WO2014054091A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2014054091A1
WO2014054091A1 PCT/JP2012/075310 JP2012075310W WO2014054091A1 WO 2014054091 A1 WO2014054091 A1 WO 2014054091A1 JP 2012075310 W JP2012075310 W JP 2012075310W WO 2014054091 A1 WO2014054091 A1 WO 2014054091A1
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WO
WIPO (PCT)
Prior art keywords
flow rate
temperature
side heat
heat exchanger
refrigerant
Prior art date
Application number
PCT/JP2012/075310
Other languages
English (en)
Japanese (ja)
Inventor
博文 ▲高▼下
博幸 岡野
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP12886003.8A priority Critical patent/EP2905552B1/fr
Priority to JP2014539488A priority patent/JP5759080B2/ja
Priority to PCT/JP2012/075310 priority patent/WO2014054091A1/fr
Priority to US14/419,371 priority patent/US20150211776A1/en
Publication of WO2014054091A1 publication Critical patent/WO2014054091A1/fr

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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
    • 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 conditioner.
  • a conventional air conditioner includes a plurality of heat source unit side heat exchangers and a plurality of use side heat exchangers, and individually controls the outlet temperature of the use side heat exchanger that performs cooling operation during simultaneous cooling and heating operation. (For example, refer to Patent Document 1).
  • the present invention has been made to solve the above-described problems, and performs cooling operation even when there are a plurality of use side heat exchangers performing cooling operation during simultaneous cooling and heating operation.
  • An object of the present invention is to provide an air conditioner that can simplify control.
  • a flow rate regulator that adjusts the flow rate of the refrigerant that is distributed to the use side heat exchanger during cooling operation, and a control unit that adjusts the flow rate regulator, wherein the control unit includes the flow rate regulator.
  • the temperature during the cooling operation of the plurality of use side heat exchangers Air for obtaining a target control temperature of the downstream side temperature based on the liquid pipe temperature of the use side heat exchanger, adjusting the flow rate regulator according to the target control temperature, and controlling the liquid pipe temperature It is a harmony device.
  • the present invention controls the temperature detected by the temperature detection means provided in the repeater, so that the cooling operation can be performed even when there are a plurality of use side heat exchangers performing the cooling operation during the simultaneous cooling and heating operation.
  • the control to be performed can be simplified. Therefore, the cooling operation can be continued at low cost.
  • FIG. 1 It is a figure which shows the structural example of the air conditioning apparatus 1 in Embodiment 1 of this invention. It is the figure which modeled and showed the connection relation of the 2nd flow control device 122 in Embodiment 1 of the present invention, the 3rd flow control device 123, and the 3rd flow regulator 115 of relay machine B. It is a cooling-heating simultaneous operation in Embodiment 1 of this invention, Comprising: It is a figure which shows the structural example of the air conditioning apparatus 1 explaining the driving
  • the outside air temperature and the flow rate ratio according to the opening of the second flow control device 122, the opening of the third flow control device 123, and the opening of the third flow regulator 115 in Embodiment 1 of the present invention It is a figure explaining an example of correlation of these. It is a figure explaining an example of the correlation of the outside temperature and the heating capability ratio according to the case where there is the case where there is appropriate control of the 2nd flow control device 122 in Embodiment 1 of the present invention. It is a figure explaining an example of the correlation of the outside temperature and the heating capacity ratio according to the case where there is no proper control of the 4th flow regulating valve 124 in Embodiment 1 of the present invention. It is a flowchart explaining the operation example of the control part 141 with which the heat-source equipment A in Embodiment 1 of this invention is provided, and the operation example of the control part 151 with which the relay machine B is provided.
  • FIG. 1 is a diagram illustrating a configuration example of an air-conditioning apparatus 1 according to Embodiment 1 of the present invention.
  • the air conditioner 1 uses an indoor unit C, an indoor unit D, a relay unit B, a check valve 118 to a check valve 121, a four-way valve 102, and the like.
  • a cooling refrigeration cycle and a heating refrigeration cycle are formed, and simultaneous cooling and heating operations are performed.
  • the repeater B side controls the repeater temperature detected by the temperature detecting means 125 provided in the repeater B.
  • the temperature difference between the liquid pipe temperature of the individual use side heat exchanger 105 provided in each indoor unit and the temperature of the relay unit is kept constant. With this operation, it is not necessary to control the liquid pipe temperature of each user-side heat exchanger 105 to maintain the temperature difference from the repeater. As a result, the cooling operation is continued at low cost even when the outside air temperature decreases during the simultaneous cooling and heating operation.
  • the air conditioner 1 includes a heat source unit A, a relay unit B, an indoor unit C, an indoor unit D, and the like.
  • the relay unit B is provided between the heat source unit A, the indoor unit C, and the indoor unit D.
  • the heat source machine A and the relay machine B are connected by a first connection pipe 106 and a second connection pipe 107 having a smaller pipe diameter than the first connection pipe 106.
  • the relay machine B and the indoor unit C are connected by the 1st connection piping 106c and the 2nd connection piping 107c.
  • the relay machine B and the indoor unit D are connected by the 1st connection piping 106d and the 2nd connection piping 107d.
  • the relay unit B relays the refrigerant flowing between the heat source unit A, the indoor unit C, and the indoor unit D.
  • the present invention is not particularly limited thereto.
  • the case where two or more indoor units are provided may be used.
  • a plurality of heat source machines may be used.
  • a plurality of relay machines B may be provided.
  • the heat source machine A includes a compressor 101, a four-way valve 102, a heat source machine side heat exchanger 103, and an accumulator 104.
  • the heat source machine A includes a check valve 118, a check valve 119, a check valve 120, and a check valve 121.
  • the heat source machine A includes a second flow rate control device 122, a third flow rate control device 123, a fourth flow rate adjustment valve 124, and a control unit 141.
  • the heat source device A includes an outside air temperature detecting unit 131 that measures the outside air temperature and supplies the measurement result to the control unit 141.
  • the compressor 101 is provided between the four-way valve 102, the accumulator 104 and the second flow control device 122.
  • the compressor 101 compresses and discharges the refrigerant.
  • the discharge side is connected to the four-way valve 102 and the suction side is connected to the accumulator 104 and the second flow control device 122.
  • the four-way valve 102 includes four ports. Each port includes a discharge side of the compressor 101, a heat source unit side heat exchanger 103, an accumulator 104, an outlet side of the check valve 119, and an inlet of the check valve 120. And the refrigerant flow path is switched.
  • the heat source machine side heat exchanger 103 is provided between the four-way valve 102, the third flow rate control device 123, and the fourth flow rate adjustment valve 124.
  • One of the heat source device side heat exchangers 103 is connected to the four-way valve 102 and the other is connected to a pipe connected to the third flow rate control device 123 and the fourth flow rate adjustment valve 124.
  • the heat source device side heat exchanger 103 exchanges heat between the refrigerant flowing in the heat source device side heat exchanger 103 and the ambient air of the heat source device side heat exchanger 103.
  • the accumulator 104 is connected between the four-way valve 102 and the suction side of the compressor 101, separates the liquid refrigerant, and supplies the gas refrigerant to the compressor 101.
  • the compressor 101, the four-way valve 102, and the heat source device side heat exchanger 103 described above constitute a part of the refrigerant circuit.
  • the check valve 118 includes an outlet side of the fourth flow rate adjustment valve 124 and the check valve 121 connected to the heat source apparatus side heat exchanger 103, and an outlet side of the second connection pipe 107 and the check valve 120. Between.
  • the inlet side of the check valve 118 is connected to piping connected to the fourth flow rate adjustment valve 124 and the outlet side of the check valve 121.
  • the outlet side of the check valve 118 is connected to the second connection pipe 107 and a pipe connected to the outlet side of the check valve 120.
  • the check valve 118 allows the refrigerant to flow only from one direction to the second connection pipe 107 through the fourth flow rate adjustment valve 124 from the heat source apparatus side heat exchanger 103.
  • the check valve 119 is provided between the inlet side of the four-way valve 102 and the check valve 120 and the inlet side of the first connection pipe 106 and 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 flow only from one direction from the first connection pipe 106 to the four-way valve 102.
  • the check valve 121 includes an inlet side of the check valve 119 and the first connection pipe 106, and a fourth flow rate adjustment valve 124 connected to the inlet side of the check valve 118 and the heat source unit side heat exchanger 103. Between.
  • 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 flow rate adjustment valve 124.
  • the check valve 121 allows the refrigerant to flow only from one direction from the first connection pipe 106 to the heat source apparatus side heat exchanger 103 via the fourth flow rate adjustment valve 124.
  • the second flow control device 122 has one end connected to the inlet side of the check valve 121 and the other end 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 repeater B. Due to this connection configuration, the second flow control device 122 is connected in series with the relay machine B, and the refrigerant is supplied from the relay machine B.
  • the second flow control device 122 is a flow control device having a variable opening.
  • the second flow control device 122 controls the amount of refrigerant flowing from the relay B by adjusting the opening, and supplies the refrigerant to the suction side of the compressor 101 in a state where the amount of refrigerant is controlled.
  • the second flow rate control device 122 corresponds to the compressor flow rate control device in the present invention.
  • the fourth flow rate adjusting valve 124 is provided between the outlet side of the check valve 121 and the inlet side of the check valve 118 and the heat source unit side heat exchanger 103, and in parallel with the third flow rate control device 123. Connected. Specifically, one end of the fourth flow rate adjustment 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 adjustment valve 124 is connected to piping on the side connected to the heat source device side heat exchanger 103 in both ends of the third flow rate control device 123. Due to this connection configuration, the fourth flow rate adjustment valve 124 is connected in series via the relay B and the check valve 121, and the refrigerant is supplied from the relay B.
  • the first branching unit 110 includes an electromagnetic valve 108a and an electromagnetic valve 108b.
  • the solenoid valve 108a and the solenoid valve 108b are connected to the indoor unit C through the first connection pipe 106c.
  • the solenoid valve 108a and the solenoid valve 108b are connected to the indoor unit D through the first connection pipe 106d.
  • the solenoid valve 108a is a valve that can be opened and closed, and has one end connected to the first connection pipe 106 and the other end connected to one terminal of the first connection pipe 106c, the first connection pipe 106d, and the solenoid valve 108b. It is connected.
  • the second branch portion 111 is connected to the indoor unit C via the second connection pipe 107c.
  • the second branch portion 111 is connected to the indoor unit D via the second connection pipe 107d.
  • the second branch part 111 is connected to the second flow rate regulator 113 and the first heat exchanger 116 via the meeting part 137a_all.
  • the second branch part 111 is connected to the third flow rate regulator 115 and the first heat exchanger 116 via the meeting part 137b_all.
  • the gas-liquid separator 112 is provided in the middle of the second connection pipe 107, the gas phase portion is connected to the electromagnetic valve 108b of the first branching portion 110, and the liquid phase portion is the first heat exchange.
  • the second branching unit 111 is connected to the second branching unit 111 through the second unit 116, the second flow rate regulator 113, the second heat exchanger 117, and the third flow rate regulator 115.
  • the second flow rate regulator 113 has one end connected to the first heat exchanger 116 and the other end connected to one end of the second heat exchanger 117 and the meeting part 137a_all of the second branching part 111. .
  • the piping connected between the first heat exchanger 116 and the second flow rate regulator 113 is provided with a pressure detection means 127a described later in detail.
  • a pipe connected between the second flow rate regulator 113, the second heat exchanger 117, and the meeting portion 137a_all is provided with a pressure detection means 127b described later in detail.
  • the second flow rate regulator 113 is a flow rate regulator whose opening degree can be adjusted so that the difference between the pressure value detected by the pressure detection means 127a and the pressure value detected by the pressure detection means 127b is constant. Adjust the opening.
  • the third flow rate regulator 115 is a flow rate regulator whose opening degree can be adjusted, and is any one or a plurality of the outside air temperature detection means 131, the temperature detection means 125, the pressure detection means 127a, and the pressure detection means 127b. Adjust the opening by the combination.
  • the bypass pipe 114 has one end connected to the first connection pipe 106 and the other end connected to the third flow rate regulator 115. Therefore, the amount of refrigerant supplied to the heat source unit A varies depending on the opening of the third flow rate regulator 115.
  • the first heat exchanger 116 is provided between the gas-liquid separator 112, the second heat exchanger 117, and the second flow rate regulator 113, and includes a bypass pipe 114, the gas-liquid separator 112, and the first heat exchanger 116. Heat exchange is performed with a pipe provided between the two flow rate regulators 113.
  • the temperature detection means 125 is formed by a thermistor, for example.
  • the temperature detection means 125 detects the temperature of the refrigerant flowing between the third flow regulator 115 and the second heat exchanger 117, that is, in the pipe provided on the downstream side of the third flow regulator 115. Measure and supply the measurement result to the controller 151.
  • the temperature detection unit 125 may supply the measurement result to the control unit 151 as it is, or may supply the measurement result accumulated after a certain period of accumulation to the control unit 151 at a predetermined cycle interval.
  • the temperature detection unit 125 is described as an example of a thermistor, but is not particularly limited thereto.
  • the pressure detection unit 127 a measures the pressure of the refrigerant flowing in the pipe provided between the first heat exchanger 116 and the second flow rate regulator 113 and supplies the measurement result to the control unit 151.
  • the pressure detection means 127b measures the pressure of the refrigerant flowing in the pipe provided between the second flow rate regulator 113, the second heat exchanger 117, and the second branch part 111, and the measurement result is obtained. It supplies to the control part 151.
  • the pressure detection means 127a and the pressure detection means 127b are collectively referred to as a pressure detection means 127.
  • the pressure detection unit 127 may supply the measurement result as it is to the control unit 151, or may supply the measurement result accumulated after a certain period of accumulation to the control unit 151 at a predetermined cycle interval.
  • the indoor unit C includes a use side heat exchanger 105c, a liquid pipe temperature detecting means 126c, a first flow rate regulator 109c, and the like.
  • a plurality of use side heat exchangers 105c are provided. Between the use side heat exchanger 105c and the first flow rate regulator 109c, a liquid pipe temperature detecting means 126c for detecting the temperature of the pipe is provided.
  • the utilization side heat exchanger 105c and the first flow rate regulator 109c described above constitute a part of the refrigerant circuit.
  • the indoor unit D includes a use side heat exchanger 105d, a liquid pipe temperature detection means 126d, a first flow rate regulator 109d, and the like.
  • a plurality of use side heat exchangers 105d are provided. Between the use side heat exchanger 105d and the first flow rate regulator 109d, a liquid pipe temperature detecting means 126d for detecting the temperature of the pipe is provided.
  • the utilization side heat exchanger 105d and the first flow rate regulator 109d described above constitute a part of the refrigerant circuit.
  • FIG. 2 is a diagram showing a modeled connection relationship between the second flow rate control device 122, the third flow rate control device 123, and the third flow rate regulator 115 of the repeater B in the first embodiment of the present invention. It is. As shown in FIG. 2, a second flow rate control device 122 is provided between the relay machine B and the compressor 101. In addition, a third flow rate control device 123 and a fourth flow rate adjustment valve 124 are provided between the relay unit B and the heat source unit side heat exchanger 103. The third flow control device 123 and the fourth flow control valve 124 are connected in parallel, and the third flow control device 123 and the second flow control device 122 are connected in parallel.
  • the 2nd flow control device 122, the 3rd flow control device 123, and the 4th flow control valve 124 have a parallel relation mutually, and have a serial relation to relay machine B.
  • the relay unit B includes the third flow rate regulator 115 and adjusts the amount of refrigerant to the heat source unit A side.
  • the third flow rate regulator 115 determines the amount of refrigerant flowing through the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate adjustment valve 124.
  • the control unit 141 adjusts the opening degrees of the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate adjustment valve 124.
  • the control unit 151 adjusts the opening degree of the third flow rate regulator 115. And the control part 141 and the control part 151 supply mutual control content by transmitting / receiving various signals.
  • 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 them, the refrigerant flows to the check valve 118 and the check valve 119, while the refrigerant does not flow to the check valve 120 and the check valve 121.
  • the liquid refrigerant separated by the gas-liquid separator 112 passes through the second flow rate regulator 113 that controls the pressure difference between the high pressure and the intermediate pressure to be constant, and flows into the second branch portion 111.
  • the supplied liquid refrigerant passes through the check valve 108d connected to the indoor unit C and flows into the indoor unit C.
  • the inflowing liquid refrigerant is decompressed to a low pressure by using the first flow rate regulator 109c controlled according to the degree of superheat at the outlet of the utilization side heat exchanger 105c of the indoor unit C. It is supplied to the heat exchanger 105c.
  • the gas refrigerant flows into the check valve 119 having a lower pressure than the check valve 121, and is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104. With such an operation, a refrigeration cycle is formed and a cooling main operation is performed.
  • FIG. 4 is a diagram showing a configuration example of the air-conditioning apparatus 1 for explaining an operation state in the case of heating and cooling simultaneous operation in Embodiment 1 of the present invention and mainly heating.
  • a heating operation is set for the indoor unit C and a cooling operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by heating.
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 passes through the four-way valve 102, the check valve 120, the second connection pipe 107, and the relay machine.
  • B gas-liquid separator 112 is supplied.
  • the gas-liquid separator 112 supplies a high-temperature and high-pressure gas refrigerant to the first branch part 110.
  • the gas refrigerant supplied to the first branch part 110 is supplied to the indoor unit C in which the heating operation is set, through the open solenoid valve 108b and the first connection pipe 106c.
  • the use side heat exchanger 105c exchanges heat with a use medium such as air, and the supplied gas refrigerant is condensed and liquefied.
  • the use side heat exchanger 105c is controlled by the first flow rate regulator 109c based on the degree of supercooling at the outlet of the use side heat exchanger 105c.
  • the first flow controller 109c depressurizes the liquid refrigerant condensed and liquefied by the use side heat exchanger 105c, and converts it to an intermediate pressure liquid refrigerant that is an intermediate pressure between the high pressure and the low pressure.
  • the liquid refrigerant that has reached the intermediate pressure flows into the second branch portion 111.
  • the liquid refrigerant that has flowed into the second branch portion 111 joins at the meeting portion 137a_all.
  • the liquid refrigerant merged at the meeting part 137a_all passes through the second heat exchanger 117.
  • the liquid refrigerant that has previously passed through the second heat exchanger 117 partially passes through the third flow rate regulator 115 and is subjected to the second heat exchange via the bypass pipe 114 in a decompressed state.
  • the vessel 117 Into the vessel 117.
  • the refrigerant that has been gasified to become a gas refrigerant passes through the first connection pipe 106d and flows into the first branch 110.
  • the solenoid valve 108a by the side connected with the indoor unit D is opening. Therefore, the gas refrigerant that has flowed in passes through the electromagnetic valve 108 a on the side 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 pressure lower than that of the check valve 119, and flows into the fourth flow rate adjustment valve 124 and the heat source unit side heat exchanger 103 to evaporate into a gas state.
  • the air is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104. With such an operation, a refrigeration cycle is formed, and a heating main operation is performed.
  • 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 them, the refrigerant flows to the check valve 120 and the check valve 121, while the refrigerant does not flow to the check valve 118 and the check valve 119.
  • the control can be performed with one control parameter having a correlation with each liquid pipe temperature.
  • a control parameter for example, there is a relay machine temperature described in FIG.
  • FIG. 5 is a diagram illustrating an example of a temperature difference between the indoor unit temperature and the relay unit temperature during cooling according to Embodiment 1 of the present invention.
  • the relay unit temperature detected by the temperature detection unit 125 of the relay unit B and the indoor unit temperature detected by the liquid pipe temperature detection unit 126d of the indoor unit D in the cooling operation have a certain correlation.
  • the vertical axis indicates that the temperature difference between the indoor unit temperature detected by the liquid pipe temperature detection unit 126d of the indoor unit D in the cooling operation and the relay unit temperature detected by the temperature detection unit 125 of the relay unit B is ⁇ T.
  • a reference temperature difference is assumed to be ⁇ . Further, it is assumed that ⁇ Qjc is the total heat amount during cooling, and ⁇ Qjh is the total heat amount during heating. Also, when the total amount of heat during cooling is divided by the total amount of heat during heating, if the division result is small, it is represented by a circle symbol, if the division result is large, it is represented by a triangle symbol, and the division result is not small or large. It is assumed that it is represented by a square symbol and plotted as shown in FIG.
  • the liquid tube temperature is 3 (° C.).
  • the relay unit temperature detected by the temperature detector 125 of the relay unit B was 2 (° C.) during the heating and cooling simultaneous operation and before the refrigerant flow rate increased during the heating main operation.
  • the reference temperature difference is 1 (° C.).
  • the relay unit temperature detected by the temperature detection means 125 of the relay unit B has reached 5 (° C.) after the refrigerant flow rate is increased during the heating and cooling simultaneous operation and the heating main operation.
  • the current temperature difference is ⁇ 2 (° C.).
  • a value obtained by subtracting 3 (WB ° C.) from the temperature detected by the temperature detecting means 125 of the relay B may be controlled as the target control temperature of the third flow rate regulator 115. Because of this operation, it is not necessary to individually set the target control temperature for each indoor unit temperature, and control may be performed based on the detection result of the temperature detection means 125 of the relay unit B. Therefore, control becomes easy and stable cooling operation can be maintained.
  • the case where the refrigerant flow rate is increased has been described, but the same process can be performed when the refrigerant flow rate is decreased.
  • the heat source apparatus side heat exchanger 103, the second flow control device 122, the third flow control device 123 are mutually influential. Specifically, as the outside air temperature decreases, the air conditioner 1 cannot maintain a high pressure at a high level, and the heating capacity decreases. Moreover, since the low-pressure pressure decreases, the indoor unit D that is performing the cooling operation cannot maintain the continuous operation, and a problem occurs in both 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 according to the opening degree of the second flow control device 122 according to Embodiment 1 of the present invention.
  • the reference temperature on the horizontal axis is ⁇ and the reference heating capacity ratio on the vertical axis is ⁇ .
  • the heating capacity ratio is improved. In other words, in order to increase the heating capacity, the high pressure can be maintained high by increasing the opening of the second flow control device 122.
  • the high-pressure pressure increases and the heating capacity can be increased.
  • the heating capacity increases by about 8%.
  • the opening degree of the third flow control device 123 is also examined.
  • the third flow control device 123 is opened to a certain degree of opening or more, the second flow control device 122 and the third flow control device 123 are connected in parallel.
  • the flow rate decreases.
  • the liquid pipe temperature detecting means 126 of the indoor unit D becomes a certain value or less.
  • the cooling operation cannot be maintained.
  • priority is given to the injection amount to the compressor 101 at the same time as the liquid pipe temperature of the indoor unit D is raised by suppressing the opening of the third flow control device 123. With this operation, a comfortable operation can be performed regardless of whether it is a cooling operation or a heating operation.
  • the opening degree of the second flow control device 122 and the opening degree of the third flow control device 123 will be described.
  • FIG. 7 illustrates an example of the correlation between the outside air temperature and the flow rate ratio according to the opening of the second flow control device 122 and the opening of the third flow control device 123 according to Embodiment 1 of the present invention.
  • FIG. 7 it is assumed that the reference temperature on the horizontal axis is ⁇ and the reference flow rate ratio on the vertical axis is ⁇ .
  • the outside air temperature is ⁇ -20 ° C.
  • the flow rate of the third flow rate control device 123 is decreased and the flow rate of the second flow rate control device 122 is increased.
  • the heating capacity can be increased.
  • the low pressure is also lowered, there is no influence on the cooling capacity.
  • FIG. 9 is a diagram for explaining an example of the correlation between the outside air temperature and the heating capacity ratio depending on whether or not there is proper control of the second flow control device 122 in Embodiment 1 of the present invention. .
  • the influence on the cooling capacity can be reduced by adjusting the appropriate opening degree of the second flow rate control device 122, and the stable cooling capacity. Can be maintained.
  • FIG. 10 is a diagram for explaining an example of the correlation between the outside air temperature and the heating capacity ratio depending on whether or not the fourth flow regulating valve 124 is appropriately controlled in Embodiment 1 of the present invention. .
  • the opening degree of the fourth flow rate adjustment valve 124 by adjusting the opening degree of the fourth flow rate adjustment valve 124, the influence on the cooling capacity can be reduced, and the stable cooling capacity can be maintained.
  • the opening degree of the fourth flow rate adjustment valve 124 is reduced, and when the outside air temperature is high compared to a certain value, the opening degree of the fourth flow rate adjustment valve 124.
  • Increase With this operation the influence on the cooling capacity can be reduced, and a stable cooling capacity can be maintained.
  • Step S54 The control unit 141 of the heat source machine A changes the opening degree of the second flow rate control device 122.
  • the control unit 141 of the heat source device A changes the ratio of the degree of opening to be reduced in a stepwise manner according to the outside air temperature.
  • Step S56 The control unit 141 of the heat source machine A determines whether or not there is an end command.
  • the control part 141 of the heat source machine A ends the process when there is an end command.
  • the control unit 141 of the heat source machine A returns to step S51 and repeats the processing of steps S51 to S55.
  • Step S82 The control unit 151 of the relay machine B acquires the high pressure side pressure value.
  • the control unit 151 of the relay machine B acquires the pressure value on the high pressure side among the pressure detection units 127a and 127b. Which is on the high voltage side may be determined by the control unit 151 of the relay B holding a correspondence table in which which corresponds to the high voltage side is registered in advance according to the operating state.
  • Step S84 The control unit 151 of the relay machine B obtains a differential pressure between the high pressure side pressure value and the intermediate pressure side pressure value.
  • Step S87 The control unit 151 of the relay machine B acquires the temperature on the third flow rate regulator 115 side of the relay machine B. For example, the control unit 151 of the relay machine B acquires the relay machine temperature detected by the temperature detection unit 125.
  • Step S88 The control unit 151 of the relay machine B acquires the liquid pipe temperature of the indoor unit during the cooling operation. For example, as illustrated in FIG. 4, the control unit 151 of the relay machine B acquires the liquid pipe temperature detected by the liquid pipe temperature detection unit 126 d of the indoor unit D during the cooling operation. For example, it is assumed that the liquid tube temperature is detected by the left liquid tube temperature detecting means 126d shown in FIG.
  • Step S91 The control unit 151 of the relay machine B determines whether or not the opening degree is significantly smaller than the previous time.
  • the control unit 151 of the relay machine B determines that the opening degree is significantly smaller than that at the time of the previous adjustment, the control part 151 transmits the fact to the heat source machine A and the process shifts to step S55 of the heat source machine A side process. I will do it.
  • the control unit 151 of the relay machine B proceeds to step S92.
  • the relay unit B includes the heat source unit side heat exchanger 103, a plurality of A third flow rate regulator 115 that adjusts the flow rate of the refrigerant distributed to the usage side heat exchanger 105 in the cooling operation of the usage side heat exchanger 105, and a control unit that adjusts the third flow rate regulator 115. 151, and the control unit 151 includes a third flow rate regulator. 15, the target control temperature of the downstream side temperature is obtained based on the downstream side temperature of 15 and the liquid pipe temperature of the usage side heat exchanger 105 during the cooling operation among the plurality of usage side heat exchangers 105.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention porte sur un dispositif de climatisation (1), lequel dispositif comprend : un échangeur de chaleur côté machine de source de chaleur (103) ; une pluralité d'échangeurs de chaleur côté utilisation (105) ; et une machine de relais (B) qui est disposée entre l'échangeur de chaleur côté machine de source de chaleur (103) et la pluralité d'échangeurs de chaleur côté utilisation (105), et qui commute certains de la pluralité d'échangeurs de chaleur côté utilisation (105) vers un côté d'opération de refroidissement et qui commute certains de la pluralité d'échangeurs de chaleur côté utilisation (105) vers un côté d'opération de chauffage. Le dispositif de climatisation (1) commute, en fonction d'un ordre de commande, chacun de la pluralité d'échangeurs de chaleur côté utilisation (105) vers le côté d'opération de refroidissement et le côté d'opération de chauffage, et effectue une opération de refroidissement et de chauffage simultanée. La machine de relais (B) comprend : un troisième dispositif de réglage de débit d'écoulement (115) qui règle le débit d'écoulement d'un agent de refroidissement distribué à l'échangeur de chaleur côté machine de source de chaleur (103) et à l'échangeur de chaleur côté utilisation (105) effectuant l'opération de refroidissement ; et une unité de commande (151) qui règle le troisième dispositif de réglage de débit d'écoulement (115). L'unité de commande (151) trouve la température de commande cible pour la température aval, sur la base de la température en aval du troisième dispositif de réglage de débit d'écoulement (115) et de la température de tuyau de fluide des échangeurs de chaleur côté utilisation (105), et, en fonction de la température de commande cible, règle le troisième dispositif de réglage de débit d'écoulement (115) et commande la température de tuyau de fluide.
PCT/JP2012/075310 2012-10-01 2012-10-01 Dispositif de climatisation WO2014054091A1 (fr)

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EP12886003.8A EP2905552B1 (fr) 2012-10-01 2012-10-01 Dispositif de climatisation
JP2014539488A JP5759080B2 (ja) 2012-10-01 2012-10-01 空気調和装置
PCT/JP2012/075310 WO2014054091A1 (fr) 2012-10-01 2012-10-01 Dispositif de climatisation
US14/419,371 US20150211776A1 (en) 2012-10-01 2012-10-01 Air-conditioning apparatus

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EP2905552A1 (fr) 2015-08-12
EP2905552A4 (fr) 2016-06-01
EP2905552B1 (fr) 2019-04-17
JPWO2014054091A1 (ja) 2016-08-25
US20150211776A1 (en) 2015-07-30

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