WO2016174750A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2016174750A1
WO2016174750A1 PCT/JP2015/062888 JP2015062888W WO2016174750A1 WO 2016174750 A1 WO2016174750 A1 WO 2016174750A1 JP 2015062888 W JP2015062888 W JP 2015062888W WO 2016174750 A1 WO2016174750 A1 WO 2016174750A1
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WIPO (PCT)
Prior art keywords
heat exchanger
outdoor
temperature
compressor
outdoor unit
Prior art date
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PCT/JP2015/062888
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English (en)
Japanese (ja)
Inventor
和久 岩▲崎▼
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.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2017515333A priority Critical patent/JP6448775B2/ja
Priority to PCT/JP2015/062888 priority patent/WO2016174750A1/fr
Publication of WO2016174750A1 publication Critical patent/WO2016174750A1/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
    • F24F11/89—Arrangement or mounting of control or safety devices
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the present invention relates to an air conditioner that corrects an excessive increase in high pressure.
  • the present invention has been made to solve the above-described problems, and it is an object of the present invention to provide an air conditioner that corrects an excessive increase in high-pressure pressure and is capable of continuous operation without causing an abnormal stop. .
  • An air conditioner includes at least one outdoor unit and at least one indoor unit connected in parallel to the outdoor unit, wherein the outdoor unit is a variable capacity compressor.
  • the outdoor unit has an expansion valve and an indoor heat exchanger, the compressor, the outdoor heat exchanger, the high and low pressure heat exchanger, the expansion
  • a first pressure sensor for detecting a pressure on the discharge side of the compressor, wherein the valve and the indoor heat exchanger are sequentially connected to each other by pipes to constitute a refrigeration cycle in which the refrigerant circulates;
  • a second pressure sensor for detecting the pressure on the suction side of the compressor, a first temperature sensor for detecting an outside air temperature, and a second temperature sensor for detecting a temperature on the outlet side of the outdoor heat exchanger during cooling operation;
  • the outlet of the high-low pressure heat exchanger during cooling operation A third temperature sensor that detects the temperature of the compressor and a control device that controls the frequency of the compressor.
  • the control device is calculated based on the pressure detected by the first pressure sensor.
  • Evaporating temperature a preset target evaporating temperature, a first increase / decrease value calculated based on the outside temperature detected by the first temperature sensor, the evaporating temperature, the target evaporating temperature, A first temperature calculated based on the condensation temperature calculated based on the pressure detected by the second pressure sensor and the degree of supercooling on the outlet side of the outdoor heat exchanger determined by the temperature detected by the second temperature sensor. 2 based on the increase / decrease value, the evaporation temperature, the target evaporation temperature, the degree of supercooling on the outlet side of the high / low pressure heat exchanger calculated by the condensation temperature and the temperature detected by the third temperature sensor.
  • Calculated A third variation value, the change amount of the frequency of the compressor from the determined which is intended to update the frequency of the compressor based on the bulking decrease value.
  • the frequency of the compressor is increased or decreased in consideration of the ambient load temperature (outside air temperature) and the refrigerant distribution state (supercooling degree) in addition to the evaporation temperature and the target evaporation temperature. Determine the value.
  • the air conditioner can be continuously operated without abnormally stopping.
  • FIG. 1 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • This air conditioner performs a cooling operation or a heating operation using a refrigeration cycle (heat pump cycle) for circulating a refrigerant.
  • a refrigeration cycle heat pump cycle
  • the air conditioner according to Embodiment 1 includes a heat source unit (outdoor unit 10) and two usage-side units (indoor unit 50a and indoor unit 50b) connected by refrigerant piping.
  • the two usage-side units are connected in parallel to one heat source machine to communicate with each other.
  • the air conditioner connects each device (component) mounted on one heat source unit and each device (component) mounted on two usage-side units by refrigerant piping.
  • the refrigerant piping of the air conditioner includes gas branch pipes connected to each indoor unit (a gas branch pipe 206a connected to the indoor unit 50a and a gas branch pipe 206b connected to the indoor unit 50b), and an outdoor unit. 10 and the gas branch pipe 206 connecting the gas branch pipe 206 and the liquid branch pipe connected to each indoor unit (the liquid branch pipe 207a connected to the indoor unit 50a and the liquid branch connected to the indoor unit 50b). A pipe 207b) and a liquid pipe 205 connecting the outdoor unit 10 and the liquid branch pipe 207.
  • the outdoor unit 10 and the indoor unit 50a are connected via a gas pipe 204, a gas branch pipe 206a, a liquid branch pipe 207a, and a liquid pipe 205.
  • the outdoor unit 10 and the indoor unit 50b are connected to the gas pipe 204.
  • the gas branch pipe 206b, the liquid branch pipe 207b, and the liquid pipe 205 are connected to each other.
  • the outdoor unit 10 includes a compressor 1, an oil separator 2, a check valve 3, four-way valves 4-1 and 4-2 (hereinafter also collectively referred to as a four-way valve 4), an outdoor heat exchanger 5, , High / low pressure heat exchanger 6, flow rate adjustment valve 8, liquid side on / off valve 9, gas side on / off valve 11, accumulator 12, oil return bypass capillary 13, oil return bypass solenoid valve 14, bypass A flow rate adjusting valve 7 is mounted.
  • Compressor 1, oil separator 2, check valve 3, four-way valve 4, outdoor heat exchanger 5, high / low pressure heat exchanger 6, flow control valve 8, liquid side on / off valve 9, gas side on / off valve 11, and accumulator 12 are provided so as to be connected in series by a refrigerant pipe.
  • the high / low pressure heat exchanger 6 is provided in the liquid pipe 26 between the outdoor heat exchanger 5 and the flow rate adjusting valve 8.
  • the high / low pressure heat exchanger 6 includes a liquid pipe 26 and a liquid pipe 26 between the high / low pressure heat exchanger 6 and the flow rate adjusting valve 8, that is, a liquid pipe 26 on the upstream side of the high / low pressure heat exchanger 6.
  • a bypass pipe 23 connected to the upstream side of the accumulator 12 is connected.
  • the bypass flow rate adjusting valve 7 is provided in the bypass pipe 23 between the high / low pressure heat exchanger 6 and the flow rate adjusting valve 8.
  • the oil return bypass capillary 13 and the oil return bypass solenoid valve 14 are provided in the oil return bypass circuit 30 connecting the oil separator 2 and the suction pipe 31 connecting the accumulator 12 and the compressor 1. It has been.
  • the oil return bypass capillary 13 is provided to connect the upstream side and the downstream side of the oil return bypass electromagnetic valve 14 so as to bypass the oil return bypass electromagnetic valve 14.
  • a point where the liquid pipe 26 and the bypass pipe 23 are connected is a connection point 25, a pipe on the upstream side of the bypass pipe 23 and the accumulator 12 (a refrigerant pipe between the four-way valve 4 and the accumulator 12). ) Is connected to a connection point 24.
  • the outdoor unit 10 is equipped with a control device 27 that controls driving of each actuator (for example, the compressor 1, the four-way valve 4, an outdoor blower not shown) mounted on the outdoor unit 10.
  • the outdoor unit 10 includes a first pressure sensor 15 (hereinafter, the pressure detected by the first pressure sensor 15 is referred to as 63 hs), a second pressure sensor 16 (hereinafter, the pressure detected by the second pressure sensor 16 is 63 ls).
  • a first temperature sensor 17 (hereinafter, the temperature detected by the first temperature sensor 17 is referred to as th4), a second temperature sensor 18 (hereinafter, the temperature detected by the second temperature sensor 18 is referred to as th7), Third temperature sensor 19 (hereinafter, temperature detected by third temperature sensor 19 is referred to as th3), fourth temperature sensor 20 (hereinafter, temperature detected by fourth temperature sensor 20 is referred to as th2), fifth temperature sensor 21 (hereinafter, the temperature detected by the fifth temperature sensor 21 is referred to as th6), the sixth temperature sensor 22 (hereinafter, the temperature detected by the sixth temperature sensor 22 is referred to as th5), and the seventh temperature Sensor 28 (hereinafter, the temperature detected by the seventh temperature sensor 28 is referred to as th9) is provided.
  • the compressor 1 has an inverter circuit (not shown), and the compressor rotational speed is controlled by power frequency conversion by the inverter circuit, and the capacity is controlled, that is, the capacity is variable. Is compressed to a high temperature and high pressure state.
  • the oil separator 2 is provided on the discharge side of the compressor 1 and has a function of separating the refrigerating machine oil component from the refrigerant gas discharged from the compressor 1 and containing refrigerating machine oil.
  • the check valve 3 is provided in a refrigerant pipe between the oil separator 2 and the four-way valve 4, and prevents reverse flow of the refrigerant to the discharge side of the compressor 1 when the compressor 1 is stopped. .
  • the four-way valve 4 functions as a flow path switching device, and switches the refrigerant flow between the cooling operation and the heating operation.
  • the outdoor heat exchanger 5 functions as a condenser (or a radiator) during cooling operation and as an evaporator during heating operation, and performs heat exchange between air and refrigerant supplied from an outdoor blower (not shown). .
  • the high / low pressure heat exchanger 6 exchanges heat between the refrigerant flowing through the liquid pipe 26 and the refrigerant flowing through the bypass pipe 23.
  • the flow rate adjusting valve 8 is installed on the downstream side of the connection point 25 in the cooling circuit, functions as a pressure reducing valve and an expansion valve, expands the refrigerant by decompressing it, and also flows into the indoor unit 50. The amount is adjusted.
  • the flow rate adjusting valve 8 may be configured by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve.
  • the liquid side on / off valve 9 is opened / closed manually by the control device 27 or may not conduct the refrigerant.
  • the gas side on / off valve 11 is also opened / closed manually by the control device 27 or manually, and may or may not conduct the refrigerant.
  • the liquid side on / off valve 9 and the gas side on / off valve 11b are installed to adjust the pressure fluctuation in the refrigeration cycle by being opened and closed.
  • the accumulator 12 is provided on the suction side of the compressor 1 and stores excess refrigerant circulating in the refrigerant circuit.
  • the bypass flow rate adjusting valve 7 is installed in the bypass pipe 23 between the connection point 25 and the high / low pressure heat exchanger 6, functions as a pressure reducing valve and an expansion valve, and decompresses the refrigerant to expand it. Further, the amount of refrigerant flowing through the bypass pipe 23 is adjusted.
  • the bypass flow rate adjusting valve 7 may be configured by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve.
  • the oil return bypass circuit 30 is configured to return the refrigeration oil separated by the oil separator 2 to the suction side of the compressor 1.
  • the oil return bypass capillary 13 is for adjusting the flow rate of the refrigerating machine oil passing through the oil return bypass circuit 30.
  • the oil return bypass solenoid valve 14 is controlled to open and close to adjust the flow rate of the refrigerating machine oil together with the oil return bypass capillary 13.
  • the first pressure sensor 15 is provided between the oil separator 2 and the four-way valve 4 and detects the pressure (high pressure) of the refrigerant discharged from the compressor 1.
  • the second pressure sensor 16 is provided on the upstream side of the accumulator 12 and detects the pressure (low pressure) of the refrigerant sucked into the compressor 1.
  • the first temperature sensor 17 is provided between the compressor 1 and the oil separator 2 and detects the temperature of the refrigerant discharged from the compressor 1.
  • the second temperature sensor 18 detects the ambient temperature (outside air temperature) of the outdoor unit 10.
  • the third temperature sensor 19 is provided between the outdoor heat exchanger 5 and the high / low pressure heat exchanger 6 and detects the temperature of the refrigerant passing between the outdoor heat exchanger 5 and the high / low pressure heat exchanger 6. It is.
  • the fourth temperature sensor 20 is provided in the bypass pipe 23 after passing through the high / low pressure heat exchanger 6 and detects the temperature of the refrigerant passing through the bypass pipe 23 after passing through the high / low pressure heat exchanger 6.
  • the fifth temperature sensor 21 is provided between the connection point 25 and the flow rate adjustment valve 8, and detects the temperature of the refrigerant passing through the liquid pipe 26 between the connection point 25 and the flow rate adjustment valve 8.
  • the sixth temperature sensor 22 is provided between the connection point 24 and the accumulator 12 and detects the temperature of the refrigerant passing between the connection point 24 and the accumulator 12.
  • the seventh temperature sensor 28 is provided between the accumulator 12 and the compressor 1 and detects the temperature of the refrigerant sucked into the compressor 1.
  • the pressure information detected by each pressure sensor and the temperature information detected by each temperature sensor are sent to the control device 27 as signals.
  • the control device 27 controls each actuator based on signals transmitted from each pressure sensor and each temperature sensor.
  • the type of the control device 27 is not particularly limited.
  • the control device 27 may be composed of a microcomputer that can control each actuator mounted on the outdoor unit 10.
  • an indoor heat exchanger 100a and an expansion valve 101a are mounted in series by a gas branch pipe 206a and a liquid branch pipe 207a.
  • the indoor unit 50a is equipped with a control device 102a that controls driving of each actuator (for example, the expansion valve 101a and an indoor fan not shown) mounted on the indoor unit 50a.
  • the indoor unit 50a is provided with an eighth temperature sensor 103a and a ninth temperature sensor 104a.
  • the indoor heat exchanger 100a functions as an evaporator during the cooling operation and as a condenser (or a radiator) during the heating operation, and performs heat exchange between the refrigerant and the air.
  • the expansion valve 101a functions as a pressure reducing valve and an expansion valve, expands the refrigerant by decompressing it, and adjusts the amount of refrigerant flowing into the indoor heat exchanger 100a.
  • the expansion valve 101a may be constituted by a valve whose opening degree can be variably controlled, for example, an electronic expansion valve.
  • the eighth temperature sensor 103a is provided in the gas branch pipe 206a connected to the indoor heat exchanger 100a, and detects the temperature of the refrigerant at the gas side outlet of the indoor heat exchanger 100a.
  • the ninth temperature sensor 104a is provided in the liquid branch pipe 207a connected to the indoor heat exchanger 100a, and detects the temperature of the refrigerant at the liquid side outlet of the indoor heat exchanger 100a.
  • the temperature information detected by each temperature sensor is sent as a signal to the control device 102a.
  • the control device 102a controls each actuator based on a signal transmitted from each temperature sensor.
  • the type of the control device 102a is not particularly limited.
  • the control device 102a may be composed of a microcomputer that can control each actuator mounted on the indoor unit 50a.
  • the indoor unit 50b has the same configuration as the indoor unit 50a. That is, if the subscript “a” of the component part of the indoor unit 50a is changed to “b”, the component part of the indoor unit 50b is obtained.
  • FIG. 1 shows an example in which a control device is mounted on both the indoor unit 50a and the indoor unit 50b.
  • the single control device controls both the indoor unit 50a and the indoor unit 50b. It may be.
  • the control devices can communicate with each other by wire or wirelessly.
  • the control device mounted on the indoor unit can communicate with the control device mounted on the outdoor unit by wire or wirelessly.
  • the compressor 1 In the cooling circuit of the air conditioner, as indicated by the arrows shown in FIG. 1, the compressor 1, the oil separator 2, the check valve 3, the four-way valve 4, the outdoor heat exchanger 5, the high and low pressure heat exchanger 6, and the flow rate adjusting valve. 8, liquid side opening / closing valve 9, expansion valve (expansion valve 101a and expansion valve 101b), indoor heat exchanger (indoor heat exchanger 100a and indoor heat exchanger 100b), gas side opening / closing valve 11, four-way valve 4, and It is connected so that the refrigerant flows in the order of the accumulator 12.
  • FIG. 2 is a diagram showing a refrigerant distribution in the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the total refrigerant amount in the air conditioner is: refrigerant amount ACC in the accumulator 12 + refrigerant amount in the outdoor heat exchanger 5 + refrigerant amount in the liquid pipe 26 + refrigerant amount in the liquid pipe 205 + It can be determined from the amount of refrigerant in the liquid branch pipe 207 (hereinafter, the liquid pipe 26, the liquid pipe 205, and the liquid branch pipe 207 are collectively referred to as a liquid pipe A).
  • the amount of refrigerant in the outdoor heat exchanger 5 is obtained from the degree of supercooling SCO on the outlet side of the outdoor heat exchanger 5 obtained from the pressure 63 hs detected by the first pressure sensor 15 and th3 detected by the third temperature sensor 19. be able to.
  • the amount of refrigerant in the liquid pipe A is the degree of supercooling SCC on the outlet side of the high / low pressure heat exchanger 6 determined by the pressure 63 hs detected by the first pressure sensor 15 and the temperature th6 detected by the fifth temperature sensor 21. Can be obtained from Therefore, the total amount of refrigerant can be obtained from ACC, SCO, and SCC.
  • the SCO is obtained by the difference between the saturation temperature (condensation temperature) Tc converted from the pressure 63 hs detected by the first pressure sensor 15 and the temperature th3 detected by the third temperature sensor 19, that is, Tc ⁇ th3. It is done. Further, the SCC is obtained by the difference between the saturation temperature (condensation temperature) Tc converted from the pressure 63 hs detected by the first pressure sensor 15 and the temperature th6 detected by the fifth temperature sensor 21, that is, Tc ⁇ th6. It is done.
  • the four-way valve 4 is switched so that the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 5. That is, in the four-way valve 4, piping is connected in the direction of the solid line shown in FIG. Further, the operation is started with the flow rate adjusting valve 8 being fully opened or nearly fully opened, the bypass flow rate adjusting valve 7 being set to an appropriate opening degree, and the expansion valve 101 being set to an appropriate opening degree.
  • the refrigerant flow in this case is as follows.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 first passes through the oil separator 2. At this time, most of the refrigerating machine oil mixed in the refrigerant is separated from the refrigerant, accumulated in the bottom of the inside, passes through the oil return bypass capillary 13 (if the oil return bypass solenoid valve 14 is opened, there is also Pass through) and returned to the suction pipe 31 of the compressor 1. Thereby, the refrigerating machine oil which flows out of the outdoor unit 10 can be reduced, and the reliability of the compressor 1 can be improved.
  • the high-temperature and high-pressure refrigerant in which the ratio of the refrigerating machine oil is reduced passes through the four-way valve 4, is condensed and liquefied by the outdoor heat exchanger 5, and passes through the high-low pressure heat exchanger 6.
  • the refrigerant that has flowed out of the high / low pressure heat exchanger 6 is branched into a refrigerant that flows into the bypass pipe 23 and a refrigerant that flows into the liquid pipe 26.
  • the refrigerant flowing through the bypass pipe 23 is appropriately adjusted in flow rate by the bypass flow rate adjusting valve 7 to become a low-pressure / low-temperature refrigerant, and exchanges heat with the refrigerant exiting the outdoor heat exchanger 5 in the high-low pressure heat exchanger 6. Therefore, the enthalpy is lower in the refrigerant state on the outlet side of the high / low pressure heat exchanger 6 than the refrigerant state on the outlet side of the outdoor heat exchanger 5, that is, the degree of supercooling is increased.
  • the low-pressure refrigerant that has passed through the bypass flow rate adjusting valve 7 and has flowed out of the high-low pressure heat exchanger 6 flows through the bypass pipe 23, and is connected to the connection point 24 where the bypass pipe 23 and the upstream pipe of the accumulator 12 are connected. It reaches. Thereby, since the enthalpy difference increases, the required refrigerant flow rate in the case of the same capacity can be reduced, and there is an effect of performance improvement by reducing pressure loss.
  • the high-pressure refrigerant flowing out of the high-low pressure heat exchanger 6 passes through the flow rate adjustment valve 8, but the flow rate adjustment valve 8 is fully opened, so that it is supplied to the liquid pipe 205 as a high-pressure liquid refrigerant without reducing the pressure.
  • the indoor units 50a and 50b is decompressed by the expansion valves 101a and 101b, becomes a low-pressure two-phase refrigerant, and is evaporated and gasified by the indoor heat exchangers 100a and 100b.
  • the cooling air is supplied to the air-conditioning target space such as a room, and the cooling operation of the air-conditioning target space is realized.
  • the refrigerant that has flowed out of the indoor heat exchangers 100a and 100b passes through the gas pipe 204, the four-way valve 4, and the accumulator 12, and is sucked into the compressor 1 again.
  • the accumulator 12 is provided with a U-shaped tube as shown in FIG. 1, when a gas-liquid two-phase refrigerant flows into the accumulator 12, the liquid refrigerant accumulates in the lower part of the container, and the U-shaped tube. The gas-rich refrigerant that has flowed in through the upper opening flows out of the accumulator 12.
  • a gas-rich refrigerant is sucked into the compressor 1. Therefore, the liquid back of the compressor 1 can be temporarily prevented until the transient liquid and the gas-liquid two-phase refrigerant are accumulated in the accumulator 12 and overflow, and the effect of maintaining the reliability of the compressor 1 is obtained. It is done.
  • FIG. 3 is a flowchart showing a flow of control processing of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the flow of the control processing until the frequency increase / decrease value Fp of the compressor 1 of the air-conditioning apparatus according to Embodiment 1 is determined will be described in detail.
  • the control device 27 The driving of the compressor 1 is started and the operation of the air conditioner is started (step S101).
  • the control device 27 determines whether or not the cooling operation is being performed (step S102). When it is determined that the cooling operation is being performed (Yes in step S102), the control device 27 calculates a first increase / decrease value Fp_th7 of the frequency of the compressor 1 according to the outside air temperature th7.
  • Fp_th7 is the outside air temperature th7, the (current) suction side evaporation temperature (hereinafter referred to as evaporation temperature) Te of the compressor 1, and the suction side target evaporation temperature of the compressor 1 (hereinafter referred to as target evaporation temperature).
  • Table 1 shows Tem as a parameter.
  • the target evaporation temperature Tem is set from a remote controller (not shown) or the like, and a room temperature detected by a room temperature sensor (not shown) set in a room (where the indoor unit 50 is installed). It is determined based on the difference temperature.
  • control device 27 calculates a second increase / decrease value Fp_SCO of the frequency of the compressor 1 according to the SCO.
  • the control device 27 calculates a third increase / decrease value (hereinafter referred to as Fp_SCC) of the frequency of the compressor 1 according to the SCC.
  • Fp is determined by the sum (Fp_th7 + Fp_SCO + Fp_SCC) of Fp_th7, Fp_SCO, and Fp_SCC calculated in steps S103 to S105 (step S106). Then, Fp is added to the current frequency of the compressor 1 to update the frequency of the compressor 1 (step S107). Thereafter, the processes of steps S103 to S107 are performed at predetermined timings, and the frequency of the compressor 1 is updated as needed.
  • the increase / decrease value Fp of the frequency of the compressor 1 is determined only by the evaporation temperature Te and the target evaporation temperature Tem.
  • the ambient load temperature outside air temperature th7
  • the increase / decrease value Fp of the frequency of the compressor 1 is determined by the steps S103 to S106, and the compression is performed based on the values.
  • the frequency of the machine 1 is updated.
  • FIG. 4 is a flowchart showing a flow of control processing of the air-conditioning apparatus according to Embodiment 2 of the present invention.
  • the Fi of the compressor 1 at the start-up is appropriately set from the outside air temperature just before the start-up when the compressor 1 is started and the refrigerant distribution state before the stop.
  • the control device 27 causes the supercooling degree SCO0 on the outlet side of the outdoor heat exchanger 5 when operating before stopping, and the outlet of the high and low pressure heat exchanger 6 when operating before stopping.
  • the subcooling degree SCC0 on the side is calculated to check the refrigerant distribution state in the system (step S201).
  • the control device 27 stops the compressor 1 (step S202). After that (in the case of a configuration with a plurality of outdoor units, after stopping all the units), in order to perform cooling operation by changing the room temperature load or starting the operation of the indoor unit from a remote controller, etc.
  • control device 27 detects the outside air temperature th70 before the compressor 1 is started (immediately) (step S205), and the initial frequency of the compressor 1 with respect to Fit according to the outside air temperature th70. 1 Increase / decrease value Fpi_th7 is determined. Fpi_th7 is expressed as shown in Table 2 using th70 as a parameter. It is set so that Fpi_th7 becomes smaller (decelerates) as th70 is higher (step S206).
  • control device 27 determines an initial second increase / decrease value Fpi_SCO of the frequency of the compressor 1 with respect to Fit according to SCO0.
  • Fpi_SCO is expressed as shown in Table 2 with SCO0 as a parameter.
  • the initial second increase / decrease value Fpi_SCO is set to be smaller (decelerate) as th70 is higher (step S207).
  • control device 27 determines an initial third increase / decrease value Fpi_SCC of the frequency of the compressor 1 with respect to Fit according to SCC0.
  • Fpi_SCC is expressed as shown in Table 2 with SCC0 as a parameter. It is set so that Fpi_SCC becomes smaller (decelerates) as th70 is higher (step S208).
  • the ambient load temperature (outside air temperature th70) and the refrigerant distribution state (the degree of supercooling SCO0 and the degree of supercooling SCC0) are also considered.
  • the initial frequency of the compressor 1 is determined by the steps S206 to S209. Therefore, it becomes possible to correct the excessive increase in pressure due to excessive frequency acceleration when starting up the compressor 1 in a state where the liquid refrigerant is distributed in a large amount in the outdoor heat exchanger. It is possible to correct the pressure overshoot that deviates from the allowable value of the high pressure. As a result, the air conditioner can be continuously operated without abnormally stopping.
  • FIG. 5 is a refrigerant circuit diagram showing a refrigerant circuit configuration of the air-conditioning apparatus according to Embodiment 3 of the present invention.
  • This air conditioner performs a cooling operation or a heating operation using a refrigeration cycle (heat pump cycle) for circulating a refrigerant.
  • a refrigeration cycle heat pump cycle
  • the air conditioner according to the third embodiment has a circuit configuration that does not include the high-low pressure heat exchanger 6 as compared with the air conditioner according to the first embodiment.
  • the total amount of refrigerant in the air conditioner according to Embodiment 3 is: refrigerant amount ACC in accumulator 12 + refrigerant amount in outdoor heat exchanger 5 + liquid pipe A (liquid pipe 26, liquid pipe 205, and liquid branch pipe) 207).
  • the refrigerant amount in the outdoor heat exchanger 5 and the refrigerant amount in the liquid pipe A are determined by the pressure 63 hs detected by the first pressure sensor 15 and the th3 detected by the third temperature sensor 19, and the outlet of the outdoor heat exchanger 5. It can be determined from the degree of supercooling SCO on the side. Therefore, the total refrigerant amount can be obtained from ACC and SCO.
  • the SCO is obtained by the difference between the saturation temperature (condensation temperature) Tc converted from the pressure 63 hs detected by the first pressure sensor 15 and the temperature th3 detected by the third temperature sensor 19, that is, Tc ⁇ th3. It is done.
  • FIG. 6 is a flowchart showing a flow of control processing of the air-conditioning apparatus according to Embodiment 3 of the present invention.
  • the flow of the control processing until the frequency increase / decrease value Fp of the compressor 1 of the air-conditioning apparatus according to Embodiment 3 is determined will be described in detail.
  • the control device 27 The driving of the compressor 1 is started and the operation of the air conditioner is started (step S301).
  • the control device 27 determines whether or not the cooling operation is being performed (step S102). When determining that the cooling operation is being performed (Yes in step S302), the control device 27 calculates a first increase / decrease value Fp_th7 of the frequency of the compressor 1 according to the outside air temperature th7.
  • Fp_th7 is the outside air temperature th7, the (current) suction side evaporation temperature (hereinafter referred to as evaporation temperature) Te of the compressor 1, and the suction side target evaporation temperature of the compressor 1 (hereinafter referred to as target evaporation temperature).
  • Table 1 shows Tem as a parameter.
  • the target evaporation temperature Tem is set from a remote controller (not shown) or the like, and a room temperature detected by a room temperature sensor (not shown) set in a room (where the indoor unit 50 is installed). It is determined based on the difference temperature.
  • the control device 27 calculates a second increase / decrease value Fp_SCO of the frequency of the compressor 1 according to the SCO.
  • Fp is determined by Fp_th7 calculated in steps S303 to S304 and the sum of Fp_SCO (Fp_th7 + Fp_SCO) (step S305). Then, Fp is added to the current frequency of the compressor 1 to update the frequency of the compressor 1 (step S306). Thereafter, the processes in steps S303 to S306 are performed at predetermined timings, and the frequency of the compressor 1 is updated as needed.
  • FIG. 7 is a flowchart showing a flow of control processing of the air-conditioning apparatus according to Embodiment 4 of the present invention.
  • the air-conditioning apparatus according to Embodiment 4 has the same refrigerant circuit configuration as that of Embodiment 3.
  • the flow of the control process until the initial frequency Fi of the compressor 1 of the air-conditioning apparatus according to Embodiment 4 is determined will be described in detail.
  • the Fi of the compressor 1 at the start-up is appropriately set from the outside air temperature just before the start-up when the compressor 1 is started and the refrigerant distribution state before the stop.
  • the control device 27 causes the supercooling degree SCO0 on the outlet side of the outdoor heat exchanger 5 when operating before stopping, and the outlet of the high and low pressure heat exchanger 6 when operating before stopping.
  • the subcooling degree SCC0 on the side is calculated to check the refrigerant distribution state in the system (step S401).
  • the control device 27 stops the compressor 1 (step S402). After that (in the case of a configuration with a plurality of outdoor units, after stopping all the units), in order to perform cooling operation by changing the room temperature load or starting the operation of the indoor unit from a remote controller, etc.
  • control device 27 detects the outside air temperature th70 before the compressor 1 is started (immediately) (step S405), and the initial frequency of the compressor 1 with respect to the Fit according to the outside air temperature th70. 1 Increase / decrease value Fpi_th7 is determined. Fpi_th7 is expressed as shown in Table 2 using th70 as a parameter. It is set so that Fpi_th7 becomes smaller (decelerates) as th70 is higher (step S406).
  • control device 27 determines an initial second increase / decrease value Fpi_SCO of the frequency of the compressor 1 with respect to Fit according to SCO0.
  • Fpi_SCO is expressed as shown in Table 2 with SCO0 as a parameter.
  • the initial second increase / decrease value Fpi_SCO is set to be smaller (decelerate) as th70 is higher (step S407).
  • FIG. 8 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of an air-conditioning apparatus according to Embodiment 5 of the present invention.
  • This air conditioner performs a cooling operation or a heating operation using a refrigeration cycle (heat pump cycle) for circulating a refrigerant.
  • a refrigeration cycle heat pump cycle
  • the air-conditioning apparatus includes two heat source units (outdoor unit 10a and outdoor unit 10b) and two use side units (indoor unit 50a and indoor unit 50b). And are connected by refrigerant piping.
  • the two usage-side units are connected in parallel to the two heat source units so as to communicate with each other. That is, the air conditioner connects each device (component) mounted on the two heat source units and each device (component) mounted on the two usage-side units through refrigerant piping.
  • a refrigerant circuit reffrigeration cycle
  • the configuration includes two indoor units.
  • the configuration is not limited to this, and may be one or three or more.
  • the refrigerant piping of the air conditioner includes a gas branch pipe connected to each outdoor unit (a gas branch pipe 202a connected to the outdoor unit 10a and a gas branch pipe 202b connected to the outdoor unit 10b), and each indoor unit.
  • Gas branch pipes connected to the machine gas branch pipe 206a connected to indoor unit 50a and gas branch pipe 206b connected to indoor unit 50b
  • gas branch pipe 202 and gas branch pipe 206 are connected.
  • Common gas piping 204 liquid branch pipes connected to each outdoor unit (liquid branch pipe 203a connected to outdoor unit 10a and liquid branch pipe 203b connected to outdoor unit 10b), The liquid branch pipe (liquid branch pipe 207a connected to the indoor unit 50a and the liquid branch pipe 207b connected to the indoor unit 50b), the liquid branch pipe 203, and the liquid branch pipe 207 are connected to each other.
  • a common liquid piping 205 consisting of.
  • FIG. 8 shows an example in which the gas distributor 200a and the liquid distributor 200b are mounted on the air conditioner, but the present invention is not limited to mounting the gas distributor 200a and the liquid distributor 200b.
  • the gas branch pipe 202a, the gas branch pipe 202b, and the gas pipe 204 constitute a gas pipe
  • the liquid branch pipe 203a, the liquid branch pipe 203b, and the liquid pipe 205 constitute a liquid pipe.
  • the outdoor unit 10a and the indoor unit 50a are connected via a gas branch pipe 202a, a gas pipe 204, a gas branch pipe 206a, a liquid branch pipe 207a, a liquid pipe 205, and a liquid branch pipe 203a.
  • the indoor unit 50b is connected to the gas branch pipe 202a, the gas pipe 204, the gas branch pipe 206b, the liquid branch pipe 207b, the liquid pipe 205, and the liquid branch pipe 203a.
  • the outdoor unit 10b and the indoor unit 50a are connected via a gas branch pipe 202b, a gas pipe 204, a gas branch pipe 206a, a liquid branch pipe 207a, a liquid pipe 205, and a liquid branch pipe 203b.
  • the outdoor unit 10b and the indoor unit 50b are connected via a gas branch pipe 202b, a gas pipe 204, a gas branch pipe 206b, a liquid branch pipe 207b, a liquid pipe 205, and a liquid branch pipe 203b.
  • the outdoor unit 10a includes a compressor 1a, an oil separator 2a, a check valve 3a, four-way valves 4-1a and 4-2a (hereinafter also collectively referred to as a four-way valve 4a), an outdoor heat exchanger 5a, , High / low pressure heat exchanger 6a, flow rate adjusting valve 8a, liquid side on / off valve 9a, gas side on / off valve 11a, accumulator 12a, oil return bypass capillary 13a, oil return bypass solenoid valve 14a, bypass And a flow rate adjusting valve 7a.
  • Compressor 1a oil separator 2a, check valve 3a, four-way valve 4a, outdoor heat exchanger 5a, high / low pressure heat exchanger 6a, flow rate adjusting valve 8a, liquid side on / off valve 9a, gas side on / off valve 11a, and accumulator 12a is provided so that it may be connected in series by refrigerant piping.
  • the high / low pressure heat exchanger 6a is provided in the liquid pipe 26a between the outdoor heat exchanger 5a and the flow rate adjusting valve 8a.
  • the high / low pressure heat exchanger 6a includes a liquid pipe 26a and a liquid pipe 26a between the high / low pressure heat exchanger 6a and the flow rate adjusting valve 8a, that is, a liquid pipe 26a upstream of the high / low pressure heat exchanger 6a.
  • a bypass pipe 23a connected to the upstream side of the accumulator 12a is connected.
  • the bypass flow rate adjusting valve 7a is provided in the bypass pipe 23a between the high / low pressure heat exchanger 6a and the flow rate adjusting valve 8a.
  • the oil return bypass capillary 13a and the oil return bypass solenoid valve 14a are provided in the oil return bypass circuit 30a connecting the oil separator 2a and the suction pipe 31a connecting the accumulator 12a and the compressor 1a. It has been.
  • the oil return bypass capillary 13a is provided to connect the upstream side and the downstream side of the oil return bypass solenoid valve 14a so as to bypass the oil return bypass solenoid valve 14a.
  • a point where the liquid pipe 26a and the bypass pipe 23a are connected is a connection point 25a, a pipe on the upstream side of the bypass pipe 23a and the accumulator 12a (a refrigerant pipe between the four-way valve 4a and the accumulator 12a). ) Is connected to a connection point 24a.
  • the outdoor unit 10a is equipped with a control device 27a for controlling the driving of each actuator (for example, the compressor 1a, the four-way valve 4a, an outdoor fan not shown) mounted on the outdoor unit 10a.
  • the outdoor unit 10a includes a first pressure sensor 15a (hereinafter, pressure detected by the first pressure sensor 15a is referred to as 63hsa), a second pressure sensor 16a (hereinafter, pressure detected by the second pressure sensor 16a is 63 lsa).
  • a first temperature sensor 17a (hereinafter, the temperature detected by the first temperature sensor 17a is referred to as th4a), a second temperature sensor 18a (hereinafter, the temperature detected by the second temperature sensor 18a is referred to as th7a), Third temperature sensor 19a (hereinafter, temperature detected by third temperature sensor 19a is referred to as th3a), fourth temperature sensor 20a (hereinafter, temperature detected by fourth temperature sensor 20a is referred to as th2a), fifth temperature sensor 21a (hereinafter, the temperature detected by the fifth temperature sensor 21a is referred to as th6a), a sixth temperature sensor 22a (hereinafter, the sixth temperature sensor 22a) It refers to the detected temperature Th5a), and, the seventh temperature sensor 28a (hereinafter, the temperature detected by the seventh temperature sensor 28a is referred to as Th9a) is provided.
  • Th9a the seventh temperature sensor 28a
  • the outdoor unit 10b has the same configuration as the outdoor unit 10a. That is, if the subscript “a” of the component part of the outdoor unit 10a is changed to “b”, the component part of the outdoor unit 10b is obtained.
  • FIG. 8 shows an example in which a control device is mounted on both the outdoor unit 10a and the outdoor unit 10b, but it is assumed that a single control device controls both the outdoor unit 10a and the outdoor unit 10b. It may be. Further, in a state where the control device is mounted on both the outdoor unit 10a and the outdoor unit 10b, the control devices can communicate with each other by wire or wirelessly.
  • an indoor heat exchanger 100a and an expansion valve 101a are mounted in series by a gas branch pipe 206a and a liquid branch pipe 207a.
  • the indoor unit 50a is equipped with a control device 102a that controls driving of each actuator (for example, the expansion valve 101a and an indoor fan not shown) mounted on the indoor unit 50a.
  • the indoor unit 50a is provided with an eighth temperature sensor 103a and a ninth temperature sensor 104a.
  • the indoor unit 50b has the same configuration as the indoor unit 50a. That is, if the subscript “a” of the component part of the indoor unit 50a is changed to “b”, the component part of the indoor unit 50b is obtained.
  • FIG. 8 shows an example in which a control device is mounted on both the indoor unit 50a and the indoor unit 50b.
  • the single control device controls both the indoor unit 50a and the indoor unit 50b. It may be.
  • the control devices can communicate with each other by wire or wirelessly.
  • the control device mounted on the indoor unit can communicate with the control device mounted on the outdoor unit by wire or wirelessly.
  • a compressor compressor 1a and compressor 1b
  • an oil separator oil separator 2a and oil separator 2b
  • a check valve check valve 3a and Check valve 3b
  • four-way valve four-way valve
  • outdoor heat exchanger outdoor heat exchanger 5a and outdoor heat exchanger 5b
  • high-low pressure heat exchanger high-low pressure heat exchanger 6a and high Low pressure heat exchanger 6b
  • flow rate regulating valves flow rate regulating valve 8a and flow rate regulating valve 8b
  • liquid side on / off valve liquid side on / off valve 9a and liquid side on / off valve 9b
  • expansion valve expansion valve (expansion valve 101a and expansion valve 101b).
  • Indoor heat exchanger indoor heat exchanger 100a and indoor heat exchanger 100b
  • gas side on / off valve gas side on / off valve 11a and gas side on / off valve 11b
  • four-way valve 4 accumulator (accumulator) It is connected so that the refrigerant flows in the order of over motor 12a and the accumulator 12b).
  • the four-way valves 4a and 4b are switched so that the refrigerant discharged from the compressors 1a and 1b flows into the outdoor heat exchangers 5a and 5b. That is, in the four-way valve 4a and the four-way valve 4b, piping is connected in the direction of the solid line shown in FIG. Further, the operation is started with the flow rate adjusting valves 8a and 8b being fully opened or close to being fully opened, the bypass flow rate adjusting valves 7a and 7b being set to appropriate openings, and the expansion valves 101a and 101b being set to appropriate openings.
  • the refrigerant flow in this case is as follows.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressors 1a and 1b first passes through the oil separators 2a and 2b. At this time, most of the refrigerating machine oil mixed in the refrigerant is separated from the refrigerant and stored in the inner bottom portion, and passes through the oil return bypass capillaries 13a and 13b (the oil return bypass solenoid valves 14a and 14b are opened). In this case, it passes there) and is returned to the suction pipe of the compressor 1a. Thereby, the refrigeration oil which flows out of the outdoor units 10a and 10b can be reduced, and the reliability of the compressors 1a and 1b can be improved.
  • the refrigerant distribution state can be calculated from the degree of supercooling SCCa and SCCb on the outlet side of the high and low pressure heat exchangers 6a and 6b determined by the five temperature sensors 21a and 21b.
  • SCOa and SCOb are saturation temperatures (condensation temperatures) Tca and Tcb converted from the pressures 63hsa and 63hsb detected by the first pressure sensors 15a and 15b, and temperatures th3a and th3b detected by the third temperature sensors 19a and 19b. Temperature difference, that is, Tca ⁇ th3a and Tcb ⁇ th3b.
  • SCCa and SCCb are saturation temperatures (condensation temperatures) Tca and Tcb converted from pressures 63hsa and 63hsb detected by the first pressure sensors 15a and 15b, and temperatures th6a and th6b detected by the fifth temperature sensors 21a and 21b. Temperature difference, i.e., Tca-th6a and Tcb-th6b.
  • the refrigerant flowing out of the high and low pressure heat exchangers 6a and 6b is branched into a refrigerant flowing through the bypass pipes 23a and 23b and a refrigerant flowing through the liquid pipes 26a and 26b.
  • the refrigerant flowing through the bypass pipes 23a, 23b is moderately adjusted in flow rate by the bypass flow rate adjusting valves 7a, 7b to become low-pressure / low-temperature refrigerant, and the refrigerant that has exited the outdoor heat exchangers 5a, 5b and the high-low pressure heat exchanger 6a, Heat exchange is performed in 6b.
  • the enthalpy is lower in the refrigerant state on the outlet side of the high and low pressure heat exchangers 6a and 6b than the refrigerant state on the outlet side of the outdoor heat exchangers 5a and 5b, that is, the degree of supercooling is increased.
  • the high pressure and the low pressure represent the relative relationship of the pressure in the refrigerant circuit (the same applies to the temperature).
  • the high-pressure refrigerant flowing out of the high-low pressure heat exchangers 6a and 6b passes through the flow rate adjusting valves 8a and 8b.
  • the high-pressure liquid refrigerant is not reduced. Supplied to the liquid pipe 205. Then, it enters into the indoor units 50a and 50b, is decompressed by the expansion valves 101a and 101b, becomes a low-pressure two-phase refrigerant, and is evaporated and gasified by the indoor heat exchangers 100a and 100b.
  • the cooling air is supplied to the air-conditioning target space such as a room, and the cooling operation of the air-conditioning target space is realized.
  • the refrigerant that has flowed out of the indoor heat exchanger 100 passes through the gas pipe 204, the four-way valve 4, and the accumulators 12a and 12b, and is again sucked into the compressors 1a and 1b.
  • the accumulators 12a and 12b are provided with U-shaped tubes as shown in FIG. 8, when the gas-liquid two-phase refrigerant flows into the accumulators 12a and 12b, the liquid refrigerant is accumulated in the lower part of the container.
  • the gas-rich refrigerant flowing in from the upper opening of the U-shaped tube flows out of the accumulators 12a and 12b.
  • gas-rich refrigerant is sucked into the compressors 1a and 1b.
  • the liquid back of the compressors 1a and 1b can be temporarily prevented until the transient liquid and the gas-liquid two-phase refrigerant are accumulated in the accumulators 12a and 12b and overflow, and the reliability of the compressors 1a and 1b can be prevented.
  • the effect of maintaining sex is obtained.
  • FIG. 9 is a refrigerant circuit diagram showing the flow of the refrigerant in the air-conditioning apparatus according to Embodiment 5 of the present invention
  • FIG. 10 shows the flow of control processing of the air-conditioning apparatus according to Embodiment 5 of the present invention. It is a flowchart to show.
  • the flow of the control processing for adjusting the refrigerant amount between the outdoor units 10 of the air-conditioning apparatus according to Embodiment 5 will be described in detail.
  • the controller 27a, 27b when the controller 27a, 27b is operating before stopping, the degree of supercooling SCO0 (SCO0a, SCO0b) on the outlet side of the outdoor heat exchanger 5a, 5b when operating before stopping, and when operating before stopping
  • the subcooling degree SCC0 (SCC0a, SCC0b) on the outlet side of the high and low pressure heat exchangers 6a, 6b is calculated to check the refrigerant distribution state in the system (step S501).
  • the control device stops the compressor (step S502).
  • one of the two outdoor units is outdoors.
  • the control device the control device 27a or the control device 27b
  • the two outdoor units were operating simultaneously (both cooling operations) immediately before stopping, or one of the outdoor units (the outdoor unit 10a (the compressor 1a) or the outdoor unit 10b (the compressor 1b)) ) Determines whether the single lung operation (cooling operation) was performed (step S504).
  • step S504 When one outdoor unit is operated in one lung (No in step S504), the operation is the same as that in step S204 and subsequent steps in FIG. 4, and the description is omitted (step S511).
  • step S5 When the two outdoor units are operating simultaneously (both are in cooling operation) (Yes in step S504), SCO0a and SCO0b are compared (step S505).
  • thermo-ON permission signal is transmitted to the outdoor unit 10a by the control device 27a so that the outdoor unit 10a is started at the time of startup (step S506a).
  • control device 27 opens the bypass flow rate adjustment valve 7b of the outdoor unit 10b that is stopped. Then, excess liquid refrigerant existing between the check valve 3c and the flow rate adjustment valve 8c in the refrigerant circuit of the outdoor unit 10c is transferred to the operating outdoor unit 10a according to the arrow in FIG.
  • step S508a When the degree of supercooling SCOa on the outlet side of the outdoor heat exchanger 5a of the outdoor unit 10a currently in operation (current state) exceeds SCO0b (Yes in step S508a), the bypass flow rate adjustment valve 7b is closed. This is assumed to be performed (step S509a). Therefore, it is determined by the above-described operation that the transfer of the refrigerant has been completed and the refrigerant has been properly distributed, and the operation proceeds to the operation after step S204 in FIG. 4 (step S510a).
  • Step S506b to S510b have the same contents if the subscript “a” is changed to “b” in the above-described Steps S506a to S510a, and thus description thereof is omitted.
  • the high pressure is excessive due to the influence of the liquid refrigerant excessively distributed in the outdoor unit 10b (or the outdoor unit 10a). It can correct rising.
  • the refrigerant distribution state is determined from th7, SCO, and SCC as in the first embodiment shown in FIG. 3, and the excessive increase in the high pressure is corrected.
  • FIG. 11 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of an air-conditioning apparatus according to Embodiment 6 of the present invention.
  • the air-conditioning apparatus includes three heat source units (outdoor unit 10a, outdoor unit 10b, and outdoor unit 10c), and two usage-side units (indoor unit 50a). And the indoor unit 50b) are connected by a refrigerant pipe.
  • the two usage-side units are connected in parallel to the three heat source machines and communicate with each other. That is, the air conditioner connects each device (component) mounted on the three heat source units and each device (component) mounted on the two usage-side units by means of refrigerant piping.
  • the configuration includes three outdoor units and two indoor units.
  • the present invention is not limited to this, and the number of outdoor units may be four or more. The number may be three or more, and the same applies to the seventh embodiment described later.
  • FIG. 12 is a refrigerant circuit diagram illustrating the flow of the refrigerant in the air-conditioning apparatus according to Embodiment 6 of the present invention
  • FIG. 13 illustrates the flow of control processing of the air-conditioning apparatus according to Embodiment 6 of the present invention. It is a flowchart to show. Hereinafter, based on FIG. 13, the flow of the control processing for adjusting the refrigerant amount between the outdoor units of the air-conditioning apparatus according to Embodiment 6 will be described in detail.
  • the control device was operating before the stop, and the degree of supercooling SCO0 (SCO0a, SCO0b, SCO0c) on the outlet side of the outdoor heat exchangers 5a, 5b, 5c when operating before the stop.
  • the supercooling degree SCC0 (SCC0a, SCC0b, SCC0c) on the outlet side of the high and low pressure heat exchangers 6a, 6b, 6c is calculated to check the refrigerant distribution state in the system (step S601).
  • the control device stops the compressor (step S602). Thereafter, in order to perform cooling operation from a state in which all the outdoor units are stopped, by a room temperature load change or an operation start operation of the indoor unit from a remote controller, etc., one of the three outdoor units is When receiving an instruction to activate the outdoor unit (the outdoor unit 10a, the outdoor unit 10b, or the outdoor unit 10c) (when a thermo-ON signal is transmitted to the outdoor unit 10a, the outdoor unit 10b, or the outdoor unit 10c) (step S603), Whether all three outdoor units were operating simultaneously (all cooling operations) immediately before stopping by the control device (control device 27a, control device 27b, or control device 27c) (step S604), one or two It is determined whether the outdoor unit is operating (cooling operation) (step S605).
  • step S605 When one outdoor unit is operating (No in step S604, Yes in step S605), the operation is the same as that in step S204 and subsequent steps in FIG. 4, and thus description thereof is omitted (step S611). Further, when two outdoor units are operating (both are in cooling operation) (No in step S604, No in step S605), the operation is the same as that after step S505 in FIG. (Step S612).
  • thermo-ON permission signal is transmitted to the outdoor unit 10a by the control device 27a so that the outdoor unit 10a (compressor 1a) having the smallest SCO0 is started at the time of startup (step S606).
  • control device 27c opens the bypass flow rate adjustment valve 7c of the stopped outdoor unit 10c having the largest SCO0. Excess liquid refrigerant existing between the check valve 3c and the flow rate adjusting valve 8c in the refrigerant circuit of the outdoor unit 10c is transferred to the operating outdoor unit 10a according to the arrow in FIG.
  • Embodiment 7 FIG.
  • Embodiment 7 of the present invention will be described. However, the description of (the part of) overlapping with Embodiments 1 to 6 is omitted, and the same or corresponding parts as Embodiments 1 to 6 are omitted. Are given the same symbols.
  • FIG. 14 is a refrigerant circuit diagram showing the flow of refrigerant in the air-conditioning apparatus according to Embodiment 7 of the present invention
  • FIG. 15 shows the flow of control processing of the air-conditioning apparatus according to Embodiment 7 of the present invention. It is a flowchart to show.
  • the flow of the control processing for adjusting the refrigerant amount between the outdoor units 10 of the air-conditioning apparatus according to Embodiment 7 will be described in detail.
  • the control device was operating before the stop, and the degree of supercooling SCO0 (SCO0a, SCO0b, SCO0c) on the outlet side of the outdoor heat exchangers 5a, 5b, 5c when operating before the stop.
  • the subcooling degree SCC0 (SCC0a, SCC0b, SCC0c) on the outlet side of the high and low pressure heat exchangers 6a, 6b, 6c is calculated to check the refrigerant distribution state in the system.
  • step S702 When receiving a command to stop the outdoor unit due to a change in room temperature load or an operation of stopping the indoor unit from a remote controller or the like, the control device stops the compressor (step S702). Thereafter, in order to perform the cooling operation from the state in which all the outdoor units are stopped, by the room temperature load change or the operation start operation of the indoor unit from a remote controller or the like, among the three outdoor units, SCO0 is SCOavg0.
  • step S703 When a command for starting less than the number of outdoor units is received (when a thermo-ON signal is transmitted to the number of outdoor units whose number is less than SCOavg0) (step S703), all three outdoor units are immediately stopped by the control device. Are simultaneously operating (all cooling operations) (step S704), and it is determined whether the two outdoor units are operating (cooling operation) (step S705).
  • step S712 When one outdoor unit is operating (No in step S704, Yes in step S705), the operation is the same as that in step S204 and subsequent steps in FIG. 4, and thus the description thereof is omitted (step S711). Further, when the two outdoor units are in operation (both are in cooling operation) (No in step S704, No in step S705), the operation is the same as that after step S505 in FIG. (Step S712).
  • step S704 When all three outdoor units are operating simultaneously (all cooling operations) (Yes in step S704), the controller turns on the outdoor unit so that the outdoor unit (compressor) whose SCO0 is less than SCOavg0 is activated.
  • a permission signal is transmitted (step S706).
  • an outdoor unit whose SCO0 is less than SCOavg0 is an outdoor unit 10a
  • an outdoor unit whose SCO0 is SCOavg0 or more is an outdoor unit 10b or 10c.
  • the thermo-ON permission signal is transmitted to the outdoor unit 10a by the control device 27a so that the outdoor unit 10a whose SCO0 is less than SCOavg0 is activated at the time of activation.
  • control devices 27b and 27c open the bypass flow rate adjusting valves 7b and 7c of the stopped outdoor units 10b and 10c whose SCO0 is SCOavg0 or more. Between the excess liquid refrigerant existing between the check valve 3b and the flow rate adjustment valve 8b in the refrigerant circuit of the outdoor unit 10b, and between the check valve 3c and the flow rate adjustment valve 8c in the refrigerant circuit of the outdoor unit 10c. Excess liquid refrigerant present is transferred to the outdoor unit 10a in operation according to the arrow in FIG.
  • the high and low pressure heat exchanger 6b is connected to the bypass pipe 23b, the four-way valve 4-1b, the gas side on / off valve 11b, the gas branch pipe 202d, the gas branch pipe 202c, the gas side on / off valve. 11a and the four-way valve 4-1a, and is transferred to the accumulator 12a.
  • the bypass flow rate adjusting valve 7c the bypass pipe 23c, the four-way valve 4-1c, the gas side on-off valve 11c, the gas branch pipe 202e, the gas branch pipe 202f, and the gas branch pipe 202c are connected from the high / low pressure heat exchanger 6c. Then, the gas passes through the gas-side on-off valve 11a and the four-way valve 4-1a, and is transferred to the accumulator 12a (step S707).
  • Step S709 the degree of supercooling SCOa on the outlet side of the outdoor heat exchanger 5a of the outdoor unit 10a currently operating (current state) (in FIG. 15, the current outdoor heat exchange in the outdoor unit where SCO0 is less than SCOavg0)
  • the bypass flow rate adjusting valves 7b and 7c are closed (Step S709). Therefore, it is determined by the above-described operation that the transfer of the refrigerant has been completed and the refrigerant has been properly distributed, and the operation proceeds to step S204 and subsequent steps in FIG. 4 (step S710).

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Abstract

L'invention porte sur un dispositif de climatisation dans lequel, pendant des opérations de refroidissement, un dispositif de commande (27) détermine la valeur augmentée/diminuée de la fréquence d'un compresseur (1) de premières valeurs augmentées/diminuées à des troisièmes valeurs augmentées/diminuées et met à jour la fréquence du compresseur (1) sur la base de ladite valeur augmentée/diminuée. La première valeur augmentée/diminuée est calculée sur la base de la température d'évaporation calculée sur la base de la pression détectée par un premier capteur de pression (15), d'une température d'évaporation cible prédéfinie et de la température de l'air extérieur détectée par une première sonde de température (17). La deuxième valeur augmentée/diminuée est calculée sur la base de la température d'évaporation, de la température d'évaporation cible et du degré de surfusion du côté sortie d'un échangeur de chaleur extérieur (5), qui est déterminé par la température de condensation calculée sur la base de la pression détectée par un second capteur de pression (16) et la température détectée par une deuxième sonde de température (18). La troisième valeur augmentée/diminuée est calculée sur la base de la température d'évaporation, de la température d'évaporation cible et du degré de surfusion du côté sortie d'un échangeur de chaleur à haute et basse pression (6) qui est calculé par la température de condensation et la température détectée par une troisième sonde de température (19).
PCT/JP2015/062888 2015-04-28 2015-04-28 Dispositif de climatisation WO2016174750A1 (fr)

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CN111536677A (zh) * 2020-05-13 2020-08-14 广东美的制冷设备有限公司 空调回油控制方法、空调及可读存储介质
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CN113654223A (zh) * 2021-07-19 2021-11-16 青岛海尔空调器有限总公司 目标排气温度的确定方法
CN113932399A (zh) * 2020-07-13 2022-01-14 广东美的暖通设备有限公司 防冻控制方法、装置、冷热水机及计算机存储介质
CN114484830A (zh) * 2022-01-14 2022-05-13 青岛海尔空调器有限总公司 空调器的控制方法、控制系统、电子设备和储存介质
CN114608263A (zh) * 2022-03-11 2022-06-10 长虹美菱股份有限公司 一种基于电子膨胀阀的冰箱制冷系统速冻控制方法
WO2022215889A1 (fr) * 2021-04-07 2022-10-13 삼성전자주식회사 Climatiseur et son procédé de commande
WO2023246531A1 (fr) * 2022-06-20 2023-12-28 青岛海尔空调器有限总公司 Appareil et procédé de commande de réfrigération d'un climatiseur, climatiseur et support de stockage

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CN112032975A (zh) * 2019-06-04 2020-12-04 青岛海尔空调器有限总公司 空调器的控制方法
CN111397080B (zh) * 2020-03-27 2021-07-16 广东美的制冷设备有限公司 高温除菌下的回油控制方法、空调器及计算机存储介质
CN111397080A (zh) * 2020-03-27 2020-07-10 广东美的制冷设备有限公司 高温除菌下的回油控制方法、空调器及计算机存储介质
CN111536677B (zh) * 2020-05-13 2021-11-23 广东美的制冷设备有限公司 空调回油控制方法、空调及可读存储介质
CN111536677A (zh) * 2020-05-13 2020-08-14 广东美的制冷设备有限公司 空调回油控制方法、空调及可读存储介质
CN113932399A (zh) * 2020-07-13 2022-01-14 广东美的暖通设备有限公司 防冻控制方法、装置、冷热水机及计算机存储介质
CN113932399B (zh) * 2020-07-13 2023-07-07 广东美的暖通设备有限公司 防冻控制方法、装置、冷热水机及计算机存储介质
WO2022215889A1 (fr) * 2021-04-07 2022-10-13 삼성전자주식회사 Climatiseur et son procédé de commande
CN113654223A (zh) * 2021-07-19 2021-11-16 青岛海尔空调器有限总公司 目标排气温度的确定方法
WO2023000551A1 (fr) * 2021-07-19 2023-01-26 青岛海尔空调器有限总公司 Procédé de détermination de température d'échappement cible
CN114484830A (zh) * 2022-01-14 2022-05-13 青岛海尔空调器有限总公司 空调器的控制方法、控制系统、电子设备和储存介质
CN114608263A (zh) * 2022-03-11 2022-06-10 长虹美菱股份有限公司 一种基于电子膨胀阀的冰箱制冷系统速冻控制方法
WO2023246531A1 (fr) * 2022-06-20 2023-12-28 青岛海尔空调器有限总公司 Appareil et procédé de commande de réfrigération d'un climatiseur, climatiseur et support de stockage

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