WO2015140950A1 - Climatiseur - Google Patents

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Publication number
WO2015140950A1
WO2015140950A1 PCT/JP2014/057465 JP2014057465W WO2015140950A1 WO 2015140950 A1 WO2015140950 A1 WO 2015140950A1 JP 2014057465 W JP2014057465 W JP 2014057465W WO 2015140950 A1 WO2015140950 A1 WO 2015140950A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
side heat
heat exchanger
liquid
compressor
Prior art date
Application number
PCT/JP2014/057465
Other languages
English (en)
Japanese (ja)
Inventor
宗史 池田
若本　慎一
直史 竹中
山下　浩司
傑 鳩村
亮宗 石村
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 PCT/JP2014/057465 priority Critical patent/WO2015140950A1/fr
Publication of WO2015140950A1 publication Critical patent/WO2015140950A1/fr

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    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/2515—Flow 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
    • F25B2700/2103—Temperatures near a 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to an air conditioner using a single R32 refrigerant or a mixed refrigerant containing R32 refrigerant.
  • a refrigerant having a high global warming potential (GWP) such as R410A refrigerant, R407c refrigerant, and R134a refrigerant is used as a natural refrigerant.
  • GWP global warming potential
  • Conversion to a refrigerant having a low GWP such as a carbon, hydrocarbon refrigerant, HFO refrigerant, R32 refrigerant or the like is being studied.
  • the R32 refrigerant has substantially the same operating pressure as the current R410A refrigerant, and the refrigerating capacity per unit volume is larger than that of the R410A refrigerant.
  • R32 refrigerant has a larger specific heat ratio than R410A refrigerant. For this reason, the discharge temperature of the refrigerant becomes high. For example, when the evaporation temperature is 0 ° C., the condensation temperature is 50 ° C., and the superheat degree of the refrigerant at the time of suction of the compressor is 2 ° C., the R32 refrigerant has a discharge temperature of 20 than the R410A refrigerant. It rises by about °C. When the discharge temperature becomes high, the temperature exceeds the guaranteed temperature of the refrigerating machine oil or the sealing material, and therefore a measure for reducing the discharge temperature is required.
  • Patent Document 1 a liquid pipe that circulates a liquid refrigerant and a compressor are connected, and the liquid pipe has an injection circuit provided with a flow rate adjusting valve for controlling the flow rate. The liquid injection from the injection circuit to the compressor is performed.
  • a refrigeration apparatus for performing the above is disclosed.
  • Patent Document 2 further includes an injection pipe connected to the suction pipe between the accumulator and the compressor, and a flow rate control means for controlling the refrigerant flow rate provided on the injection pipe.
  • a refrigeration apparatus for liquid injection is disclosed.
  • Patent Literatures 1 and 2 during cooling operation and heating operation, liquid injection is performed on the suction side of the compressor, thereby lowering the refrigerant discharge temperature and causing the compressor to operate stably.
  • the dryness of the refrigerant flowing into the injection flow path may change depending on the outside air temperature or the load condition of the indoor unit.
  • the dryness of the refrigerant flowing into the injection flow path changes, there is a problem that vibration or the like is generated due to the injection and it is difficult to stably operate the compressor.
  • Patent Document 2 since the flow rate control device attached to the injection circuit is controlled to open when the discharge temperature of the refrigerant discharged from the compressor reaches a predetermined temperature or higher, the discharge temperature from the start of the injection. A rise in discharge temperature is unavoidable until it starts to decrease.
  • the control start temperature target temperature
  • the discharge temperature rises from the start of the injection until the discharge temperature starts to decrease. There is a problem that it is necessary to decelerate or stop operation for protection, and it is difficult to operate stably.
  • the air conditioner according to the present invention has been made in response to the above problems, and an object thereof is to provide an air conditioner that stably operates a compressor when injecting the compressor.
  • An air conditioner includes a compressor, a flow path switching device that switches flow paths for heating operation and cooling operation, a heat source side heat exchanger, a plurality of usage side heat exchangers, and a plurality of usage side heat exchangers.
  • a plurality of expansion devices installed corresponding to the above have a refrigerant circuit connected through a pipe, and difluoromethane (R32) alone or a mixed refrigerant having a mass ratio of difluoromethane (R32) larger than 40 wt% is used as the refrigerant.
  • the air conditioner used is provided between an injection pipe for injecting liquid refrigerant to the suction side of the compressor, a heat source side heat exchanger, and a use side heat exchanger, and the heat source side heat exchanger Of the refrigerant flowing between the use-side heat exchangers, the liquid refrigerant supply device that supplies liquid refrigerant to the injection pipe, and the liquid that is provided on the injection pipe and supplied from the liquid refrigerant supply device
  • a flow rate regulator that decompresses the medium into a gas-liquid two-phase state and supplies the refrigerant to the suction side of the compressor, a discharge temperature sensor that detects the temperature of the refrigerant discharged from the compressor as a discharge temperature, and a discharge temperature sensor
  • the opening of the flow regulator is controlled based on the discharge temperature detected by the control unit and the number of heating-side heat exchangers among the plurality of usage-side heat exchangers decreases, depending on the rate of change in the number of operating units
  • a control means for controlling the opening degree
  • the R32 refrigerant that increases the discharge temperature from the compressor is obtained by injecting the liquid refrigerant supplied from the liquid refrigerant supply device into a gas-liquid two-phase state and injecting the compressor. Even when it is used, the compressor can be stably operated while reducing the discharge temperature from the compressor. Moreover, by having a control means for controlling the opening degree of the flow regulator according to the change rate of the number of operating units, the discharge temperature of the compressor is reduced, the deterioration of the refrigerant and the refrigeration oil, the compressor sealing material, etc. Fatigue can be reduced and operation can be performed with high reliability.
  • FIG. 3 is a Ph diagram when no injection is performed during the cooling operation of the air-conditioning apparatus of FIG. 2. It is a refrigerant circuit figure which shows the flow of the refrigerant
  • FIG. 5 is a Ph diagram when injection is performed during a cooling operation of the air-conditioning apparatus of FIG. 4.
  • FIG. 7 is a Ph diagram when no injection is performed during the heating operation of the air-conditioning apparatus of FIG. 6.
  • FIG. 9 is a Ph diagram when injection is performed during the heating operation of the air conditioner of FIG. 8.
  • FIG. 17 is a graph showing a Ph line when injection is performed during heating operation of the air conditioner of FIG. 16.
  • Embodiment 4 of the air conditioning apparatus of this invention It is a refrigerant circuit figure which shows the flow of the refrigerant
  • FIG. 1 is a refrigerant circuit diagram illustrating Embodiment 1 of the air-conditioning apparatus of the present invention.
  • the circuit configuration of the air-conditioning apparatus 100 will be described with reference to FIG.
  • the air conditioner 100 performs a cooling operation and a heating operation using a refrigeration cycle in which a refrigerant is circulated, and difluoromethane (hereinafter referred to as “R32”) is used as a refrigerant flowing through the refrigerant circuit of the air conditioner 100.
  • R32 difluoromethane
  • a single refrigerant mixture of R32 and tetrafluoropropene (hereinafter referred to as “HFO-1234yf” or “HFO-1234ze (E)”) is used.
  • the air conditioner 100 of FIG. 1 has a configuration in which an outdoor unit (heat source unit) 10 and a plurality of indoor units 20A and 20B are connected by pipes 101 and 102.
  • an outdoor unit (heat source unit) 10 and a plurality of indoor units 20A and 20B are connected by pipes 101 and 102.
  • FIG. 1 the case where one outdoor unit 10 and two indoor units 20A and 20B are connected is illustrated, but two or more indoor units 20A and 20B may be connected.
  • the pipes 101 and 102 only need to connect the outdoor unit 10 and the indoor units 20A and 20B, and may use extension pipes in the middle.
  • the outdoor unit 10 includes a compressor 1, a flow path switch 2, a heat source side heat exchanger 3, and an accumulator 5.
  • the compressor 1 sucks a refrigerant, compresses the refrigerant, and discharges the refrigerant in a high temperature / high pressure state.
  • the compressor 1 has a discharge side connected to the flow path switch 2 and a suction side connected to a suction pipe 9.
  • the compressor 1 is assumed to be a compressor having a low pressure shell structure, but may be a compressor having a high pressure shell structure.
  • the flow path switching unit 2 switches between a heating flow path and a cooling flow path in accordance with switching of an operation mode of cooling operation or heating operation, and includes, for example, a four-way valve.
  • the flow path switching unit 2 connects the pipe 101 and the accumulator 5 and connects the discharge side of the compressor 1 and the heat source side heat exchanger 3.
  • the refrigerant discharged from the compressor 1 flows to the heat source side heat exchanger 3 side
  • the refrigerant flowing out from the indoor units 20A and 20B flows into the outdoor unit 10 side through the pipe 101.
  • the flow path switch 2 connects the heat source side heat exchanger 3 and the accumulator 5 and connects the discharge side of the compressor 1 and the pipe 101.
  • the refrigerant discharged from the compressor 1 flows toward the indoor units 20A and 20B, and the refrigerant flowing out from the indoor units 20A and 20B flows into the outdoor unit 10 through the pipe 102.
  • a four-way valve is used as the flow path switching device 2
  • the present invention is not limited to this, and for example, a plurality of two-way valves may be combined.
  • the heat source side heat exchanger 3 is connected between the flow path switch 2 and the flow rate control device 4 and functions as a condenser that condenses and liquefies the refrigerant during the cooling operation, and evaporates the refrigerant during the heating operation. It functions as a vaporizer that vaporizes.
  • the flow rate control device 4 is disposed between the heat source side heat exchanger 3 and the indoor units 20A and 20B, and is configured to variably control the opening degree of an electronic expansion valve, for example.
  • the flow control device 4 has a function as a pressure reducing valve or an expansion valve that decompresses and expands the refrigerant.
  • the indoor unit 20 ⁇ / b> A, 20 ⁇ / b> B is changed to the outdoor unit during heating operation.
  • the intermediate temperature (intermediate pressure) of the refrigerant flowing into the refrigerant 10 can be controlled.
  • the accumulator 5 is provided on the suction side of the compressor 1, and either an excess refrigerant or a transitional operation change (for example, the indoor units 20 ⁇ / b> A and 20 ⁇ / b> B) due to a difference between the cooling operation and the heating operation.
  • an excess refrigerant or a transitional operation change for example, the indoor units 20 ⁇ / b> A and 20 ⁇ / b> B
  • the refrigerant is introduced from the flow path switching device 2 side, and the refrigerant is supplied to the suction side of the compressor 1 through the suction pipe 9.
  • the accumulator 5 is not necessarily required, and the flow path switch 2 and the suction pipe 9 may be directly connected without providing the accumulator 5.
  • the outdoor unit 10 is provided with an injection circuit between the pipe 102 connected to the indoor units 20A and 20B and the flow control device 4, and the injection circuit includes the liquid refrigerant supply device 6, the injection pipe 7, A flow rate regulator 8 is provided.
  • the liquid refrigerant supply device 6 supplies liquid phase refrigerant to the compressor 1 among refrigerant flowing between the heat source side heat exchanger 3, and a gas phase refrigerant and a liquid phase refrigerant coexist. It consists of a gas-liquid separator that separates a two-phase refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant.
  • an injection pipe 7 is connected to the lower side (liquid phase side) of the liquid refrigerant supply device 6, and the liquid refrigerant supply device 6 supplies the liquid refrigerant to the injection pipe 7.
  • the liquid refrigerant supply device 6 distributes refrigerant other than the liquid refrigerant supplied to the injection pipe 7 between the heat source side heat exchanger 3 and the indoor units 20A and 20B via the pipe 102.
  • the injection pipe 7 is a pipe for connecting the liquid refrigerant supply device 6 and the suction pipe 9 of the compressor 1 and performing injection from the liquid refrigerant supply device 6 to the suction side of the compressor 1.
  • a flow rate regulator 8 is provided on the injection pipe 7.
  • the flow rate regulator 8 depressurizes the liquid refrigerant supplied from the liquid refrigerant supply device 6 to a gas-liquid two-phase state of a gas phase and a liquid phase, and controls the flow rate of the refrigerant flowing into the suction pipe 9 of the compressor 1.
  • it comprises an electronic expansion valve whose opening degree can be variably controlled.
  • Each indoor unit 20A, 20B includes use side heat exchangers 21A, 21B, expansion devices 22A, 22B, and blowers 23A, 23B, respectively.
  • the use side heat exchangers 21A and 21B function as an evaporator (heat absorber) during cooling operation and function as a condenser (heat radiator) during heating operation.
  • use side heat exchanger 21A, 21B performs heat exchange between the air supplied from air blower 23A, 23B, and a refrigerant
  • the expansion devices 22A and 22B are composed of, for example, an electronic expansion valve that can change the opening, and are connected in series to the use side heat exchangers 21A and 21B, respectively.
  • the expansion devices 22A and 22B function as pressure reducing valves and expansion valves, and adjust the pressure of the refrigerant passing through the use side heat exchangers 21A and 21B.
  • the air conditioner 100 includes an outdoor unit control means 30, an indoor unit control means 40, a discharge temperature sensor 51, and an intermediate temperature sensor 52.
  • the discharge temperature sensor 51 is provided on the discharge side of the compressor 1 and detects the temperature of the refrigerant discharged from the compressor 1 as the discharge temperature T1.
  • the intermediate temperature sensor 52 is provided between the expansion devices 22A and 22B and the flow rate control device 4, and detects the intermediate temperature T2 of the refrigerant flowing into the flow rate control device 4 during the heating operation.
  • the outdoor unit control means 30 controls the operation of the outdoor unit 10, and includes refrigerant pressure information, refrigerant temperature information, and outdoor temperature detected by the discharge temperature sensor 51, the intermediate temperature sensor 52, or various detectors (not shown). Based on information, room temperature information, etc., control of driving of the compressor 1, switching of the flow path switch 2, driving of the fan motor of the fan 3a associated with the heat source side heat exchanger 3, opening degree of each flow control device, etc. To do.
  • the indoor unit control means 40 controls the operation of the indoor units 20A and 20B, drives the blower motors of the blowers 23A and 23B associated with the use side heat exchangers 21A and 21B, and opens the expansion devices 22A and 22B. Control the degree etc.
  • the outdoor unit control means 30 is connected to the indoor unit control means 40 and is based on the operation state information of each indoor unit 20A, 20B such as cooling operation, heating operation, thermo-off operation without heat load (heating load), stop, etc. It controls the driving of the compressor 1, the switching of the flow path switching device 2, the driving of the blower 3a associated with the heat source side heat exchanger 3, the opening of the flow regulator 8, the opening of other flow control devices, and the like.
  • Each indoor unit 20A, 20B is given a model code determined according to the capacity (cooling capacity or heating capacity), and the outdoor unit control means 30 is a model of each indoor unit 2A, 2B that is operating. The total capacity corresponding to the code is stored as operation status information.
  • the indoor unit 20A has a capacity of 5.0 horsepower and the model code is 50
  • the indoor unit 20B has a capacity of 2.5 horsepower and the model code is 25, the operation is performed when both the indoor units 20A and 20B are stopped.
  • the state information is 0, the operation state information when only the indoor unit 20A is operating is 50, the operation state information when only the indoor unit 20B is operating is 25, and the operation state information when both the indoor units 20A and 20B are operating becomes 75.
  • capacitance is a horsepower
  • a cooling capability or a heating capability (kW) may be sufficient.
  • the operation operation of the air conditioner 100 described above includes two types of operation modes, cooling operation and heating operation.
  • the cooling operation is an operation mode in which both or one of the indoor units 20A and 20B performs the cooling operation
  • the heating operation is an operation mode in which both or one of the indoor units 20A and 20B performs the heating operation. is there.
  • the refrigerant flow in the case of not performing the injection in each of the cooling operation and the heating operation will be described with a Ph diagram.
  • FIG. 2 is a refrigerant circuit diagram showing a refrigerant flow when no injection is performed during the cooling operation of the air conditioning apparatus 100 of FIG. 1
  • FIG. 3 is a Ph diagram during the cooling operation of the air conditioning apparatus 100 of FIG.
  • the portion where the refrigerant flows during the cooling operation is indicated by a thick line
  • the portion where the refrigerant does not flow is indicated by a thin line
  • the points (a) to (d) in FIG. Shows the state.
  • the flow path switching unit 2 is switched so that the refrigerant discharged from the compressor 1 flows into the heat source side heat exchanger 3.
  • the flow rate control device 4 is set to fully open
  • the flow rate regulator 8 is set to fully closed so that refrigerant is not injected into the compressor 1.
  • the low-temperature and low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the refrigerant compression process of the compressor 1 is compressed so as to be heated as compared with the case of adiabatic compression with an isentropic line by the amount of the adiabatic efficiency of the compressor 1 (point (a) ⁇ (b)).
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switch 2 and flows into the heat source side heat exchanger 3.
  • the refrigerant that has flowed into the heat source side heat exchanger 3 is cooled by exchanging heat with outdoor air, and becomes a medium-temperature and high-pressure liquid refrigerant.
  • the refrigerant change in the heat source side heat exchanger 3 is represented by a slightly inclined horizontal line (point (b) ⁇ (c)) in consideration of the pressure loss of the heat source side heat exchanger 3.
  • the medium-temperature and high-pressure liquid refrigerant flowing out of the heat source side heat exchanger 3 passes through the fully-opened flow control device 4, the liquid refrigerant supply device 6 and the pipe 102, and then enters the expansion devices 22A and 22B of the indoor units 20A and 20B. Inflow.
  • the refrigerant is squeezed and expanded and depressurized by the expansion devices 22A and 22B to be in a low-temperature low-pressure gas-liquid two-phase state.
  • the change of the refrigerant in the expansion devices 22A and 22B is performed under a constant enthalpy (point (c) ⁇ (d)).
  • the low-temperature and low-pressure gas-liquid two-phase refrigerant that has flowed out of the expansion devices 22A and 22B flows into the use-side heat exchangers 21A and 21B.
  • the refrigerant that has flowed into the use-side heat exchangers 21A and 21B is heated while exchanging heat with room air, and becomes a low-temperature and low-pressure gas refrigerant.
  • the indoor air is cooled by this heat exchange.
  • the expansion devices 22A and 22B are controlled by the indoor unit control means 40 so that the superheat (superheat degree) of the low-temperature and low-pressure gas refrigerant is about 2 to 5K.
  • the change of the refrigerant in the use side heat exchangers 21A and 21B is represented by a slightly inclined straight line (point (d) ⁇ (a)) in consideration of pressure loss.
  • the low-temperature and low-pressure gas refrigerant that has flowed out of the use side heat exchangers 21A and 21B enters the outdoor unit 10 after passing through the pipe 101, flows into the compressor 1 through the flow path switch 2 and the accumulator 5, and is compressed.
  • FIG. 4 is a refrigerant circuit diagram showing the flow of refrigerant when the air-conditioning apparatus 100 of FIG. 1 is injected during the cooling operation
  • FIG. 5 is a Ph diagram when the air-conditioning apparatus 100 of FIG. 4 is injected during the cooling operation. It is.
  • the portion where the refrigerant flows during the cooling operation is indicated by a thick line
  • the portion where the refrigerant does not flow is indicated by a thin line
  • points (a) to (g) in FIG. Indicates the state.
  • Both the flow rate control device 4 and the flow rate regulator 8 are set to fully open.
  • the liquid refrigerant discharged from the compressor 1 and passing through the flow path switching device 2 and cooled by the heat source side heat exchanger 3 passes through the flow rate control device 4 and flows into the liquid refrigerant supply device 6.
  • the liquid refrigerant that has flowed into the liquid refrigerant supply device 6 branches into a liquid refrigerant that flows into the injection pipe 7 side and a refrigerant that flows into the indoor units 20A and 20B via the pipe 102.
  • the liquid refrigerant that has flowed into the injection pipe 7 is depressurized by the flow rate regulator 8 (point (f) ⁇ (g)). Then, the refrigerant that has been decompressed by the flow rate regulator 8 to become a gas-liquid two-phase is injected into the suction pipe 9.
  • gas-liquid two-phase refrigerant merges with the gas refrigerant flowing through the suction pipe 9 and is heated while cooling the gas refrigerant (gas-liquid two-phase refrigerant: point (g) in FIG. 5 ⁇ ( a), gas refrigerant: point (e) ⁇ (a)).
  • FIG. 6 is a refrigerant circuit diagram showing a refrigerant flow when the air-conditioning apparatus 100 of FIG. 1 is not injected during the heating operation
  • FIG. 7 is a diagram of P ⁇ when the air-conditioning apparatus 100 of FIG. 6 is not injected during the heating operation.
  • FIG. 6 the portion where the refrigerant flows during the heating operation is indicated by a thick line, the portion where the refrigerant does not flow is indicated by a thin line, and points (a) to (e) in FIG. Indicates the state.
  • the flow path switching unit 2 is switched so that the refrigerant discharged from the compressor 1 flows into the indoor units 20A and 20B, and the flow rate regulator 8 is fully closed so that the refrigerant does not flow. Is set.
  • the low-temperature and low-pressure gas refrigerant is compressed by the compressor 1 and discharged as a high-temperature and high-pressure gas refrigerant (point (a) ⁇ (b)).
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the flow path switch 2 and the pipe 101 and then flows into the use side heat exchangers 21A and 21B of the indoor units 20A and 20B, respectively.
  • the refrigerant that has flowed into the use-side heat exchangers 21A and 21B is cooled while heating the outdoor air, and becomes a medium-temperature and high-pressure liquid refrigerant.
  • the refrigerant change in the use side heat exchangers 21A and 21B is represented by a slightly inclined horizontal line in consideration of the pressure loss of the use side heat exchangers 21A and 21B (point (b) ⁇ (c)). .
  • the medium temperature and high pressure liquid refrigerant flowing out from the use side heat exchangers 21A and 21B is expanded and decompressed in the expansion devices 22A and 22B to be in a medium pressure gas-liquid two-phase state.
  • the change of the refrigerant in the expansion devices 22A and 22B is performed under a constant enthalpy (point (c) ⁇ (d)), and the expansion devices 22A and 22B are, for example, subcools (supercooling degree) of the medium temperature and high pressure liquid refrigerant. ) Is controlled to be about 5K to 20K.
  • the medium-pressure gas-liquid two-phase refrigerant that has flowed out of the expansion devices 22A and 22B passes through the pipe 102 and then flows into the flow rate control device 4 through the liquid refrigerant supply device 6 in the outdoor unit 10.
  • the medium-pressure gas-liquid two-phase refrigerant is squeezed to expand and depressurize to a low-temperature and low-pressure gas-liquid two-phase state.
  • the change of the refrigerant in the flow control device 4 is performed under a constant enthalpy (point (d) ⁇ (e)).
  • the flow rate control device 4 is controlled, for example, so as to be fixed in a fully opened state, or so that the saturation temperature of the intermediate pressure of the pipe 102 or the like becomes about 0 to 20 ° C.
  • the low-temperature low-pressure gas-liquid two-phase refrigerant that has flowed out of the flow control device 4 flows into the heat source side heat exchanger 3.
  • the refrigerant flowing into the heat source side heat exchanger 3 is heated while cooling the indoor air, and becomes a low-temperature and low-pressure gas refrigerant.
  • the change of the refrigerant in the heat source side heat exchanger 3 is expressed by a slightly inclined straight line (point (e) ⁇ (a)) in consideration of pressure loss.
  • point (e) ⁇ (a) a slightly inclined straight line
  • FIG. 8 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 according to Embodiment 1 of the present invention performs the heating operation
  • FIG. 9 illustrates the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. It is a Ph diagram in the case of injection during heating operation.
  • the portion where the refrigerant flows during the heating operation is indicated by a thick line
  • the portion where the refrigerant does not flow is indicated by a thin line
  • the refrigerant that has flowed into the indoor units 20A and 20B is cooled by the use-side heat exchangers 21A and 21B, and becomes medium-pressure gas-liquid two-phase refrigerant in the expansion devices 22A and 22B.
  • the medium-pressure gas-liquid two-phase refrigerant flows from the expansion devices 22A and 22B into the liquid refrigerant supply device 6 via the pipe 102.
  • the liquid refrigerant supply device 6 the gas-liquid two-phase refrigerant is separated into a gas phase and a liquid phase, and a part of the separated liquid refrigerant flows into the injection pipe 7 (point (h)).
  • the remaining refrigerant flows out from the liquid refrigerant supply device 6, is depressurized by the flow rate control device 4 (point (e) ⁇ (f)), and flows into the heat source side heat exchanger 3.
  • the liquid refrigerant that has passed through the injection pipe 7 flows into the flow rate regulator 8 and is reduced in pressure to become a gas-liquid two-phase state (point (h) ⁇ (i)).
  • the refrigerant in the gas-liquid two-phase state is injected into the suction pipe 9. Is done.
  • the injected gas-liquid two-phase refrigerant joins with the gas refrigerant flowing through the suction pipe 9 and is heated while cooling the gas refrigerant (gas-liquid two-phase refrigerant: point (i) ⁇ (a), gas refrigerant : Point (g) ⁇ (a)).
  • the discharge of the compressor 1 is performed by injecting the liquid refrigerant supplied from the liquid refrigerant supply device 6 into the suction pipe 9 during the cooling operation and the heating operation of the air conditioner 100 using the R32 refrigerant. Since the temperature can be reduced, deterioration of the refrigerant and refrigerating machine oil and fatigue of the seal material of the compressor 1 can be reduced.
  • the R32 refrigerant alone, the mixed refrigerant of the R32 refrigerant and the HFO-1234yf refrigerant, or the mixed refrigerant of the R32 refrigerant and the HFO-1234ze (E) refrigerant is used. It is used.
  • R32 refrigerant has a larger specific heat ratio than refrigerants such as R410A refrigerant.
  • FIG. 10 is a graph showing the temperature of the refrigerant discharged from the compressor 1 with respect to the mixing ratio of the R32 refrigerant.
  • FIG. 10 shows simulation results of the temperature of the refrigerant discharged from the compressor 1 in the R410A refrigerant alone, the mixed refrigerant of the R32 refrigerant and the HFO-1234yf refrigerant, and the mixed refrigerant of the R32 refrigerant and the HFO-1234ze (E) refrigerant. ing.
  • the evaporation temperature of the compressor suction is 0 ° C.
  • the condensation temperature is 50 ° C.
  • the suction superheat degree is 2 ° C.
  • the heat insulation efficiency of the compressor 1 is 65%.
  • the higher the mixing ratio of R32 the higher the discharge temperature of the refrigerant discharged from the compressor 1.
  • the discharge temperature rises by about 20 ° C. compared to the case where the R410A refrigerant is used alone.
  • the compression ratio of the refrigerant in the compressor 1 is increased.
  • the refrigerant discharge temperature exceeds 120 ° C. There is a possibility that the temperature of the discharged refrigerant becomes high.
  • the discharge temperature of the refrigerant is required to be suppressed to 120 ° C. or less, for example.
  • the R32 refrigerant in the mixed refrigerant of R32 and HFO-1234yf, is 40 wt% or more, and the R32 and HFO-1234ze (E) In the mixed refrigerant, it is necessary to reduce the discharge temperature when R32 is 50 wt% or more.
  • the mixed refrigerant of the R32 refrigerant and the HFO-1234yf refrigerant is 60 wt% or more of the R32 refrigerant, and the mixture of the R32 refrigerant and the HFO-1234ze (E) refrigerant.
  • the refrigerant it is necessary to reduce the discharge temperature when the R32 refrigerant is 50 wt% or more.
  • FIG. 11 is a graph showing the temperature of the refrigerant discharged from the compressor 1 when the number of operating indoor units of R32 refrigerant and R410A refrigerant decreases.
  • FIG. 11 it is the outline of the change of the discharge temperature in R410A refrigerant
  • coolant Depending on the lengths of the pipes 101 and 102, the operating state of the indoor units 20A and 20B, the indoor air temperature, and the outdoor air temperature, the situation shown in FIG. 11 may occur.
  • the injection start temperature of R410A is 95 ° C.
  • the discharge temperature T1 rises from 80 ° C. to 110 ° C. after the number of indoor units in which the heating operation is performed decreases.
  • the injection is started at 95 ° C., it takes time until the effect of the injection appears, and after that, the discharge temperature T1 rises to 110 ° C., and then the discharge temperature T1 falls.
  • the injection start temperature needs to be set higher than R410A.
  • the injection start temperature of the R32 refrigerant is 110 ° C.
  • the injection is started at 110 ° C. after the number of heating operation is reduced.
  • the compressor 1 is stopped by protection control.
  • the injection start temperature and the protection control temperature are not limited to these.
  • an injection circuit is provided in the refrigerant circuit as described above, and liquid or gas-liquid two-phase refrigerant is injected into the suction pipe 9 during cooling operation and heating operation.
  • the discharge temperature of the compressor 1 can be reduced, deterioration of a refrigerant
  • the flow rate regulator 8 is provided in the above-described injection circuit, and the flow rate of the liquid or the gas-liquid two-phase refrigerant flowing into the suction pipe 9 is controlled during the cooling operation and the heating operation. Thereby, since the discharge temperature of the compressor 1 can be controlled, the compressor 1 can be stably operated.
  • the liquid refrigerant supply device 6 is provided in the above-described injection circuit, and the refrigerant in the liquid single phase state is supplied to the flow rate regulator 8 during the cooling operation and the heating operation. Yes.
  • coolant state can be supplied to the injection piping 7 irrespective of external temperature or load condition.
  • the enthalpy of the refrigerant becomes smaller than that of the gas-liquid two-phase refrigerant, and the refrigerant flow rate can be reduced.
  • liquid refrigerant supply device 6 and the flow rate regulator 8 are included in the above-described injection circuit, the liquid single-phase refrigerant is supplied to the flow rate regulator 8 to suppress the generation of pressure vibration.
  • the flow rate regulator 8 can be reduced in size by suppressing the refrigerant flow rate.
  • the outdoor unit control means 30 of the air conditioner 100 has a function of controlling the injection so as to start when it is determined that the discharge temperature is necessary for the injection.
  • the outdoor unit control means 30 has a function of controlling the flow rate regulator 8 based on the discharge temperature T 1 detected by the discharge temperature sensor 51.
  • the outdoor unit control means 30 opens the flow rate regulator 8 and performs injection.
  • the outdoor unit control means 30 closes the flow rate regulator 8 and does not perform injection.
  • the injection is started when it is determined that the discharge temperature T1 of the compressor 1 is increased and the above-described problem occurs by performing the injection based on the discharge temperature T1. Further, it is possible to prevent a decrease in operating efficiency due to excessive cooling.
  • the outdoor unit control means 30 has a function of controlling the opening degree of the flow rate regulator 8 based on the indoor unit operation information (capacity) transmitted by the indoor unit control means 40 during the heating operation. Specifically, the outdoor unit control means 30 detects the number of indoor units 20A and 20B that are performing the heating operation, and when the number of heating operations decreases, the flow rate adjustment is performed as in the following formula (1). The opening of the vessel 8 is corrected.
  • Opening correction amount C x (Sum of model code before change-Sum of model code after change) (1)
  • C is a correction coefficient, which is determined according to the resistance coefficient of the flow rate regulator 8 and the like.
  • the opening correction amount is determined by the change in the sum of the model codes.
  • the present invention is not limited to this, and may be the change rate of the number of operating indoor units 20A and 20B.
  • FIG. 12 is a flowchart showing an operation example, and an operation example when the opening degree of the flow rate regulator 8 is controlled will be described with reference to FIGS. 1 to 12.
  • the discharge temperature sensor 51 detects the discharge temperature T1 of the compressor 1 (step ST1).
  • the opening degree of the flow rate regulator 8 is calculated based on the discharge temperature T1 (step ST2), and the number of operating indoor units 20A and 20B is detected (step ST3).
  • the calculated opening degree of the flow rate regulator 8 is corrected based on the opening degree correction amount (step ST6), and is controlled so that the opening degree of the flow rate regulator 8 becomes the calculated opening degree (step ST7).
  • the discharge temperature can be controlled even when the load state of the refrigerant circuit changes by performing the control for correcting the opening degree of the flow rate regulator 8 according to the change rate of the operating units almost at the same time.
  • the injection can be performed without raising and can be operated stably.
  • the change rate of the number of operating units is composed of the difference between the sum before the change of the model code determined based on the capacities of the indoor units 20A and 20B and the sum after the change.
  • the opening degree of the flow rate regulator 8 can be opened according to the change in the number of operating units of the indoor units 20A and 20B.
  • the discharge temperature T1 can be reduced.
  • the indoor unit control means 40 when the use side heat exchangers 21A and 21B are in the heating operation, the expansion device 22 and the use side heat so that the liquid refrigerant flows out from the use side heat exchangers 21A and 21B.
  • the blower 23 attached to the exchanger is controlled. Therefore, liquid refrigerant flows into the injection circuit inlet.
  • the gas refrigerant flows from the usage-side heat exchanger 21A in the stopped state.
  • the expansion devices 22A and 22B and the blowers 23A and 23B are controlled so that the refrigerant in the two-phase state flows out and the liquid refrigerant flows out from the use-side heat exchanger 21B performing the heating operation. Therefore, the two-phase refrigerant flows into the injection circuit inlet.
  • the liquid refrigerant supply device 6 in the injection circuit, liquid refrigerant can be supplied to the injection circuit even when the number of operating units of the indoor units 2A and 2B decreases, so the load state of the refrigerant circuit changes.
  • the injection can be performed without increasing the discharge temperature T1, and the operation can be stably performed. In particular, even when the use-side heat exchanger 21A in the stopped state exists, the liquid refrigerant flows out, and the liquid refrigerant necessary for the injection can be generated.
  • the outdoor unit control means 30 has a function of controlling the opening degree of the flow control device 4 based on the intermediate temperature T2 detected by the intermediate temperature sensor 52 during the heating operation. Specifically, the outdoor unit control means 30 measures an intermediate temperature (saturation temperature) T2 in an intermediate pressure region that is a gas-liquid two-phase from the intermediate temperature sensor 52, and the intermediate temperature is expressed by the following equation (2). Control is performed so that T2 falls within the set range.
  • the medium pressure threshold Tref is set to a temperature within the range of 0 ° C. to 20 ° C., and ⁇ T is set to 5 ° C.
  • the pressure of the refrigerant injected into the compressor 1 is increased by controlling the flow rate control device 4 so that the intermediate temperature T2 of the refrigerant flowing into the liquid refrigerant supply device 6 during the heating operation becomes the target temperature T2ref.
  • FIG. FIG. 13 is a refrigerant circuit diagram illustrating Embodiment 2 of the air-conditioning apparatus 200 of the present invention.
  • part which has the same structure as the air conditioning apparatus 100 of FIG. 1 attaches
  • the air conditioning apparatus 200 of FIG. 11 is different from the air conditioning apparatus 100 of FIG.
  • the liquid refrigerant supply device 206 of FIG. 13 is composed of an inter-refrigerant heat exchanger, one of which is connected between the flow control device 4 and the expansion devices 22A and 22B, and the other is the heat source side heat exchanger 3 and the flow control. It is connected to the device 4.
  • the liquid refrigerant supply device 206 exchanges heat between the medium-pressure gas-liquid two-phase refrigerant and the low-temperature low-pressure gas-liquid two-phase refrigerant during the heating operation.
  • the injection pipe 7 is connected between the flow control device 4 and the liquid refrigerant supply device 206, and the injection pipe 7 is connected to the flow control device 4 side after flowing through the liquid refrigerant supply device 206 from the expansion devices 22A and 22B. The refrigerant flowing to is supplied.
  • FIG. 14 is a refrigerant circuit diagram showing the flow of refrigerant when the air-conditioning apparatus 200 of FIG. 13 is injected during the heating operation
  • FIG. 15 is a Ph line when the air-conditioning apparatus 200 of FIG. 14 is injected during the heating operation. It is a graph to show.
  • the portion where the refrigerant flows during the heating operation is indicated by a thick line
  • the portion where the refrigerant does not flow is indicated by a thin line
  • points (a) to (i) in FIG. Indicates the state.
  • the refrigerant that has flowed into the indoor units 20A and 20B is cooled by the use-side heat exchangers 21A and 21B, and becomes medium-pressure gas-liquid two-phase refrigerant in the expansion devices 22A and 22B.
  • the medium-pressure gas-liquid two-phase refrigerant flows into the liquid refrigerant supply device 6 from the expansion devices 22 ⁇ / b> A and 22 ⁇ / b> B via the pipe 102 and is depressurized by the flow rate control device 4. Then, the refrigerant is cooled while heating the low-temperature low-pressure gas-liquid two-phase refrigerant, and becomes a medium-pressure liquid refrigerant (point (d) ⁇ (e)).
  • the branched liquid refrigerant passes through the injection pipe 7 and then flows into the flow rate regulator 8 to be depressurized (point (e) ⁇ (i)).
  • the refrigerant that has been decompressed by the flow rate regulator 8 to become a gas-liquid two-phase is injected into the suction pipe 9.
  • the injected gas-liquid two-phase refrigerant joins with the gas refrigerant flowing through the suction pipe 9 and is heated while cooling the gas refrigerant (gas-liquid two-phase refrigerant: point (i) ⁇ (a), gas refrigerant : Point (h) ⁇ (a)).
  • the refrigerant in the gas-liquid two-phase state flows into the liquid refrigerant supply device 206 to become a medium pressure liquid refrigerant, and then the liquid refrigerant enters the injection pipe 7. To supply.
  • the liquid refrigerant supplied from the liquid refrigerant supply device 6 is decompressed to be in a gas-liquid two-phase state and then injected into the suction pipe 9.
  • the discharge temperature of the compressor 1 can be reduced, deterioration of refrigerant and refrigerating machine oil and fatigue of the seal material of the compressor 1 can be reduced.
  • the liquid refrigerant supply device 206 supplies the liquid single-phase refrigerant to the flow rate regulator 8, the refrigerant in almost the same refrigerant state is supplied to the injection pipe 7 regardless of the outside air temperature and the load condition. can do.
  • FIG. FIG. 16 is a refrigerant circuit diagram illustrating Embodiment 3 of the air-conditioning apparatus 300 of the present invention.
  • symbol is attached
  • the air conditioning apparatus 300 in FIG. 16 is different from the air conditioning apparatus 100 in FIG. 1 in the configuration of the liquid refrigerant supply apparatus 306.
  • the liquid refrigerant supply device 306 in FIG. 16 includes a refrigerant heat exchanger, one of which is connected between the inlet side of the injection pipe 7 and the inlet side of the flow regulator 8, and the other of the flow regulator 8. The outlet side and the outlet side of the injection pipe 7 are connected.
  • the liquid refrigerant supply device 306 exchanges heat between the medium-pressure gas-liquid two-phase refrigerant and the low-temperature low-pressure gas-liquid two-phase refrigerant during the heating operation.
  • FIG. 17 is a refrigerant circuit diagram showing a refrigerant flow when the air-conditioning apparatus 300 in FIG. 16 is injected during the heating operation
  • FIG. 18 is a Ph line when the air-conditioning apparatus 300 in FIG. 16 is injected during the heating operation. It is a graph to show.
  • the portion where the refrigerant flows during the heating operation is indicated by a bold line
  • the portion where the refrigerant does not flow is indicated by a thin line
  • points (a) to (i) in FIG. Indicates the state.
  • the refrigerant that has flowed into the indoor units 20A and 20B is cooled by the use-side heat exchangers 21A and 21B, and becomes medium-pressure gas-liquid two-phase refrigerant in the expansion devices 22A and 22B. Then, after the medium-pressure gas-liquid two-phase refrigerant passes through the pipe 102 from the expansion devices 22A and 22B, a part of the gas-liquid two-phase refrigerant flows into the injection pipe 7, and the liquid refrigerant supply device 306 Is cooled to become a medium-pressure liquid refrigerant (point (d) ⁇ point (g)). The liquid refrigerant flows into the flow regulator 8 and is depressurized (point (g) ⁇ (h)).
  • the refrigerant that has been depressurized by the flow rate regulator 8 to become a gas-liquid two-phase flows into the liquid refrigerant supply device 306 and is heated to become a low-pressure gas-liquid two-phase refrigerant (point (g) ⁇ point (h). ) And injected into the suction pipe 9.
  • the injected gas-liquid two-phase refrigerant merges with the gas refrigerant flowing through the suction pipe 9 and is heated while cooling the gas refrigerant (gas-liquid two-phase refrigerant: point (h) ⁇ (a), gas refrigerant. : Point (f) ⁇ (a)). That is, in the air conditioner 300, when performing injection during heating operation, heat exchange is performed between the refrigerants flowing into the injection pipe 7 to generate medium-pressure liquid refrigerant, and the liquid refrigerant is supplied to the flow regulator 8. It comes to supply.
  • FIG. FIG. 19 is a refrigerant circuit diagram showing Embodiment 4 of the air-conditioning apparatus 400 of the present invention.
  • part which has the same structure as the air conditioning apparatus 100 of FIG. 1 attaches
  • the air conditioning apparatus 400 of FIG. 18 differs from the air conditioning apparatus 100 of FIG.
  • the liquid refrigerant supply device 406 shown in FIG. 19 includes an inter-refrigerant heat exchanger, one of which is connected between the heat source side heat exchanger 3 and the flow rate control device 4, and the other is connected to the inlet side of the injection pipe 7 and the flow rate. It is connected between the inlet side of the regulator 8.
  • the liquid refrigerant supply device 406 exchanges heat between the medium-pressure gas-liquid two-phase refrigerant and the low-temperature low-pressure gas-liquid two-phase refrigerant during the heating operation.
  • FIG. 20 is a refrigerant circuit diagram showing the flow of refrigerant when the air-conditioning apparatus 400 in FIG. 19 performs the heating operation
  • FIG. 21 shows the Ph line when the air-conditioning apparatus 400 in FIG. 19 is injected during the heating operation. It is a graph to show.
  • the portion where the refrigerant flows during the heating operation is indicated by a thick line
  • the portion where the refrigerant does not flow is indicated by a thin line
  • points (a) to (i) in FIG. Indicates the state.
  • the refrigerant that has flowed into the indoor units 20A and 20B is cooled by the use-side heat exchangers 21A and 21B, and becomes medium-pressure gas-liquid two-phase refrigerant in the expansion devices 22A and 22B. Then, after the medium-pressure gas-liquid two-phase refrigerant passes through the pipe 102 from the expansion devices 22A and 22B, a part of the gas-liquid two-phase refrigerant flows into the injection pipe 7, and the rest flows.
  • the refrigerant is depressurized at 4 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant (point (d) ⁇ (e)).
  • the low-temperature and low-pressure refrigerant flows into the liquid refrigerant supply device 406 and is heated (point (e) ⁇ point (f)), and then flows into the heat source side heat exchanger 3.
  • the branched liquid refrigerant passes through the injection pipe 7 and then flows into the liquid refrigerant supply device 406 to be cooled to become medium pressure liquid refrigerant (point (d) ⁇ point (h)).
  • the liquid refrigerant flows into the flow regulator 8 and is depressurized (point (h) ⁇ (i)), and is injected into the suction pipe 9.
  • the injected gas-liquid two-phase refrigerant joins with the gas refrigerant flowing through the suction pipe 9 and is heated while cooling the gas refrigerant (gas-liquid two-phase refrigerant: point (i) ⁇ (a), gas refrigerant : Point (f) ⁇ (a)).
  • the air conditioner 400 when performing injection during heating operation, heat exchange is performed between the refrigerant that has flowed into the injection pipe 7 and the refrigerant that has been depressurized by the flow control device 4, thereby generating medium-pressure liquid refrigerant.
  • the liquid refrigerant is supplied to the flow rate regulator 8.
  • Embodiment 4 even in the case of Embodiment 4 described above, during the cooling operation and the heating operation, by performing heat exchange between the refrigerant that has flowed into the injection pipe 7 and the refrigerant that has been depressurized by the flow control device 4, a medium-pressure liquid can be obtained.
  • the discharge temperature of the compressor 1 can be reduced. Fatigue such as sealing materials can be reduced.
  • the liquid refrigerant supply device 406 supplies the liquid single-phase refrigerant to the flow rate regulator 8, substantially the same refrigerant refrigerant is supplied to the injection pipe 7 regardless of the outside air temperature and the load condition. can do.
  • FIG. FIG. 22 is a refrigerant circuit diagram showing Embodiment 5 of the air-conditioning apparatus 500 of the present invention.
  • symbol is attached
  • the air conditioner 500 of FIG. 22 is different from the air conditioner 100 of FIG. 1 in the configuration of the heat source side heat exchanger 3.
  • the heat source side heat exchanger 503 in FIG. 22 is composed of a water-refrigerant heat exchanger, and performs heat exchange between the refrigerant and water, and is composed of, for example, a plate heat exchanger.
  • the heat source side heat exchanger 503 is connected to a circuit that supplies water, the other is connected to a refrigerant circuit, and the refrigerant exchanges heat with water. It functions as a condenser that condenses and liquefies the refrigerant during the cooling operation, and functions as an evaporator that evaporates and vaporizes the refrigerant during the heating operation. Since the operation of the fifth embodiment is the same as that of the first embodiment, the description thereof is omitted.
  • the heat transfer rate of water is improved, and the discharge temperature can be reduced by improving the performance of the heat source side heat exchanger 503. Further, since the water temperature is maintained at 0 ° C. or higher to prevent freezing, the discharge temperature is reduced and the required injection amount is reduced, so that the flow regulator 8 can be reduced in size and cost.
  • FIGS. 13 to 21 exemplifies a case where a gas-liquid separator is used as the liquid refrigerant supply device 6, but as shown in FIGS. 13 to 21, a liquid consisting of an inter-refrigerant heat exchanger is used.
  • the refrigerant supply devices 206, 306, and 406 may be applied.
  • the embodiments of the present invention are not limited to the above embodiments.
  • the case where the direction of the refrigerant flow path flowing through the pipes 101 and 102 is reversed between the cooling operation and the heating operation is illustrated.
  • four check valves are used. It can also be applied to an air conditioner in which the direction of the refrigerant flow path flowing in the pipes 101 and 102 is the same in the cooling operation and the heating operation by a known method such as a flow path forming unit.

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Abstract

La présente invention concerne un climatiseur comprenant : une conduite d'injection permettant d'injecter un réfrigérant liquide dans le côté entrée d'un compresseur ; un dispositif d'alimentation en réfrigérant liquide qui est disposé entre un échangeur de chaleur côté source de chaleur et un échangeur de chaleur côté utilisation et qui délivre, à la conduite d'injection, le réfrigérant liquide à partir du réfrigérant s'écoulant entre l'échangeur de chaleur côté source de chaleur et l'échangeur de chaleur côté utilisation ; un dispositif de commande de débit qui est disposé sur la conduite d'injection, qui place le réfrigérant liquide délivré à partir du dispositif d'alimentation en réfrigérant liquide dans un état à deux phases gaz-liquide par réduction de sa pression et qui commande le débit du réfrigérant qui est délivré au côté entrée du compresseur ; et un moyen de commande qui commande la quantité d'ouverture du dispositif de commande de débit. Le moyen de commande commande la quantité d'ouverture du dispositif de commande de débit sur la base de la température de refoulement qui est détectée par un capteur de température de refoulement et, lorsque le nombre d'une pluralité d'échangeurs de chaleur côté utilisation en cours de fonctionnement de chauffe diminue, commande la quantité d'ouverture du dispositif de commande de débit en fonction de la vitesse de variation du nombre d'unités en fonctionnement.
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