EP2905552B1 - Air conditioning device - Google Patents

Air conditioning device Download PDF

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Publication number
EP2905552B1
EP2905552B1 EP12886003.8A EP12886003A EP2905552B1 EP 2905552 B1 EP2905552 B1 EP 2905552B1 EP 12886003 A EP12886003 A EP 12886003A EP 2905552 B1 EP2905552 B1 EP 2905552B1
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EP
European Patent Office
Prior art keywords
flow rate
rate control
unit
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.)
Active
Application number
EP12886003.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2905552A1 (en
EP2905552A4 (en
Inventor
Hirofumi Koge
Hiroyuki Okano
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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Publication date
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Publication of EP2905552A1 publication Critical patent/EP2905552A1/en
Publication of EP2905552A4 publication Critical patent/EP2905552A4/en
Application granted granted Critical
Publication of EP2905552B1 publication Critical patent/EP2905552B1/en
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Classifications

    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control 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
    • F25B2313/023—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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air

Definitions

  • the present invention relates to an air-conditioning apparatus.
  • a known air-conditioning apparatus includes a plurality of heat-source-unit-side heat exchangers and a plurality of use-side heat exchangers and independently controls the outlet temperature of a use-side heat exchanger that is performing a cooling operation during a cooling and heating simultaneous operation (see, for example, Patent Literature 1).
  • Patent Literature 1 Japanese Patent No. 4675810 (Paragraph [0034]) US2010/0101256 discloses an air conditioner according to the preamble of claim 1.
  • US2006/0254294 discloses an air conditioner according to the preamble of claim 1.
  • US2009/0272135 discloses an air conditioner according to the preamble of claim 1.
  • An object of the present invention is to provide an air-conditioning apparatus which is able to simplify control for performing a cooling operation even in the case where a plurality of use-side heat exchangers are performing a cooling operation during a cooling and heating simultaneous operation.
  • An air-conditioning apparatus according to the present invention is set out in claim 1.
  • the present invention by controlling the temperature detected by the temperature detection means provided in the relay unit, even in the case where a plurality of use-side heat exchangers are performing a cooling operation during a cooling and heating simultaneous operation, it is possible to simplify control for performing a cooling operation. Therefore, an effect of being able to continue a cooling operation with low cost can be achieved.
  • Fig. 1 is a diagram illustrating an example of the configuration of an air-conditioning apparatus 1 according to Embodiment 1 of the present invention.
  • the air-conditioning apparatus 1 forms a refrigeration cycle for cooling and a refrigeration cycle for heating within the air-conditioning apparatus 1 using an indoor unit C, an indoor unit D, a relay unit B, check valves 118 to 121, a four-way valve 102, and the like to perform a cooling and heating simultaneous operation.
  • the relay unit B side controls the relay unit temperature detected by temperature detection means 125 provided in the relay unit B, and therefore the temperature difference between the liquid pipe temperature of a use-side heat exchanger 105 provided in each of the indoor units and the relay unit temperature can be maintained constant.
  • the air-conditioning apparatus 1 includes a heat source unit A, the relay unit B, the indoor unit C, the indoor unit D, and the like.
  • the relay unit B is provided between the heat source unit A and each of the indoor unit C and the indoor unit D.
  • the heat source unit A and the relay unit B are connected to each other by a first connection pipe 106 and a second connection pipe 107, which has a pipe diameter smaller than the first connection pipe 106.
  • the relay unit B and the indoor unit C are connected to each other by first connection pipes 106c and second connection pipes 107c.
  • the relay unit B and the indoor unit D are connected to each other by first connection pipes 106d and second connection pipes 107d.
  • the relay unit B relays a refrigerant flowing between the heat source unit A and each of the indoor unit C and the indoor unit D.
  • one heat source unit and two indoor units are provided will be explained below.
  • the present invention is not limited to this.
  • two or more indoor units may be provided.
  • a plurality of heat source units may be provided.
  • a plurality of relay units B may be provided.
  • the heat source unit A includes a compressor 101, the four-way valve 102, a heat-source-unit-side heat exchanger 103, and an accumulator 104.
  • the heat source unit A also includes the check valve 118, the check valve 119, the check valve 120, and the check valve 121.
  • the heat source unit A also includes a second flow rate control device 122, a third flow rate control device 123, a fourth flow rate control valve 124, and a controller 141.
  • the heat source unit A also includes outside air temperature detection means 131 that measures the outside air temperature and supplies a measurement result to the controller 141.
  • the compressor 101 is provided between the four-way valve 102, the accumulator 104, and the second flow rate control device 122.
  • the compressor 101 compresses the refrigerant and discharges the compressed refrigerant.
  • the discharge side of the compressor 101 is connected to the four-way valve 102, and the suction side of the compressor 101 is connected to the accumulator 104 and the second flow rate control device 122.
  • the four-way valve 102 includes four ports which are connected to the discharge side of the compressor 101, the heat-source-unit-side heat exchanger 103, the accumulator 104, and the outlet side of the check valve 119 and the inlet side of the check valve 120, so that switching of the flow passage of the refrigerant can be performed.
  • the heat-source-unit-side heat exchanger 103 is provided between the four-way valve 102, the third flow rate control device 123, and the fourth flow rate control valve 124.
  • the heat-source-unit-side heat exchanger 103 is connected to a pipe whose one end is connected to the four-way valve 102 and whose other end is connected to the third flow rate control device 123 and the fourth flow rate control valve 124.
  • the heat-source-unit-side heat exchanger 103 exchanges heat between the refrigerant flowing inside the heat-source-unit-side heat exchanger 103 and the ambient air of the heat-source-unit-side heat exchanger 103.
  • the accumulator 104 is connected between the four-way valve 102 and the suction side of the compressor 101, performs separation of a liquid refrigerant, and supplies a gas refrigerant to the compressor 101.
  • the compressor 101, the four-way valve 102, and the heat-source-unit-side heat exchanger 103 explained above constitute part of a refrigerant circuit.
  • the check valve 118 is provided between the fourth flow rate control valve 124, which is connected to the heat-source-unit-side heat exchanger 103, and the outlet side of the check valve 121; and the second connection pipe 107 and the outlet side of the check valve 120.
  • the inlet side of the check valve 118 is connected to a pipe connected to the fourth flow rate control valve 124 and the outlet side of the check valve 121.
  • the outlet side of the check valve 118 is connected to a pipe connected to the second connection pipe 107 and the outlet side of the check valve 120.
  • the check valve 118 allows the refrigerant to circulate only in one direction from the heat-source-unit-side heat exchanger 103 through the fourth flow rate control valve 124 to the second connection pipe 107.
  • the check valve 119 is provided between the four-way valve 102 and the inlet side of the check valve 120; and the first connection pipe 106 and the inlet side of the check valve 121.
  • the inlet side of the check valve 119 is connected to a pipe connected to the first connection pipe 106 and the inlet side of the check valve 121.
  • the outlet side of the check valve 119 is connected to a pipe connected to the four-way valve 102 and the inlet side of the check valve 120.
  • the check valve 119 allows the refrigerant to circulate only in one direction from the first connection pipe 106 to the four-way valve 102.
  • the check valve 120 is provided between the four-way valve 102 and the outlet side of the check valve 119; and the outlet side of the check valve 118 and the second connection pipe 107.
  • the inlet side of the check valve 120 is connected to a pipe connected to the four-way valve 102 and the outlet side of the check valve 119.
  • the outlet side of the check valve 120 is connected to a pipe connected to the outlet side of the check valve 118 and the second connection pipe 107.
  • the check valve 120 allows the refrigerant to circulate only in one direction from the four-way valve 102 to the second connection pipe 107.
  • the check valve 121 is provided between the inlet side of the check valve 119 and the first connection pipe 106; and the inlet side of the check valve 118 and the fourth flow rate control valve 124 connected to the heat-source-unit-side heat exchanger 103.
  • the inlet side of the check valve 121 is connected to a pipe connected to the inlet side of the check valve 119 and the first connection pipe 106.
  • the outlet side of the check valve 121 is connected to a pipe connected to the inlet side of the check valve 118 and the fourth connection pipe 124.
  • the check valve 121 allows the refrigerant to circulate only in one direction from the first connection pipe 106 through the fourth flow rate control valve 124 to the heat-source-unit-side heat exchanger 103.
  • the check valves 118 to 121 explained above form a flow switching valve of the refrigerant circuit.
  • the flow switching valve and the relay unit B, the indoor unit C, and the indoor unit D which will be described in detail later, form a refrigeration cycle for the cooling operation and a refrigeration cycle for a heating operation in the refrigerant circuit during the cooling and heating simultaneous operation.
  • One end of the second flow rate control device 122 is connected to the inlet side of the check valve 121 and the other end of the second flow rate control device 122 is connected to the suction side of the compressor 101.
  • the inlet side of the check valve 121 is connected to one end of the first connection pipe 106.
  • the other end of the first connection pipe 106 is connected to the relay unit B.
  • the second flow rate control device 122 is connected in series to the relay unit B, so that the refrigerant is supplied from the relay unit B. Furthermore, the second flow rate control device 122 is a flow rate control device whose opening degree is variable.
  • the second flow rate control device 122 adjusts the opening degree thereof to control the amount of refrigerant which has flowed from the relay unit B, and supplies the controlled amount of refrigerant to the suction side of the compressor 101.
  • the second flow rate control device 122 corresponds to a compressor flow rate control device according to the present invention.
  • the third flow rate control device 123 is provided between the second flow rate control device 122 and the heat-source-unit-side heat exchanger 103 and is connected in parallel to the second flow rate control device 122. More specifically, the third flow rate control device 123 is connected to one of end portions of the second flow rate control device 122 that is connected to the inlet side of the check valve 121.
  • the third flow rate control device 123 is connected in series to the relay unit B, so that the refrigerant is supplied from the relay unit B. Furthermore, the third flow rate control device 123 is a flow rate control device whose opening degree is variable.
  • the third flow rate control device 123 adjusts the opening degree thereof to control the amount of refrigerant which has flowed from the relay unit B, and supplies the controlled amount of refrigerant to the heat-source-unit-side heat exchanger 103.
  • the third flow rate control device 123 is connected in parallel to the second flow rate control device 122 and is connected in series to the relay unit B.
  • the refrigerant flowing from the relay unit B is distributed and supplied to the second flow rate control device 122 and the third flow rate control device 123 in accordance with the opening degree of the second flow rate control device 122 and the opening degree of the third flow rate control device 123.
  • the fourth flow rate control valve 124 is provided between the outlet side of the check valve 121, the inlet side of the check valve 118, and the heat-source-unit-side heat exchanger 103, and is connected in parallel to the third flow rate control device 123. More specifically, one end of the fourth flow rate control valve 124 is connected to a pipe connected to the outlet side of the check valve 121 and the inlet side of the check valve 118. The other end of the fourth flow rate control valve 124 is connected to a pipe on a side of one of end portions of the third flow rate control device 123 that is connected to the heat-source-unit-side heat exchanger 103.
  • the fourth flow rate control valve 124 is connected in series to the relay unit B via the check valve 121, so that the refrigerant is supplied from the relay unit B. Furthermore, the fourth flow rate control valve 124 is a flow rate control valve whose opening degree is variable.
  • the fourth flow rate control valve 124 adjusts the opening degree thereof to control the amount of refrigerant which has flowed from the relay unit B, and supplies the controlled amount of refrigerant to the heat-source-unit-side heat exchanger 103.
  • the fourth flow rate control valve 124 is connected in parallel to the second flow rate control device 122 and the third flow rate control device 123 via the check valve 121, and is connected in series to the relay unit B.
  • the controller 141 includes, for example, a microprocessor unit as a main element, and performs the integrated control of the entire heat source unit A, communication with an external device, such as the relay unit B, and various arithmetic operations.
  • the present invention is not particularly limited to this.
  • the relay unit B includes a first branch part 110, a second branch part 111, a gas/liquid separator 112, a second flow rate control unit 113, a third flow rate control unit 115, a first heat exchanger 116, a second heat exchanger 117, the temperature detection means 125, pressure detection means 127a, pressure detection means 127b, a controller 151, and the like.
  • the relay unit B is connected to the heat source unit A via the first connection pipe 106 and the second connection pipe 107.
  • the relay unit B is connected to the indoor unit C via the first connection pipes 106c and the second connection pipe 107c.
  • the relay unit B is connected to the indoor unit D via the first connection pipes 106d and the second connection pipes 107d.
  • the solenoid valves 108a are valves that can be opened and closed. One end of each of the solenoid valves 108a is connected to the first connection pipe 106, and the other end of each of the solenoid valves 108a is connected to the corresponding first connection pipe 106c, the corresponding first connection pipe 106d, and one terminal of the corresponding solenoid valve 108b.
  • the solenoid valves 108b are valves that can be opened and closed.
  • the first branch part 110 is connected to the indoor unit C via the first connection pipes 106c.
  • the first branch part 110 is connected to the indoor unit D via the first connection pipes 106d.
  • the first branch part 110 is connected to the heat source unit A via the first connection pipe 106 and the second connection pipe 107.
  • the first branch part 110 allows connection between the first connection pipes 106c and either the first connection pipe 106 or the second connection pipe 107 using the solenoid valves 108a and the solenoid valves 108b.
  • the first branch part 110 allows connection between the first connection pipes 106d and either the first connection pipe 106 or the second connection pipe 107 using the solenoid valves 108a and the solenoid valves 108b.
  • the second branch part 111 includes check valves 137a and check valves 137b.
  • the check valves 137a and the check valves 137b are connected in antiparallel to each other.
  • the input side of the check valves 137a and the output side of the check valves 137b are connected to the indoor unit C via the second connection pipes 107c and are connected to the indoor unit D via the second connection pipes 107d.
  • the output side of the check valves 137a is connected to a junction part 137a_all.
  • the input side of the check valves 137b is connected to a junction part 137b_all.
  • the second branch part 111 is connected to the indoor unit C via the second connection pipes 107c.
  • the second branch part 111 is connected to the indoor unit D via the second connection pipes 107d.
  • the second branch part 111 is connected to the second flow rate control unit 113 and the first heat exchanger 116 via the junction part 137a_all.
  • the second branch part 111 is connected to the third flow rate control unit 115 and the first heat exchanger 116 via the junction part 137b_all.
  • One end of the second flow rate control unit 113 is connected to the first heat exchanger 116, and the other end of the second flow rate control unit 113 is connected to one end of the second heat exchanger 117 and the junction part 137a_all of the second branch part 111.
  • the pressure detection means 127a which will be described in detail later, is provided.
  • the pressure detection means 127b which will be described in detail later, is provided.
  • bypass pipe 114 One end of the bypass pipe 114 is connected to the first connection pipe 106, and the other end of the bypass pipe 114 is connected to the third flow rate control unit 115.
  • the amount of refrigerant to be supplied to the heat source unit A varies according to the opening degree of the third flow rate control unit 115.
  • the first heat exchanger 116 is connected between the gas/liquid separator 112, the second heat exchanger 117, and the second flow rate control unit 113, and exchanges heat between the bypass pipe 114 and a pipe provided between the gas/liquid separator 112 and the second flow rate control unit 113.
  • the second heat exchanger 117 is connected between the first heat exchanger 116 and the second flow rate control unit 113; and one end of the third flow rate control unit 115 and the other end of the third flow rate control unit 115. In this case, the other end of the third flow rate control unit 115 is connected to the junction part 137b_all.
  • the second heat exchanger 117 exchanges heat between the bypass pipe 114, and a pipe provided between the second flow rate control unit 113 and the third flow rate control unit 115.
  • the temperature detection device 125 is, for example, a thermistor.
  • the temperature detection device 125 measures the temperature of the refrigerant flowing between the third flow rate control unit 115 and the second heat exchanger 117, that is, the refrigerant flowing inside a pipe provided on the downstream side of the third flow rate control unit 115, and supplies a measurement result to the controller 151.
  • the temperature detection device 125 may supply the measurement result directly to the controller 151 or may accumulate measurement results for a certain period of time and then supply the accumulated measurement results to the controller 151 with predetermined time intervals.
  • the pressure detection device 127a measures the pressure of the refrigerant flowing inside a pipe provided between the first heat exchanger 116 and the second flow rate control unit 113, and supplies a measurement result to the controller 151.
  • the pressure detection device 127b measures the pressure of the refrigerant flowing inside a pipe provided between the second flow rate control unit 113, the second heat exchanger 117, and the second branch part 111, and supplies a measurement result to the controller 151.
  • the controller 151 includes, for example, a microprocessor unit as a main element, and performs the integrated control of the entire relay unit B, communication with an external device, such as the heat source unit A, and various arithmetic operations.
  • the indoor unit C includes use-side heat exchangers 105c, liquid pipe temperature detection devices 126c, first flow rate control units 109c, and the like. A plurality of use-side heat exchangers 105c are provided. The liquid pipe temperature detection devices 126c for detecting the temperature of a pipe are provided between the use-side heat exchangers 105c and the first flow rate control units 109c.
  • the use-side heat exchangers 105c and the first flow rate control units 109c explained above constitute part of the refrigerant circuit.
  • the indoor unit D includes use-side heat exchangers 105d, liquid pipe temperature detection devices 126d, first flow rate control units 109d, and the like. A plurality of use-side heat exchangers 105d are provided. The liquid pipe temperature detection devices 126d for detecting the temperature of a pipe are provided between the use-side heat exchangers 105d and the first flow rate control units 109d.
  • the above-mentioned use-side heat exchangers 105d and the first flow rate control units 109d constitute part of the refrigerant circuit.
  • Fig. 2 illustrates a modeled connection relationship between the second flow rate control device 122, the third flow rate control device 123, and the third flow rate control unit 115 of the relay unit B according to Embodiment 1 of the present invention.
  • the second flow rate control device 122 is provided between the relay unit B and the compressor 101.
  • the third flow rate control device 123 and the fourth flow rate control valve 124 are provided between the relay unit B and the heat-source-unit-side heat exchanger 103.
  • the third flow rate control device 123 and the fourth flow rate control valve 124 are connected in parallel to each other, and the third flow rate control device 123 and the second flow rate control device 122 are connected in parallel to each other.
  • the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate control valve 124 are connected in parallel to one another and are connected in series to the relay unit B.
  • the relay unit B includes the third flow rate control unit 115, and adjusts the amount of refrigerant to the heat source unit A side.
  • the third flow rate control unit 115 determines the amount of refrigerant flowing in the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate control valve 124.
  • the controller 141 adjusts the opening degree of the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate control valve 124.
  • the controller 151 adjusts the opening degree of the third flow rate control unit 115.
  • the controller 141 and the controller 151 transmit and receive various signals to supply control contents to each other.
  • Fig. 3 is a diagram illustrating an example of the configuration of the air-conditioning apparatus 1 for explaining a cooling main operation state in the cooling and heating simultaneous operation according to Embodiment 1 of the present invention.
  • the cooling operation and the heating operation are set for the indoor unit C and the indoor unit D, respectively, and the operation of the air-conditioning apparatus 1 is performed based on a cooling main operation.
  • the solenoid valves 108a on the indoor unit C side are opened, and the solenoid valves 108a on the indoor unit D side are closed.
  • the solenoid valves 108b on the indoor unit C side are closed, and the solenoid valves 108b on the indoor unit D side are opened.
  • the opening degree of the second flow rate control unit 113 is controlled so that the pressure difference between the pressure detection means 127a and the pressure detection means 127b has an appropriate value.
  • the heat-source-unit-side heat exchanger 103 exchanges heat with a heat source medium such as air or water.
  • the high-temperature and high-pressure gas refrigerant which has been subjected to heat exchange turns into a two-phase gas-liquid, high-temperature and high-pressure refrigerant.
  • the two-phase gas-liquid, high-temperature and high-pressure refrigerant passes through the fourth flow rate control valve 124, the check valve 118, and the second connection pipe 107, and is supplied to the gas/liquid separator 112 of the relay unit B.
  • the gas/liquid separator 112 separates the two-phase gas-liquid, high-temperature and high-pressure refrigerant into a gas-state refrigerant and a liquid-state refrigerant.
  • the separated gas-state refrigerant flows into the first branch part 110.
  • the gas-state refrigerant which has flowed into the first branch part 110 passes through the opened solenoid valves 108b and the first connection pipes 106d, and is supplied to the indoor unit D, for which the heating operation is set.
  • the use-side heat exchangers 105d exchange heat with a use-side medium such as air, and condense and liquefy the supplied gas-state refrigerant.
  • the use-side heat exchangers 105d are controlled by the first flow rate control units 109d on the basis of the degree of subcooling at the outlet of the use-side heat exchangers 105d.
  • the first flow rate control units 109d decompress a liquid refrigerant, which has been condensed and liquefied by the use-side heat exchangers 105d, into the refrigerant having an intermediate pressure, which is between a high pressure and a low pressure.
  • the refrigerant which has the intermediate pressure, is caused to flow into the second branch part 111.
  • the first connection pipe 106 has a low pressure
  • the second connection pipe 107 has a high pressure. Therefore, due to the pressure difference between the first connection pipe 106 and the second connection pipe 107, the refrigerant flows to the check valve 118 and the check valve 119, while the refrigerant does not flow to the check valve 120 or the check valve 121.
  • the liquid-state refrigerant which has been separated by the gas/liquid separator 112 passes through the second flow rate control unit 113, which controls the pressure difference between the high pressure and the intermediate pressure to be maintained constant, and flows into the second branch part 111.
  • the supplied liquid-state refrigerant passes through the check valves 108d which are connected to the indoor unit C side, and flows into the indoor unit C.
  • the liquid-state refrigerant which has flowed into the indoor unit C is decompressed into a low pressure using the first flow rate control units 109c which are controlled in accordance with the degree of superheat at the outlet of the use-side heat exchangers 105c of the indoor unit C, and is supplied to the use-side heat exchangers 105c.
  • the supplied liquid-state refrigerant evaporates and gasifies by heat exchange with a use-side medium such as air.
  • the refrigerant which has been gasified into a gas refrigerant, passes through the first connection pipes 106c and flows into the first branch part 110.
  • the solenoid valves 108a on a side that is connected to the indoor unit C are opened.
  • the gas refrigerant which has flowed into the first branch part 110 passes through the solenoid valves 108a on a side that is connected to the indoor unit C, and flows into the first connection pipe 106.
  • the gas refrigerant flows into the check valve 119 side at a lower pressure than the check valve 121, passes through the four-way valve 102 and the accumulator 104, and is sucked into the compressor 101.
  • liquid-state refrigerant which has been separated by the gas/liquid separator 112 and has flowed into the second branch part 111 does not flow into the indoor unit C.
  • Such a liquid-state refrigerant passes through the second flow rate control unit 113 and the second heat exchanger 117, and flows not into the second branch part 111 but into the third flow rate control unit 115.
  • the third flow rate control unit 115 decompresses the liquid-state refrigerant which has flowed into the third flow rate control unit 115 into a low pressure to lower the evaporating temperature of the refrigerant.
  • Fig. 4 is a diagram illustrating an example of the configuration of the air-conditioning apparatus 1 for explaining a heating main operation state in the cooling and heating simultaneous operation according to Embodiment 1 of the present invention.
  • the heating operation and the cooling operation are set for the indoor unit C and the indoor unit D, respectively, and the operation of the air-conditioning apparatus 1 is performed based on a heating main operation.
  • the solenoid valves 108a on the indoor unit C side are closed, and the solenoid valves 108a on the indoor unit D side are opened.
  • the solenoid valves 108b on the indoor unit C side are opened, and the solenoid valves 108b on the indoor unit D side are closed.
  • the opening degree of the second flow rate control unit 113 is controlled so that the pressure difference between the pressure detection means 127a and the pressure detection means 127b has an appropriate value.
  • the gas/liquid separator 112 supplies the high-temperature and high-pressure gas refrigerant to the first branch part 110.
  • the gas refrigerant which has been supplied to the first branch part 110 passes through the opened solenoid valves 108b and the first connection pipes 106c, and is supplied to the indoor unit C, for which the heating operation is set.
  • the use-side heat exchangers 105c exchange heat with a use-side medium such as air, and condense and liquefy the supplied gas refrigerant.
  • the use-side heat exchangers 105c are controlled by the first flow rate control units 109c on the basis of the degree of subcooling at the outlet of the use-side heat exchangers 105c.
  • the first flow rate control units 109c decompress a liquid refrigerant, which has been condensed and liquefied by the use-side heat exchangers 105c, into a liquid refrigerant having an intermediate pressure, which is between a high pressure and a low pressure.
  • the liquid refrigerant which has the intermediate pressure, is caused to flow into the second branch part 111.
  • the liquid refrigerant which has flowed into the second branch part 111 merges at the junction part 137a_all.
  • the liquid refrigerant which has been merged at the junction part 137a_all passes through the second heat exchanger 117.
  • part of the liquid refrigerant which has passed through the second heat exchanger 117 earlier passes through the third flow rate control unit 115, and the refrigerant in the decompressed state flows into the second heat exchanger 117 via the bypass pipe 114.
  • heat exchange is performed between the intermediate-pressure liquid refrigerant and the low-pressure liquid refrigerant.
  • the low-pressure liquid refrigerant has a low evaporating temperature, and is therefore turns into a gas refrigerant.
  • the gas refrigerant passes through the bypass pipe 114 and flows into the first connection pipe 106. Meanwhile, the intermediate-pressure liquid refrigerant reaches the junction part 137b_all, passes through the check valves 137b which are connected to the indoor unit D, passes through the second connection pipes 107d, and flows into the indoor unit D.
  • the liquid-state refrigerant which has flowed into the indoor unit D is decompressed into a low pressure using the first flow rate control units 109d which are controlled in accordance with the degree of superheat at the outlet of the use-side heat exchangers 105d of the indoor unit D.
  • the liquid refrigerant, which has a low evaporating temperature, is supplied to the use-side heat exchangers 105d.
  • the supplied liquid refrigerant having the low evaporating temperature evaporates and gasifies by heat exchange with a use-side medium such as air.
  • the refrigerant which has been gasified into a gas refrigerant, passes through the first connection pipes 106d and flows into the first branch part 110.
  • the solenoid valves 108a on a side that is connected to the indoor unit D are opened.
  • the gas refrigerant which has flowed into the first branch part 110 passes through the solenoid valves 108a on a side that is connected to the indoor unit D, and flows into the first connection pipe 106.
  • the gas refrigerant flows into the check valve 121 side having a lower pressure than the check valve 119, flows into the fourth flow rate control valve 124 and the heat-source-unit-side heat exchanger 103, and is evaporated and gasified into a gas state.
  • the refrigerant passes through the four-way valve 102 and the accumulator 104, and is sucked into the compressor 101.
  • the first connection pipe 106 has a low pressure
  • the second connection pipe 107 has a high pressure. Therefore, due to the pressure difference between the first connection pipe 106 and the second connection pipe 107, the refrigerant flows to the check valve 120 and the check valve 121, while the refrigerant does not flow to the check valve 118 or the check valve 119.
  • the suction temperature of the heat source unit A decreases as the outside air temperature decreases. Consequently, the evaporating temperature of the heat-source-unit-side heat exchanger 103 provided in the heat source unit A, that is, a low-pressure pressure, also decreases. Due to such a phenomenon, the liquid pipe temperatures detected by the liquid pipe temperature detection means 126 of the indoor unit D that is performing the cooling operation decrease. Consequently, the indoor unit D repeats start and stop. Therefore, the air-conditioning apparatus 1 cannot continue the cooling operation, which makes a user of the air-conditioning apparatus 1 feel uncomfortable.
  • the liquid pipe temperatures detected by the liquid pipe temperature detection means 126 of the indoor unit D In order to prevent start and stop of the indoor unit D, it is necessary to increase the liquid pipe temperatures detected by the liquid pipe temperature detection means 126 of the indoor unit D to a predetermined value or more.
  • the liquid pipe temperatures detected by the liquid pipe temperature detection means 126 of the indoor unit D for the use-side heat exchangers 105d of the indoor unit D differ from one another. Therefore, in the case where processing for increasing the liquid pipe temperatures is performed, it is necessary to individually control the liquid pipe temperatures in accordance with the individual use-side heat exchangers 105d, and such control is complicated.
  • control may be performed using a single control parameter having a correlation with individual liquid pipe temperatures.
  • Such a control parameter is, for example, a relay unit temperature which will be explained with reference to Fig. 5 .
  • Fig. 5 is a diagram illustrating an example of a temperature difference between an indoor unit temperature and a relay unit temperature at the time of cooling according to Embodiment 1 of the present invention.
  • the relay unit temperature detected by the temperature detection means 125 of the relay unit B and the indoor unit temperature detected by the liquid pipe temperature detection means 126d of the indoor unit D have a certain correlation with each other.
  • the horizontal axis represents the flow rate (kg/h) of the refrigerant. Furthermore, it is assumed that the vertical axis represents a temperature difference ⁇ T between the indoor unit temperature detected by the liquid pipe temperature detection means 126d of the indoor unit D that is performing the cooling operation and the relay unit temperature detected by the temperature detection means 125 of the relay unit B. It is assumed that a reference temperature difference is represented by ⁇ . Furthermore, it is assumed that ⁇ Qjc represents a cooling-time total heat quantity and ⁇ Qjh represents a heating-time total heat quantity. It is assumed that plotting is performed as illustrated in Fig. 5 such that a circle mark indicates that a division result obtained by dividing the cooling-time total heat quantity by the heating-time total heat quantity is small, a triangle mark indicates that the division result is large, and a square mark indicates that the division result is neither small or large.
  • a circle mark indicates that the heating-time total heat quantity is relatively large. This is equivalent to that a heating main operation is being performed.
  • a triangle mark indicates that the cooling-time total heat quantity is relatively large. This is equivalent to that a cooling main operation is being performed.
  • a square mark is equivalent to that there is a relatively negligible amount of difference between the cooling operation and the heating operation.
  • the liquid pipe temperature is 3 (degrees Centigrade). It is assumed that, at this time, in a heating main operation during the cooling and heating simultaneous operation, the relay unit temperature detected by the temperature detection means 125 of the relay unit B before the flow rate of the refrigerant increases is 2 (degrees Centigrade). In this case, the reference temperature difference is 1 (degree Centigrade). It is assumed that, after that, in a heating main operation during the cooling and heating simultaneous operation, the relay unit temperature detected by the temperature detection means 125 of the relay unit B after the flow rate of the refrigerant increases is 5 (degrees Centigrade). In this case, the current temperature difference is -2 (degrees Centigrade).
  • the temperature difference changes from the reference temperature difference 1 (degree Centigrade) to the current temperature difference -2 (degrees Centigrade), and the current temperature difference may be smaller than the reference temperature difference by 3 (degrees Centigrade).
  • the value corrected by 3 can be defined as a target control temperature of the relay unit temperature.
  • control may be performed using the value obtained by subtracting 3 (WB degrees Centigrade) from the temperature detected by the temperature detection means 125 of the relay unit B as the target control temperature of the third flow rate control unit 115.
  • 3 WB degrees Centigrade
  • control may be simplified, and a stable cooling operation can be maintained.
  • a method for detecting the flow rate of the refrigerant is not particularly limited.
  • a flow meter may be provided at a pipe through which the refrigerant flows.
  • the flow rate may be obtained by conversion from variations of the discharge pressure of the compressor 101.
  • the air-conditioning apparatus 1 As the outside air temperature decreases, it becomes more difficult for the air-conditioning apparatus 1 to maintain a high-pressure pressure high and the heating capacity degrades. Furthermore, lowering the low-pressure pressure causes the indoor unit D which is currently performing the cooling operation not to continue the operation, and a problem thus occurs both in the cooling operation and the heating operation.
  • Fig. 6 is a diagram for explaining an example of the correlation between the outside air temperature and the heating capacity ratio in accordance with the opening degree of the second flow rate control device 122 according to Embodiment 1 of the present invention.
  • the heating capacity ratio is low when the opening degree of the second flow rate control device 122 is small, while the heating capacity ratio increases when the opening degree of the second flow rate control device 122 increases.
  • the heating capacity is thus increased. For example, at an outside air temperature of ⁇ -30 degrees Centigrade, when the amount of injection is increased by 30 percent to 40 percent, the heating capacity is increased by about 8 percent.
  • the opening degree of the third flow rate control device 123 will now be discussed. In the case where the opening degree of the third flow rate control device 123 is opened at a certain value or more, since the second flow rate control device 122 and the third flow rate control device 123 are connected in parallel to each other, the flow rate to the second flow rate control device 122 decreases.
  • the opening degree of the second flow rate control device 122 and the opening degree of third flow rate control device 123 will be described below.
  • Fig. 7 is a diagram for explaining an example of the correlation between the outside air temperature and the flow rate ratio in accordance with the opening degree of the second flow rate control device 122 and the opening degree of the third flow rate control device 123 according to Embodiment 1 of the present invention.
  • the heating capacity can be increased.
  • a low-pressure pressure also decreases, and therefore the cooling capacity is not affected.
  • Fig. 8 is a diagram for explaining an example of the correlation between the outside air temperature and the flow rate ratio in accordance with the opening degree of the second flow rate control device 122, the opening degree of the third flow rate control device 123, and the opening degree of the third flow rate control unit 115 according to Embodiment 1 of the present invention.
  • the third flow rate control unit 115 provided in the relay unit B for controlling the pressure difference between the high pressure and the intermediate pressure before and after the pressure detection means 127a and 127b to be maintained constant, decreases the opening degree thereof as the outside air temperature decreases, in a manner similar to the operation of the third flow rate control device 123.
  • Fig. 10 is a diagram for explaining an example of the correlation between the outside air temperature and the heating capacity ratio in accordance with the case where the fourth flow rate control valve 124 is properly controlled and the case where the fourth flow rate control valve 124 is not properly controlled according to Embodiment 1 of the present invention.
  • the opening degree of the fourth flow rate control valve 124 by adjusting the opening degree of the fourth flow rate control valve 124, it is possible to reduce the influence on the cooling capacity and thus maintain a stable cooling capacity. For example, when the outside air temperature is lower than a certain value, the opening degree of the fourth flow rate control valve 124 is reduced. Meanwhile, when the outside air temperature is higher than the certain value, the opening degree of the fourth flow rate control valve 124 is increased.
  • Embodiment 1 Although a cooling main operation and a heating main operation have been explained in Embodiment 1, the present invention is not particularly limited to this. For example, only the heating operation may be performed.
  • Fig. 11 is a flowchart for explaining an operation example of the controller 141 provided in the heat source unit A and an operation example of the controller 151 provided in the relay unit B according to Embodiment 1 of the present invention.
  • step S89 of the relay unit B Before processing of step S55 of the heat source unit A. That is, a significant reduction in the opening degree of the third flow rate control unit 115 of the relay unit B is a prerequisite to proceed to step S55 of the heat source unit A.
  • the controller 141 of the heat source unit A determines whether or not the cooling and heating simultaneous operation is being performed. When it is determined that the cooling and heating simultaneous operation is being performed, the controller 141 of the heat source unit A proceeds to step S52. When it is determined that the cooling and heating simultaneous operation is not being performed, the controller 141 of the heat source unit A proceeds to step S56.
  • the controller 141 of the heat source unit A acquires outside air temperature.
  • the controller 141 of the heat source unit A acquires, for example, outside air temperature data detected by the outside air temperature detection means 131.
  • the controller 141 of the heat source unit A determines whether or not the outside air temperature corresponds to a predetermined threshold.
  • the controller 141 of the heat source unit A proceeds to step S54.
  • the injection start threshold (WB degrees Centigrade) corresponds to, for example, ⁇ -5 (WB degrees Centigrade) which is the start temperature at which the opening degree of the second flow rate control device 122 gradually increases, as illustrated in Fig. 8 . It is assumed that ⁇ -5 (WB percent) is, for example, 0 degrees Centigrade.
  • ⁇ -5 WB percent
  • WB percent 0 degrees Centigrade
  • the controller 141 of the heat source unit A proceeds to step S55.
  • the controller 141 of the heat source unit A changes the opening degree of the second flow rate control device 122.
  • the controller 141 of the heat source unit A gradually changes the ratio at which the opening degree is reduced in accordance with the outside air temperature, as illustrated in Fig. 8 .
  • the controller 141 of the heat source unit A reduces the opening degree of the third flow rate control device 123.
  • the opening degree of the third flow rate control device 123 is fully opened when the outside air temperature is within a range from ⁇ (WB percent) to ⁇ -20 (WB percent)
  • the third flow rate control device 123 is throttled and the opening degree thereof is reduced when the outside air temperature is at ⁇ -20 (WB percent) or below.
  • the controller 141 of the heat source unit A determines whether or not a termination instruction exists. When a termination instruction exists, the controller 141 of the heat source unit A ends the process. When a termination instruction does not exist, the controller 141 of the heat source unit A returns to step S51, and repeats processing of steps S51 to S55.
  • the controller 151 of the relay unit B determines whether or not the cooling and heating simultaneous operation is being performed. When it is determined that the cooling and heating simultaneous operation is being performed, the controller 151 of the relay unit B proceeds to step S82. When it is determined that the cooling and heating simultaneous operation is not being performed, the controller 151 of the relay unit B proceeds to step S92.
  • the controller 151 of the relay unit B acquires a high-pressure-side pressure value.
  • the controller 151 of the relay unit B acquires a pressure value of a high-pressure side of the pressure detection means 127a or 127b.
  • the determination as to which one of the pressure detection means 127a and 127b is on a high-pressure side is performed based on a correspondence table held by the controller 151 of the relay unit B in which information indicating which one of the pressure detection means 127a and 127b corresponds to a high pressure side is registered in advance in accordance with the operation state.
  • the controller 151 of the relay unit B acquires an intermediate-pressure-side pressure value. For example, the controller 151 of the relay unit B acquires a pressure value of an intermediate-pressure side of the pressure detection means 127a or 127b. The determination as to which one of the pressure detection means 127a and 127b is on an intermediate pressure side is performed based on a correspondence table held by the controller 151 of the relay unit B in which information indicating which one of the pressure detection means 127a and 127b corresponds to an intermediate pressure side is registered in advance in accordance with the operation state.
  • the controller 151 of the relay unit B obtains a pressure difference between the high-pressure-side pressure value and the intermediate-pressure-side pressure value.
  • the controller 151 of the relay unit B determines whether or not the pressure difference is constant. When the pressure difference is constant, the controller 151 of the relay unit B proceeds to step S87. When the pressure difference is not constant, the controller 151 of the relay unit B proceeds to step S86.
  • the controller 151 of the relay unit B makes the pressure difference constant by the third flow rate control unit 115 of the relay unit B.
  • the controller 151 of the relay unit B acquires the liquid pipe temperature of the indoor unit that is performing the cooling operation.
  • the controller 151 of the relay unit B acquires, for example, the liquid pipe temperature detected by the liquid pipe temperature detection means 126d of the indoor unit D that is performing the cooling operation, as illustrated in Fig. 4 .
  • liquid pipe temperature detection means 126d which is on the left side of Fig. 4 .
  • the controller 151 of the relay unit B acquires a temperature difference ⁇ T between the temperature on the third flow rate control unit 115 side and the liquid pipe temperature of the indoor unit D. For example, the controller 151 of the relay unit B obtains a temperature difference ⁇ T between the relay unit temperature detected by the temperature detection means 125 and the liquid pipe temperature detected by the liquid pipe temperature detection means 126d on the left side of Fig. 4 .
  • the controller 151 of the relay unit B determines, based on the temperature difference ⁇ T and the reference temperature difference, whether the temperature difference ⁇ T falls within a specific range.
  • the reference temperature difference represents a predetermined specific range based on the temperature difference between the liquid pipe temperature and the relay unit temperature, as described above.
  • the controller 151 of the relay unit B determines whether or not the opening degree is significantly smaller than the previous time. When it is determined that the opening degree is significantly smaller than the previous adjustment time, the controller 151 of the relay unit B transmits to the heat source unit A information indicating that the opening degree is significantly smaller than the previous adjustment time, and at the same time, the process proceeds to step S55 of the heat source unit A side. When it is determined that the opening degree is not significantly smaller than the previous adjustment time, the controller 151 of the relay unit B proceeds to step S92.
  • the controller 151 of the relay unit B determines whether or not a termination instruction exists. When a termination instruction exists, the controller 151 of the relay unit B ends the process. When a termination instruction does not exist, the controller 151 of the relay unit B returns to step S81, and repeats processing of steps S81 to S91.
  • control for performing the cooling operation can be simplified even in the case where a plurality of use-side heat exchangers are performing the cooling operation during the cooling and heating simultaneous operation. Therefore, the cooling operation can continue to be performed with low cost.
  • the relay unit B includes the third flow rate control unit 115 which adjusts the flow rate of the refrigerant to be distributed to the heat-source-unit-side heat exchanger 103 and a use-side heat exchanger 105 that is performing the cooling operation among the plurality of use-side heat exchangers 105, and the controller

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US20130233006A1 (en) * 2011-01-26 2013-09-12 Mitsubishi Electric Corporation Air-conditioning apparatus
CN103328909B (zh) * 2011-01-31 2015-04-01 三菱电机株式会社 空气调节装置
WO2013111176A1 (ja) * 2012-01-23 2013-08-01 三菱電機株式会社 空気調和装置

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JP5759080B2 (ja) 2015-08-05
EP2905552A1 (en) 2015-08-12
EP2905552A4 (en) 2016-06-01
JPWO2014054091A1 (ja) 2016-08-25
US20150211776A1 (en) 2015-07-30
WO2014054091A1 (ja) 2014-04-10

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