WO2017122264A1 - Climatiseur - Google Patents

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Publication number
WO2017122264A1
WO2017122264A1 PCT/JP2016/050653 JP2016050653W WO2017122264A1 WO 2017122264 A1 WO2017122264 A1 WO 2017122264A1 JP 2016050653 W JP2016050653 W JP 2016050653W WO 2017122264 A1 WO2017122264 A1 WO 2017122264A1
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WO
WIPO (PCT)
Prior art keywords
compressor
refrigerant
temperature
pressure
heat exchanger
Prior art date
Application number
PCT/JP2016/050653
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English (en)
Japanese (ja)
Inventor
靖人 熊城
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 PCT/JP2016/050653 priority Critical patent/WO2017122264A1/fr
Publication of WO2017122264A1 publication Critical patent/WO2017122264A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the present invention relates to an air conditioner.
  • the present invention has been made to solve the above-described problems, and an air conditioner that can ensure the reliability of the operation of the compressor even when the evaporation pressure of the refrigerant sucked by the compressor is lowered.
  • the purpose is to obtain.
  • the air conditioner according to the present invention includes a compressor, a refrigerant flow switching device, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger connected via a refrigerant pipe, and constitutes a refrigeration cycle in which the refrigerant circulates.
  • the first temperature measuring device that is provided in the indoor heat exchanger and that measures one of the condensation temperature or evaporation temperature of the refrigerant, and the condensation heat or evaporation of the refrigerant that is provided in the outdoor heat exchanger.
  • a second temperature measuring device that measures the other of the temperatures; and a control device that calculates a condensation pressure based on the condensation temperature and obtains the evaporation pressure based on the evaporation temperature.
  • a predetermined range of the operating speed of the compressor is stored in accordance with the pressure and the evaporation pressure, and the actual speed of the compressor is controlled to be within the range of the operating speed. .
  • the control device stores a predetermined operating speed range of the compressor according to the condensation pressure and the evaporating pressure, and the actual speed of the compressor falls within the operating speed range. To control. By doing in this way, even if the evaporation pressure of the refrigerant
  • FIG. 1 is a schematic configuration diagram illustrating an example of a refrigerant circuit of an air conditioner according to an embodiment of the present invention.
  • the air conditioner 100 includes a heat source unit A and a utilization unit B.
  • the heat source unit A and the utilization unit B are connected via a liquid connection pipe 11 and a gas connection pipe 10 which are refrigerant communication pipes.
  • refrigerant used in the air conditioner 100 examples include an HFC refrigerant such as R410A, R407C, R404A, and R32, an HFO refrigerant such as R1234yf / ze, an HCFC refrigerant such as R22 and R134a, or carbon dioxide (CO 2 ).
  • HFC refrigerant such as R410A, R407C, R404A, and R32
  • HFO refrigerant such as R1234yf / ze
  • HCFC refrigerant such as R22 and R134a
  • CO 2 carbon dioxide
  • natural refrigerants such as hydrocarbons, helium, propane and the like.
  • the utilization unit B is connected to the heat source unit A via the liquid connection pipe 11 and the gas connection pipe 10 to constitute a part of the refrigerant circuit.
  • the utilization unit B constitutes an indoor refrigerant circuit that is a part of the refrigerant circuit, and includes an indoor air blower 12 and an indoor heat exchanger 7.
  • the indoor heat exchanger 7 is composed of, for example, a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the indoor heat exchanger 7 functions as a refrigerant evaporator during cooling operation to cool indoor air, and functions as a refrigerant condenser during heating operation to heat indoor air.
  • the indoor air blower 12 is a fan capable of varying the flow rate of air supplied to the indoor heat exchanger 7, and includes, for example, a centrifugal fan driven by a DC motor (not shown), a multiblade fan, or the like. It is configured.
  • the indoor air blower 12 sucks room air into the use unit B, and exchanges heat with the refrigerant in the indoor heat exchanger 7. And the indoor air blower 12 supplies the air which heat-exchanged indoors as supply air.
  • the indoor heat exchanger 7 is provided with a first temperature measuring device 6 for detecting the temperature of the refrigerant in the gas-liquid two-phase state.
  • the first temperature measuring device 6 is composed of a thermistor, and measures the condensation temperature Tc of the refrigerant flowing through the indoor heat exchanger 7 during the heating operation, and measures the refrigerant evaporation temperature Te during the cooling operation.
  • Heat source unit A Next, a detailed configuration of the heat source unit A will be described.
  • the heat source unit A is connected to the utilization unit B via the liquid connection pipe 11 and the gas connection pipe 10 and constitutes a part of the refrigerant circuit.
  • the heat source unit A includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 4, an outdoor air blower 13, an expansion device 5, an accumulator 8, and a control device 20.
  • the four-way valve 2 corresponds to the “refrigerant flow switching device” in the present invention.
  • the compressor 1 is a device capable of changing the rotation speed (frequency), and here, a positive displacement compressor driven by a motor (not shown) controlled by an inverter is used.
  • the four-way valve 2 is a valve having a function of switching the direction of refrigerant flow.
  • the four-way valve 2 connects the discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 4 as shown by the dotted line of the four-way valve 2 in FIG.
  • the refrigerant flow path is switched so as to connect to the gas connection pipe 10 side.
  • the outdoor heat exchanger 4 functions as a condenser for the refrigerant compressed in the compressor 1
  • the indoor heat exchanger 7 is a refrigerant that is condensed in the outdoor heat exchanger 4. It functions as an evaporator.
  • the four-way valve 2 connects the discharge side of the compressor 1 and the gas connection pipe 10 side as shown by the solid line of the four-way valve 2 in FIG.
  • the refrigerant flow path is switched so as to connect the gas side of the heat exchanger 4.
  • the indoor heat exchanger 7 functions as a condenser for the refrigerant compressed in the compressor 1
  • the outdoor heat exchanger 4 is a refrigerant that is condensed in the indoor heat exchanger 7. It functions as an evaporator.
  • the outdoor heat exchanger 4 is composed of a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the outdoor heat exchanger 4 has a gas side pipe connected to the four-way valve 2, a liquid side pipe connected to the liquid connection pipe 11, functions as a refrigerant condenser during cooling operation, and a refrigerant evaporator during heating operation. Function as.
  • the outdoor air blower 13 is a fan capable of changing the flow rate of air supplied to the outdoor heat exchanger 4, and is composed of, for example, a propeller fan driven by a DC motor (not shown).
  • the outdoor blower 13 has a function of sucking outdoor air into the heat source unit A and discharging the air heat-exchanged with the refrigerant in the outdoor heat exchanger 4 to the outside.
  • the expansion device 5 is a device that is connected to the liquid side of the heat source unit A and adjusts the flow rate of the refrigerant flowing in the refrigerant circuit.
  • the accumulator 8 is a refrigerant container that is connected to the suction side piping of the compressor 1.
  • the accumulator 8 returns the refrigeration oil that has flowed out of the compressor 1 together with the refrigerant to the compressor 1 while suppressing the excessive inflow of liquid refrigerant to the compressor 1 and the function of storing surplus refrigerant during operation. It has a function to do.
  • the outdoor heat exchanger 4 is provided with a second temperature measuring device 3 for detecting the temperature of the refrigerant in the gas-liquid two-phase state.
  • the second temperature measuring device 3 is composed of a thermistor, and measures the evaporation temperature Te of the refrigerant flowing through the outdoor heat exchanger 4 during the heating operation, and measures the refrigerant condensation temperature Tc during the cooling operation.
  • the control device 20 is constituted by, for example, a microcomputer.
  • the control device 20 calculates the first refrigerant pressure of the refrigerant flowing through the indoor heat exchanger 7 based on the refrigerant temperature detected from the first temperature measuring device 6. Further, the control device 20 calculates the second refrigerant pressure of the refrigerant flowing through the outdoor heat exchanger 4 based on the refrigerant temperature detected from the second temperature measuring device 3.
  • the first refrigerant pressure means the refrigerant condensing pressure Pd
  • the second refrigerant pressure means the refrigerant evaporating pressure Ps.
  • the first refrigerant pressure means the refrigerant evaporation pressure Ps
  • the second refrigerant pressure means the refrigerant condensation pressure Pd.
  • the control device 20 controls the compressor 1 at a rotational speed in a range determined in advance with reference to the first refrigerant pressure and the second refrigerant pressure by a method described later.
  • the control device 20 is built in the air conditioner 100, but the present invention is not limited to this.
  • the main control unit is provided in the heat source unit A
  • the sub-control unit having a part of the function of the control device 20 is provided in the use unit B
  • data communication is performed between the main control unit and the sub-control unit, thereby performing the cooperation process You may make it the structure to perform.
  • a configuration in which the control device 20 having all functions is installed in the use unit B, or a configuration in which the control device 20 is separately installed outside the air conditioner 100 may be used.
  • the heat source unit A and the utilization unit B are connected via the liquid connection pipe 11 and the gas connection pipe 10 to constitute the refrigerant circuit of the air conditioner 100.
  • the present invention is not limited to this, and two heat source units A and utilization units B are provided. A plurality of units may be provided. Further, in the case where both the heat source unit A and the utilization unit B are composed of a plurality of units, the respective capacities may be different or all may have the same capacity.
  • the four-way valve 2 is in the state indicated by the dotted line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4, and the suction side of the compressor 1 is the indoor heat exchanger 7 It is in the state connected to the gas side.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the outdoor heat exchanger 4 that is a condenser via the four-way valve 2, and the refrigerant is condensed and liquefied by the blowing action of the outdoor air blower 13, and the high-pressure and low-temperature refrigerant. It becomes.
  • the condensed and liquefied high-pressure and low-temperature refrigerant is decompressed by the expansion device 5 to become a two-phase refrigerant, is sent to the utilization unit B via the liquid connection pipe 11, and is sent to the indoor heat exchanger 7.
  • the decompressed two-phase refrigerant is evaporated by the blower action of the indoor blower 12 in the indoor heat exchanger 7 which is an evaporator, and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 1 again via the four-way valve 2 and the accumulator 8.
  • the heating operation will be described with reference to FIG.
  • the four-way valve 2 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the indoor heat exchanger 7 and the suction side of the compressor 1 is the outdoor heat exchanger 4. It is in the state connected to the gas side.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is sent to the utilization unit B via the four-way valve 2 and the gas connection pipe 10. Then, the high-temperature and high-pressure gas refrigerant reaches the indoor heat exchanger 7 that is a condenser, and the refrigerant is condensed and liquefied by the blowing action of the indoor air blower 12 to become a high-pressure and low-temperature refrigerant.
  • the condensed and liquefied high-pressure and low-temperature refrigerant is sent to the heat source unit A via the liquid connection pipe 11, is decompressed by the expansion device 5, becomes a two-phase refrigerant, and is sent to the outdoor heat exchanger 4.
  • the decompressed two-phase refrigerant is evaporated by the blowing action of the outdoor blower 13 in the outdoor heat exchanger 4 as an evaporator, and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 1 again via the four-way valve 2 and the accumulator 8.
  • the defrosting operation will be described with reference to FIG.
  • the four-way valve 2 is in the state indicated by the dotted line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 4, and the suction side of the compressor 1 is the indoor heat exchanger. 7 is connected to the gas side.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the outdoor heat exchanger 4 that is a condenser via the four-way valve 2, is heat-exchanged by the outdoor heat exchanger 4, and is generated in the outdoor heat exchanger 4. Thaw frost. And a refrigerant
  • coolant is pressure-reduced with the expansion device 5, heat-exchanges with the indoor heat exchanger 7, and cools indoor air. Thereafter, the refrigerant is sucked into the compressor 1 again via the four-way valve 2 and the accumulator 8.
  • FIG. 2 is a schematic configuration diagram showing another example of the refrigerant circuit of the air conditioner according to the embodiment of the present invention.
  • the basic configuration of the air conditioner 101 is the same as that of the air conditioner 100 of FIG. 1, but the air conditioner 101 includes an indoor heat exchanger 7, an outdoor heat exchanger 4, and the like.
  • the diaphragm device 5a and the diaphragm device 5b are provided between the two. Moreover, it differs in the point provided with the receiver tank 9 which stores a liquid refrigerant between the expansion device 5a and the expansion device 5b.
  • an air conditioner is good also as the above structures.
  • FIG. 3 is a diagram showing the relationship between the rotation speed of the compressor of the air conditioner according to the embodiment of the present invention, the evaporation pressure, and the condensation pressure.
  • the vertical axis of the figure represents the condensation pressure Pd
  • the horizontal axis of the figure represents the evaporation pressure Ps.
  • the control device 20 obtains the condensing pressure Pd and the evaporating pressure Ps based on the refrigerant condensing temperature Tc and the evaporating temperature Te detected from the first temperature measuring device 6 and the second temperature measuring device 3.
  • the control device 20 stores in advance a pressure operating range of the compressor 1 and a range of operating rotational speeds of the compressor 1 in accordance with the condensation pressure Pd and the evaporation pressure Ps.
  • the operating rotational speed range of the compressor 1 is A to B (rps).
  • the control device 20 checks the actual rotational speed Z (rps) of the compressor 1 and controls the compressor 1 so that the rotational speed of the compressor 1 falls within the range of A to B (rps).
  • the control device 20 collates the actual rotational speed Z (rps) of the compressor 1 and controls the compressor 1 so that the rotational speed of the compressor 1 falls within the range of C to D (rps).
  • the range of the operating rotational speed of the compressor 1 is E to F (rps).
  • the control device 20 collates the actual rotational speed Z (rps) of the compressor 1 and controls the compressor 1 so that the rotational speed of the compressor 1 falls within the range of E to F (rps).
  • the operation rotation speed determined in advance in the control device 20 has a range of a plurality of operation rotation speeds, and the control device 20 adjusts the compressor 1 according to the values of the condensation pressure Pd and the evaporation pressure Ps. Control the number of revolutions.
  • pressure operating range of the compressor 1 and the operating rotational speed range of the compressor 1 shown in FIG. 3 of the present embodiment are examples, and may be appropriately changed according to the type or specification of the compressor.
  • the control device 20 performs control to switch from the heating operation to the defrosting operation after elapse of a predetermined time ⁇ T.
  • the value of the evaporating pressure Ps obtained from the evaporating temperature Te during the heating operation becomes Pe2, and may be reduced to less than PL, which is the lower limit value of the pressure that can be used by the compressor 1.
  • the control device 20 controls the air conditioner 100 so that the heating operation is terminated and the defrosting operation is performed even before the time ⁇ T has elapsed.
  • FIG. 4 is a flowchart showing the control of the rotation speed of the compressor of the air conditioner according to the embodiment of the present invention.
  • the control operation of the control device 20 of the air conditioner 100 will be described based on the steps of FIG. 4 with reference to FIG.
  • Step S1 The control device 20 receives a command to start the heating operation, and starts the operation of the compressor 1. Thereafter, the control device 20 proceeds to (Step S2).
  • Step S2 The controller 20 detects the condensation temperature Tc from the first temperature measuring device 6 and calculates the condensation pressure Pd by converting the temperature. Further, the control device 20 detects the evaporation temperature Te from the second temperature measuring device 3 and calculates the evaporation pressure Ps by converting the temperature. Thereafter, the control device 20 proceeds to (Step S3).
  • Step S3 The control device 20 obtains the range of the operating rotational speed of the compressor 1 based on the evaporation pressure Ps and the condensation pressure Pd. Then, the control device 20 collates the actual rotational speed Z (rps) of the compressor 1 with the operating rotational speed range of the compressor 1. Thereafter, the control device 20 proceeds to (Step S4).
  • Step S4 The control device 20 determines whether the actual rotation speed Z (rps) of the compressor 1 is within the range of the operation rotation speed of the compressor 1. If the actual rotational speed Z (rps) of the compressor 1 is within the operating rotational speed range of the compressor 1, the process proceeds to (Step S6), and otherwise, the process proceeds to (Step S5).
  • Step S5 The control device 20 controls the actual rotation speed Z (rps) of the compressor 1 so as to be within the range of the number of operations of the compressor 1 determined by the evaporation pressure Ps and the condensation pressure Pd. Thereafter, the control device 20 proceeds to (Step S6).
  • Step S6 The control device 20 continues the heating operation of the air conditioner 100.
  • FIG. 5 is a flowchart showing an operation operation when starting a normal defrosting operation of the air conditioner according to the embodiment of the present invention.
  • the control operation of the control device 20 of the air conditioner 100 will be described based on each step of FIG.
  • Step S11 The control device 20 receives a command to start the heating operation, and starts the operation of the compressor 1. Thereafter, the control device 20 proceeds to (Step S12).
  • Step S12 The control device 20 determines whether the temperature of the outdoor heat exchanger 4 is the defrosting start temperature. When the temperature of the outdoor heat exchanger 4 is the defrosting start temperature, the control device 20 proceeds to (Step S13), and otherwise repeats (Step S12).
  • Step S13 The control device 20 determines whether the heating operation time is longer than the time ⁇ T that is the time for switching from the heating operation to the defrosting operation. When the heating operation time is longer than the time ⁇ T that is the time for switching from the heating operation to the defrosting operation, the control device 20 proceeds to (Step S14), and repeats (Step S13) otherwise.
  • Step S14 The control device 20 starts the defrosting operation of the air conditioner 100. Thereafter, the control device 20 proceeds to (Step S15).
  • Step S15 The control device 20 determines whether the temperature of the outdoor heat exchanger 4 has reached the defrosting end temperature. When the temperature of the outdoor heat exchanger 4 reaches the defrosting end temperature, the control device 20 proceeds to (Step S16), and otherwise repeats (Step S15).
  • Step S16 The control device 20 ends the defrosting operation of the air conditioner 100 and starts the heating operation.
  • the control device 20 of the air conditioner 100 determines whether or not to perform the defrosting operation using the ⁇ T time stored in the control device 20 in advance as a determination criterion.
  • the evaporation pressure Ps may deviate from the pressure operating range of the compressor 1 shown in FIG. Therefore, the control operation of the control device 20 when the evaporation pressure Ps deviates from the pressure operation range of the compressor 1 shown in FIG. 3 will be described below.
  • FIG. 6 is a flowchart showing an operation operation when starting an exceptional defrosting operation of the air conditioner according to the embodiment of the present invention.
  • the control operation of the control device 20 of the air conditioner 100 will be described based on the steps of FIG. 6 with reference to FIG.
  • Step S21 The control device 20 receives a command to start the heating operation, and starts the operation of the compressor 1. Thereafter, the control device 20 proceeds to (Step S22).
  • Step S22 The control device 20 detects the evaporation temperature Te from the second temperature measuring device 3, and calculates the evaporation pressure Ps by converting the temperature. Thereafter, the control device 20 proceeds to (Step S23).
  • Step S23 The control device 20 determines whether the evaporation pressure Ps is less than PL, which is the lower limit value of the usable pressure range of the compressor 1. When it is determined that the evaporation pressure Ps is less than PL, which is the lower limit value of the usable pressure range of the compressor 1, the control device 20 proceeds to (Step S24), and otherwise (Step S25). Migrate to
  • Step S24 The control device 20 starts the defrosting operation of the air conditioner 100. Thereafter, the control device 20 proceeds to (Step S26).
  • Step S25 The control device 20 continues the heating operation of the air conditioner 100. Thereafter, the control device 20 proceeds to (Step S23).
  • Step S26 The control device 20 determines whether the temperature of the outdoor heat exchanger 4 has reached the defrosting end temperature. When the temperature of the outdoor heat exchanger 4 reaches the defrosting end temperature, the control device 20 proceeds to (Step S27), and repeats (Step S26) otherwise.
  • Step S27 The control device 20 ends the defrosting operation of the air conditioner 100 and starts the heating operation.
  • the air conditioner 100 includes the compressor 1, the four-way valve 2, the indoor heat exchanger 7, the expansion device 5, and the outdoor heat exchanger 4 sequentially via the refrigerant pipe.
  • an air conditioner 100 that is connected and constitutes a refrigeration cycle in which a refrigerant circulates, a first temperature measurement device 6 that is provided in the indoor heat exchanger 7 and measures one of the condensation temperature or evaporation temperature of the refrigerant, and the outdoor heat
  • a second temperature measuring device 3 that is provided in the exchanger 4 and measures the other of the refrigerant condensation temperature or the evaporation temperature
  • a control device that calculates the condensation pressure based on the condensation temperature and obtains the evaporation pressure based on the evaporation temperature.
  • control device 20 stores a predetermined range of the operating speed of the compressor 1 according to the condensation pressure and the evaporation pressure, and the actual rotational speed of the compressor 1 is a range of the operating speed. Control to fit within. By doing in this way, even if the evaporation pressure of the refrigerant
  • control device 20 stops the heating operation and starts the defrosting operation when the evaporation pressure falls below the lower limit value of the operating pressure of the compressor 1 during the heating operation. By doing in this way, before reaching the time to switch from heating operation to defrost operation, it can switch to defrost operation, and obtain air conditioner 100 which can secure the reliability of compressor 1 more. Can do.
  • the predetermined operating rotational speed is constituted by a plurality of operating rotational speeds.

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

Abstract

Climatiseur équipé : d'un premier dispositif de mesure de température qui est disposé dans un échangeur de chaleur intérieur de manière à mesurer une température parmi la température de condensation et la température d'évaporation d'un fluide frigorigène ; d'un second dispositif de mesure de température qui est disposé dans un échangeur de chaleur extérieur de manière à mesurer l'autre température parmi la température de condensation et la température d'évaporation du fluide frigorigène ; et un dispositif de commande qui calcule la pression de condensation sur la base de la température de condensation, et détermine la pression d'évaporation sur la base de la température d'évaporation. Le dispositif de commande stocke des plages de vitesse de rotation de fonctionnement de compresseur prédéfinies en fonction de la pression de condensation et de la pression d'évaporation, et effectue une commande de telle sorte que la vitesse de rotation de compresseur réelle tombe dans la plage de vitesse de rotation de fonctionnement de compresseur.
PCT/JP2016/050653 2016-01-12 2016-01-12 Climatiseur WO2017122264A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107449192A (zh) * 2017-07-28 2017-12-08 广东美的制冷设备有限公司 变频压缩机的频率调节方法、装置及可读存储介质
CN109163414A (zh) * 2018-07-23 2019-01-08 青岛海尔空调器有限总公司 空调系统压力控制方法及装置、存储介质及空调
WO2019031561A1 (fr) * 2017-08-08 2019-02-14 ダイキン工業株式会社 Dispositif frigorifique

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0350437A (ja) * 1989-07-17 1991-03-05 Toshiba Corp 空気調和機
JPH0443273A (ja) * 1990-06-11 1992-02-13 Hitachi Ltd 空気熱源ヒートポンプ式冷凍装置の除霜制御回路
JP2013170797A (ja) * 2012-02-22 2013-09-02 Hitachi Appliances Inc 冷凍装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0350437A (ja) * 1989-07-17 1991-03-05 Toshiba Corp 空気調和機
JPH0443273A (ja) * 1990-06-11 1992-02-13 Hitachi Ltd 空気熱源ヒートポンプ式冷凍装置の除霜制御回路
JP2013170797A (ja) * 2012-02-22 2013-09-02 Hitachi Appliances Inc 冷凍装置

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107449192A (zh) * 2017-07-28 2017-12-08 广东美的制冷设备有限公司 变频压缩机的频率调节方法、装置及可读存储介质
WO2019031561A1 (fr) * 2017-08-08 2019-02-14 ダイキン工業株式会社 Dispositif frigorifique
JP2019032110A (ja) * 2017-08-08 2019-02-28 ダイキン工業株式会社 冷凍装置
CN111033152A (zh) * 2017-08-08 2020-04-17 大金工业株式会社 制冷机
CN111033152B (zh) * 2017-08-08 2021-05-25 大金工业株式会社 制冷机
US11029067B2 (en) 2017-08-08 2021-06-08 Daikin Industries, Ltd. Refrigeration apparatus with defrost during heating operation
CN109163414A (zh) * 2018-07-23 2019-01-08 青岛海尔空调器有限总公司 空调系统压力控制方法及装置、存储介质及空调

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