EP3260790B1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
EP3260790B1
EP3260790B1 EP15882576.0A EP15882576A EP3260790B1 EP 3260790 B1 EP3260790 B1 EP 3260790B1 EP 15882576 A EP15882576 A EP 15882576A EP 3260790 B1 EP3260790 B1 EP 3260790B1
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EP
European Patent Office
Prior art keywords
heat exchanger
compressor
outdoor heat
fan
outdoor
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.)
Active
Application number
EP15882576.0A
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German (de)
English (en)
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EP3260790A1 (fr
EP3260790A4 (fr
Inventor
Satoru Yanachi
Yohei Kato
Kohei Kasai
Shinichi Uchino
Hirokazu Minamisako
Takafumi Mito
Tsubasa TANDA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3260790A4 publication Critical patent/EP3260790A4/fr
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Classifications

    • 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-conditioning apparatus.
  • a conventional air-conditioning apparatus detects, in a heating operation, the current value of an outdoor fan motor and the rotation speed of an outdoor fan, and determines whether to start a defrosting operation based on whether the current value of the outdoor fan motor becomes equal to or larger than a reference current value or the rotation speed of the outdoor fan decreases by a predetermined rotation speed (refer to Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2009-58222
  • the reference current value is determined in advance and cannot be changed with taken into account decrease in a fan input due to decrease in the fan rotation speed when the efficiency of the outdoor fan motor degrades by aging.
  • This configuration prevents transition to the defrosting operation at appropriate timing in the heating operation. In other words, defrosting cannot be performed efficiently.
  • the present invention is intended to solve the above-described problem and provide an air-conditioning apparatus that performs a defrosting operation more efficiently than conventionally practiced.
  • An air-conditioning apparatus includes, by connecting, a compressor, an outdoor heat exchanger, an indoor heat exchanger, and a switching device, the switching device being provided closer to a discharge side of the compressor than the outdoor heat exchanger and provided closer to the discharge side of the compressor than the indoor heat exchanger.
  • the air-conditioning apparatus includes a fan configured to deliver air toward the outdoor heat exchanger, a power unit configured to supply electric power to the fan, a fan input detector configured to detect a physical value related to the electric power supplied to the fan, and a controller configured to control the switching device 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.
  • the first operation is switched to the second operation when the physical value detected by the fan input detector is equal to or larger than a reference value.
  • the controller adjusts the reference value so that the reference value when refrigerant flowing through the outdoor heat exchanger has a high temperature is smaller than the reference value when the refrigerant has a low temperature.
  • the air-conditioning apparatus includes the controller configured to control the switching device to switch between the first operation in which the outdoor heat exchanger functions as an evaporator and the second operation in which the outdoor heat exchanger functions as a condenser.
  • the first operation is switched to the second operation when the physical value detected by the fan input detector is equal to or larger than the reference value.
  • the controller adjusts the reference value so that the reference value when the refrigerant flowing through the outdoor heat exchanger has a high temperature is smaller than the reference value when the refrigerant flowing through the outdoor heat exchanger has a low temperature.
  • Fig. 1 is a schematic view illustrating the 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 compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, and the indoor heat exchanger 5 are, for example, sequentially connected by pipes to form a refrigerant circuit 90.
  • the compressor 1 is a variable capacity compressor configured to compress sucked refrigerant and discharge the refrigerant as high-temperature and highpressure refrigerant.
  • the four-way valve 2 is a switching device that switches a direction in which the refrigerant discharged from the compressor 1 flows, in response to, for example, execution of a heating operation or a cooling operation.
  • the four-way valve 2 is provided closer to the discharge side of the compressor 1 than the outdoor heat exchanger 3 and provided closer to the discharge side of the compressor 1 than the indoor heat exchanger 5.
  • Fig. 1 illustrates an exemplary state in which the four-way valve 2 is switched to perform a cooling operation.
  • a solid line arrow indicates the flow of the refrigerant when the cooling operation is performed.
  • a dashed line arrow indicates the flow of the refrigerant when a heating operation is performed.
  • the outdoor heat exchanger 3 is a heat exchanger configured to function as a condenser at the cooling operation and function as an evaporator at the heating operation.
  • An outdoor side fan 31 is an air-sending unit configured to supply external air to the outdoor heat exchanger 3 and form airflow.
  • the outdoor side fan 31 is, for example, an axial-flow fan or a centrifugal fan.
  • the outdoor side fan 31 rotates when an outdoor side motor (not illustrated) is driven. Heat is exchanged between the air supplied from the outdoor side fan 31 and the refrigerant flowing inside the outdoor heat exchanger 3.
  • the outdoor side fan 31 is driven by a power unit (not illustrated) configured to supply electric power.
  • the expansion valve 4 is used to decompress and expand the refrigerant flowed out of the outdoor heat exchanger 3 at the cooling operation, and decompress and expand the refrigerant flowed out of the indoor heat exchanger 5 at the heating operation.
  • the indoor heat exchanger 5 is a heat exchanger configured to function as an evaporator at the cooling operation and function as a condenser at the heating operation.
  • An indoor side fan 51 is an air-sending unit configured to supply indoor air to the indoor heat exchanger 5 and form airflow.
  • the indoor side fan 51 is, for example, an axial-flow fan or a centrifugal fan.
  • the indoor side fan 51 rotates when an indoor side motor (not illustrated) is driven. Heat is exchanged between the air supplied from the indoor side fan 51 and the refrigerant flowing inside the indoor heat exchanger 5.
  • An outdoor side refrigerant temperature sensor 32 is a temperature detection unit configured to detect the temperature of the refrigerant flowing through the outdoor heat exchanger 3.
  • An indoor side refrigerant temperature sensor 52 is a sensor configured to detect the temperature of the refrigerant flowing through the indoor heat exchanger 5.
  • a "refrigerant temperature” refers to the temperature of the refrigerant flowing inside the outdoor heat exchanger 3.
  • a controller 80 controls the outdoor side motor to control the rotation speed of the outdoor side fan 31, and controls the indoor side motor to control the rotation speed of the indoor side fan 51.
  • the controller 80 controls the outdoor side motor by changing voltage and current input to the outdoor side motor.
  • the control of the rotation speed of the outdoor side fan 31 by the controller 80 allows control of the volume of air passing through the outdoor heat exchanger 3.
  • a rotation speed detection unit configured to detect the rotation speed of the outdoor side fan 31 may be provided to detect the current rotation speed of the outdoor side fan 31.
  • the current rotation speed of the outdoor side fan 31 may be estimated from information on current applied to the outdoor side motor and voltage applied to the outdoor side motor.
  • a "fan input" refers to a physical value related to electric power supplied to the outdoor side fan 31 (the outdoor side motor configured to rotate the outdoor side fan 31).
  • the controller 80 controls the indoor side motor so that the outdoor side fan 31 rotates, for example, when the air-conditioning apparatus 100 starts operating.
  • the controller 80 is, for example, hardware such as a circuit device or software executed on an arithmetic device such as a microcomputer or a CPU, which are configured to achieve this functionality.
  • the cooling operation is executed when the controller 80 switches the four-way valve 2 to cooling.
  • the heating operation is executed when the controller 80 switches the four-way valve 2 to heating.
  • a "defrosting operation” refers to an operation executed when the controller 80 switches the four-way valve 2 to cooling and stops the outdoor side fan 31.
  • the heating operation corresponds to a "first operation” of the present invention
  • the defrosting operation corresponds to a "second operation” of the present invention.
  • the refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3. Having flowed into the outdoor heat exchanger 3, the refrigerant exchanges heat with the air supplied to the outdoor heat exchanger 3 through rotation of the outdoor side fan, and then flows out of the outdoor heat exchanger 3. Having flowed out of the outdoor heat exchanger 3, the refrigerant flows in the expansion valve 4 and is depressurized therein, and then flows out of the expansion valve 4 before flowing into the indoor heat exchanger 5.
  • the refrigerant exchanges heat with the air supplied to the indoor heat exchanger 5 through rotation of the indoor side fan, and then flows out of the indoor heat exchanger 5. Having flowed out of the indoor heat exchanger 5, the refrigerant flows into the compressor 1.
  • the refrigerant discharged from the compressor 1 flows into the indoor heat exchanger 5. Having flowed into the indoor heat exchanger 5, the refrigerant exchanges heat with the air supplied to the indoor heat exchanger 5 through rotation of the indoor side fan, and then flows out of the indoor heat exchanger 5. Having flowed out of the indoor heat exchanger 5, the refrigerant flows in the expansion valve 4 and is depressurized therein, and then flows out of the expansion valve 4 before flowing into the outdoor heat exchanger 3.
  • the refrigerant exchanges heat with the air supplied to the outdoor heat exchanger 3 through rotation of the outdoor side fan, and then flows out of the outdoor heat exchanger 3. Having flowed out of the outdoor heat exchanger 3, the refrigerant flows into the compressor 1.
  • Fig. 2 is a diagram illustrating change in a frosting amount and total electric power with elapsed time in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • Fig. 3 is a diagram illustrating change in the frosting amount and total current value with elapsed time in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the horizontal axis represents elapsed time [min]
  • the vertical axis represents the frosting amount [g] and a total electric power amount [W].
  • a solid line indicates the frosting amount
  • a dashed line indicates the total electric power.
  • the frosting amount increases as time elapses
  • the total electric power increases as time elapses.
  • the horizontal axis represents elapsed time [min]
  • the vertical axis represents the frosting amount [g] and a total current value [A].
  • a solid line indicates the frosting amount
  • a dashed line indicates the total current value.
  • the frosting amount increases as time elapses
  • the total current value increases as time elapses.
  • Fig. 4 is a diagram illustrating change in an electric power amount with elapsed time in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • Fig. 5 is a diagram illustrating change in the total electric power amount with elapsed time in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • Figs. 4 and 5 illustrate a case in which the fan input is the electric power amount, which is the product of current value applied to an outdoor fan motor and voltage value applied to the outdoor fan motor. Processing illustrated in Figs. 4 and 5 is performed at the heating operation.
  • the controller 80 calculates ⁇ Wtotal by summing ⁇ W(t) according to Expression (1.2) below.
  • ⁇ ⁇ Wtotal ⁇ ⁇ W t
  • the controller 80 determines whether ⁇ Wtotal is equal to or larger than a threshold ⁇ as in Expression (1.3) below.
  • the controller 80 controls the four-way valve 2 to start the defrosting operation.
  • the controller 80 continues the heating operation.
  • the threshold ⁇ varies with the refrigerant temperature. Specifically, for example, it is assumed that the density of frost on the outdoor heat exchanger 3 is larger at a higher refrigerant temperature, and thus the controller 80 decreases the value of ⁇ accordingly. When the value of ⁇ is decreased in this manner, ⁇ Wtotal becomes equal to or larger than ⁇ at earlier timing and the defrosting operation is started earlier. For example, it is assumed that the density of frost on the outdoor heat exchanger 3 is smaller at a lower refrigerant temperature, and thus the controller 80 increases the value of ⁇ accordingly. When the value of ⁇ is increased in this manner, ⁇ Wtotal becomes equal to or larger than ⁇ at later timing and start of the defrosting operation is delayed.
  • the fan input is the electric power, but the present invention is not limited thereto.
  • the fan input may be the current value applied to the outdoor fan motor or the voltage value applied to the outdoor fan motor.
  • Fig. 6 is a schematic view illustrating a state in which frost exists on the outdoor heat exchanger 3 of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the frost on the outdoor heat exchanger 3 has a height Hf_total [mm], and adjacent fins 3b are apart from each other by a distance Fp [mm]. It is assumed that wind blows from one end of each fin 3b in the longitudinal direction thereof to the other end. Since frost exists on the outdoor heat exchanger 3 as illustrated in Fig. 6 , a wind speed ua decreases, and thus heat exchange at the outdoor heat exchanger 3 is hindered as compared to a case in which no frost exists on the outdoor heat exchanger 3.
  • frost exists on a heat transfer tube 3a and the fins 3b included in the outdoor heat exchanger 3.
  • the frost has a lower density as the heat transfer tube 3a and the fins 3b have lower temperatures. In other words, the frost density is smaller at a lower refrigerant temperature.
  • the defrosting operation needs different defrosting heat amounts for an identical blockage state of the outdoor heat exchanger 3 and an identical amount of increase in the fan input. Specifically, at a higher refrigerant temperature, a larger amount of heat is needed to melt frost on the outdoor heat exchanger 3.
  • Fig. 7 is a diagram illustrating a relation between a relative humidity ⁇ and a frost density ⁇ in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the horizontal axis represents the relative humidity ⁇ [%]
  • the vertical axis represents the frost density ⁇ [kg/m 3 ].
  • Fig. 7 illustrates cases with the refrigerant temperature Ts [degrees C] at -30 degrees C and -20 degrees C.
  • the frost density ⁇ decreases as the relative humidity ⁇ increases.
  • the frost density ⁇ is larger when the refrigerant temperature Ts is -20 degrees C than when the refrigerant temperature Ts is -30 degrees C.
  • the frost density ⁇ increases as the refrigerant temperature Ts increases.
  • a defrosting duration increases as the frost density ⁇ increases, and a larger defrosting capacity is needed as the frost density ⁇ increases.
  • the defrosting duration increases as the refrigerant temperature Ts increases.
  • Fig. 8 is a diagram illustrating a relation between the refrigerant temperature and a necessary defrosting heat amount in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the necessary defrosting heat amount is proportional to the temperature of the refrigerant flowing through the refrigerant circuit 90 inside the outdoor heat exchanger 3.
  • the defrosting duration increases as the refrigerant temperature Ts increases.
  • a minimum defrosting duration is one minute when an average refrigerant temperature is -40 degrees C to -30 degrees C.
  • the minimum defrosting duration is three minutes when the average refrigerant temperature is -10 degrees C to -5 degrees C.
  • the minimum defrosting duration is five minutes when the average refrigerant temperature is -5 degrees C to 0 degrees C.
  • Fig. 8 illustrates, for sake of simplicity of description, the proportional relation between the necessary defrosting heat amount and the refrigerant temperature Ts
  • the present invention is not limited to such a relation.
  • the amount of increase in the necessary defrosting heat amount for increase in the refrigerant temperature Ts does not need to be constant.
  • Fig. 9 is a diagram illustrating change in the frequency of the compressor 1 with elapsed time in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • Fig. 10 is a diagram illustrating change in the frequency of the compressor 1 with elapsed time in the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • a solid line indicates change in the frequency of the compressor 1 when the refrigerant temperature is relatively high
  • a dashed line indicates change in the frequency of the compressor 1 when the refrigerant temperature is relatively low.
  • the defrosting operation can be performed in a shorter time at a relatively low refrigerant temperature than at a relatively high refrigerant temperature.
  • efficient execution of the defrosting operation requires a time for melting frost on the outdoor heat exchanger 3 and a time for allowing melted frost to drop from the outdoor heat exchanger 3.
  • melted frost potentially freezes again when the duration of the defrosting operation at a relatively low refrigerant temperature is shorter than the duration of the defrosting operation at a relatively high refrigerant temperature.
  • the operation is performed with identical defrosting durations at a relatively low refrigerant temperature and a relatively high refrigerant temperature and with a low frequency of the compressor 1, which will be described below.
  • Interval (a) refers to an interval in which the heating operation is executed
  • Interval (b) refers to an interval in which the defrosting operation is executed
  • Interval (c) refers to an interval in which the heating operation is executed after the defrosting operation.
  • the controller 80 controls the compressor 1 so that the compressor 1 has a predetermined frequency while the four-way valve 2 is switched to heating. After the compressor 1 is operated at the predetermined frequency for a predetermined time, the controller 80 controls the compressor 1 to decrease the frequency thereof. Then, when the frequency of the compressor 1 becomes zero (t11), the controller 80 switches the four-way valve 2 to cooling and starts the defrosting operation.
  • the controller 80 controls the compressor 1 so that the compressor 1 has a predetermined frequency fmax while the four-way valve 2 is switched to cooling. After the compressor 1 is operated at the predetermined frequency fmax for a predetermined time, the controller 80 controls the compressor 1 to decrease the frequency of the compressor 1. Then, when the frequency of the compressor 1 becomes zero (time t14), the controller 80 switches the four-way valve 2 to heating again and starts the heating operation.
  • the controller 80 controls the compressor 1 so that the compressor 1 has the predetermined frequency fmax while the four-way valve 2 is switched to cooling. After the compressor 1 is operated at the predetermined frequency fmax for a predetermined time (time t12), the controller 80 controls the compressor 1 to decrease the frequency thereof so that the compressor 1 has a predetermined frequency f1. After the frequency of the compressor 1 is decreased to the predetermined frequency f1 (time t13), the controller 80 operates the compressor 1 at the predetermined frequency f1 for a predetermined time.
  • the controller 80 controls the compressor 1 to decrease the frequency of the compressor 1. Then, when the frequency of the compressor 1 becomes zero (time t14), the controller 80 switches the four-way valve 2 to heating again and starts the heating operation.
  • the controller 80 controls the compressor 1 so that the frequency thereof has a predetermined frequency while the four-way valve 2 is switched to heating.
  • Interval (a) refers to an interval in which the heating operation is executed
  • Interval (b) refers to an interval in which the defrosting operation is executed
  • Interval (c) refers to an interval in which the heating operation is executed after the defrosting operation.
  • change in the frequency of the compressor 1 as time elapses in Interval (a) and Interval (c) is identical to that in Fig. 9 , and thus description thereof will be omitted.
  • the controller 80 controls the compressor 1 so that the compressor 1 has the predetermined frequency fmax while the four-way valve 2 is switched to cooling. After the compressor 1 is operated at the predetermined frequency fmax for a predetermined time, the controller 80 controls the compressor 1 to decrease the frequency of the compressor 1. Then, when the frequency of the compressor 1 becomes zero (time t24), the controller 80 switches the four-way valve 2 to heating again and starts the heating operation.
  • the controller 80 controls the compressor 1 so that the compressor 1 has a predetermined frequency f2 while the four-way valve 2 is switched to cooling. After the compressor 1 acquires the predetermined frequency f2 (time t22) and has operated for a predetermined time (time t23), the controller 80 controls the compressor 1 to decrease the frequency of the compressor 1. Then, when the frequency of the compressor 1 becomes zero (time t24), the controller 80 switches the four-way valve 2 to heating again and starts the heating operation.
  • the compressor 1, the outdoor heat exchanger 3, the indoor heat exchanger 5, and the four-way valve 2 provided closer to the discharge side of the compressor 1 than the outdoor heat exchanger 3 and provided closer to the discharge side of the compressor 1 than the indoor heat exchanger 5 are connected with each other.
  • the air-conditioning apparatus 100 includes the fan 31 configured to deliver air toward the outdoor heat exchanger 3, the power unit configured to supply electric power to the fan 31, a fan input detector configured to detect a physical value related to the electric power supplied to the fan 31, and the controller 80 configured to control the four-way valve 2 to switch between the first operation in which the outdoor heat exchanger 3 functions as an evaporator and the second operation in which the outdoor heat exchanger 3 functions as a condenser.
  • the first operation is switched to the second operation when the physical value detected by the fan input detector is equal to or larger than a reference value.
  • the controller 80 adjusts the reference value so that the reference value when the refrigerant flowing through the outdoor heat exchanger 3 has a high temperature is smaller than the reference value when the refrigerant has a low temperature.
  • the compressor 1, the outdoor heat exchanger 3, the indoor heat exchanger 5, and the four-way valve 2 provided closer to the discharge side of the compressor 1 than the outdoor heat exchanger 3 and provided closer to the discharge side of the compressor 1 than the indoor heat exchanger 5 are connected with each other.
  • the air-conditioning apparatus 100 includes the fan 31 configured to deliver air toward the outdoor heat exchanger 3, the power unit configured to supply electric power to the fan 31, the fan input detector configured to detect a physical value related to the electric power supplied to the fan 31, and the controller 80 configured to control the four-way valve 2 to switch between the first operation in which the outdoor heat exchanger 3 functions as an evaporator and the second operation in which the outdoor heat exchanger 3 functions as a condenser.
  • the first operation is switched to the second operation when the physical value detected by the fan input detector is equal to or larger than a reference value.
  • the controller 80 controls the frequency of the compressor 1 so that the frequency of the compressor 1 when the refrigerant flowing through the outdoor heat exchanger 3 has a high temperature is higher than the frequency of the compressor 1 when the refrigerant has a low temperature.
  • Embodiment 2 is not part of the claimed invention, but only as an example for further understanding the invention.
  • the timing of execution of the defrosting operation is determined based on a frosting amount Mf
  • the frequency of the compressor 1 in the defrosting operation is determined based on the frosting amount Mf.
  • any characteristic is same as that of Embodiment 1 unless otherwise stated, and any identical function and configuration will be described by using identical reference signs.
  • the frosting amount mf(t) is given based on a surface area A0 [m 2 ], the frost density pf [kg/m 3 ], and a frost height Hf(t) through Expression (2.1) below.
  • mf t A 0 ⁇ ⁇ ⁇ f t ⁇ Hf t
  • the surface area AO [m 2 ] is a heat exchange surface area of the outdoor heat exchanger 3.
  • the frost density pf [kg/m 3 ] is the density of frost on the outdoor heat exchanger 3, which is affected by a cooling surface temperature and a relative humidity.
  • the frost height Hf(t) is the height of frost on the outdoor heat exchanger 3.
  • the frosting amount Mf is given based on the frosting amount mf(t) through Expression (2.2) below.
  • Mf ⁇ ⁇ m t
  • a defrosting heat amount Qf [kJ] is given based on the frosting amount Mf [kg] and a latent heat ⁇ H [kJ/kg] through Expression (2.3) below.
  • Qf Mf ⁇ ⁇ H
  • Tf Qf / P
  • the controller 80 of the air-conditioning apparatus 100 according to Embodiment 2 determines the defrosting duration in accordance with the frosting amount. Accordingly, the defrosting operation can be performed more efficiently than conventionally practiced.
  • the outdoor side fan 31 corresponds to a "fan" of the present invention.

Landscapes

  • 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)

Claims (3)

  1. Appareil de climatisation comprenant :
    un compresseur (1) ;
    un échangeur de chaleur extérieur (3) ;
    un échangeur de chaleur intérieur (5) ;
    un dispositif de commutation (2), le dispositif de commutation (2) étant disposé plus près du côté évacuation du compresseur (1) que l'échangeur de chaleur extérieur (3), et disposé plus près du côté évacuation du compresseur (1) que l'échangeur de chaleur intérieur (5), le compresseur (1), l'échangeur de chaleur extérieur (3), l'échangeur de chaleur intérieur (5), et le dispositif de commutation (2) étant connectés les uns aux autres ;
    une soufflante (31) configurée pour délivrer l'air vers l'échangeur de chaleur extérieur (3) ;
    une unité d'alimentation configurée pour fournir le courant électrique à la soufflante (31) ;
    un détecteur d'entrée de soufflante configuré pour détecter une valeur physique corrélée avec l'alimentation fournie à la soufflante (31) ; et
    un contrôleur (80) configuré pour commander le dispositif de commutation (2) pour le faire commuter entre un premier mode de fonctionnement dans lequel l'échangeur de chaleur extérieur (3) sert d'évaporateur, et un second mode de fonctionnement dans lequel l'échangeur de chaleur extérieur (3) sert de condenseur,
    où le premier mode de fonctionnement est commuté vers le second mode de fonctionnement lorsque la valeur physique détectée par le détecteur d'entrée de soufflante, est égale ou supérieure à une valeur de référence, et est caractérisé en ce que
    le contrôleur (80) est configuré pour régler la valeur de référence de telle sorte que la valeur de référence soit moins élevée, à une température de fluide frigorigène plus élevée d'un fluide frigorigène qui pénètre dans l'échangeur de chaleur extérieur (3).
  2. Appareil de climatisation comprenant :
    un compresseur (1) ;
    un échangeur de chaleur extérieur (3) ;
    un échangeur de chaleur intérieur (5) ;
    un dispositif de commutation (2), le dispositif de commutation (2) étant disposé plus près du côté évacuation du compresseur (1) que l'échangeur de chaleur extérieur (3), et disposé plus près du côté évacuation du compresseur (1) que l'échangeur de chaleur intérieur (5), le compresseur (1), l'échangeur de chaleur extérieur (3), l'échangeur de chaleur intérieur (5), et le dispositif de commutation (2) étant connectés les uns aux autres ;
    une soufflante (31) configurée pour délivrer l'air vers l'échangeur de chaleur extérieur (3) ;
    une unité d'alimentation configurée pour fournir le courant électrique à la soufflante (31) ;
    un détecteur d'entrée de soufflante configuré pour détecter une valeur physique corrélée avec l'alimentation fournie à la soufflante (31) ; et
    un contrôleur (80) configuré pour commander le dispositif de commutation (2) pour le faire commuter entre un premier fonctionnement dans lequel l'échangeur de chaleur extérieur (3) sert d'évaporateur, et un second fonctionnement dans lequel l'échangeur de chaleur extérieur (3) sert de condenseur,
    où le premier mode de fonctionnement est commuté vers le second mode de fonctionnement lorsque la valeur physique détectée par le détecteur d'entrée de soufflante, est égale ou supérieure à une valeur de référence, et est caractérisé en ce que
    le contrôleur (80) est configuré pour commander le compresseur (1) de telle sorte que la fréquence du compresseur (1) soit plus élevée, à une température de fluide frigorigène plus élevée d'un fluide frigorigène qui circule dans l'échangeur de chaleur extérieur (3).
  3. Appareil de climatisation selon la revendication 1 ou 2, où le détecteur d'entrée de soufflante détecte une valeur du courant ou une valeur de la tension appliquée à un moteur du côté extérieur, configuré pour entraîner la soufflante (31), ou une puissance électrique sur la base de la valeur du courant et de la valeur de la tension.
EP15882576.0A 2015-02-18 2015-02-18 Dispositif de climatisation Active EP3260790B1 (fr)

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PCT/JP2015/054402 WO2016132473A1 (fr) 2015-02-18 2015-02-18 Dispositif de climatisation

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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
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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JPH01107056A (ja) * 1987-10-21 1989-04-24 Toshiba Corp 空気調和機
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EP3260790A1 (fr) 2017-12-27
WO2016132473A1 (fr) 2016-08-25
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
CN107250679A (zh) 2017-10-13

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