WO2016207992A1 - Climatiseur - Google Patents

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Publication number
WO2016207992A1
WO2016207992A1 PCT/JP2015/068140 JP2015068140W WO2016207992A1 WO 2016207992 A1 WO2016207992 A1 WO 2016207992A1 JP 2015068140 W JP2015068140 W JP 2015068140W WO 2016207992 A1 WO2016207992 A1 WO 2016207992A1
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WIPO (PCT)
Prior art keywords
refrigerant
unit
liquid phase
phase temperature
reference value
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Application number
PCT/JP2015/068140
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English (en)
Japanese (ja)
Inventor
貴玄 中村
齊藤　信
正樹 豊島
青木　正則
雅史 冨田
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.)
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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/JP2015/068140 priority Critical patent/WO2016207992A1/fr
Priority to JP2017524330A priority patent/JP6410935B2/ja
Publication of WO2016207992A1 publication Critical patent/WO2016207992A1/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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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

Definitions

  • the present invention relates to an air conditioner having a function of determining leakage of a refrigerant filled in a refrigerant circuit.
  • a heat pump type air conditioner in which an outdoor unit and an indoor unit are connected by piping, and a refrigerant flows between the outdoor unit and the indoor unit to perform a heating operation or a cooling operation.
  • the refrigerant gas is compressed in the compressor on the outdoor unit side, cooled and liquefied in the outdoor heat exchanger, and sent to the indoor unit.
  • the liquid refrigerant sent to the indoor unit expands and vaporizes in the expansion device, and the indoor air is cooled by the heat of vaporization of the refrigerant in the indoor heat exchanger.
  • an abnormality may occur in the compression process of the compressor, and an abnormality may occur in which the refrigerant does not become high pressure even when compressed, and this abnormality is mainly caused by an insufficient amount of cooling gas due to refrigerant leakage. It has become. Therefore, in an air conditioner having a liquid reservoir in the refrigerant circuit, an air conditioner has been proposed that determines the suitability of the refrigerant amount in a refrigerant amount determination mode in which surplus refrigerant in the liquid reservoir is stored on the high pressure side (for example, Patent Documents). 1).
  • Patent Document 1 in the refrigerant amount determination mode, in the forced cooling operation in which the outdoor heat exchanger becomes a condenser, the suitability of the refrigerant amount is determined based on the degree of supercooling at the outlet of the outdoor heat exchanger. Is disclosed.
  • the present invention has been made in order to solve the above-described problems, and is capable of creating a reference value used for accurately determining the suitability of the refrigerant amount under any connection conditions.
  • the purpose is to provide a harmony machine.
  • the air conditioner of the present invention controls a refrigerant circuit based on a refrigerant circuit having a condenser, a state detection unit that detects a refrigerant state in the refrigerant circuit, and a refrigerant state detected in the state detection unit. And a control device having a function of executing a refrigerant amount determination mode for controlling the operation of the refrigerant circuit when determining the suitability of the refrigerant amount in the refrigerant circuit.
  • the operation control unit that controls the refrigerant circuit based on the operation conditions set in advance sometimes, and the refrigerant state detected by the state detection unit when the refrigerant amount determination mode is executed, is related to the liquidus temperature of the condenser
  • the storage unit storing the reference value is compared with the reference value stored in the storage unit and the index related to the liquid phase temperature calculated in the index calculation unit in the second and subsequent refrigerant amount determination modes.
  • a refrigerant amount determination unit that determines whether or not the refrigerant amount of the refrigerant is decreasing, and the reference setting unit includes an index determination unit that determines whether an index related to the liquidus temperature is equal to or higher than a set threshold value, and an operating condition
  • the index determination unit determines that the index related to the liquid phase temperature is less than the set threshold value during operation by the refrigerant amount determination
  • the refrigerant amount is determined so that the suction superheat degree is increased until the index related to the liquid phase temperature becomes larger than the set threshold value.
  • the condition change unit that changes the operating conditions of the mode, and if the index related to the liquid phase temperature is determined to be greater than or equal to the set threshold during operation according to the operating conditions, the index related to the liquid phase temperature that is greater than or equal to the set threshold is used as the reference value.
  • Memorize in the memory When it is determined that the index related to the liquid phase temperature is equal to or higher than the set threshold after the operating condition is changed, the reference value determination is performed to store the index related to the liquid phase temperature in the changed operating condition as a reference value in the storage unit. Part.
  • the reference value differs depending on whether the index related to the liquid phase temperature is equal to or higher than the set threshold value and the index related to the liquid phase temperature is less than the set threshold value. Therefore, it is possible to create a reference value used when accurately determining whether or not the refrigerant amount is appropriate under any connection condition.
  • coolant amount determination mode in the air conditioner of FIG. 2 is a flowchart showing an example of setting of a reference value in a first refrigerant amount determination mode in the air conditioner of FIG. It is a refrigerant circuit figure which shows Embodiment 2 of the indoor unit of the air conditioner of this invention. It is a refrigerant circuit figure which shows Embodiment 3 of the indoor unit of the air conditioner of this invention.
  • FIG. 1 is a refrigerant circuit diagram showing Embodiment 1 of an air conditioner of the present invention.
  • the air conditioner 1 of FIG. 1 is an apparatus used for indoor cooling operation and heating operation by performing, for example, a vapor compression refrigeration cycle operation.
  • the air conditioner 1 includes an outdoor unit 10, an indoor unit 20, and connection pipes 2 and 3 that connect the outdoor unit 10 and the indoor unit 20.
  • the outdoor unit 10 and the indoor unit 20 are connected to the connection pipes 2 and 3 respectively.
  • the refrigerant circuit 1 ⁇ / b> A connected by is configured.
  • refrigerant used in the air conditioner 1 examples include HFC refrigerants such as R410A, R407C, and R404A, HCFC refrigerants such as R22 and R134a, or natural refrigerants such as hydrocarbon and helium.
  • the outdoor unit 10 includes a compressor 11, a flow path switching device 12, an outdoor heat exchanger 13, an outdoor blower 14, a first throttle device 15, a receiver 16, and a second throttle device 17.
  • the compressor 11 compresses and discharges the refrigerant, and includes, for example, a positive displacement compressor whose operating capacity is variably driven by a motor (not shown) controlled by an inverter.
  • a motor not shown
  • two or more compressors 11 are connected in parallel depending on the number of connected indoor units 20 or the like. May be.
  • the flow path switching device 12 is composed of, for example, a four-way valve, and switches the direction of refrigerant flow in the refrigerant circuit 1A. During the cooling operation, the flow path switching device 12 connects the discharge side of the compressor 11 and the outdoor heat exchanger 13, and connects the suction side of the compressor 11 and the indoor heat exchanger 21. On the other hand, during the cooling operation, the flow path switching device 12 connects the discharge side of the compressor 11 and the indoor heat exchanger 21, and connects the suction side of the compressor and the outdoor heat exchanger 13.
  • the outdoor heat exchanger 13 is, for example, a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the outdoor heat exchanger 13 functions as a refrigerant condenser during the cooling operation, and functions as a refrigerant evaporator during the heating operation.
  • One of the outdoor heat exchangers 13 is connected to the flow path switching device 12 and the other is connected to the connection pipe 2.
  • the outdoor heat exchanger 13 is illustrated as being divided into a plurality of heat exchangers 13A and 13B, but may be composed of a single heat exchanger.
  • the outdoor heat exchanger 13 that blows outside air is provided in the outdoor heat exchanger 13, and heat is exchanged between the outdoor air and the refrigerant flowing through the outdoor heat exchanger 13.
  • the outdoor blower 14 can change the flow rate of the air supplied to the outdoor heat exchanger 13, and includes a fan such as a propeller fan and a motor that drives the fan.
  • the outdoor heat exchanger 13 has illustrated about the case where it is the fin tube type heat exchanger used as the heat absorption object of the condensation heat
  • the indoor air blower 22 is a multi-tube heat exchanger or It consists of a plate heat exchanger, and the heat absorption target of the refrigerant condensation heat may be water, a heat medium, brine, or the like, and the heat absorption target supply device may be a pump or the like.
  • the first expansion device 15 is composed of, for example, an electronic expansion valve, and decompresses and expands the high-temperature and high-pressure liquid condensed by the condenser to form a low-temperature and low-pressure refrigerant. When the first expansion device 15 receives the first pressure reduction and expands, the liquid state is changed.
  • the receiver 16 stores the surplus refrigerant amount, is provided on the downstream side of the first expansion device 15, and is connected to the indoor unit 20 via the connection pipe 3. Note that, since there is a difference in the amount of refrigerant required between the cooling operation and the heating operation, surplus refrigerant generated in the normal operation is stored in the receiver 16. Moreover, since the excess refrigerant
  • the second expansion device 17 performs decompression of the refrigerant flowing in the refrigerant circuit 1 ⁇ / b> A or adjustment of the flow rate of the refrigerant.
  • One of the second expansion devices 17 is connected to the indoor heat exchanger 21, and the other is connected to the receiver 16 via the connection pipe 3. It is connected to the.
  • the indoor unit 20 includes an indoor heat exchanger 21 and an indoor blower 22.
  • the indoor heat exchanger 21 is, 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 21 functions as a condenser during the cooling operation, and functions as an evaporator during the heating operation.
  • the indoor heat exchanger 21 is provided with an indoor blower 22 for blowing outside air, and heat is exchanged between the outdoor air and the refrigerant flowing through the indoor heat exchanger 21.
  • the indoor blower 22 can change the flow rate of air supplied to the indoor heat exchanger 21, and includes a fan such as a centrifugal fan or a multiblade fan, and a motor that drives the fan.
  • the indoor heat exchanger 21 has illustrated about the case where the thing which becomes the heat absorption object of the heat of condensation of a refrigerant
  • coolant is a fin tube type heat exchanger
  • the indoor air blower 22 is a multitubular heat exchanger. Or it consists of a plate type heat exchanger, the heat absorption object of the condensation heat
  • coolant may be water, a heat medium, a brine, etc., and the supply apparatus of heat absorption object may be a pump.
  • the air conditioner 1 includes a control device 40 that controls the operation of the refrigerant circuit 1A.
  • the control device 40 performs a normal operation mode in which the cooling operation and the heating operation are performed according to the air conditioning load, and a refrigerant amount determination mode that is an operation mode for determining the refrigerant amount in the refrigerant circuit 1A.
  • the refrigerant flow in each operation mode will be described below.
  • the refrigerant flow path in the flow path switching device 12 is switched so that the outdoor heat exchanger 13 becomes a condenser and the indoor heat exchanger 21 becomes an evaporator.
  • a low-temperature / low-pressure refrigerant is compressed by the compressor 11 and discharged as a high-temperature / high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant passes through the flow path switching device 12 and exchanges heat with the outdoor air blown by the outdoor blower 14 in the outdoor heat exchanger 13 acting as a condenser to dissipate heat to the outdoor air. To be cooled.
  • the refrigerant is depressurized by the first expansion device 15 disposed at the outlet of the outdoor heat exchanger 13, and becomes a refrigerant in a gas-liquid two-phase state of medium temperature / medium pressure.
  • the medium-temperature / medium-pressure refrigerant flows into the receiver 16, is depressurized by the second expansion device 17, becomes a low-temperature / low-pressure refrigerant, and flows from the outdoor unit 10 into the indoor unit 20 through the connection pipe 3.
  • the refrigerant that has flowed into the indoor unit 20 exchanges heat with the indoor air blown by the indoor blower 22 in the indoor heat exchanger 21 that operates as an evaporator, and removes heat from the indoor air, thereby cooling the room.
  • the refrigerant flowing out of the indoor unit 20 flows into the outdoor unit 10 again, passes through the flow path switching device 12, becomes a low-temperature / low-pressure refrigerant, and is sucked into the compressor 11.
  • the refrigerant flow path in the flow path switching device 12 is switched so that the outdoor heat exchanger 13 becomes an evaporator and the indoor heat exchanger 21 becomes a condenser.
  • the refrigerant discharged from the compressor 11 flows to the indoor unit 20 through the flow path switching device 12, and the indoor heat exchanger 21 heats the indoor air by radiating heat to the indoor air.
  • the refrigerant that has flowed out of the indoor heat exchanger 21 flows into the outdoor unit 10 through the connection pipe 3, is reduced to an intermediate pressure in the second expansion device 17, and is stored in the receiver 16.
  • the refrigerant flowing out from the receiver 16 is decompressed to a low pressure by the first expansion device 15 and flows into the outdoor heat exchanger 13.
  • the refrigerant exchanges heat with outdoor air, and then becomes a low-temperature / low-pressure refrigerant and is sucked into the compressor 11.
  • the refrigerant amount determination mode is an operation mode in which refrigerant including surplus refrigerant is collected on the high pressure side of the refrigerant circuit 1A.
  • control may be performed so that the refrigerant flows through a cooling flow path in which the outdoor heat exchanger 13 becomes a condenser, or a heating flow path in which the indoor heat exchanger 21 becomes a condenser.
  • the refrigerant may be controlled so as to flow.
  • the case where the refrigerant flows in the refrigerant circuit 1A in the cooling flow path in which the outdoor heat exchanger 13 is a condenser will be exemplified.
  • the control device 40 controls so that the refrigerant amount sucked or discharged in the compressor 11 is stabilized and the refrigerant amount in the outdoor heat exchanger 13 is made constant. Specifically, the control device 40 controls the rotation speed of the compressor 11 so as to be constant at a predetermined value, and sets the suction superheat degree SHs at the suction position of the compressor 11 so as to be constant at a predetermined value. One diaphragm device 15 is controlled. At this time, the second expansion device 17 is fully opened or substantially fully opened. Thereby, the refrigerant
  • the control device 40 controls the operation of the refrigerant circuit 1A based on the information detected by the state detection unit 30. That is, the control device 40 includes the compressor 11, the flow path switching device 12, and the first throttling device that are components of the refrigerant circuit 1A so that the state quantity detected by the state detection unit 30 falls within the desired control target range. 15, the 2nd aperture device 17, the outdoor air blower 14, the indoor air blower 22, etc. are controlled.
  • the state detector 30 detects the state of the refrigerant in the refrigerant circuit 1A.
  • the state detection unit 30 is provided on the discharge side of the compressor 11, and includes a discharge sensor 31 that detects the discharge temperature and discharge pressure of the refrigerant discharged from the compressor 11, and the outdoor air suction of the outdoor unit 10.
  • An outdoor temperature sensor 32 that detects the outdoor temperature of the outdoor air
  • a condensation temperature sensor 33 that detects the condensation temperature of the outdoor heat exchanger 13 in the heating channel, and the outdoor heat exchanger 13 in the heating channel.
  • a liquid-side temperature sensor 34 that detects the temperature of the liquid refrigerant.
  • the state detection unit 30 includes an inlet temperature sensor 35 that detects the evaporator inlet temperature of the refrigerant flowing into the indoor heat exchanger 21 in the heating channel, and an evaporation temperature sensor 36 that detects the evaporation temperature in the indoor heat exchanger 21.
  • a suction sensor 39 that detects a suction temperature and a suction pressure of the refrigerant sucked into the compressor 11.
  • FIG. 2 is a block diagram showing an example of a control device in the air conditioner of FIG.
  • the configuration of the control device 40 shown in FIG. 2 is constructed by executing a program on hardware such as a microcomputer.
  • 2 illustrates the case where the control device 40 is provided on the outdoor unit 10 side, the control device 40 may be provided on the indoor unit 20 side, or the outdoor unit 10 and the indoor unit 20 such as a centralized controller. It may be provided as a separate body.
  • 2 includes an operation control unit 41, an index calculation unit 42, a refrigerant amount determination unit 43, a storage unit 44, and a reference setting unit 45.
  • the operation control unit 41 controls the refrigerant circuit 1A based on preset operation conditions in the refrigerant amount determination mode.
  • a set suction superheat degree SHsref is set as a preset operation condition.
  • the operation control unit 41 controls the refrigerant circuit 1A so that the suction superheat degree SHs at the refrigerant suction position in the compressor 11 becomes the set suction superheat degree SHsref.
  • the operation control unit 41 controls the rotation speed of the compressor 11 to be constant at a predetermined value, and the suction superheat degree SHs at the suction position of the compressor 11 is constant at the set suction superheat degree SHsref.
  • the first diaphragm device 15 is controlled so that
  • the refrigerant circuit 1A It is desirable to control the refrigerant circuit 1A so that the set suction superheat degree SHsref is about 10 [K]. This is because when the suction superheat degree SHs increases, the low-pressure side refrigerant moves to the high-pressure side, and the supercooling degree SC in the outdoor heat exchanger 13 increases.
  • the air volume of the outdoor blower 14 is desirably controlled so that the difference between the outside air temperature and the condensation temperature is constant.
  • the operation control unit 41 is discharged from the compressor 11 to the operation control unit 41 in order to prevent the occurrence of problems relating to the safety of the entire apparatus due to an excessive increase in the high-pressure side pressure of the refrigerant circulating in the refrigerant circuit 1A.
  • the set pressure value (discharge temperature limit value or high pressure limit pressure value) of the refrigerant is set. And when the discharge temperature of the refrigerant
  • the index calculation unit 42 determines the liquid phase temperature of the outdoor heat exchanger 13 or the indoor heat exchanger 21 that is a condenser from the state of the refrigerant detected by the state detection unit 30 when the refrigerant amount determination mode is executed. It calculates the index related to In addition, it illustrates about the case where the outdoor heat exchanger 13 is a condenser.
  • FIG. 3 is a graph showing the state of the outdoor heat exchanger in the refrigerant amount determination mode in the air conditioner of FIG.
  • the index calculation unit 42 calculates the liquid phase temperature efficiency as an index indicating the state of the liquid phase using the following formula (1).
  • dTc represents the condensation temperature [° C.] ⁇ Outside air temperature [° C.].
  • the index calculation unit 42 calculates the liquid temperature efficiency as an index related to the liquid phase temperature using the condensation temperature, the condenser outlet temperature, and the outside air temperature detected by the state detection unit 30.
  • the index calculation unit 42 calculates the suction superheat degree SHs at the suction position of the compressor 11 and the discharge superheat degree SHd at the discharge position.
  • Various known methods can be used to calculate the suction superheat degree SHs and the discharge superheat degree SHd.
  • the index calculation unit 42 subtracts the suction pressure saturation temperature corresponding to the discharge pressure from the refrigerant suction temperature detected by the suction sensor 39 of the compressor 11 to calculate the suction superheat degree SHs.
  • the index calculation unit 42 subtracts the discharge pressure saturation temperature corresponding to the discharge pressure from the refrigerant discharge temperature detected by the discharge sensor 31 to calculate the discharge superheat degree SHd. Therefore, the operation control unit 41 controls the first expansion device 15 so that the suction superheat degree SHs calculated by the index calculation unit 42 becomes constant at the set suction superheat degree SHsref.
  • the refrigerant amount determination unit 43 compares the index related to the liquid phase temperature calculated by the index calculation unit 42 with the reference value RV stored in the storage unit 44, and generates a refrigerant circuit. It is determined whether or not the amount of refrigerant in 1A is decreasing.
  • the index related to the liquid phase temperature is, for example, the liquid temperature efficiency calculated by the above equation (1), and the refrigerant amount determination unit 43 is the liquid temperature after a predetermined time has elapsed since the operation in the refrigerant amount determination mode was started. The efficiency is compared with the reference value RV, and it is determined whether or not the refrigerant amount has decreased compared to the first refrigerant amount determination mode.
  • the reference setting unit 45 sets the index related to the liquid phase temperature calculated by the index calculation unit 42 as the reference value RV in the first refrigerant amount determination mode.
  • the reference value RV set in the reference setting unit 45 is stored in the storage unit 44.
  • the reference setting unit 45 sets a different reference value RV according to the state of the refrigerant circuit 1A in the first refrigerant amount determination mode, and includes an index determination unit 45a, a condition change unit 45b, and a reference value.
  • a determination unit 45c is provided.
  • the index determination unit 45a determines whether an index related to the liquidus temperature is equal to or higher than a set threshold Aref.
  • the setting threshold Aref is set to a value between 0.3 and 0.9.
  • the setting threshold value Aref is more preferably a value having a liquid temperature efficiency of 0.5 or more.
  • the liquid temperature efficiency is equal to or higher than the set threshold Aref, it means that the refrigerant is in a stable state in the refrigerant amount determination mode.
  • the liquid temperature efficiency is less than the set threshold Aref (or 0), in the refrigerant amount determination mode. It means that the refrigerant is in an unstable state.
  • the condition changing unit 45b increases the suction superheat degree SHs until the index related to the liquid phase temperature becomes equal to or higher than the set threshold Aref.
  • the operation condition in the operation control unit 41 is changed. Specifically, the condition changing unit 45b changes the operating condition so that the set suction superheat degree SHsref, which is a control target value, is increased by a predetermined amount. Then, the operation control unit 41 performs control to reduce the opening degree of the first expansion device 15 so that the intake superheat degree SHs becomes the changed set intake superheat degree SHsref. Then, the condition changing unit 45b changes the operating condition until the index determining unit 45a determines that the liquid phase temperature efficiency is equal to or higher than the set threshold value Aref.
  • connection pipe length when the connection pipe length is long within the range of the specified connection pipe length (long connection), the volume in the refrigerant circuit 1A is increased by the volume of the connection pipes 2 and 3.
  • the connection pipe length may be long.
  • the refrigerant amount determination mode when the refrigerant amount determination mode is performed in the heating operation, liquid refrigerant accumulates in the volume of the connection pipe on the high pressure side.
  • the degree of supercooling SC in the outdoor heat exchanger 13 becomes difficult to be applied, and the liquidus temperature efficiency becomes less than the set threshold value Aref.
  • the refrigerant on the low pressure side is moved to the high pressure side by changing it higher by a predetermined amount (for example, 3 to 5 [K]).
  • a predetermined amount for example, 3 to 5 [K]
  • the reference value determination unit 45 c determines a different reference value RV depending on whether the index related to the liquid phase temperature is equal to or higher than the set threshold Aref or less than the set threshold Aref, and stores the reference value RV in the storage unit 44. That is, when it is determined that the index related to the liquid phase temperature is equal to or higher than the set threshold value Aref under the preset operating condition, the reference value determining unit 45c sets the index related to the liquid phase temperature equal to or higher than the set threshold value Aref.
  • the reference value RV is stored in the storage unit 44.
  • the refrigerant amount determination unit 43 determines whether or not the index related to the liquid phase temperature is equal to or higher than the reference value RV stored in the storage unit 44, and the liquid phase temperature efficiency. Is less than the reference value RV, it is determined that the refrigerant is decreasing.
  • the reference value determining unit 45c displays the index related to the liquid phase temperature under the changed operating condition.
  • the reference value RV is stored in the storage unit 44.
  • the reference value determination unit 45c stores the changed operating condition in the storage unit 44 together with the reference value RV.
  • the changed operating condition stored in the storage unit 44 is, for example, the reference discharge superheat degree SHdref when the liquid phase temperature efficiency is equal to or higher than the set threshold Aref.
  • the operation control unit 41 stores the discharge superheat degree SHd of the refrigerant discharged from the compressor 11 in the storage unit 44.
  • the refrigerant circuit 1A is controlled so that the reference discharge superheat degree SHdref is obtained.
  • the refrigerant amount determination unit 43 determines that the refrigerant amount has decreased from the reference value RV.
  • the outside air temperature may be corrected for the liquid temperature efficiency.
  • the operation condition preset in the operation control unit 41 is the set suction superheat degree SHsref and the changed operation condition stored in the storage unit 44 is the set discharge superheat degree SHdref is illustrated.
  • the changed set suction superheat degree SHsref in which the index related to the liquid phase temperature becomes equal to or higher than the set threshold value Aref may be stored as the changed operating condition.
  • the reference setting unit 45 has a function of storing that high-pressure protection control has been executed when the operation control unit 41 performs high-pressure protection control in the first refrigerant amount determination mode. That is, when high-pressure protection is activated during operation in the refrigerant amount determination mode, it means that there is not enough refrigerant to be collected on the high-pressure side of the refrigerant circuit 1A in the operation range of the normal operation mode. ing.
  • the refrigerant in a chargeless type air conditioner shipped in a state where a specified amount of refrigerant is filled, when the length of the connection pipes 2 and 3 is within the range of the specified connection pipe length, the refrigerant is usually used in cooling operation.
  • the amount determination mode By performing the amount determination mode, the above-described problems such as high-pressure protection control and increase in discharge temperature do not occur.
  • the refrigerant amount determination mode is performed in the heating flow path in which the indoor heat exchanger 21 is a condenser
  • the outdoor heat exchange is performed when the lengths of the connection pipes 2 and 3 are shorter than the specified connection pipe length range.
  • the high-pressure protection control is performed in order to move the refrigerant to the indoor heat exchanger 21 having a smaller capacity than the condenser 13.
  • the reference setting unit 45 activates the high pressure protection control in order to determine that the refrigerant amount determination unit 43 does not have a shortage of refrigerant due to refrigerant leakage or the like. Is stored in the storage unit 44. Then, in the second and subsequent refrigerant amount determination modes, the refrigerant amount determination unit 43 determines that the refrigerant amount has not decreased as a result that matches the state stored in the storage unit 44 when the high pressure protection control is activated. To do.
  • the refrigerant amount determination mode and the determination operation may not be performed.
  • the indoor environmental temperature is sufficiently low (for example, 10 ° C. or less)
  • the determination may not be performed.
  • the volume of the outdoor heat exchanger 13 and the indoor heat exchanger 21 is significantly different depending on the combination of the outdoor unit 10 and the indoor unit 20, the determination may not be performed.
  • FIG. 4 is a flowchart showing an example of setting of the reference value in the first refrigerant amount determination mode in the air conditioner of FIG. 1, and an operation example at the time of setting the reference value will be described with reference to FIGS. .
  • the refrigerant amount determination mode is first set at the time of stationary or the like (step ST1)
  • the refrigerant circuit 1A is operated so that the refrigerant state circulating in the refrigerant circuit is stabilized in the operation control unit 41.
  • the first throttle device 15 is controlled so that the rotation speed of the compressor 11 is constant, and the suction superheat degree SHs at the suction position of the compressor 11 is constant at the set suction superheat degree SHsref. Is done.
  • step ST2 it is determined whether or not the high pressure protection control by the operation control unit 41 has been activated (step ST2).
  • an index related to the liquid phase temperature (liquid phase temperature efficiency) is stored in the storage unit 44 as the reference value RV for refrigerant leakage determination (step ST3).
  • the high-pressure protection control is not activated (NO in step ST2), it is determined whether or not the index related to the liquidus temperature is equal to or higher than the set threshold Aref after a predetermined time has elapsed since the start of operation. Thereby, it is determined whether or not the state of the refrigerant in each part of the refrigerant circuit 1A is stable (step ST4).
  • step ST4 When the liquid phase temperature efficiency is equal to or higher than the set threshold Aref, it is determined that the state of the refrigerant is stable (YES in step ST4), and an index related to the liquid phase temperature is stored in the storage unit 44 as the reference value RV. (Step ST5).
  • the first expansion device 15 When it is determined that the liquid phase temperature efficiency is less than the set threshold Aref (or 0) and the refrigerant state is not stable after a predetermined time has elapsed from the start of operation (NO in step ST4), the first expansion device 15 The control target is controlled in a direction to reduce the opening degree (step ST6). Specifically, the preset suction superheat degree SHsref, which is a preset operation condition, is changed so as to increase by a predetermined amount, and the suction superheat degree SHs at the suction position becomes the changed set suction superheat degree SHsref. The opening degree of the first expansion device 15 is controlled. Then, the intake gas temperature of the compressor 11 rises and the discharge temperature of the compressor 11 rises.
  • the preset suction superheat degree SHsref which is a preset operation condition
  • step ST7 it is determined whether or not the state of the refrigerant in each part of the refrigerant circuit 1A is stable. Even after the control of the first expansion device 15 is performed, the liquidus temperature efficiency remains below the set threshold Aref (or 0) and it is determined that the refrigerant state is not stable (NO in step ST4) ), It is determined whether or not the discharge temperature of the compressor 11 is within an allowable range (step ST8).
  • step ST8 If the discharge temperature is within the allowable range (YES in step ST8), the set suction superheat degree SHsref is changed by a predetermined amount, and the opening degree of the first expansion device 15 is reduced (steps ST6 to ST8). On the other hand, when the discharge temperature exceeds the allowable range (NO in step ST8), the refrigerant amount determination mode ends.
  • step ST7 If the index related to the liquid phase temperature becomes equal to or higher than the set threshold Aref after the control target of the first expansion device 15 is changed (YES in step ST7), it is determined that the refrigerant state is stable, and the index related to the liquid phase temperature efficiency. Is stored in the storage unit 44 as the reference value RV. Further, the changed reference discharge superheat degree SHdref when the refrigerant state is stabilized is stored together with the reference value RV as an operation condition (step ST9).
  • the reference value differs depending on whether the index related to the liquid phase temperature is equal to or higher than the set threshold Aref and the index related to the liquid phase temperature is less than the set threshold Aref. RV is set. For this reason, when setting the reference value RV in consideration of the relationship between the specified enclosed refrigerant amount in the refrigerant circuit 1A, the device connection conditions, and the operating conditions, any length of extension piping within the device specification range is connected. Even if it has been done, it is possible to set a reference value RV used for determining whether or not refrigerant leakage is appropriate.
  • connection state the air conditioner 1 For this reason, no matter what connection state the air conditioner 1 is installed in, the state in which the refrigerant is stable at the time of the initial installation is set as the reference value RV. Therefore, according to the installation structure of the air conditioner 1, it is possible to create the reference value RV that can accurately determine the suitability of refrigerant leakage.
  • the refrigerant amount determination mode it is possible to set the reference value RV for accurately determining the decrease of the refrigerant not only in the case of the cooling channel but also in the case of the heating channel.
  • the suitability determination of the refrigerant amount during the cooling operation is performed, but it does not correspond to the suitability determination of the refrigerant amount during the heating operation.
  • the refrigerant amount determination mode is performed in a state where the extension pipe is short even within the range specified by the equipment in the heating flow path, there is a tendency that high-pressure protection is likely to occur.
  • the air conditioner 1 has the receiver 16 in the refrigerant circuit 1A
  • the excess refrigerant in the liquid reservoir is stored on the high-pressure side in the refrigerant amount determination mode in order to store the reference value RV
  • an abnormally high pressure high pressure Operation may stop due to protection control.
  • the high pressure protection control is activated as the reference value RV, even if the excess refrigerant remains in the receiver 16 without accumulating the refrigerant on the high pressure side, the excess refrigerant in the receiver 16 is removed. Refrigerant leakage can be detected before cutting.
  • the reference value The determination unit 45c stores, in the storage unit 44, the reference discharge superheat degree SHdref when the index related to the liquidus temperature is equal to or higher than the set threshold value Aref as the changed operating condition.
  • FIG. FIG. 5 is a refrigerant circuit diagram showing Embodiment 2 of the air conditioner of the present invention, and the air conditioner 100 will be described with reference to FIG.
  • the air conditioner 100 of FIG. 5 is different from the air conditioner 1 of FIG. 1 in the structure of the receiver 116.
  • the receiver 116 is a heat recovery type intermediate pressure receiver, and has a structure in which a pipe connecting the flow path switching device 12 and the suction side of the compressor 11 passes through the receiver. .
  • the refrigerant flowing from the flow path switching device 12 to the suction side of the compressor 11 is cooled by the refrigerant stored in the receiver 116 and is sucked into the compressor 11.
  • the receiver 116 as in the second embodiment uses a heat recovery type receiver, as in the first embodiment, in the first refrigerant amount determination mode, the index related to the liquid phase temperature is equal to or higher than the set threshold Aref.
  • a different reference value RV is set depending on the case and the case where the index related to the liquidus temperature is less than the set threshold value Aref. For this reason, when setting the reference value RV in consideration of the relationship between the specified enclosed refrigerant amount in the refrigerant circuit 1A, the device connection conditions, and the operating conditions, any length of extension piping within the device specification range is connected. Even if it has been done, it is possible to set a reference value RV used for determining whether or not refrigerant leakage is appropriate.
  • FIG. FIG. 6 is a refrigerant circuit diagram showing Embodiment 3 of the air conditioner of the present invention.
  • the air conditioner 200 will be described with reference to FIG.
  • the part which has the same structure as the air conditioner 1 of FIG. 1 is attached
  • the air conditioner 200 of FIG. 6 is different from the air conditioner 1 of FIG. 1 in that only the connection position of the receiver 216 and one throttling device 215 are provided.
  • the index related to the liquid phase temperature is greater than or equal to the set threshold Aref and the index related to the liquid phase temperature is less than the set threshold Aref.
  • a different reference value RV is set depending on. For this reason, when setting the reference value RV in consideration of the relationship between the specified enclosed refrigerant amount in the refrigerant circuit 1A, the device connection conditions, and the operating conditions, any length of extension piping within the device specification range is connected. Even if it has been done, it is possible to set a reference value RV used for determining whether or not refrigerant leakage is appropriate.
  • the embodiment of the present invention is not limited to the above embodiment.
  • the case where one outdoor unit 10 and one indoor unit 20 are provided is illustrated, but a plurality of outdoor units 10 and indoor units 20 may be provided.
  • the case where the index related to the liquid phase temperature is the liquid temperature efficiency is illustrated.
  • any index related to the liquid phase temperature may be used.
  • the entire transmission of the outdoor heat exchanger 13 may be performed.
  • the phase area ratio AL% indicating the heat transfer area of the liquid phase relative to the heat area may be used, or the degree of supercooling SC of the outdoor heat exchanger 13 may be used.

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

Abstract

L'invention concerne un climatiseur qui comprend : une unité de réglage de référence qui règle, en tant que valeur de référence, un indice se rapportant à la température de phase liquide à un moment où un mode de détermination de quantité de fluide frigorigène est réalisé en premier ; et une unité de détermination de quantité de fluide frigorigène qui détermine si la quantité d'un fluide frigorigène dans un circuit de fluide frigorigène est réduite ou non en comparant, l'un avec l'autre, la valeur de référence et l'indice se rapportant à la température de phase liquide aux moments où le mode de détermination de quantité de fluide frigorigène est réalisé une seconde fois ou ultérieurement. L'unité de réglage de référence comprend une unité de détermination d'indice qui détermine si un indice se rapportant à la température de phase liquide est égal ou supérieur à une valeur seuil définie et, dans les cas où il est déterminé que l'indice se rapportant à la température de phase liquide est égal ou supérieur à la valeur seuil définie par l'unité de détermination d'indice, l'indice se rapportant à la température de phase liquide égal ou supérieur à la valeur seuil définie est stocké en tant que valeur de référence dans une unité de stockage. Tandis que, dans les cas où il est déterminé que l'indice se rapportant à la température de phase liquide est inférieur à la valeur seuil définie, un indice se rapportant à la température de phase liquide dans des conditions de fonctionnement après un changement est stocké en tant que valeur de référence dans l'unité de stockage.
PCT/JP2015/068140 2015-06-24 2015-06-24 Climatiseur WO2016207992A1 (fr)

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JP2017524330A JP6410935B2 (ja) 2015-06-24 2015-06-24 空気調和機

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WO2019065635A1 (fr) * 2017-09-29 2019-04-04 ダイキン工業株式会社 Procédé d'estimation de quantité de fluide frigorigène et climatiseur
JP2020128826A (ja) * 2019-02-07 2020-08-27 ホシザキ株式会社 冷却貯蔵庫

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JP2009079842A (ja) * 2007-09-26 2009-04-16 Mitsubishi Electric Corp 冷凍サイクル装置およびその制御方法
JP2010007995A (ja) * 2008-06-27 2010-01-14 Daikin Ind Ltd 空気調和装置の冷媒量判定方法および空気調和装置
JP2012132639A (ja) * 2010-12-22 2012-07-12 Mitsubishi Electric Corp 冷凍装置
JP2014163593A (ja) * 2013-02-26 2014-09-08 Gunma Prefecture 冷凍装置の冷媒漏れ検出方法及び冷媒漏洩検知システム

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WO2006090451A1 (fr) * 2005-02-24 2006-08-31 Mitsubishi Denki Kabushiki Kaisha Systeme de climatisation
JP2006313057A (ja) * 2005-04-07 2006-11-16 Daikin Ind Ltd 空気調和装置の冷媒量判定システム
WO2008035418A1 (fr) * 2006-09-21 2008-03-27 Mitsubishi Electric Corporation SystÈme de rÉFRIGÉration/de climatisation de l'air ayant une fonction de dÉtection de fuite de rÉFRIGÉrant, rÉFRIGÉrateur/climatiseur d'air et procÉDÉ de dÉtection d'une fuite de rÉFRIGÉrant
JP2008164250A (ja) * 2006-12-28 2008-07-17 Daikin Ind Ltd 空気調和装置
JP2009079842A (ja) * 2007-09-26 2009-04-16 Mitsubishi Electric Corp 冷凍サイクル装置およびその制御方法
JP2010007995A (ja) * 2008-06-27 2010-01-14 Daikin Ind Ltd 空気調和装置の冷媒量判定方法および空気調和装置
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JP2014163593A (ja) * 2013-02-26 2014-09-08 Gunma Prefecture 冷凍装置の冷媒漏れ検出方法及び冷媒漏洩検知システム

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Publication number Priority date Publication date Assignee Title
WO2019065635A1 (fr) * 2017-09-29 2019-04-04 ダイキン工業株式会社 Procédé d'estimation de quantité de fluide frigorigène et climatiseur
JP2019066164A (ja) * 2017-09-29 2019-04-25 ダイキン工業株式会社 冷媒量推定方法及び空気調和装置
JP2020128826A (ja) * 2019-02-07 2020-08-27 ホシザキ株式会社 冷却貯蔵庫
JP7215919B2 (ja) 2019-02-07 2023-01-31 ホシザキ株式会社 冷却貯蔵庫

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