EP3236168B1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
EP3236168B1
EP3236168B1 EP14908405.5A EP14908405A EP3236168B1 EP 3236168 B1 EP3236168 B1 EP 3236168B1 EP 14908405 A EP14908405 A EP 14908405A EP 3236168 B1 EP3236168 B1 EP 3236168B1
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EP
European Patent Office
Prior art keywords
refrigerant
outdoor
compressor
heat exchanger
expansion device
Prior art date
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Application number
EP14908405.5A
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German (de)
English (en)
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EP3236168A4 (fr
EP3236168A1 (fr
Inventor
Tadashi ARIYAMA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3236168A4 publication Critical patent/EP3236168A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2113—Temperatures of a suction accumulator

Definitions

  • the present invention relates to an air-conditioning apparatus for performing air-conditioning and the like by using a refrigeration cycle (heat-pump cycle) and particularly to an air-conditioning apparatus with improved comfort when an indoor unit is performing a heating operation.
  • a refrigeration cycle heat-pump cycle
  • An air-conditioning apparatus including a plurality of outdoor units and performing the heating operation even during the defrosting operation to maintain comfort during the defrosting operation is disclosed (see Patent Literature 1 and Patent Literature 2, for example) to cope with the aforementioned problem.
  • an intensity of a load of the entire system is determined when the defrosting operation is to be performed, and the defrosting operation is performed when a temperature on an indoor side lowers to result in a sense of discomfort, even if the defrosting operation is performed while the heating operation is continued.
  • Document JP 2008 175410 A discloses an an air-conditioning apparatus according to the preamble of claim 1.
  • the refrigerant amount runs short in the defrosting-operation side outdoor unit, which results in an excessive rise in a compressor discharge temperature or the like, while in the heating-operation side outdoor unit, the refrigerant amount increases and causes a liquid inflow (liquid-back) in a large quantity into the compressor or the like, and there is a problem that stable operation cannot be performed.
  • the present invention was made to solve the problems as above and has an object to provide an air-conditioning apparatus including a plurality of outdoor units, which corrects biased refrigerant amounts between outdoor units (between the heating-operation side outdoor unit and the defrosting-operation side outdoor unit) and performing a stable operation when the defrosting operation is performed while the heating operation is continued.
  • the at least one outdoor unit performs the defrosting operation in which the first expansion device is opened, the discharging refrigerant from the compressor is bypassed to the outdoor heat exchanger through the hot-gas bypass pipe, the third expansion device is closed, and the opening degree of the second expansion device is regulated when the other outdoor units are performing the heating operation, the bias in the refrigerant amount between the outdoor units can be corrected, and the stable operation can be performed without causing the excessive rise in the discharge temperature of the compressor, the liquid back or the like.
  • Fig. 1 is a refrigerant circuit diagram showing an example of an air-conditioning apparatus 1 according to an embodiment of the present invention.
  • the air-conditioning apparatus 1 is installed in a building, an apartment and the like and capable of a cooling operation and a heating operation at the same time by using a refrigeration cycle (heat-pump cycle) for circulating refrigerant (refrigerant for air-conditioning). Moreover, the air-conditioning apparatus 1 performs a defrosting operation.
  • a refrigeration cycle heat-pump cycle
  • refrigerant refrigerant for air-conditioning
  • the air-conditioning apparatus 1 includes, as illustrated in Fig. 1 , outdoor units (heat-source side units) 100A and 100B, an indoor unit (load side unit) 200, and a controller 300.
  • the outdoor units 100A and 100B are connected to the indoor unit 200 in parallel by refrigerant pipes, respectively, and constitute a refrigerant circuit that is an essential part and perform heating or cooling in a target space by causing the refrigerant to be circulated in the refrigerant circuit.
  • the air-conditioning apparatus 1 is constituted such that the two outdoor units 100A and 100B are connected to the single indoor unit 200, however, the configuration is not particularly limited as long as there is a plurality (two units) or more of the outdoor units 100.
  • the refrigerant pipe includes a gas pipe 105 through which a gas refrigerant (gas refrigerant) flows and a liquid pipe 106 through which a liquid refrigerant (liquid refrigerant or two-phase gas-liquid refrigerant) flows.
  • the refrigerant circulated in the refrigerant circuit is not particularly limited and it is R410A, R404A, HFO (hydro fluoro olefin) or the like that is an HFC-based refrigerant or CO 2 , ammonium or the like that is a natural refrigerant.
  • the outdoor unit 100A includes a compressor 101A, a four-way valve 102A, an outdoor heat exchanger (heat-source side heat exchanger) 103A, an accumulator 104A, a first valve 107A, a second valve 108A, a fan 109A, a first temperature sensor 110A, a second temperature sensor 111A, a third temperature sensor 112A, a first pressure sensor 113A, a second pressure sensor 114A, a liquid bypass pipe 115A, a bypass expansion device 116A, a refrigerant heat exchanger 117A, a hot-gas bypass pipe 118A, and an outdoor-side connection pipe 119A and the constitution is accommodated in a main body case 120A.
  • the indoor unit 200 includes an indoor heat exchanger (load-side heat exchanger) 201, an expansion unit 202, and a fan 203, and the constitution is accommodated in a housing 204.
  • indoor heat exchanger load-side heat exchanger
  • expansion unit 202 expansion unit
  • fan 203 fan
  • the compressor 101A, the four-way valve 102A, the indoor heat exchanger 201, the expansion unit 202, the refrigerant heat exchanger 117A, the outdoor heat exchanger 103A, and the accumulator 104A are sequentially connected by pipes.
  • the hot-gas bypass pipe 118A for bypassing discharging refrigerant flowing from the compressor 101A toward the four-way valve 102A to the outdoor heat exchanger 103A so that it flows to the outdoor heat exchanger 103A without passing through the four-way valve 102A is provided.
  • the liquid bypass pipe 115A for bypassing low-temperature refrigerant flowing from the indoor unit 200 toward the outdoor heat exchanger 103A to an inlet of the accumulator 104A (suction side of the compressor 101A) is provided.
  • the compressor 101A compresses to turn the suctioned refrigerant in a high-temperature/high-pressure state.
  • the four-way valve 102A switches a flow of the refrigerant flowing through the refrigerant circuit between a cooling operation and a heating operation.
  • the outdoor heat exchanger 103A exchanges heat between ambient air and the refrigerant flowing in the outdoor heat exchanger 103A.
  • the outdoor heat exchanger 103A serves as an evaporator, for example, and evaporates and gasifies the refrigerant.
  • the outdoor heat exchanger 103A serves as a radiator (condenser) and condenses and liquefies the refrigerant.
  • the outdoor unit 100A includes a single heat exchanger
  • it may be constituted including a plurality of heat exchangers.
  • the fan 109A is configured to blow air to the outdoor heat exchanger 103A.
  • the accumulator 104A is disposed between the suction side of the compressor 101A and the four-way valve 102A and stores excess refrigerant.
  • the accumulator 104A is a container for storing the excess refrigerant, for example.
  • the bypass expansion device 116A is disposed at a position at which the bypass expansion device 116A can regulate a passage of the liquid bypass pipe 115A.
  • the refrigerant heat exchanger 117A is disposed in a passage of the outdoor-side connection pipe 119A closer to the outdoor heat exchanger 103A side than a branch point to the liquid bypass pipe 115A and in a passage of the liquid bypass pipe 115A in the connection pipes between the expansion unit 202 and the outdoor heat exchanger 103A.
  • the bypass expansion device 116A and the refrigerant heat exchanger 117A are devices for exchanging heat between refrigerant in a liquid (liquid refrigerant) (high-temperature, high-pressure) flowing out of the outdoor heat exchanger 103A and refrigerant at a low-temperature low-pressure subjected to flow rate control by the bypass expansion device 116A during the cooling operation and for supercooling the refrigerant to be supplied to the indoor unit 200, for example.
  • the liquid flowing through the bypass expansion device 116A is returned to the accumulator 104A via the liquid bypass pipe 115A.
  • a first valve 107A and a second valve 108A are solenoid valves, for example, and control the flow rate of the refrigerant flowing through the refrigerant circuit by regulating the opening degrees thereof.
  • the first valve 107A is disposed at a position at which the first valve 107A can control a passage of the hot-gas bypass pipe 118A.
  • the second valve 108A is disposed at a position at which the second valve 108A can control a passage of the outdoor-side connection pipe 119A.
  • the first valve 107A and the second valve 108A may be opening and closing valves. Moreover, it may be so constituted that a three-way valve is provided instead of the first valve 107A and the second valve 108A for switching between the passage of the hot-gas bypass pipe 118A and the passage between a header 134 and the outdoor heat exchanger 103A.
  • the first pressure sensor 113A is a sensor for detecting a pressure of the refrigerant and detects a pressure of the refrigerant flowing into the accumulator 104A (or a pressure of the refrigerant on the suction side of the compressor 101A).
  • the first temperature sensor 110A is a thermistor, for example, and detects a temperature of the refrigerant flowing into the accumulator 104A (or a temperature of the refrigerant on the suction side of the compressor 101A).
  • a saturation temperature of the refrigerant flowing into the accumulator 104A is obtained from the pressure of the first pressure sensor 113A, and whether a state of the refrigerant flowing into the accumulator 104A is a superheated gas or not can be determined by comparing the saturation temperature with the temperature of the first temperature sensor 110A.
  • the second pressure sensor 114A is a sensor for detecting a pressure of the refrigerant and detects a pressure of the refrigerant discharged from the compressor 101A.
  • the second temperature sensor 111A is a thermistor, for example, and detects a temperature of the refrigerant discharged from the compressor 101A.
  • a saturation temperature of the refrigerant discharged from the compressor 101A is obtained from the pressure of the second pressure sensor 114A, and whether a state of the refrigerant discharged from the compressor 101A is a superheated gas or not can be determined by comparing it with the temperature of the second temperature sensor 111A.
  • the third temperature sensor 112A is a thermistor, for example, and detects a temperature of the refrigerant flowing through the outdoor heat exchanger 103A.
  • the third temperature sensor 112A is installed between the outdoor heat exchanger 103A and the four-way valve 102A so that the third temperature sensor 112A detects a refrigerant temperature on a refrigerant outflow side in a cooling operation or in a defrosting operation and detects the refrigerant temperature on a refrigerant inflow side in the heating operation. Therefore, based on a detection result of the third temperature sensor 112A, it can be determined whether the outdoor unit 100A is performing a defrosting operation or performing a heating operation.
  • the indoor heat exchanger 201 exchanges heat between ambient air and the refrigerant flowing in the indoor heat exchanger 201.
  • the indoor heat exchanger 201 serves as an evaporator, for example, and evaporates and gasifies the refrigerant.
  • the indoor heat exchanger 201 serves as a radiator (condenser) and condenses and liquefies the refrigerant.
  • the expansion unit 202 serves as a pressure reducing valve or an expansion valve, and reduces or expands a pressure of the refrigerant.
  • the expansion unit 202 is an electronic expansion valve capable of variable control of an opening degree, for example, and executes fine flow control by regulating the opening degree.
  • the expansion unit 202 may be inexpensive refrigerant flow control means such as a capillary tube.
  • the outdoor unit 100B includes a compressor 101B, a four-way valve 102B, an outdoor heat exchanger (heat-source side heat exchanger) 103B, an accumulator 104B, a first valve 107B, a second valve 108B, a fan 109B, a first temperature sensor 110B, a second temperature sensor 111B, a third temperature sensor 112B, a first pressure sensor 113B, a second pressure sensor 114B, a liquid bypass pipe 115B, a bypass expansion device 116B, a refrigerant heat exchanger 117B, and a hot-gas bypass pipe 118B, and these constitutions are accommodated in a main body case 120B.
  • the compressor 101B of the outdoor unit 100B corresponds to the compressor 101A of the outdoor unit 100A.
  • the four-way valve 102B, the outdoor heat exchanger 103B, the accumulator 104B, the first valve 107B, the second valve 108B, the fan 109B, the first temperature sensor 110B, the second temperature sensor 111B, the third temperature sensor 112B, the first pressure sensor 113B, the second pressure sensor 114B, the liquid bypass pipe 115B, the bypass expansion device 116B, the refrigerant heat exchanger 117B, the hot-gas bypass pipe 118B, and the outdoor-side connection pipe 119B also correspond to each of those with the same reference numerals of the outdoor unit 100A.
  • the outdoor unit 100B has constitution similar to that of the outdoor unit 100A, detailed description will be omitted. Moreover, since the refrigerant circuit of the air-conditioning apparatus 1 for the outdoor unit 100B and the indoor unit 200 is also similar to the refrigerant circuit of the air-conditioning apparatus 1 for the outdoor unit 100A and the indoor unit 200, the detailed description will be omitted.
  • the outdoor unit 100A and the outdoor unit 100B may be disposed in the same housing.
  • a two-way valve and a three-way valve may be used in combination instead of the four-way valve 102.
  • the air-conditioning apparatus 1 is assumed to perform the cooling operation and the heating operation but it may be so constituted that the cooling operation is not performed and in that case, the four-way valve 102 is not needed.
  • the outdoor units 100A and 100B and the indoor unit 200 are connected by the gas pipe 105 and the liquid pipe 106 via headers 132 and 134.
  • the refrigerant flowing out of the outdoor units 100A and 100B merges at the header 132, while the refrigerant flowing out of the indoor unit 200 branches at the header 134.
  • the refrigerant flowing out of the outdoor units 100A and 100B merges at the header 134, while the refrigerant flowing out of the indoor unit 200 branches at the header 132.
  • the controller 300 is constituted by a microcomputer or the like, for example, and controls the outdoor units 100 and the indoor unit 200 of the air-conditioning apparatus 1 in accordance with various operations.
  • the controller 300 controls the bypass expansion device 116 in accordance with each value of the first pressure sensor 113A, the first temperature sensor 110A, the second pressure sensor 114A, and the second temperature sensor 111A.
  • the bypass expansion device 116 corresponds to the "second expansion device” of the present invention, the first valve 107 to the “first expansion device” of the present invention, the second valve 108 to the “third expansion device” of the present invention, and the expansion unit 202 to the "indoor expansion device” of the present invention.
  • a high pressure or a low pressure is assumed to mean a relative relationship of a pressure in the refrigerant circuit.
  • a high temperature or a low temperature is, likewise, assumed to mean a relative relationship of a temperature in the refrigerant circuit.
  • a main entity of the operation of the air-conditioning apparatus 1 described below is the controller 300.
  • the first valves 107A and 107B are closed, and the second valves 108A and 108B are opened.
  • the high-temperature/high-pressure gas (gas) refrigerant pressurized in the compressors 101A and 101B in the outdoor units 100A and 100B flows into the header 132 via the four-way valves 102A and 102B.
  • the gas refrigerant pressurized in the compressor 101A and the gas refrigerant pressurized in the compressor 101B merge at the header 132 and flows into the indoor unit 200.
  • the gas refrigerant having flowed into the indoor unit 200 passes through the indoor heat exchanger 201, exchanges heat with ambient air and is condensed. Then, the pressure of the refrigerant having flowed out of the indoor heat exchanger 201 is controlled by the expansion unit 202, and the liquid at an intermediate pressure or the refrigerant in the two-phase gas-liquid state branches at the header 134 and flows into the outdoor units 100A and 100B.
  • the refrigerant having flowed into the outdoor units 100A and 100B exchanges heat with the ambient air by passing through the outdoor heat exchangers 103A and 103B and is evaporated and becomes gas refrigerant.
  • This gas refrigerant is suctioned into the compressors 101A and 101B via the four-way valves 102A and 102B and the accumulators 104A and 104B.
  • the refrigerant having been suctioned into the compressors 101A and 101B is pressurized again and is discharged.
  • the heating operation is performed in the outdoor unit 100B. It may be so constituted that the defrosting operation is performed in the outdoor unit 100B, and the heating operation is performed in the outdoor unit 100A.
  • the air-conditioning apparatus 1 performs the defrosting operation while the heating operation is continued by performing the defrosting operation in either one of the outdoor unit 100A and the outdoor unit 100B and by performing the heating operation in the other of the outdoor unit 100A and the outdoor unit 100B.
  • the first valve 107A is opened, and the second valve 108A is closed.
  • a part of the high-temperature refrigerant discharged from the compressor 101A passes through the first valve 107A and flows into the outdoor heat exchanger 103A.
  • a part other than those flowing into the outdoor heat exchanger 103A flows into the header 132 and merges with the refrigerant having flowed out of the outdoor unit 100B at the header 132 and flows into the indoor unit 200.
  • the heating operation is performed in the outdoor unit 100B. That is, the high-temperature/high-pressure gas refrigerant pressurized in the compressor 101B passes through the gas pipe 105 and flows into the indoor unit 200.
  • the gas refrigerant having flowed into the indoor unit 200 passes through the indoor heat exchanger 201 and becomes the liquid at the intermediate pressure or brings into the two-phase gas-liquid state.
  • the liquid at the intermediate pressure or the refrigerant in the two-phase gas-liquid state passes through the liquid pipe 106 and passes through the outdoor heat exchanger 103B of the outdoor unit 100B and becomes the gas refrigerant.
  • This gas refrigerant is suctioned into the compressor 101A again and is pressurized and discharged.
  • the outdoor unit 100A a part of the high-temperature refrigerant discharged from the compressor 101A flows into the indoor heat exchanger 201 of the indoor unit 200.
  • the low-temperature refrigerant having flowed out of the indoor unit 200 does not flow into the outdoor unit 100A since the second valve 108A is closed and thus, a refrigerant amount is biased to the outdoor unit 100B into which the low-temperature refrigerant flows.
  • the bypass expansion device 116A of the outdoor unit 100A is opened so that the low-temperature refrigerant from the liquid pipe 106 passes through the liquid bypass pipe 115A and is returned also to (the accumulator 104A of) the outdoor unit 100A without passing through the outdoor heat exchanger 103A.
  • the liquid refrigerant is returned also to the outdoor unit 100A without lowering the defrosting performance of the air-conditioning apparatus 1, and bias in the refrigerant amount between the outdoor units 100 (between the outdoor unit 100A and the outdoor unit 100B) can be prevented.
  • the liquid bypass pipe 115A and the bypass expansion device 116A can be used for supercooling the refrigerant to be supplied to the indoor unit 200 in the cooling operation in the refrigerant heat exchanger 117A.
  • Fig. 2 is a control flowchart in the defrosting operation of the air-conditioning apparatus 1 according to the embodiment of the present invention.
  • Fig. 2 is a flowchart illustrating a control flow relating to opening-degree control of the bypass expansion device 116A for preventing bias in the refrigerant amount between the outdoor units 100 in the defrosting operation.
  • the bias in the refrigerant amount between the outdoor units 100 is determined by a degree of superheat (SH-A) of the refrigerant at the accumulator 104A inlet (or the suction side of the compressor 101A) of the outdoor unit 100A performing the defrosting operation.
  • SH-A degree of superheat
  • the degree of superheat (SH-A) of the refrigerant at the accumulator 104A inlet is calculated from a difference between the saturation temperature acquired from a value of the first pressure sensor 113A and a value of the first temperature sensor 110A (STEP11).
  • SH-A acquired from the above is 3 degrees C (a first threshold value determined in advance) or more, it is determined that the liquid refrigerant has not been returned to the outdoor unit 100A, and the bypass expansion device 116A is opened only by a value X determined in advance (the opening degree of the bypass expansion device 116A is set to +X).
  • SH-A is less than 3 degrees C, the opening degree of the bypass expansion device 116A is not changed (STEP12).
  • Whether excess refrigerant has been returned or not to the outdoor unit 100A is determined by the degree of superheat (TdSH-A) of the refrigerant on a discharge side of the compressor 101A of the outdoor unit 100A performing the defrosting operation.
  • the degree of superheat (TdSH-A) of the refrigerant on the discharge side of the compressor 101A is calculated from a difference between the saturation temperature acquired from a value of the second pressure sensor 114A and a value of the second temperature sensor 111A (STEP13).
  • TdSH-A acquired from the above is less than 20 degrees C (a second threshold value determined in advance)
  • the bypass expansion device 116A is closed only by the value X determined in advance (the opening degree of the bypass expansion device 116A is set to -X).
  • TdSH-A is 20 degrees C or more
  • the opening degree of the bypass expansion device 116A is not changed (STEP14).
  • the liquid refrigerant flowing into the outdoor unit 100A performing the defrosting operation is controlled, and the bias in the refrigerant amount between the outdoor units 100 can be corrected.
  • the refrigerant control illustrated in Fig. 2 is also applied similarly when the outdoor unit 100 performing the defrosting operation is switched or in the case where the number of the outdoor units 100 is three or more.
  • the air-conditioning apparatus 1 when the other outdoor unit 100 is performing the heating operation, at least one unit of the outdoor unit 100 performs the defrosting operation in which the first valve 107 is opened, the discharging refrigerant from the compressor 101 is bypassed to the outdoor heat exchanger 103 via the hot-gas bypass pipe 118, the second valve 108 is closed, and the opening degree of the bypass expansion device 116 is regulated, whereby the bias in the refrigerant amount between the outdoor units 100 can be corrected, and stable operation can be performed without causing the excessive rise in the discharge temperature of the compressor 101, the liquid back or the like.
  • the opening degree of the bypass expansion device 116 is regulated in accordance with the degree of superheat (SH-A) of the refrigerant at the inlet of the accumulator 104 and the degree of superheat (TdSH-A) of the refrigerant on the discharge side of the compressor 101A. Then, the low-temperature refrigerant from the liquid pipe 106 is returned also to (the accumulator 104 of) the outdoor unit 100 performing the defrosting operation via the liquid bypass pipe 115 without passing through the outdoor heat exchanger 103.
  • SH-A degree of superheat
  • TdSH-A degree of superheat
  • the bias in the refrigerant amount between the outdoor units 100 can be corrected, and stable operation can be performed without causing the excessive rise in the discharge temperature of the compressor 101, the liquid back or the like.
  • the first threshold value and the second threshold value are not limited to the aforementioned values but are determined in accordance with a type of the refrigerant and the like. Moreover, a value at which the bypass expansion device 116A is opened when the value is the first threshold value or more and a value at which the bypass expansion device 116A is closed when the value is less than the second threshold value may be different values.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)

Claims (5)

  1. Appareil de climatisation (1) comprenant :
    au moins deux unités extérieures (100A, 100B) sur chacune desquelles sont montés un compresseur (101A, 101B) et un échangeur de chaleur extérieur (103A, 103B) ; et
    au moins une unité intérieure (200) sur laquelle sont montés un dispositif d'expansion intérieur (202) et un échangeur de chaleur intérieur (201),
    les unités extérieures (100A, 100B) étant connectées à l'unité intérieure (200) en parallèle,
    le compresseur (101A, 101B), l'échangeur de chaleur intérieur (201), le dispositif d'expansion intérieur (202), et l'échangeur de chaleur extérieur (103A, 103B), étant connectés séquentiellement par des canalisations, et constituant un circuit de fluide frigorigène dans lequel circule un fluide frigorigène,
    l'unité extérieure (100A, 100B) comprenant
    une canalisation de dérivation des gaz chauds (118A, 118B) destinée à dériver le fluide frigorigène d'évacuation en provenance du compresseur (101A, 101B) vers l'échangeur de chaleur extérieur (103A, 103B) ;
    un premier dispositif d'expansion (107A, 107B) configuré pour réguler le débit du fluide frigorigène circulant à travers la canalisation de dérivation des gaz chauds (118A, 118B) ;
    une canalisation de dérivation de liquide (115A, 115B) se ramifiant à partir d'une canalisation de connexion, destinée à connecter l'unité intérieure (200) et l'échangeur de chaleur extérieur (103A, 103B), et connectée à un côté aspiration du compresseur (101A, 101B) ;
    un deuxième dispositif d'expansion (116) configuré pour réguler le débit du fluide frigorigène circulant à travers la canalisation de dérivation de liquide (115A, 115B) ; caractérisé en ce que l'appareil de climatisation (1) comprend en outre
    un troisième dispositif d'expansion (108) configuré pour réguler le débit du fluide frigorigène circulant à travers une canalisation de connexion du côté extérieur (119A, 119B), agencé d'un côté de l'échangeur de chaleur extérieur (103A, 103B) par rapport à un point de ramification à partir de la canalisation de dérivation de liquide (115A, 115B) dans la canalisation de connexion,
    et un contrôleur (300) configuré pour commander la ou les unités extérieures (100A, 100B) afin de procéder à une opération de dégivrage dans laquelle le premier dispositif d'expansion (107A, 107B) est ouvert, le fluide frigorigène d'évacuation en provenance du compresseur (101A, 101B) est dérivé vers l'échangeur de chaleur extérieur (103A, 103B) à travers la canalisation de dérivation des gaz chauds (118A, 118B), le troisième dispositif d'expansion (108) est fermé, et le degré d'ouverture du deuxième dispositif d'expansion (116) est régulé lorsque les autres unités extérieures (100A, 100B) exécutent une opération de chauffage.
  2. Appareil de climatisation (1) selon la revendication 1, où le contrôleur (300) est configuré, lors de la commande de l'unité extérieure (100A, 100B) pour exécuter l'opération de dégivrage, pour réguler le degré d'ouverture du deuxième dispositif d'expansion (116) selon le degré de surchauffe du fluide frigorigène du côté d'aspiration du compresseur (101A, 101B) et le degré de surchauffe du fluide frigorigène du côté évacuation du compresseur (101A, 101B).
  3. Appareil de climatisation (1) selon la revendication 2, où le contrôleur (300) est configuré, lors de la commande de l'unité extérieure (100A, 100B) pour exécuter l'opération de dégivrage, lorsque le degré de surchauffe du fluide frigorigène du côté aspiration du compresseur (101A, 101B) se situe à une première valeur de seuil déterminée à l'avance ou plus, pour augmenter le degré d'ouverture du deuxième dispositif d'expansion (116) seulement d'une valeur déterminée à l'avance ; et
    lorsque le degré de surchauffe du fluide frigorigène du côté évacuation du compresseur (101A, 101B) est inférieur à une seconde valeur de seuil déterminée à l'avance, pour diminuer le degré d'ouverture du deuxième dispositif d'expansion (116) seulement d'une valeur déterminée à l'avance.
  4. Appareil de climatisation (1) selon la revendication 3, où l'unité extérieure (100A, 100B) comprend
    un premier capteur de pression (113A, 113B) configuré pour détecter la pression du fluide frigorigène du côté aspiration du compresseur (101A, 101B),
    un premier capteur de température (110A, 110B) configuré pour détecter la température du fluide frigorigène du côté aspiration du compresseur (101A, 101B),
    un second capteur de pression (114A, 114B) configuré pour détecter la pression du fluide frigorigène du côté évacuation du compresseur (101A, 101B), et
    un second capteur de température (111A, 111B) configuré pour détecter la température du fluide frigorigène du côté évacuation du compresseur (101A, 101B), où,
    lors de la commande de l'unité extérieure (100A, 100B) pour exécuter l'opération de dégivrage, le contrôleur (300) est configuré pour calculer le degré de surchauffe du fluide frigorigène du côté aspiration du compresseur (101A, 101B), à partir la différence entre une température de saturation acquise à partir d'une valeur du premier capteur de pression (113A, 113B), et une valeur du premier capteur de température (110A, 110B) ; et
    pour calculer le degré de surchauffe du fluide frigorigène du côté évacuation du compresseur (101A, 101B), à partir la différence entre une température de saturation acquise à partir d'une valeur du second capteur de pression (114A, 114B), et une valeur du second capteur de température (111A, 111B).
  5. Appareil de climatisation (1) selon l'une quelconque des revendications 1 à 4, où
    l'unité extérieure (100A, 100B) comprend un échangeur de chaleur de fluide frigorigène (117A, 117B), configuré pour échanger la chaleur entre le fluide frigorigène circulant à travers la canalisation de connexion du côté extérieur (119A, 119B), et le fluide frigorigène circulant à travers la canalisation de dérivation de liquide (115A, 115B).
EP14908405.5A 2014-12-17 2014-12-17 Dispositif de climatisation Active EP3236168B1 (fr)

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US11156393B2 (en) * 2016-07-07 2021-10-26 Mitsubishi Electric Corporation Air-conditioning apparatus with pressure control for defrosting and heating
WO2020161834A1 (fr) * 2019-02-06 2020-08-13 三菱電機株式会社 Dispositif à cycle frigorifique
JP7214533B2 (ja) * 2019-03-29 2023-01-30 三菱重工サーマルシステムズ株式会社 空気調和機
JP7225001B2 (ja) * 2019-03-29 2023-02-20 三菱重工サーマルシステムズ株式会社 空気調和機
US20220186993A1 (en) * 2019-05-21 2022-06-16 Mitsubishi Electric Corporation Air-conditioning apparatus

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JP2002286273A (ja) * 2001-03-28 2002-10-03 Mitsubishi Electric Corp 空気調和装置
JP5258197B2 (ja) * 2007-01-16 2013-08-07 三菱電機株式会社 空気調和システム
JP5274174B2 (ja) * 2008-09-18 2013-08-28 三菱電機株式会社 空気調和装置
JP5352512B2 (ja) * 2010-03-31 2013-11-27 日立アプライアンス株式会社 空気調和機
JP5517891B2 (ja) * 2010-11-16 2014-06-11 三菱電機株式会社 空気調和装置
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WO2016098195A1 (fr) 2016-06-23
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EP3236168A1 (fr) 2017-10-25
JPWO2016098195A1 (ja) 2017-04-27

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