10 via the four-way valve 11 and the accumulator 17 .
  • the expansion valve 16 e and the expansion valve 16 a or 16 c are made to have a small opening-degree so that no refrigerant flows therethrough.
  • the secondary side heat medium water, anti-freezing liquid, etc.
  • heating energy of the primary side refrigerant is transferred to the secondary side heat medium and the heated heat medium is made to flow in the secondary side piping by the pump 21 a .
  • the heat medium flowed out of the pump 21 a passes through the stop valves 24 a to 24 d via the flow path switching valves 22 a to 22 d to flow into the use side heat exchangers 26 a to 26 d and the flow amount adjustment valves 25 a to 25 d .
  • the heat medium passing through the bypasses 27 a to 27 d merges with the heat medium passing through the use side heat exchangers 26 a to 26 d , passes through the flow path switching valves 23 a to 23 d , and flows into the intermediate heat exchanger 15 a to be sucked again into the pump 21 a .
  • the air-conditioning load required indoors can be covered by controlling a difference between the detection temperatures of the third temperature sensors 33 a to 33 d and the fourth temperature sensors 34 a to 34 d to maintain a target value in advance.
  • the flow path is closed by the stop valves 24 a to 24 d and the heat medium is made not to flow into the use side heat exchanger.
  • the heat medium is made to flow because of a air-conditioning load
  • the use side heat exchangers 26 c and 26 d there is no air-conditioning load and corresponding stop valves 24 c and 24 d are closed.
  • FIG. 6 is a circuit diagram showing a refrigerant and a heat medium flow at the time of cooling-main operation.
  • the refrigerant is compressed by the compressor 10 , turned into a high-temperature high-pressure gas refrigerant to be guided into the heat source side heat exchanger 12 via the four-way valve 11 .
  • the gas-state refrigerant is condensed to turn into a two-phase refrigerant, flows out of the heat source side heat exchanger 12 in the two-phase state, flows out of the heat source apparatus 1 via the check valve 13 a , and flows into the relay unit 3 via the refrigerant pipeline 4 .
  • the refrigerant enters the gas-liquid separator 14 and a gas refrigerant and a liquid refrigerant in the two-phase refrigerant are separated.
  • the gas refrigerant is guided into the intermediate heat exchanger 15 a , condensed and liquefied therein to pass through the expansion valve 16 d .
  • the liquid refrigerant separated in the gas-liquid separator 14 is flowed to the expansion valve 16 e , joined with the liquid refrigerant condensed and liquefied in the intermediate heat exchanger 15 a and passing through the expansion valve 16 d , and guided to the intermediate heat exchanger 15 b via the expansion valve 16 a .
  • the refrigerant is expanded by the expansion valve 16 a to turn into a low-temperature low-pressure two-phase refrigerant and the intermediate heat exchanger 15 b operates as an evaporator.
  • the refrigerant turns into a low-temperature low-pressure gas refrigerant in the intermediate heat exchanger 15 b and flows out of the relay unit 3 via the expansion valve 16 c to flow into the heat source apparatus 1 again via the refrigerant pipeline 4 .
  • the refrigerant passes through the check valve 13 d to be sucked into the compressor 10 via the four-way valve 11 and the accumulator 17 .
  • the expansion valves 16 b has an opening-degree small enough for the refrigerant not to flow and the expansion valve 16 c is made to be a full open state so as not to cause a pressure loss.
  • the secondary side heat medium water, anti-freezing liquid, etc.
  • heating energy of the refrigerant on the primary side is transferred to the heat medium on the secondary side, and heated heat medium is made to flow in the secondary side piping by the pump 21 a .
  • cooling energy of the refrigerant on the primary side is transferred to the heat medium on the secondary side, and cooled heat medium is made to flow in the secondary side piping by the pump 21 b .
  • the heat medium flowed out of the pumps 21 a and 21 b passes through the stop valves 24 a to 24 d via the flow path switching valves 22 a to 22 d to flow into the use side heat exchangers 26 a to 26 d and the flow amount adjustment valves 25 a to 25 d . Then, through the operation of the flow amount adjustment valves 25 a to 25 d , only the heat medium having a flow amount necessary to cover the air-conditioning load required indoors is made to flow into the use side heat exchangers 26 a to 26 d , and the remaining passes through the bypasses 27 a to 27 d to make no contribution to heat exchange.
  • the heat medium passing through the bypasses 27 a to 27 d merges with the heat medium passing through the use side heat exchangers 26 a to 26 d , and passes through the flow path switching valves 23 a to 23 d .
  • the heated heat medium flows into the intermediate heat exchanger 15 a to return to the pump 21 a again, and the cooled heat medium flows into the intermediate heat exchanger 15 b to return to the pump 21 b again, respectively. Meanwhile, the heated heat medium and the cooled heat medium are guided to the use side heat exchangers 26 a to 26 d having the heating load and the cooling load, respectively, without being mixed through the operation of the flow path switching valves 22 a to 22 d and 23 a to 23 d .
  • the air-conditioning load required indoors can be covered by controlling a difference between the detection temperatures of the third temperature sensors 33 a to 33 d and the fourth temperature sensors 34 a to 34 d to maintain a target value.
  • FIG. 6 shows a state in which a heating load is generated in the use side heat exchanger 26 a and a cooling load is generated in the use side heat exchanger 26 b , respectively.
  • the flow path is closed by the stop valves 24 a to 24 d and the heat medium is made not to flow into the use side heat exchanger.
  • the heat medium is made to flow because of a air-conditioning load
  • the use side heat exchangers 26 c and 26 d there is no air-conditioning load and corresponding stop valves 24 c and 24 d are closed.
  • FIG. 7 is a circuit diagram showing a refrigerant and heat medium flow at the time of heating-main operation.
  • the refrigerant is compressed by the compressor 10 , turns into a high-temperature high-pressure gas refrigerant, passes through the check valve 13 b via the four-way valve 11 , and flows out of the heat source apparatus 1 to flow into the relay unit 3 via the refrigerant pipeline 4 .
  • the refrigerant is introduced into the intermediate heat exchanger 15 a through the gas-liquid separator 14 , and condensed and liquefied in the intermediate heat exchanger 15 a .
  • the refrigerant passing through the expansion valve 16 d is branched into flow paths through the expansion valves 16 a and 16 b .
  • the refrigerant passing through the expansion valve 16 a is expanded by the expansion valve 16 a to turn into a low-temperature low-pressure two-phase refrigerant and flows into the intermediate heat exchanger 15 b .
  • the intermediate heat exchanger 15 b operates as an evaporator.
  • the refrigerant flowed out of the intermediate heat exchanger 15 b evaporates to turn into a gas refrigerant and passes through the expansion valve 16 c .
  • the refrigerant passing through the expansion valve 16 b is expanded by the expansion valve 16 b to turn into a low-temperature low-pressure two-phase refrigerant, and merges with the refrigerant passing through the intermediate heat exchanger 15 b and the expansion valve 16 c to turn into a low-temperature low-pressure refrigerant having larger dryness. Then, the merged refrigerant flows out of the relay unit 3 to flow into the heat source apparatus 1 again through the refrigerant pipeline 4 . In the heat source apparatus 1 , the refrigerant passes through the check valve 13 c to be guided into the heat source side heat exchanger 12 .
  • the heat source side heat exchanger 12 operates as an evaporator.
  • the low-temperature low-pressure two-phase refrigerant is evaporated into a gas refrigerant and sucked into the compressor 10 via the four-way valve 11 and the accumulator 17 .
  • the expansion valve 16 e is made to have a small opening-degree so that no refrigerant flows.
  • the secondary side heat medium water, anti-freezing liquid, etc.
  • heating energy of the primary side refrigerant is transferred to the secondary side heat medium and the heated heat medium is made to flow in the secondary side piping by the pump 21 a .
  • cooling energy of the primary side refrigerant is transferred to the secondary side heat medium and the cooled heat medium is made to flow in the secondary side piping by the pump 21 b .
  • the heat medium flowed out of the pumps 21 a and 21 b passes through the stop valves 24 a to 24 d via the flow path switching valves 22 a to 22 d to flow into the use side heat exchangers 26 a to 26 d and flow amount adjustment valves 25 a to 25 d .
  • the flow amount adjustment valves 25 a to 25 d only the heat medium having a flow amount necessary to cover the air-conditioning load required indoors is made to flow into the use side heat exchangers 26 a to 26 d , and the remaining passes through the bypasses 27 a to 27 d to make no contribution to heat exchange.
  • the heat medium passing through the bypasses 27 a to 27 d merges with the heat medium passing through the use side heat exchangers 26 a to 26 d , passes through the flow path switching valves 23 a to 23 d .
  • the heated heat medium flows into the intermediate heat exchanger 15 a to return to the pump 21 a again, and the cooled heat medium flows into the intermediate heat exchanger 15 b to return to the pump 21 b again.
  • the heated heat medium and the cooled heating medium are guided to the use side heat exchangers 26 a to 26 d having the heating load and the cooling load, respectively, without being mixed through the operation of the flow path switching valves 22 a to 22 d and 23 a to 23 d .
  • the air-conditioning load required indoors can be covered by controlling a difference between the detection temperatures of the third temperature sensors 33 a to 33 d and the fourth temperature sensors 34 a to 34 d to maintain a target value.
  • FIG. 7 shows a state in which a heating load is generated in the use side heat exchanger 26 a and a cooling load is generated in the use side heat exchanger 26 b , respectively.
  • the flow path is closed by the stop valves 24 a to 24 d and the heat medium is made not to flow into the use side heat exchanger.
  • the heat medium is made to flow because of a air-conditioning load
  • the use side heat exchangers 26 c and 26 d there is no air-conditioning load and corresponding stop valves 24 c and 24 d are closed.
  • heating operation and cooling operation can be freely performed in each indoor unit 2 by switching the corresponding flow path switching valves 22 a to 22 d and 23 a to 23 d to the flow path connected to the heating intermediate heat exchanger 15 a when heating load is generated in the use side heat exchangers 26 a to 26 d , and by switching the corresponding flow path switching valves 22 a to 22 d and 23 a to 23 d to the flow path connected to the cooling intermediate heat exchanger 15 b when cooling load is generated in the use side heat exchangers 26 a to 26 d.
  • the flow path switching valves 22 a to 22 d and 23 a to 23 d may be any that can switch flow paths such as a combination of a three-way valve to switch three-way flow paths arid a stop valve to open/close two-way flow paths.
  • the flow path switching valve may be configured by a combination of a stepping-motor-driven mixing valve to change the flow amount of three-way flow paths and an electronic expansion valve to change the flow amount of two-way flow paths. In that case, water hammer can be prevented by a sudden opening/closing of the flow path.
  • the air-conditioning load in the use side heat exchangers 26 a to 26 d is expressed by formula 1, being obtained by multiplying the flow rate, the density, the constant pressure specific heat of the heat medium and the difference in temperature of the heat medium at the inlet and at the outlet of the use side heat exchangers 26 a to 26 d .
  • Vw denotes the flow amount of the heat medium
  • ⁇ w the density of the heat medium
  • Cpw the constant pressure specific heat of the heat medium
  • Tw the temperature of the heat medium
  • suffix “in” the value at the inlet of the heat medium of the use side heat exchangers 26 a to 26 d
  • suffix “out” the value at the outlet of the heat medium of the use side heat exchangers 26 a to 26 d , respectively.
  • the temperature difference at the inlet and outlet of the use side heat exchanger 26 a to 26 d is set to be a temporary target and it is possible to flow surplus heat medium to the bypasses 27 a to 27 d to control the flow amount that follows to the use side heat exchangers 26 a to 26 d by controlling the flow amount adjustment valves 25 a to 25 d so that the temporary target approaches a predetermined target value.
  • the target value of the temperature difference at the inlet and outlet of the use side heat exchangers 26 a to 26 d may be set at, for example, 5 degrees C.
  • Twin and Twout denote the heat medium temperatures at the inlet and the outlet of the use side heat exchangers 26 a to 26 d , Vw the flow amount of the heat medium flowing into the flow amount adjustment valves 25 a to 25 d , Vwr the flow amount of the heat medium flowing into the use side heat exchangers 26 a to 26 d , Tw the temperature of heat medium after the heat medium flowing through the use side heat exchangers 26 a to 26 d and the heat medium flowing through the bypasses 27 a to 27 d are merged.
  • T w ( V wr /V w )* T wout +(1 ⁇ V wr /V w )* T win (2)
  • the temperature difference between the heat media approaches the inlet temperature of the use side heat exchangers 26 a to 26 d by the flow amount that is bypassed.
  • the temperature after merging becomes 10 degrees C. by formula (2).
  • the heat medium having the temperature after the merging returns from each indoor unit to merge and flows into the intermediate heat exchangers 15 a and 15 b . Then, unless the heat exchange amount of the intermediate heat exchanger 15 a or 15 b changes, the temperature difference between the inlet and outlet becomes almost the same through the heat exchange in the intermediate heat exchanger 15 a or 15 b .
  • the temperature difference between the inlet and outlet of the intermediate heat exchanger 15 a or 15 b is 6 degrees C.
  • the inlet temperature of the intermediate heat exchanger 15 a or 15 b is 13 degrees C. and the outlet temperature is 7 degrees C.
  • the air-conditioning load in the use side heat exchangers 26 a to 26 d is lowered and the inlet temperature of the intermediate heat exchanger 15 a or 15 b decreases to 10 degrees C. Then, if nothing be done, since the intermediate heat exchanger 15 a or 15 b performs heat exchange of almost the same amount, the heat medium flows out of the intermediate heat exchanger 15 a or 15 b at 4 degrees C. The above is repeated and the temperature of the heat medium rapidly decreases.
  • the rotation speed of the pumps 21 a and 21 b may be changed according to changes in the air-conditioning load of the use side heat exchangers 26 a to 26 d so that the heat medium outlet temperature of the intermediate heat exchanger 15 a or 15 b approaches a target value.
  • the rotation speed of the pump decreases to achieve energy-saving.
  • the rotation speed of the pump increases to cover the air-conditioning load.
  • the pump 21 b operates when cooling load or dehumidifying load occurs in any of the use side heat exchangers 26 a to 26 d , and is stopped when there is neither cooling load nor dehumidifying load in each use side heat exchangers 26 a to 26 d .
  • the pump 21 a operates when the heating load occurs in any of the use side heat exchangers 26 a to 26 d , and is stopped when there is no heating load in any of use side heat exchangers 26 a to 26 d.
  • the heat medium flow path at ‘the secondary side from the intermediate heat exchangers 15 a and 15 b to the use side heat exchangers 26 a to 26 d is in general disposed inside of the building and is usually maintained at a hi g her temperature than a freezing temperature of the heat medium, 0 degree C. in the case of water, for example.
  • the heat medium flow path may he cooled to reach the refrigeration temperature. Accordingly, an anti-freezing operation is required that prevents the heat medium from freezing. Descriptions will be given to the heat medium anti-freezing operation (anti-freezing operation mode).
  • the anti-freezing operation is performed through the operation of heat medium anti-freezing operation means of the controller 300 .
  • the controller 300 performs the anti-freezing operation when the detection temperature of any of the first temperature sensors 31 a and 31 b , the second temperature sensors 32 a and 32 b , the third temperature sensors 33 a to 33 b , and the fourth temperature sensors 34 a to 34 d becomes equal to or lower than a predetermined set temperature.
  • the temperature of the whole heat medium flow path can be made uniform by making the pump 21 a or 21 b to operate to circulate the heat medium and agitating the heat medium in the heat medium piping to rise the temperature of the heat medium at the part where the temperature has decreased and prevent freezing.
  • the pump 21 a or 21 b It depends on which of the above-mentioned detection temperature detection means has detected equal to or lower than the set temperature to operate either the pump 21 a or 21 b . That is, when either the first temperature sensor 31 a or the second temperature sensor 32 a detects equal to or lower than the set temperature, the pump 21 a is made to operate. When either the first temperature sensor 31 b or the second temperature sensor 32 b detects equal to or lower than the set temperature, the pump 21 b is made to operate.
  • the flow path switching valves 22 a to 22 d are explained as the flow path switching valve 22 , the flow path switching valves 23 a to 23 d as the flow path switching valve 23 , the stop valves 24 a to 24 d as the stop valve 24 , the flow amount adjustment valves 25 a to 25 d as the flow amount adjustment valve 25 , the bypasses 27 a to 27 d as the bypass 27 , the third temperature sensors 33 a to 33 d as the third temperature sensor 33 ,and the fourth temperature sensors 34 a to 34 d as the fourth temperature sensor 34 .
  • the controller 300 After the processing starts (STO), the controller 300 operates the pump 21 a (ST 5 ) when the first temperature sensor 31 a or the second temperature sensor 32 a detects the temperature equal to or lower than the set temperature Ts (ST 1 , ST 2 ).
  • the controller 300 operates the pump 21 b (ST 6 ) when the first temperature sensor 31 b or the second temperature sensor 32 b detects the temperature equal to or lower than the set temperature Ts (ST 3 , ST 4 ).
  • the flow path switching valve 22 corresponding to the use side heat exchanger 26 a of the first indoor unit ( 1 ) is switched to the heating intermediate heat exchanger 15 a , the flow path switching valve 23 to the cooling intermediate heat exchanger 15 b , for example.
  • the flow path switching valve 22 corresponding to the use side heat exchanger 26 b of the second indoor unit ( 2 ) is switched to the cooling intermediate heat exchanger 15 b , the flow path switching valve 23 to the heating intermediate heat exchanger 15 a , for example (ST 7 ).
  • the stop valve 24 of the use side heat exchangers 26 a and 26 b is made to be open and the flow amount adjustment valve 25 is made to be full open to the bypass 27 side.
  • the detection temperatures of the third temperature sensor 33 and the fourth temperature sensor 34 corresponding to each unit are searched in order (ST 9 , ST 15 , ST 16 ).
  • the pump 21 a or 21 b is made to operate (ST 12 ).
  • the flow path switching valve 22 of the n-th indoor unit (n) that detected the temperature equal to or lower than the set temperature is switched to the heating intermediate heat exchanger 15 a , and the flow path switching valve 23 to the cooling intermediate heat exchanger 15 b .
  • the flow path switching valve 22 of the (n+1)-th indoor unit (n+1) is switched to the cooling intermediate heat exchanger 15 b , and the flow path switching valve 23 to the heating intermediate heat exchanger 15 a (ST 13 ).
  • the stop valve 24 of the indoor units (n) and (n+1) is made to be open and the flow amount adjustment valve 25 of the indoor unit (n) is made to be full open at the use side heat exchanger 26 side (ST 14 ).
  • the above-mentioned heat medium anti-freezing operation mode is a method of performing anti-freezing by making the heat medium to circulate with use of the pumps 21 a and 21 b and agitating the heat medium in the flow path to make the temperature uniform.
  • this method since no heat medium is heated, the heat medium gets refrigerated eventually when the heat medium flow path continues to be cooled.
  • each temperature sensor detects the temperature equal to or lower than the set temperature
  • the compressor 10 is made to operate, the four-way valve 11 is switched to the heating side, the high-temperature high-pressure refrigerant is introduced into the intermediate heat exchanger 15 a or 15 b corresponding to the temperature sensor that detected the temperature equal to or lower than the set temperature, and anti-freezing is performed by heating the heat medium to rise the temperature.
  • any of the third temperature sensors 33 a to 33 d or the fourth temperature sensors 34 a to 34 d detect the temperature equal to or lower than the set temperature, either the pump 21 a or 21 b is operated and the heat medium is circulated in the intermediate heat exchanger 15 a or 15 b corresponding thereto.
  • the compressor 10 is made to operate, the four-way valve is switched to the heating side, a high-temperature high-pressure refrigerant is guided into the intermediate heat exchanger 15 a or 15 b where the heat medium circulates, the heat medium is heated to increase temperature, and the heated heat medium having a increased temperature is made to circulate in the use side heat exchangers 26 a to 26 d corresponding to the temperature sensor that detected the temperature equal to or lower than the set temperature by switching the flow path switching valves 22 a to 22 d and 23 a to 23 d to perform anti-freezing operation.
  • the intermediate heat exchanger is divided into a heating intermediate heat exchanger 15 a and a cooling intermediate heat exchanger 15 b .
  • a first temperature sensor 31 b or a second temperature sensor 32 b detects a temperature equal to or lower than the set temperature, a high-temperature high-pressure refrigerant cannot directly be guided into the cooling intermediate heat exchanger 15 b.
  • the refrigeration cycle is operated such that a high-temperature high-pressure refrigerant is made to circulate in the heating intermediate heat exchanger 15 a .
  • the flow path switching valves 22 a to 22 d corresponding to the use side heat exchanger (here, 26 a ) as a part of the use side heat exchangers 26 a to 26 d are switched so as to be connected with the intermediate heat exchanger 15 a
  • the flow path switching valves 23 a to 23 d are switched so as to be connected with the intermediate heat exchanger 15 b .
  • the flow path switching valves 22 a to 22 d corresponding to another use side heat exchanger are switched so as to be connected with the intermediate heat exchanger 15 b
  • flow path switching valves 23 a to 23 d are switched so as to be connected with the intermediate heat exchanger 15 a .
  • the pumps 21 a and 21 b are operated and the heat medium heated by the intermediate heat exchanger 15 a is made to circulate in the cooling intermediate heat exchanger 15 b .
  • the flow path switching valve 22 a is switched to the outlet side of the heating intermediate heat exchanger 15 a , the flow path switching valve 23 a to the inlet side of the cooling intermediate heat exchanger 15 b , the flow path switching valve 22 b to the outlet side of the cooling intermediate heat exchanger 15 b , the flow path switching valve 23 b to the inlet side of the heating intermediate heat exchanger 15 a , and the heat medium is made to circulate between the intermediate heat exchangers 15 a and 15 b.
  • FIG. 14 is a flow chart illustrating an operation of the above. Since from RT 0 to RT 17 in FIG. 14 are the same as from ST 0 to ST 17 in FIG. 13 and regarding the circulation of the heat medium, it is the same as what is explained in the above, descriptions is omitted.
  • the compressor 10 is made to operate, the four-way valve 11 is switched to the heating side, a step (RT 20 ) is added to guide a high-temperature high-pressure refrigerant to the heating intermediate heat exchanger 15 a . While heating the heating intermediate heat exchanger 15 a by the refrigerant, the heat medium heated by the refrigerant is made to circulate. Then the temperature of the heat medium is increased and freezing can be prevented.
  • RT 18 the set temperature detection means
  • a valve is used having a structure allowing to set at an opening-degree in the midway between full open and full close such as a stepping motor type.
  • the refrigeration cycle is operated so that a high-temperature high-pressure refrigerant is circulated in the heating intermediate heat exchanger 15 a .
  • the pumps 21 a and 21 b are operated.
  • the heat medium flow path switching valves 22 a and 22 d corresponding to part of the use side heat exchangers 26 a to 26 d are set at a midway opening-degree that both of two paths, the heat medium flow path for heating and the heat medium flow path for cooling, are neither full open nor completely closed.
  • the heat medium heated by the intermediate heat exchanger 15 a and the heat medium passing through the cooling intermediate heat exchanger 15 b are mixed.
  • the heat medium flow path switching valves 23 a to 23 d are set at a midway opening-degree that the flow path is neither full open nor completely closed, as well.
  • the heat medium mixed in the flow path switching valves 22 a to 22 d is adapted to be distributed into the intermediate heat exchanger 15 a and the intermediate heat exchanger 15 b .
  • the heat medium flowing into the intermediate heat exchanger 15 b gets to be a higher temperature than the heat medium prior to mixing by the heat amount of the heat medium heated by the intermediate heat exchanger 15 a , therefore, freezing of the heat medium can be prevented in the intermediate heat exchanger 15 b.
  • the control of the above-mentioned configuration is shown at a flow chart in FIG. 15 .
  • the heat medium flow path switching valves 22 and 23 those that can set at an intermediate opening-degree between full open and full close by a stepping motor or the like will be used.
  • the controller 300 After the processing starts (GT 0 ), when the detection temperature of the first temperature sensor 31 a or the second temperature sensor 32 a corresponding to the intermediate heat exchanger 15 a or the detection temperature of the first temperature sensor 31 b or the second temperature sensor 32 b corresponding to the intermediate heat exchanger 15 b is detected to be equal to or lower than the set temperature Ts (GT 1 to GT 4 ), the controller 300 operates the pumps 21 a and 21 b (GT 5 ). Then, the flow path switching valves 22 and 23 of a first indoor unit 1 arc set at an intermediate opening (GT 6 ), for example, and the stop valve 24 of the first indoor unit 1 is made to be open and the flow amount adjustment valve 25 is made to be full open at the bypass 27 side (GT 7 ).
  • the detection temperatures of the third temperature sensor 33 and the fourth temperature sensor 34 corresponding to each unit are searched in order (ST 9 , ST 15 , ST 16 ).
  • the pumps 21 a and 21 b are made to operate (ST 11 ).
  • the flow path switching valves 22 and 23 of the indoor unit (n) that detected the temperature equal to or lower than the set temperature Ts is set at an intermediate opening-degree (GT 12 ), the stop valve 24 of the indoor unit (n) is made to be open, and the flow amount adjustment valve 25 is made to be full open to the use side heat exchanger 26 side (GT 13 ).
  • the compressor 10 is made to operate, the four-way valve 11 is switched to the heating side, the high-temperature high-pressure refrigerant is introduced into the intermediate heat exchanger 15 a or 15 b corresponding to the temperature sensor that detected the temperature equal to or lower than the set temperature, and the heat medium is heated to rise the temperature, so as to perform anti-freezing.
  • FIG. 16 is a flow chart illustrating this operation. Since from UT 0 to UT 16 in FIG. 16 are the same as from GT 0 to GT 16 in FIG. 15 and regarding the circulation of the heat medium it is the same as what is explained in the above, descriptions will be omitted.
  • the compressor 10 is operated, the four-way valve 11 is switched to the heating side, a step (UT 19 ) is added to guide a high-temperature high-pressure refrigerant to the heating intermediate heat exchanger 15 a . While heating the heating intermediate heat exchanger 15 a by the refrigerant, by circulating the heat medium, the temperature of the heat medium passing through the intermediate heat exchangers 15 a and 15 b is increased and freezing can be prevented.
  • the detection temperatures of all the temperature sensors become higher than the set temperature Ts (UT 16 ), the pumps 21 a and 21 b and the compressor 10 are stopped. (UT 17 )
  • FIG. 11 a flow path configuration of the heat medium as shown in FIG. 11 is effective.
  • the outlet side of the pump 21 b of the outlet side of the cooling intermediate heat exchanger 15 b and the inlet side of the heating intermediate heat exchanger 15 a are bypass-connected via a bypass stop valve 28 a
  • the outlet side of the pump 21 a of the outlet side of the heating intermediate heat exchanger 15 a and the inlet side of the cooling intermediate heat exchanger 15 b are bypass-connected via a bypass stop valve 28 b .
  • the controller 300 judges whether the detection temperatures of the first temperature sensor 31 a or the second temperature sensor 32 a related to the intermediate heat exchanger 15 a or the detection temperature of the first temperature sensor 31 b or the second temperature sensor 32 b related to the intermediate heat exchanger 15 b are equal to or lower than the set temperature Ts or not (HT 1 to HT 4 ).
  • the pumps 21 a and 21 b are operated (HT 5 )
  • the bypass stop valves 28 a and 28 b are made to be open (HT 6 )
  • the heat medium is made to circulate via the bypass between the intermediate heat exchangers 15 a and 15 b .
  • the circulation circuit thereof is shown by a thick line in the heat medium circuit of FIG. 11 .
  • the stop valve 24 of the indoor unit (n) is made to be open and the flow amount adjustment valve 25 is made to be full open to the use side heat exchanger 26 side (HT 12 ).
  • the bypass stop valves 28 a and 28 b are made to be close (HT 13 ).
  • a flow path is configured to make the heat medium to circulate to the use side heat exchangers 26 a to 26 d side.
  • HT 16 When the detection temperatures of all the above-mentioned temperature sensors become higher than the set temperature Is (HT 16 ), the pumps 21 a and 21 b are stopped (HT 17 ), and processing is terminated (HT 18 ). In HT 5 and HT 10 , either the pump 21 a or 21 b may be operated.
  • Ts is set at a temperature a little higher than a freezing temperature.
  • Ts may be set at 3 degrees C., a little higher than the freezing temperature 0 degree C.
  • a circulation flow path of the heat medium has to be secured before or at the same time as the pump 21 a or 21 b is operated. Therefore, in order to form a heat medium circulation circuit, after any or all of the stop valves 24 a to 24 d are made to be open state, and the flow amount adjustment valves 25 a to 25 d are controlled to the direction in which the flow path is secured, the pump 21 a or 21 b is made to operate so as to circulate the heat medium.
  • a two-way flow amount adjustment valve may be used as the flow amount adjustment valves 25 a to 25 d . Then, the stop valves 24 a to 24 d need not to be provided. After controlling the opening-degree of the flow amount adjustment valves 25 a to 25 d to secure the circulation flow path of the heat medium, the pumps 21 a to 21 d are operated.
  • temperature sensors are installed at the inlet and outlet of the intermediate heat exchangers 15 a and 15 b .
  • the temperature sensor may be installed either at the inlet or at the outlet.
  • the refrigerant may be a single refrigerant such as R-22 and R-134a, a pseudo-azeotropic mixture refrigerant such as R-410A and R-404A, an azeotropic mixture refrigerant such as R-407C, a refrigerant and its mixture that is regarded to have a smaller global warming potential such as CF 3 CF ⁇ CH 2 including a double bond in the chemical formula, or a natural refrigerant such as CO 2 and propane.
  • the refrigerant circuit is configured to contain an accumulator, a circuit having no accumulator is possible.
  • Descriptions are given to the case where there are the check valves 13 a to 13 d , however, they are not an indispensable component, the present invention can be configured by a circuit without them, and then the same operation and the same working effect can be achieved.
  • a fan should be attached to the heat source side heat exchanger 12 and the use side heat exchangers 26 a to 26 d and it is preferable to accelerate condensation or evaporation by blowing. It is not limited thereto, but as for the use side heat exchangers 26 a to 26 d , a panel heater utilizing radiation may be used. As for the heat source side heat exchanger 12 , a water-cooled type may be used that transfers heat by water and anti-freezing liquid. Any type can be used having a structure that can release or absorb heat.
  • a flow amount adjustment valve of a two-way flow path adjustment valve may be employed that can sequentially change the opening area by a stepping motor or the like as shown in FIG. 12 .
  • the control in this case is similar to the case of the three-way flow path adjustment valve.
  • the opening of the two-way flow path adjustment valves 25 a to 25 d is adjusted to control the flow amount to be flowed into the use side heat exchangers 26 a to 26 d so that the difference in temperature between the inlet and outlet of the use side heat exchangers 26 a to 26 d becomes a predetermined target value, for example, 5 degrees C.
  • the rotation speed of the pumps 21 a and 21 b may be controlled so that the inlet side or the outlet side temperature of the intermediate heat exchangers 15 a and 15 b becomes a predetermined target value.
  • the two-way flow path adjustment valve as the flow amount adjustment valves 25 a to 25 d , since it can he used for opening and closing the flow path, no stop valves 24 a to 24 d are required and low-cost system construction is enabled advantageously.
  • the flow amount adjustment valves 25 a to 25 d , the third temperature sensors 33 a to 33 d , the fourth temperature sensors 34 a to 34 d are installed inside of the relay unit 3 , however, it is not limited thereto. If they are installed near the use side heat exchangers 26 a to 26 d , that is, inside of or near the indoor unit 2 , there is no functional problem and the same operation and the same working effect can be achieved.
  • the third temperature sensors 33 a to 33 d and the fourth temperature sensors 34 a to 34 d may be installed inside of or near the relay unit 3 and the flow amount adjustment valves 25 a to 25 d may he installed inside of or near the indoor unit 2 .
  • the air-conditioning apparatus prevents freezing of the heat medium in pipelines to safely and steadily achieve energy saving by performing anti-freezing operation such as operating the pump to circulate the heat medium.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air Conditioning Control Device (AREA)
US13/055,841 2008-10-29 2008-10-29 Air-conditioning apparatus Abandoned US20110146339A1 (en)

Applications Claiming Priority (1)

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PCT/JP2008/069606 WO2010050003A1 (ja) 2008-10-29 2008-10-29 空気調和装置

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US14/625,209 Active 2029-06-20 US9797618B2 (en) 2008-10-29 2015-02-18 Air-conditioning apparatus

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JP (1) JP5127931B2 (zh)
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WO (1) WO2010050003A1 (zh)

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US20150000325A1 (en) * 2012-03-09 2015-01-01 Mitsubishi Electric Corporation Flow switching device and air-conditioning apparatus including the same
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Publication number Publication date
EP2341296B1 (en) 2018-08-08
CN102105749A (zh) 2011-06-22
US20150159897A1 (en) 2015-06-11
EP2341296A1 (en) 2011-07-06
WO2010050003A1 (ja) 2010-05-06
EP2341296A4 (en) 2014-10-08
CN102105749B (zh) 2013-06-26
JPWO2010050003A1 (ja) 2012-03-29
US9797618B2 (en) 2017-10-24
JP5127931B2 (ja) 2013-01-23

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