WO2016132473A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2016132473A1
WO2016132473A1 PCT/JP2015/054402 JP2015054402W WO2016132473A1 WO 2016132473 A1 WO2016132473 A1 WO 2016132473A1 JP 2015054402 W JP2015054402 W JP 2015054402W WO 2016132473 A1 WO2016132473 A1 WO 2016132473A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
outdoor heat
compressor
fan
outdoor
Prior art date
Application number
PCT/JP2015/054402
Other languages
English (en)
Japanese (ja)
Inventor
悟 梁池
加藤　央平
浩平 葛西
進一 内野
博和 南迫
美藤　尚文
翼 丹田
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2017500189A priority Critical patent/JP6338762B2/ja
Priority to CN201580075922.1A priority patent/CN107250679B/zh
Priority to US15/543,289 priority patent/US20170363332A1/en
Priority to EP15882576.0A priority patent/EP3260790B1/fr
Priority to PCT/JP2015/054402 priority patent/WO2016132473A1/fr
Publication of WO2016132473A1 publication Critical patent/WO2016132473A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—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
    • F24F11/64—Electronic processing using pre-stored data
    • 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
    • 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
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • 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
    • F24F11/67—Switching between heating and cooling modes
    • 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
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/60—Energy consumption
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2700/15—Power, e.g. by voltage or current

Definitions

  • the present invention relates to an air conditioner.
  • the present invention has been made against the background of the above-described problems, and an object thereof is to provide an air conditioner that can perform a defrosting operation more efficiently than in the past.
  • the air conditioner of the present invention includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a discharge side of the compressor with respect to the outdoor heat exchanger, and the compressor of the compressor with respect to the indoor heat exchanger.
  • An air conditioner configured to be connected to a switching unit provided on the discharge side, the fan for blowing air to the outdoor heat exchanger, a power supply device for supplying power to the fan, and the fan Switching between a fan input detection means for detecting a physical quantity related to the power to be output, a first operation in which the outdoor heat exchanger functions as an evaporator, and a second operation in which the outdoor heat exchanger functions as a condenser.
  • Control means for controlling the switching means, and when the physical quantity detected by the fan input detection means is a reference amount or more, the first operation is switched to the second operation, and the control means, Outdoor heat In which the reference quantity when the coolant temperature is high through the exchangers to adjust the reference amount to be smaller than the reference amount when the refrigerant temperature flowing in the outdoor heat exchanger is low.
  • the air conditioner of the present invention controls the switching means to switch between a first operation in which the outdoor heat exchanger functions as an evaporator and a second operation in which the outdoor heat exchanger functions as a condenser.
  • Control means and when the physical quantity detected by the fan input detection means is greater than or equal to a reference quantity, the first operation is switched to the second operation, and the control means flows through the outdoor heat exchanger.
  • the reference amount is adjusted so that the reference amount when the refrigerant temperature is high is smaller than the reference amount when the temperature of the refrigerant flowing through the outdoor heat exchanger is low. For this reason, the defrosting operation can be started at an appropriate timing when the heating operation is performed. Therefore, the defrosting operation can be performed more efficiently than before.
  • Embodiment 1 FIG.
  • the air conditioning apparatus 100 of the present invention will be described in detail with reference to the drawings.
  • the size relationship of each component may be different from the actual one.
  • the same reference numerals denote the same or corresponding parts, and this is common throughout the entire specification.
  • the forms of the constituent elements shown in the entire specification are merely examples, and are not limited to these descriptions.
  • FIG. 1 is a schematic diagram showing an air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the air conditioning apparatus 100 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 4, and an indoor heat exchanger 5.
  • the refrigerant circuit 90 is configured by sequentially connecting, for example, the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, and the indoor heat exchanger 5.
  • the compressor 1 is a variable capacity compressor that compresses sucked refrigerant and discharges it as a high-temperature and high-pressure refrigerant.
  • the four-way valve 2 is a switching unit capable of switching the flow direction of the refrigerant discharged from the compressor 1 according to, for example, a heating operation or a cooling operation being performed.
  • the four-way valve 2 is provided on the discharge side of the compressor 1 with respect to the outdoor heat exchanger 3 and on the discharge side of the compressor 1 with respect to the indoor heat exchanger 5.
  • FIG. 1 illustrates an example in which the four-way valve 2 is switched so as to perform a cooling operation.
  • the solid line arrow of FIG. 1 has shown the flow of the refrigerant
  • the broken line arrow of FIG. 1 has shown the flow of the refrigerant
  • the outdoor heat exchanger 3 is a heat exchanger that functions as a condenser during cooling operation and functions as an evaporator during heating operation.
  • the outdoor fan 31 is a blowing unit that supplies outside air to the outdoor heat exchanger 3 to form an air flow.
  • the outdoor fan 31 is composed of, for example, an axial fan or a centrifugal fan.
  • the outdoor fan 31 rotates when an outdoor motor (not shown) is driven. Heat exchange is performed between the air supplied from the outdoor fan 31 and the refrigerant flowing in the outdoor heat exchanger 3.
  • the outdoor fan 31 is driven by a power supply device (not shown) that supplies electric power.
  • the expansion valve 4 is for decompressing and expanding the refrigerant flowing out of the outdoor heat exchanger 3 during the cooling operation, and decompressing and expanding the refrigerant flowing out of the indoor heat exchanger 5 during the heating operation.
  • the indoor heat exchanger 5 is a heat exchanger that functions as an evaporator during cooling operation and functions as a condenser during heating operation.
  • the indoor fan 51 is a blowing unit that supplies indoor air to the indoor heat exchanger 5 to form an air flow.
  • the indoor fan 51 is composed of, for example, an axial fan or a centrifugal fan.
  • the indoor fan 51 rotates when an indoor motor (not shown) is driven. Heat exchange is performed between the air supplied from the indoor fan 51 and the refrigerant flowing inside the indoor heat exchanger 5.
  • the outdoor refrigerant temperature sensor 32 is a temperature detection unit that detects the temperature of the refrigerant flowing through the outdoor heat exchanger 3.
  • the indoor side refrigerant temperature sensor 52 is a sensor that detects the temperature of the refrigerant flowing through the indoor heat exchanger 5. In the following description, when simply referred to as “refrigerant temperature”, it refers to the temperature of the refrigerant flowing in the outdoor heat exchanger 3.
  • the control means 80 controls the outdoor motor to adjust the rotational speed of the outdoor fan 31, and controls the indoor motor to adjust the rotational speed of the indoor fan 51.
  • the control means 80 controls the outdoor motor by changing the voltage and current input to the outdoor motor.
  • the control means 80 can adjust the amount of air passing through the outdoor heat exchanger 3 by adjusting the rotational speed of the outdoor fan 31.
  • the current rotational speed of the outdoor fan 31 can also be detected by providing a rotational speed detection means for detecting the rotational speed of the outdoor fan 31.
  • the current rotational speed of the outdoor fan 31 can also be estimated from information on the current applied to the outdoor motor and the voltage applied to the outdoor motor. In the following description, when it is simply described as “fan input”, it refers to a physical quantity related to electric power supplied to the outdoor fan 31 (an outdoor motor that rotates the outdoor fan 31).
  • control unit 80 controls the indoor motor so that the outdoor fan 31 rotates.
  • control unit 80 includes, for example, hardware such as a circuit device that realizes this function, or software executed on an arithmetic device such as a microcomputer or a CPU.
  • the cooling operation is executed.
  • the heating operation is performed by the control means 80 switching the four-way valve 2 to the heating side.
  • defrosting operation refers to an operation when the control unit 80 switches the four-way valve 2 to the cooling side and stops the outdoor fan 31.
  • the heating operation corresponds to the “first operation” of the present invention
  • the defrosting operation corresponds to the “second operation” of the present invention.
  • the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3.
  • the refrigerant flowing into the outdoor heat exchanger 3 flows out of the outdoor heat exchanger 3 by exchanging heat with the air supplied to the outdoor heat exchanger 3 by rotation of the outdoor fan.
  • the refrigerant that has flowed out of the outdoor heat exchanger 3 flows into the expansion valve 4 and is decompressed, then flows out of the expansion valve 4 and flows into the indoor heat exchanger 5.
  • the refrigerant flowing into the indoor heat exchanger 5 exchanges heat with the air supplied to the indoor heat exchanger 5 by the rotation of the indoor fan and flows out of the indoor heat exchanger 5.
  • the refrigerant that has flowed out of the indoor heat exchanger 5 flows into the compressor 1.
  • the refrigerant discharged from the compressor 1 flows into the indoor heat exchanger 5.
  • the refrigerant flowing into the indoor heat exchanger 5 exchanges heat with the air supplied to the indoor heat exchanger 5 by the rotation of the indoor fan and flows out of the indoor heat exchanger 5.
  • the refrigerant flowing out of the indoor heat exchanger 5 flows into the expansion valve 4 and is decompressed, then flows out of the expansion valve 4 and flows into the outdoor heat exchanger 3.
  • the refrigerant flowing into the outdoor heat exchanger 3 flows out of the outdoor heat exchanger 3 by exchanging heat with the air supplied to the outdoor heat exchanger 3 by rotation of the outdoor fan.
  • the refrigerant that has flowed out of the outdoor heat exchanger 3 flows into the compressor 1.
  • FIG. 2 is a diagram showing changes in the frost formation amount and the total power value with the elapsed time of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 3 is a diagram illustrating changes in the amount of frost formation and the total current value with the elapsed time of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the elapsed time [min] is defined on the horizontal axis of FIG. 2, and the frost formation amount [g] and the total electric energy [W] are defined on the vertical axis of FIG.
  • the amount of frost formation is indicated by a solid line, and the total power value is indicated by a broken line.
  • the amount of frost formation increases with the passage of time, and the total power value increases with the passage of time.
  • the elapsed time [min] is defined on the horizontal axis of FIG. 3, and the frost formation amount [g] and the total current amount [A] are defined on the vertical axis of FIG.
  • the amount of frost formation is indicated by a solid line, and the total current value is indicated by a broken line.
  • the amount of frost formation increases with the passage of time, and the total current value increases with the passage of time.
  • FIG. 4 is a diagram showing a change in electric energy with the elapsed time of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 5 is a diagram showing a change in the total electric energy with the elapsed time of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. 4 and 5, a case where an electric energy that is the product of a current value applied to the outdoor fan motor and a voltage value applied to the outdoor fan motor is used as the fan input will be described. 4 and 5 are performed during the heating operation.
  • control means 80 calculates ⁇ Wtotal by accumulating ⁇ W (t) according to the following equation (1.2).
  • ⁇ Wtotal ⁇ W (t) Expression (1.2)
  • control means 80 determines whether (DELTA) Wtotal became more than the threshold value (alpha) like the following formula
  • ⁇ varies depending on the refrigerant temperature. Specifically, for example, the higher the refrigerant temperature, the higher the density of frost that adheres to the outdoor heat exchanger 3, so the control means 80 decreases the value of ⁇ . Thus, by reducing the value of ⁇ , the timing at which ⁇ Wtotal becomes equal to or greater than ⁇ is advanced, and the defrosting operation is started earlier. Further, for example, the lower the refrigerant temperature, the lower the density of frost that adheres to the outdoor heat exchanger 3, so the control means 80 increases the value of ⁇ . Thus, by increasing the value of ⁇ , the timing at which ⁇ Wtotal becomes ⁇ or more is delayed, and the defrosting operation is started late.
  • FIG. 6 is a schematic diagram showing a state in which frost has adhered to the outdoor heat exchanger 3 of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the height of the frost attached to the outdoor heat exchanger 3 is Hf_total [mm]
  • the distance between adjacent fins 3b is Fp [mm].
  • a wind blows toward the other end side from the one end side of the longitudinal direction of the fin 3b is assumed.
  • the wind speed ua is attenuated, and the heat exchange in the outdoor heat exchanger 3 is frost attached to the outdoor heat exchanger 3. It will be disturbed compared to the case of not doing.
  • frost adheres to the heat transfer tubes 3a and the fins 3b constituting the outdoor heat exchanger 3, the ventilation resistance increases as the frost grows, and the input to the outdoor fan 31 increases. Moreover, the density of frost becomes small, so that the temperature of the heat exchanger tube 3a and the fin 3b is low. That is, the lower the refrigerant temperature, the smaller the frost density.
  • the amount of frost adhering to the outdoor heat exchanger 3 is different. That is, even if the closed state of the outdoor heat exchanger 3 is the same and the increase width of the fan input is the same, the amount of defrosting heat necessary for the defrosting operation is different. Specifically, the higher the refrigerant temperature, the greater the amount of heat required to melt frost attached to the outdoor heat exchanger 3.
  • FIG. 7 is a diagram showing the relationship between the relative humidity ⁇ and the frost density ⁇ of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the horizontal axis in FIG. 7 defines relative humidity ⁇ [%], and the vertical axis in FIG. 7 defines frost density ⁇ [kg / m 3 ].
  • the refrigerant temperature Ts [° C.] indicates ⁇ 30 ° C. and ⁇ 20 ° C.
  • the higher the relative humidity ⁇ the lower the frost density ⁇ .
  • the frost density ⁇ is larger than when the refrigerant temperature Ts is ⁇ 30 ° C. That is, it is understood that the frost density ⁇ increases as the refrigerant temperature Ts increases.
  • the frost density ⁇ increases, and when the frost density ⁇ increases, a large amount of defrosting capacity is required. Therefore, it can be seen that the defrosting time increases as the refrigerant temperature Ts increases.
  • FIG. 8 is a diagram showing the relationship between the refrigerant temperature and the required defrost heat amount of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 8, the relationship between the temperature of the refrigerant flowing through the refrigerant circuit 90 inside the outdoor heat exchanger 3 and the necessary amount of defrost heat is proportional.
  • the defrosting time increases as the refrigerant temperature Ts increases. Specifically, for example, when the average refrigerant temperature is ⁇ 40 ° C. to ⁇ 30 ° C., the minimum defrosting time is 1 minute. For example, when the average refrigerant temperature is ⁇ 10 ° C. to ⁇ 5 ° C., the minimum defrosting time is 3 minutes. For example, when the average refrigerant temperature is ⁇ 5 ° C. to 0 ° C., the minimum defrosting time is 5 minutes.
  • FIG. 9 is a diagram showing a change in the frequency of the compressor 1 with the elapsed time of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 10 is a diagram showing a change in the frequency of the compressor 1 with the elapsed time of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • FIGS. 9 and 10 define the elapsed time
  • the vertical axes of FIGS. 9 and 10 define the frequency of the compressor 1.
  • the change in the frequency of the compressor 1 when the refrigerant temperature is relatively high is indicated by a solid line
  • the change in the frequency of the compressor 1 when the refrigerant temperature is relatively low is indicated by a broken line. Show.
  • the refrigerant temperature when the refrigerant temperature is relatively low, it is possible to shorten the operation time of the defrosting operation as compared with the case where the refrigerant temperature is relatively high.
  • a time for melting the frost attached to the outdoor heat exchanger 3 and a time for dropping the melted frost from the outdoor heat exchanger 3 are required.
  • the time for the defrosting operation when the refrigerant temperature is relatively low is shorter than the time for the defrosting operation when the refrigerant temperature is relatively high, the melted frost may freeze again. Therefore, in the first embodiment, even when the refrigerant temperature is relatively low, the operation is performed with the same defrosting time as when the refrigerant temperature is relatively high, and the frequency of the compressor 1 is lowered. explain.
  • the section in which the heating operation is performed is the section (a)
  • the section in which the defrosting operation is performed is the section (b)
  • the section in which the heating operation is performed after the defrosting operation is the section (c).
  • the control means 80 controls the compressor 1 so that the compressor 1 has a predetermined frequency in a state where the four-way valve 2 is switched to the heating side.
  • the control means 80 controls the compressor 1 so as to reduce the frequency of the compressor 1 after operating for a predetermined time in a state where the compressor 1 is at the predetermined frequency.
  • the control means 80 switches the four-way valve 2 to the cooling side and starts the defrosting operation.
  • the control means 80 causes the compressor 1 to operate at the predetermined frequency fmax when the four-way valve 2 is switched to the cooling side.
  • the compressor 1 is controlled as follows. Next, the control unit 80 controls the compressor 1 so as to reduce the frequency of the compressor 1 after the compressor 1 has been operated for a predetermined time while the compressor 1 is at the predetermined frequency fmax. And the control means 80 switches the four-way valve 2 to the heating side again, and starts heating operation, when the frequency of the compressor 1 becomes 0 (time t14).
  • the control means 80 when the refrigerant temperature is relatively low, the control means 80 causes the compressor 1 to operate at the predetermined frequency fmax when the four-way valve 2 is switched to the cooling side.
  • the compressor 1 is controlled as follows. Next, the control means 80 operates for a predetermined time with the compressor 1 at the predetermined frequency fmax (time t12), and then reduces the frequency of the compressor 1 so that the compressor 1 becomes the predetermined frequency f1. The machine 1 is controlled. After the compressor 1 reaches the predetermined frequency f1 (time t13), the control unit 80 operates for a predetermined time while the compressor 1 is at the predetermined frequency f1.
  • the control means 80 controls the compressor 1 so as to reduce the frequency of the compressor 1 after operating for a predetermined time with the compressor 1 at the predetermined frequency f1 (time t13). And the control means 80 switches the four-way valve 2 to the heating side again, and starts heating operation, when the frequency of the compressor 1 becomes 0 (time t14).
  • control means 80 controls the compressor 1 so that the frequency of the compressor 1 becomes a predetermined frequency in a state where the four-way valve 2 is switched to the heating side. To do.
  • the section in which the heating operation is performed is the section (a)
  • the section in which the defrosting operation is performed is the section (b)
  • the section in which the heating operation is performed after the defrosting operation is the section (c).
  • the change in the frequency of the compressor 1 over time in the section (a) and the section (c) is the same as that in FIG.
  • the control unit 80 causes the compressor 1 to have a predetermined frequency fmax when the four-way valve 2 is switched to the cooling side.
  • the compressor 1 is controlled as follows. Next, the control unit 80 controls the compressor 1 so as to reduce the frequency of the compressor 1 after the compressor 1 has been operated for a predetermined time while the compressor 1 is at the predetermined frequency fmax. And the control means 80 switches the four-way valve 2 to the heating side again, and starts heating operation, when the frequency of the compressor 1 becomes 0 (time t24).
  • the control means 80 causes the compressor 1 to operate at the predetermined frequency f2 in a state where the four-way valve 2 is switched to the cooling side.
  • the compressor 1 is controlled as follows. Next, the control means 80 controls the compressor 1 so as to reduce the frequency of the compressor 1 after operating for a predetermined time (time t23) in a state where the compressor 1 has reached the predetermined frequency f2 (time t22). To do. And the control means 80 switches the four-way valve 2 to the heating side again, and starts heating operation, when the frequency of the compressor 1 becomes 0 (time t24).
  • the air-conditioning apparatus 100 includes the compressor 1, the outdoor heat exchanger 3, the indoor heat exchanger 5, and the discharge side of the compressor 1 relative to the outdoor heat exchanger 3.
  • the four-way valve 2 provided on the discharge side of the compressor 1 with respect to the indoor heat exchanger 5 is an air conditioner 100 configured to be connected to the fan 31 for blowing air to the outdoor heat exchanger 3;
  • a power supply device that supplies power to the fan 31, fan input detection means that detects a physical quantity related to the power supplied to the fan 31, a first operation that causes the outdoor heat exchanger 3 to function as an evaporator, and outdoor heat exchange Control means 80 for controlling the four-way valve 2 so as to switch between the second operation for causing the condenser 3 to function as a condenser, and when the physical quantity detected by the fan input detection means is equal to or greater than a reference quantity, One operation is switched to the second operation
  • the control means 80 adjusts the reference amount so that the reference amount when the temperature of the refrigerant flowing through the outdoor heat exchanger
  • the air conditioner 100 includes the compressor 1, the outdoor heat exchanger 3, the indoor heat exchanger 5, and the outdoor heat exchanger 3 on the discharge side of the compressor 1 and indoors.
  • the air conditioner 100 is configured by connecting a four-way valve 2 provided on the discharge side of the compressor 1 with respect to the heat exchanger 5, and includes a fan 31 that blows air to the outdoor heat exchanger 3, and a fan 31
  • a power supply device for supplying electric power, fan input detecting means for detecting a physical quantity related to electric power supplied to the fan 31, a first operation for causing the outdoor heat exchanger 3 to function as an evaporator, and an outdoor heat exchanger 3
  • a control unit 80 that controls the four-way valve 2 so as to switch between a second operation that functions as a condenser, and when the physical quantity detected by the fan input detection unit is equal to or greater than a reference amount, Switch to the second operation and control
  • the stage 80 is configured so that the frequency of the compressor 1 when the temperature of the refrigerant flowing through the outdoor heat exchanger 3 is
  • Embodiment 2 unlike the first embodiment, the execution timing of the defrosting operation is determined based on the frosting amount Mf, and the frequency of the compressor 1 in the defrosting operation is determined based on the frosting amount Mf. To decide.
  • items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
  • Equation (2.1) assumes that frost adheres with respect to the outdoor heat exchanger 3 uniformly.
  • the surface area A0 [m 2 ] is the heat exchange surface area of the outdoor heat exchanger 3.
  • the frost density ⁇ f [kg / m 3 ] is the density of frost adhering to the outdoor heat exchanger 3, and is affected by the cooling surface temperature and relative humidity.
  • the frost height Hf (t) is the height of frost attached to the outdoor heat exchanger 3.
  • the amount of defrosting heat Qf [kJ] is expressed as in Expression (2.3) based on the amount of frosting Mf [kg] and the latent heat ⁇ H [kJ / kg].
  • Qf Mf ⁇ ⁇ H (formula 2.3)
  • the defrosting time Tf [sec] is represented by the following formula (2.4) based on the defrosting heat quantity Qf [kJ] and the defrosting capacity P [kW].
  • Tf Qf / P (formula 2.4)
  • the control unit 80 determines the defrosting time according to the amount of frost formation. For this reason, defrosting operation can be performed more efficiently than before.
  • the outdoor fan 31 corresponds to the “fan” of the present invention.

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

Abstract

L'invention a pour objet un dispositif de climatisation qui permet d'effectuer des opérations de dégivrage plus efficacement que de façon classique. À cet effet l'invention porte sur un dispositif de climatisation (100) formé par le raccordement d'un compresseur (1), d'un échangeur de chaleur extérieur (3), d'un échangeur de chaleur intérieur (5) et d'une soupape à quatre voies (2) qui est disposée plus près du côté refoulement du compresseur (1) que l'échangeur de chaleur extérieur (3) et plus près du côté refoulement du compresseur (1) que l'échangeur de chaleur intérieur (5), comprenant : un ventilateur (31) pour souffler de l'air sur l'échangeur de chaleur extérieur (3) ; un dispositif formant source d'alimentation électrique pour alimenter le ventilateur (31) ; un moyen de détection d'entrée de ventilateur pour détecter une quantité physique se rapportant à la puissance fournie au ventilateur (31) ; et un moyen de commande (80) pour commander la soupape à quatre voies (2) afin de basculer entre un premier fonctionnement dans lequel l'échangeur de chaleur extérieur (3) est amené à fonctionner comme un évaporateur et un second fonctionnement dans lequel l'échangeur de chaleur extérieur (3) est amené à fonctionner comme un condenseur. Si la quantité physique détectée par le moyen de détection d'entrée de ventilateur est supérieure ou égale à une quantité de référence, le premier fonctionnement est basculé vers le second fonctionnement. Le moyen de commande (80) règle la quantité de référence de sorte que la quantité de référence, lorsque la température du fluide frigorigène circulant dans l'échangeur de chaleur extérieur (3) est élevée, est inférieure à la quantité de référence lorsque la température du fluide frigorigène circulant dans l'échangeur de chaleur extérieur (3) est faible.
PCT/JP2015/054402 2015-02-18 2015-02-18 Dispositif de climatisation WO2016132473A1 (fr)

Priority Applications (5)

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JP2017500189A JP6338762B2 (ja) 2015-02-18 2015-02-18 空気調和装置
CN201580075922.1A CN107250679B (zh) 2015-02-18 2015-02-18 空气调节装置
US15/543,289 US20170363332A1 (en) 2015-02-18 2015-02-18 Air-conditioning apparatus
EP15882576.0A EP3260790B1 (fr) 2015-02-18 2015-02-18 Dispositif de climatisation
PCT/JP2015/054402 WO2016132473A1 (fr) 2015-02-18 2015-02-18 Dispositif de climatisation

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7278496B1 (ja) * 2022-05-18 2023-05-19 三菱電機株式会社 冷凍サイクル状態予測装置、冷凍サイクル制御装置、及び冷凍サイクル装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110268203B (zh) * 2017-03-24 2021-11-30 东芝开利株式会社 空调装置
US10914503B2 (en) * 2018-02-01 2021-02-09 Johnson Controls Technology Company Coil heating systems for heat pump systems
CN114502895B (zh) * 2019-10-23 2023-04-14 日立江森自控空调有限公司 空调机、空调机的控制方法以及程序

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57124660A (en) * 1981-01-27 1982-08-03 Mitsubishi Electric Corp Frost detector
JP2010032107A (ja) * 2008-07-29 2010-02-12 Hitachi Appliances Inc 空気調和機
JP2010091118A (ja) * 2008-10-03 2010-04-22 Panasonic Corp 空気調和機
JP2010210223A (ja) * 2009-03-12 2010-09-24 Mitsubishi Heavy Ind Ltd 空気調和機

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01107056A (ja) * 1987-10-21 1989-04-24 Toshiba Corp 空気調和機
JP2831838B2 (ja) * 1990-11-06 1998-12-02 株式会社東芝 空気調和機
JP3034781B2 (ja) * 1995-06-07 2000-04-17 シャープ株式会社 冷蔵庫
KR100225640B1 (ko) * 1997-06-27 1999-10-15 윤종용 공기조화기의 제상제어방법
CN1888671A (zh) * 2005-06-30 2007-01-03 乐金电子(天津)电器有限公司 空调器的除霜运转控制装置及其运作方法
JP2009058222A (ja) * 2006-03-31 2009-03-19 Daikin Ind Ltd 室外機
AU2010253331B2 (en) * 2009-05-29 2013-04-11 Daikin Industries, Ltd. Air conditioner
JP4836212B2 (ja) * 2009-07-22 2011-12-14 シャープ株式会社 空気調和機
JP6071648B2 (ja) * 2013-03-01 2017-02-01 三菱電機株式会社 空気調和装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57124660A (en) * 1981-01-27 1982-08-03 Mitsubishi Electric Corp Frost detector
JP2010032107A (ja) * 2008-07-29 2010-02-12 Hitachi Appliances Inc 空気調和機
JP2010091118A (ja) * 2008-10-03 2010-04-22 Panasonic Corp 空気調和機
JP2010210223A (ja) * 2009-03-12 2010-09-24 Mitsubishi Heavy Ind Ltd 空気調和機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7278496B1 (ja) * 2022-05-18 2023-05-19 三菱電機株式会社 冷凍サイクル状態予測装置、冷凍サイクル制御装置、及び冷凍サイクル装置

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US20170363332A1 (en) 2017-12-21
JP6338762B2 (ja) 2018-06-06
JPWO2016132473A1 (ja) 2017-09-07
CN107250679B (zh) 2019-11-26
EP3260790A4 (fr) 2018-10-24
EP3260790B1 (fr) 2020-03-25
CN107250679A (zh) 2017-10-13

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