WO2014002145A1 - Climatiseur et son procédé de commande - Google Patents

Climatiseur et son procédé de commande Download PDF

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Publication number
WO2014002145A1
WO2014002145A1 PCT/JP2012/004235 JP2012004235W WO2014002145A1 WO 2014002145 A1 WO2014002145 A1 WO 2014002145A1 JP 2012004235 W JP2012004235 W JP 2012004235W WO 2014002145 A1 WO2014002145 A1 WO 2014002145A1
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WIPO (PCT)
Prior art keywords
discharge gas
heat exchanger
compressor
cooling
cooling device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2012/004235
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English (en)
Japanese (ja)
Inventor
悟 梁池
加藤　央平
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2012/004235 priority Critical patent/WO2014002145A1/fr
Priority to US14/402,447 priority patent/US20150153079A1/en
Priority to GB1421070.2A priority patent/GB2517346B/en
Priority to JP2014522229A priority patent/JPWO2014002145A1/ja
Publication of WO2014002145A1 publication Critical patent/WO2014002145A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0089—Systems using radiation from walls or panels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/54—Heating and cooling, simultaneously or alternatively
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve

Definitions

  • the present invention relates to an air conditioner and a control method thereof, and more particularly, to an air conditioner that performs a cooling operation and a heating operation and a control method thereof.
  • the compressor In the air conditioner, there are reciprocal type, screw type, scroll type, rotary type and the like structures for the compressor that generates the driving force for circulating the refrigerant.
  • it is common to enclose refrigeration oil for lubrication of the sliding portion.
  • it is necessary to continue to supply the compressor with a predetermined concentration and a predetermined amount.
  • the refrigerating machine oil is more than the required amount during stable operation so as to continue to supply a predetermined amount and a predetermined amount to the compressor. May be enclosed.
  • an oil separator is installed at the discharge part of the compressor, the refrigeration oil and the refrigerant are separated by this oil separator, and the separated refrigeration oil is returned to the compressor, so that A method for reducing the concentration of oil circulating in the water has been proposed (see, for example, Patent Documents 1 and 2). Further, it has been disclosed that the separation efficiency is improved by cooling the compressor discharge gas to about the condensation temperature of the refrigerant and separating the gaseous refrigerating machine oil (see, for example, Patent Document 3).
  • JP 62-80473 A Japanese Utility Model Publication No. 02-131171 JP-A-62-98170
  • 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 capable of improving COP both during cooling operation and during heating operation, and a control method therefor. It is what.
  • An air conditioner has a refrigerant circuit in which a compressor, a discharge gas cooling device, an oil separator, a four-way valve, an indoor heat exchanger, an expansion valve, and an outdoor heat exchanger are connected in an annular shape.
  • the air conditioner is capable of cooling operation and heating operation by switching the flow path by the operation determining means for determining whether the operation state is the cooling operation or the heating operation, and the operation determining means is the cooling operation. If it is determined that there is, the discharge gas cooling device is controlled so as to cool the discharge gas discharged from the compressor, and if it is determined that the heating operation is being performed, the discharge gas cooling device is controlled so as not to cool the discharge gas. And a heat dissipation control means.
  • the discharge gas is cooled by the discharge gas cooling device to promote separation in the oil separator to lower the oil circulation rate and improve the COP.
  • cooling of the discharge gas can be stopped to suppress the heat radiation in the discharge gas cooling device, and the reduction in COP can be reduced.
  • FIG. 2 is a ph diagram showing an operation state during cooling operation of the air conditioner of FIG. 1.
  • FIG. 2 is a ph diagram showing an operation state during heating operation of the air conditioner of FIG. 1.
  • It is a graph which shows the relationship between the pressure loss of a compressor suction
  • It is a graph which shows the relationship between the oil circulation rate and COP ratio in the air conditioning apparatus of FIG.
  • FIG. 1 is a schematic diagram showing Embodiment 1 of an air-conditioning apparatus of the present invention.
  • An air conditioner 100 in FIG. 1 performs both a cooling operation and a heating operation, and includes a compressor 1, a discharge gas cooling device 2, an oil separator 3, a four-way valve 4 as a flow path switch, an indoor heat. It has a refrigerant circuit in which the exchanger 6, the expansion valve 8, and the outdoor heat exchanger 9 are annularly connected by a refrigerant circuit.
  • the compressor 1, the discharge gas cooling device 2, the oil separator 3, the four-way valve 4, the expansion valve 8, and the outdoor heat exchanger 9 constitute an outdoor unit 10
  • the indoor heat exchanger 6 is an indoor unit 11. Is configured.
  • the outdoor unit 10 and the indoor unit 11 are connected by a gas side extension pipe 5 and a refrigerant liquid side extension pipe 7, and the refrigerant is connected to the outdoor unit 10 and the indoor unit via the gas side extension pipe 5 and the refrigerant liquid side extension pipe 7. Cycle between 11 and 11.
  • the compressor 1 uses the refrigerant sent from the four-way valve 4 as a high-temperature and high-pressure discharge gas.
  • Various methods can be used as the compressor 1.
  • As the compressor 1 that generates the driving force for circulating the refrigerant various techniques such as a reciprocating type, a screw type, a scroll type, and a rotary type can be used.
  • the discharge gas cooling device 2 cools the discharge gas discharged from the compressor 1 and includes a pump 12, a radiator 13, and a heat exchanger 14.
  • the pump 12, the radiator 13 and the heat exchanger 14 constitute a circulation circuit for circulating water, brine and the like.
  • the pump 12 circulates circulating materials such as water and brine between the radiator 13 and the heat exchanger 14.
  • the radiator 13 cools (heatsinks) water or brine circulating in the circulation circuit.
  • the heat exchanger 14 performs heat exchange between the discharge gas and water, brine, or the like flowing through the circulation circuit.
  • the heat exchanger 14 includes, for example, a refrigerant flow path through which the discharge gas from the compressor 1 flows and a cooling flow path 14a through which the circulating material flows.
  • the heat flow of the discharge gas flowing through the refrigerant flow path is reduced by the cooling flow path 14a.
  • the discharge gas is cooled by taking away the circulating material flowing through.
  • this heat exchanger 14 various well-known techniques, such as what is called a shell and tube type, a shell and coil type, a double pipe type, can be used.
  • the pump 12 when the pump 12 is operated, water, brine, and the like circulate in the circulation circuit, and heat exchange is performed between the water and the discharge gas in the heat exchanger 14.
  • the heat-exchanged water is radiated (cooled) by the radiator 13.
  • the discharge gas is cooled (heat radiation).
  • the pump 12 when the pump 12 is stopped, the circulation of water and the like in the circulation circuit is stopped, heat exchange in the heat exchanger 14 is not performed, and the discharge gas is not cooled.
  • the operation of the pump 12 is controlled by the heat radiation control means 22, and the heat radiation control means 22 controls whether the discharge gas is cooled by the discharge gas cooling device 2 by controlling ON / OFF of the pump 12. .
  • the oil separator 3 separates oil from the discharged gas and returns the separated oil to the compressor 1.
  • the oil separator 3 compresses the separated oil provided in the bottom portion, the inflow piping into which the gas discharged from the discharge gas cooling device 2 flows, the discharge piping for discharging the refrigerant gas to the four-way valve 4, and the bottom. It has a structure provided with a pipe returning to the machine 1. When gas flows into the hollow container from the inflow pipe, the oil adheres to the surface of the hollow container and flows down toward the bottom surface of the hollow container, and the oil on the bottom surface is returned to the compressor 1 through the pipe. On the other hand, the refrigerant gas is discharged from the discharge pipe toward the four-way valve 4.
  • the four-way valve 4 switches the direction in which the refrigerant flows according to the operation mode of the indoor unit 11. Specifically, during the cooling operation, the four-way valve 4 is controlled so that the discharge gas flows from the oil separator 3 to the outdoor heat exchanger 9. On the other hand, the switching of the four-way valve 4 is controlled so that the refrigerant flows from the oil separator 3 toward the indoor heat exchanger 6 during the heating operation.
  • the expansion valve (throttle valve) 8 throttles the refrigerant flow path in order to adjust the amount of refrigerant flowing into the evaporator.
  • the indoor heat exchanger 6 exchanges heat between the indoor air and the refrigerant
  • the outdoor heat exchanger 9 exchanges heat between the outdoor air and the refrigerant.
  • the indoor heat exchanger 6 serves as an evaporator
  • the outdoor heat exchanger 9 serves as a condenser.
  • the refrigerant absorbs heat from the indoor air and outputs cold air
  • the outdoor heat exchanger 9 the refrigerant is radiated by the outdoor air and outputs hot air.
  • the indoor heat exchanger 6 becomes a condenser and the outdoor heat exchanger 9 becomes an evaporator.
  • the refrigerant radiates heat to the indoor air and outputs hot air
  • the outdoor heat exchanger 9 absorbs heat into the outdoor air and outputs cold air.
  • the operation of the outdoor unit 10 described above is controlled by the controller 20.
  • the controller 20 is provided with an operation determination unit 21 and a heat dissipation control unit 22 in order to switch the operation of the discharge gas cooling device 2 between the cooling operation and the heating operation.
  • the operation determination means 21 determines whether the operation state is a cooling operation or a heating operation. For example, the operation determination means 21 determines the operation state based on the switching state of the four-way valve 4.
  • the heat dissipation control means 22 controls cooling in the discharge gas cooling device 2 based on the determination in the operation determination means 21. Specifically, the heat radiation control means 22 controls the heat radiation of the refrigerant in the heat exchanger 14 by controlling ON / OFF of the operation of the pump 12. When it is determined that the operation determination unit 21 is in the cooling operation, the heat radiation control unit 22 controls the pump 12 so that the cooling in the heat exchanger 14 is performed. When the operation determination unit 21 determines that the heating operation is performed, the heat radiation control unit 22 controls the pump 12 to stop and not cool.
  • FIG. 2 is a graph showing an example of a ph diagram during the cooling operation of the air conditioner 100, and an example of the operation of the air conditioner 100 during the cooling operation will be described with reference to FIGS.
  • the refrigerant is sucked into the compressor 1 in a low-pressure gas state (state a), and the low-pressure gas is compressed by the compressor 1 to become a high-temperature and high-pressure gas (state b).
  • the discharge gas from the compressor 1 is cooled by the discharge gas cooling device 2 (state c), and is separated into refrigerant and refrigerating machine oil in the oil separator 3.
  • the refrigerating machine oil separated by the oil separator 3 returns to the suction of the compressor 1.
  • the refrigerant is condensed in the outdoor heat exchanger 9 to become a high-pressure liquid refrigerant (state d).
  • the liquid refrigerant becomes a low-pressure two-phase refrigerant at the expansion valve 8 (state e), passes through the refrigerant liquid-side extension pipe 7, and becomes low-pressure gas at the indoor heat exchanger 6 (state f). Thereafter, the low pressure gas passes through the gas side extension pipe 5 and returns to the compressor 1 (state a).
  • FIG. 3 is a graph showing an example of a ph diagram during the heating operation of the air conditioner 100, and an example of the operation of the air conditioner 100 during the heating operation will be described with reference to FIGS.
  • the compressor 1 in a low-pressure gas state (state a10), and is compressed by the compressor 1 into a high-temperature and high-pressure gas (state b10).
  • the discharge gas cooling device 2 does not radiate heat, and the high-temperature and high-pressure gas is separated by the oil separator 3 into refrigerant and refrigerating machine oil.
  • the refrigerating machine oil separated by the oil separator 3 returns to the suction of the compressor 1.
  • the refrigerant passes through the gas side extension pipe 5 and is condensed in the indoor heat exchanger 6 to become a high-pressure liquid refrigerant (state d10).
  • This high-pressure liquid refrigerant becomes a low-pressure two-phase refrigerant at the expansion valve 8 (state e10).
  • the refrigerant passes through the refrigerant liquid side extension pipe 7, enters a low-pressure gas state in the outdoor heat exchanger 9 (state f10), and returns to the compressor 1 (state a10).
  • the cooling by the discharge gas cooling device 2 during the cooling operation promotes the separation of the refrigerating machine oil from the refrigerant, so that the pressure loss of the compressor suction from the evaporator outlet is reduced during the cooling operation.
  • the COP can be improved by the heat release of the refrigerant in the discharge gas cooling device 2.
  • the cooling by the discharge gas cooling device 2 is not performed during the heating operation, so that the reduction of the enthalpy difference in the outdoor heat exchanger (condenser) can be prevented and the COP reduction can be prevented.
  • FIG. 4 is a graph showing the relationship between pressure loss and COP when the compressor is sucked from the evaporator outlet.
  • the horizontal axis of FIG. 4 is (evaporator outlet pressure) / (compressor inlet pressure) ⁇ 100, indicating 100% when the pressure loss is 0, and the higher the pressure loss, the higher the pressure loss. Indicates that the ratio (%) increases (the longer the distance).
  • the vertical axis represents the COP ratio when the pressure loss is 0 (the horizontal axis is 100%). In FIG. 4, it can be seen that the COP decreases as the pressure loss from the evaporator outlet to the compressor suction increases.
  • the indoor heat exchanger 6 serves as an evaporator
  • the outdoor heat exchanger 9 serves as a condenser
  • the indoor heat exchanger 6 becomes a condenser
  • the outdoor heat exchanger 9 becomes an evaporator. That is, the distance from the evaporator outlet to the compressor 1 means the distance from the indoor heat exchanger 6 of the indoor unit 11 to the compressor 1 of the outdoor unit 10 during the cooling operation, and the outdoor unit 10 outdoor during the heating operation. It means the distance from the heat exchanger 9 to the compressor 1 of the outdoor unit 10.
  • the compressor Since the long gas side extension pipe 5 is used to connect the outdoor unit 10 and the indoor unit 11 during the cooling operation, the compressor is discharged from the outlet of the evaporator (indoor heat exchanger 6), which is a large COP lowering factor for the refrigeration cycle. The pressure loss up to the inlet of 1 increases.
  • the outdoor heat exchanger 9 serves as an evaporator, but since the constituent devices are the same in the outdoor unit 10, the piping connecting the outdoor heat exchanger 9 and the compressor 1 is the gas side described above. It is significantly shorter than the extension pipe 5. That is, there is no long pipe that causes a large pressure loss such as the gas side extension pipe 5 between the outlet of the evaporator and the suction of the compressor as in the cooling operation. Therefore, during heating operation, the pressure loss reduction from the outlet of the evaporator (outdoor heat exchanger 9) to the suction port of the compressor 1 is minimized.
  • FIG. 5 shows that the higher the oil circulation rate, the lower the COP ratio. That is, it means that the more the oil separator 3 separates the refrigerating machine oil from the discharge gas of the compressor 1, the pressure loss in the gas side extension pipe 5 is improved and the COP is improved.
  • the COP can be improved regardless of the operation state. However, it has been found that if the cooling by the discharge gas cooling device 2 is performed during the heating operation, the COP is lowered.
  • FIG. 6 is a graph showing the relationship between the heat release amount and COP in the discharge gas cooling device 2 during heating operation.
  • the horizontal axis of FIG. 6 is the ratio of the heat release amount in the discharge gas cooling device 2 to the heat release amount of the entire refrigerant during the heating operation (heat release amount in the discharge gas cooling device 2 / total heat release amount) ⁇ 100.
  • the vertical axis represents the COP ratio based on the COP when the heat release amount in the discharge gas cooling device 2 is zero. As shown in FIG. 6, the COP ratio decreases as the heat dissipation amount increases.
  • cooling the discharge gas of the compressor 1 in the discharge gas cooling device 2 during the heating operation means that the amount of heat that is originally desired for heating the room by the indoor heat exchanger 6 is on the upstream side of the indoor heat exchanger 6. It means that the discharged gas cooling device 2 radiates heat. In order to supplement the capacity required for heating, it is necessary to increase the speed of the compressor 1, so that cooling by the discharge gas cooling device 2 becomes a factor of lowering the COP ratio.
  • the heat radiation control means 22 performs control so that the discharge gas cooling device 2 performs cooling during the cooling operation.
  • COP can be improved by performing heat radiation with the discharge gas cooling device 2, reducing the pressure loss of the compressor suction
  • the heat radiation control means 22 performs control so that the discharge gas cooling device 2 is not cooled during the heating operation. Thereby, reduction of the enthalpy difference in the outdoor heat exchanger (condenser) can be prevented and COP reduction can be prevented.
  • an air conditioner that always performs cooling operation installs a heat exchanger inside a refrigerator or the like, installs an outdoor unit outside the warehouse, and connects the heat exchanger and outdoor unit inside the warehouse below the piping, It has a configuration connected by extension piping.
  • the extension pipe since the extension pipe is long, the pressure loss of the compressor suction from the evaporator outlet that greatly affects the COP of the air conditioner is large. Therefore, the COP improvement effect by the pressure loss improvement of the compressor suction from the evaporator outlet due to the improvement of the separation efficiency is great. Furthermore, COP can be improved by reducing the condensation temperature due to cooling of the compressor discharge gas.
  • the air conditioning apparatus 100 that performs cooling operation and heating operation of an air conditioner or the like, there is a problem that COP is lowered during the heating operation.
  • the indoor heat exchanger 6 is installed indoors
  • the outdoor unit 10 is installed outside
  • the indoor heat exchanger 6 and the outdoor are connected by the extension pipes 5 and 7.
  • the structure which connects the machine 10 is the same as that of a refrigerator. Accordingly, the cooling temperature is reduced by cooling the gas discharged from the compressor during the cooling operation, and the compressor suction is connected from the evaporator outlet by a long extension pipe, so that the COP improvement due to the lower oil circulation rate is great.
  • cooling the discharge gas of the compressor 1 is originally intended to be used as a heating capacity in the indoor heat exchanger 6. It means taking away heat.
  • the pipe connecting the evaporator outlet and the suction port of the compressor 1 is short because the evaporator and the compressor 1 are connected in the same outdoor unit, and the COP improvement effect due to a decrease in the oil circulation rate is also very high. small. For this reason, there exists a problem that COP will fall if the discharge gas of a compressor is cooled at the time of heating operation.
  • the discharge gas cooling device 2 performs cooling during the cooling operation.
  • COP can be improved by reducing heat loss from the outlet of the evaporator to the suction of the compressor, and by dissipating heat with the discharge gas cooling device 2.
  • cooling heat radiation
  • reduction of the enthalpy difference in the outdoor heat exchanger (condenser) can be prevented and COP reduction can be prevented.
  • FIG. 7 is a flowchart showing a preferred embodiment of the control method for the air conditioner of the present invention.
  • the control method for the air conditioner 100 will be described with reference to FIGS. 1 and 7.
  • the operation determination means 21 determines whether the operation is a cooling operation or a heating operation (step ST2).
  • the discharge gas cooling device 2 does not perform cooling (step ST3).
  • the discharge gas cooling device 2 cools the discharge gas by the action of the heat radiation control means 22.
  • FIG. FIG. 8 is a schematic diagram showing an air conditioner according to a second embodiment of the present invention.
  • the air conditioner will be described with reference to FIGS. 1 and 8.
  • the control method of the air conditioner of FIG. 8 is different from that of the air conditioner 100 of FIG. 1 in that the discharge gas cooling device 2 controls the discharge gas during the cooling operation and when the operation frequency f is equal to or higher than the set operation frequency fref. This is the point of cooling.
  • the heat dissipation control means 22 in FIG. 1 has a function of determining whether or not the operating frequency f of the compressor 1 is equal to or higher than a preset operating frequency fref.
  • the heat release control means 22 controls the discharge gas cooling device 2 to cool the discharge gas when the compressor 1 is operating at an operation frequency equal to or higher than the set operation frequency fref.
  • the compressor 1 is operating at an operation frequency lower than the set operation frequency fref even in the cooling operation, control is performed so that the discharge gas cooling device 2 does not cool the discharge gas.
  • the set operation frequency fref is determined in advance in consideration of the effect of reducing the pressure loss due to the reduction of the oil circulation rate and the influence of the input increase of the pump of the discharge gas cooling device 2.
  • the operation frequency f of the compressor 1 and the oil circulation rate are in a proportional relationship, and the higher the operation frequency, the greater the oil circulation rate.
  • the COP improvement effect obtained by reducing the oil circulation rate using the power of the pump of the discharge gas cooling device 2 is the pump of the discharge gas cooling device 2 and the like.
  • the heat radiation control means 22 does not immediately cool the discharge gas.
  • the discharge gas cooling device 2 may be controlled. Thereafter, when the operation time at the set operation frequency fref or more continues for a set time set in advance, the heat radiation control means 22 may be controlled to start cooling the discharge gas by the discharge gas cooling device 2.
  • the cooling operation in the discharge gas cooling device 2 may not be switched immediately at the set operation frequency fref due to the increase / decrease rate of the operation frequency f.
  • FIG. FIG. 9 is a schematic diagram showing Embodiment 3 of the air conditioner of the present invention.
  • the air conditioner 200 will be described with reference to FIG.
  • the air conditioning apparatus 200 in FIG. 9 is different from the air conditioning apparatus 100 in FIG. 1 in the configuration of the discharge gas cooling apparatus.
  • the discharge gas cooling device 202 has a configuration capable of cooling the discharge gas flowing through the refrigerant circuit by circulating the suction gas before compression in the cooling flow path 14a of the heat exchanger 14.
  • the heat dissipation control means 222 performs switching control by the first three-way valve 215 as to whether or not the intake gas before entering the compressor 1 is circulated through the cooling flow path 14a of the heat exchanger 14. Specifically, the heat dissipation control means 222 switches and controls the three-way valve 215 so that the intake gas flows into the heat exchanger 14 during the cooling operation. Then, heat exchange is performed between the suction gas and the discharge gas from the compressor 1 in the heat exchanger 14 to cool the discharge gas. On the other hand, the heat radiation control means 222 switches and controls the three-way valve so that the refrigerant before compression does not flow to the heat exchanger 14 during the heating operation. Then, since the suction gas does not flow in the heat exchanger 14, the discharge gas from the compressor 1 is not cooled.
  • the COP can be improved by reducing the pressure loss of the compressor suction from the outlet of the evaporator during the cooling operation and radiating the refrigerant in the discharge gas cooling device 202. .
  • the cooling by the discharge gas cooling device 202 is not performed during the heating operation, reduction of the enthalpy difference in the outdoor heat exchanger (condenser) 9 can be prevented and COP reduction can be prevented.
  • the refrigerant can be heated in the heat exchanger 14 before the refrigerant is sucked into the compressor 1, and the liquid refrigerant returns to the compressor 1 and damages the compressor 1. Can be prevented.
  • FIG. FIG. 10 is a schematic view showing Embodiment 4 of the air conditioner of the present invention, and the air conditioner 300 will be described with reference to FIG.
  • symbol is attached
  • the air conditioning apparatus 300 in FIG. 10 is different from the air conditioning apparatus 100 in FIG.
  • the discharge gas cooling device 302 in FIG. 10 is connected to the radiator 13 connected between the discharge side piping of the compressor 1 and the oil separator 3, and a part of the air blown from the blower 16 to the radiator 13. And a damper 311 for blocking or passing the air flow.
  • a duct for guiding the wind from the blower 16 may be installed between the blower 16 and the radiator 13.
  • the damper 311 has a function of changing the direction in which the wind sent from the blower 16 hits the heat radiator 13 and the direction in which the air is blocked, and its operation is controlled by the heat radiation control means 322.
  • a cooling effect can be enlarged by attaching a fin etc. to the heat radiator 13 and enlarging a surface area.
  • the heat radiation control means 322 controls to open the damper 311 and send wind to the radiator 13 during the cooling operation. Then, the discharge gas is cooled in the radiator 13. On the other hand, the heat dissipation control means 322 closes the damper 311 during the heating operation and blocks the wind to the radiator 13. Then, the discharge gas cooling device 2 does not cool the discharge gas.
  • FIG. FIG. 11 is a schematic view showing Embodiment 5 of the air-conditioning apparatus of the present invention, and the air-conditioning apparatus 400 will be described with reference to FIG.
  • the air conditioning apparatus 400 in FIG. 11 is different from the air conditioning apparatus 100 in FIG. 1 in the configuration of the discharge gas cooling apparatus.
  • the discharge gas cooling device 402 performs heat exchange between the pump 12, the radiator 13 connected to the pump 12, and the discharge gas from the compressor 1 connected to the radiator 13 and circulating water.
  • a second one connected to the discharge pipe of the compressor 1 and the heat exchanger 14, one of which is bypassed from the discharge pipe of the compressor 1 to the inlet of the oil separator 3.
  • the three-way valve 418 is provided. That is, a flow path through which the discharge gas from the compressor 1 passes through the heat exchanger 14 by switching the second three-way valve, and a flow path that bypasses the heat exchanger 14 and flows to the oil separator 3. Will be switched.
  • the operation of the second three-way valve 418 is controlled by the heat radiation control means 22.
  • the heat dissipation control means 422 switches the second three-way valve 418 so that the discharge gas from the compressor 1 passes through the heat exchanger 14 during the cooling operation. Then, the discharge gas is cooled in the heat exchanger 14. On the other hand, the heat release control means 422 switches the second three-way valve 418 so as to bypass the heat exchanger 14 that performs heat exchange with the discharge pipe of the compressor 1 during the heating operation. Then, the discharge gas flows into the oil separator 3 without passing through the heat exchanger 14, and the discharge gas is not cooled.
  • the heat radiation control means 22, 222, 322, and 422 exemplify a case where control is performed so that heat is dissipated during cooling operation, and heat is not dissipated when cooling operation is not performed. You may adjust so that it may do. For example, when the cooling operation is performed as shown in FIG. 8 and is lower than the set operation frequency fref, the flow rate on the cooling flow path 14a side in the heat exchanger 14 is reduced, or the air flow to the radiator 13 in FIG. Cooling may be performed in a state where the cooling capacity is set low by controlling the damper 311 so as to reduce the amount to be reduced.
  • a hollow container is used as an example of the configuration of the oil separator 3 .
  • Various known techniques such as a method of collecting the fine particles can be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Thermal Sciences (AREA)
  • Signal Processing (AREA)
  • Mathematical Physics (AREA)
  • Fuzzy Systems (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

Selon la présente invention, lorsqu'une opération commence dans le climatiseur (100) selon la présente invention, un moyen de détermination d'opération (21) détermine si ladite opération est une opération de refroidissement ou une opération de chauffage. Quand il est déterminé que l'opération n'est pas une opération de refroidissement, un refroidissement n'est pas effectué dans un dispositif de refroidissement de gaz de décharge (2). Quand il est déterminé que l'opération est une opération de refroidissement, un refroidissement est effectué dans le dispositif de refroidissement de gaz de décharge (2).
PCT/JP2012/004235 2012-06-29 2012-06-29 Climatiseur et son procédé de commande Ceased WO2014002145A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2012/004235 WO2014002145A1 (fr) 2012-06-29 2012-06-29 Climatiseur et son procédé de commande
US14/402,447 US20150153079A1 (en) 2012-06-29 2012-06-29 Air-conditioning apparatus and method for controlling the same
GB1421070.2A GB2517346B (en) 2012-06-29 2012-06-29 Air-conditioning apparatus and method for controlling the same
JP2014522229A JPWO2014002145A1 (ja) 2012-06-29 2012-06-29 空気調和装置およびその制御方法

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5822616U (ja) * 1982-08-02 1983-02-12 三菱電機株式会社 空気調和装置
JPH07305901A (ja) * 1994-05-09 1995-11-21 Nippon Kentetsu Co Ltd 冷凍装置
JPH11337195A (ja) * 1998-05-28 1999-12-10 Mitsubishi Electric Corp 冷凍装置
JP2005106360A (ja) * 2003-09-30 2005-04-21 Sanyo Electric Co Ltd 冷媒回路及びヒートポンプ給湯機
JP2009030840A (ja) * 2007-07-25 2009-02-12 Sanyo Electric Co Ltd 冷凍装置
JP2009216383A (ja) * 2009-06-30 2009-09-24 Toyo Eng Works Ltd 多元ヒートポンプ式蒸気・温水発生装置

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US5269153A (en) * 1991-05-22 1993-12-14 Artesian Building Systems, Inc. Apparatus for controlling space heating and/or space cooling and water heating
JP3953377B2 (ja) * 2002-07-16 2007-08-08 トヨタ自動車株式会社 空調装置
US7114347B2 (en) * 2003-10-28 2006-10-03 Ajay Khatri Closed cycle refrigeration system and mixed component refrigerant
KR101266657B1 (ko) * 2006-10-17 2013-05-28 엘지전자 주식회사 공기조화기

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5822616U (ja) * 1982-08-02 1983-02-12 三菱電機株式会社 空気調和装置
JPH07305901A (ja) * 1994-05-09 1995-11-21 Nippon Kentetsu Co Ltd 冷凍装置
JPH11337195A (ja) * 1998-05-28 1999-12-10 Mitsubishi Electric Corp 冷凍装置
JP2005106360A (ja) * 2003-09-30 2005-04-21 Sanyo Electric Co Ltd 冷媒回路及びヒートポンプ給湯機
JP2009030840A (ja) * 2007-07-25 2009-02-12 Sanyo Electric Co Ltd 冷凍装置
JP2009216383A (ja) * 2009-06-30 2009-09-24 Toyo Eng Works Ltd 多元ヒートポンプ式蒸気・温水発生装置

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GB2517346A (en) 2015-02-18
US20150153079A1 (en) 2015-06-04
JPWO2014002145A1 (ja) 2016-05-26
GB201421070D0 (en) 2015-01-14

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