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WO2025037358A1 - Dispositif à cycle de réfrigération et procédé de commande de fonctionnement de cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération et procédé de commande de fonctionnement de cycle de réfrigération Download PDF

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Publication number
WO2025037358A1
WO2025037358A1 PCT/JP2023/029390 JP2023029390W WO2025037358A1 WO 2025037358 A1 WO2025037358 A1 WO 2025037358A1 JP 2023029390 W JP2023029390 W JP 2023029390W WO 2025037358 A1 WO2025037358 A1 WO 2025037358A1
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WO
WIPO (PCT)
Prior art keywords
heat source
refrigerant
load
control device
refrigeration cycle
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.)
Pending
Application number
PCT/JP2023/029390
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English (en)
Japanese (ja)
Inventor
彰 江川
侑哉 森下
正紘 伊藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2025540529A priority Critical patent/JPWO2025037358A1/ja
Priority to PCT/JP2023/029390 priority patent/WO2025037358A1/fr
Publication of WO2025037358A1 publication Critical patent/WO2025037358A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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

  • This technology relates to a refrigeration cycle device and a refrigeration cycle operation control method.
  • it relates to the operation control of a refrigeration cycle device that has multiple heat source units in the same refrigerant circuit.
  • Refrigeration cycle devices generally use a refrigerant circuit having component devices such as a load heat exchanger, a compressor, a heat source heat exchanger, and a throttling device to cool or cool a thermal load (hereinafter referred to as the load).
  • a multi-type air conditioner which is a refrigeration cycle device that performs air conditioning by forming a refrigerant circuit by connecting multiple indoor units, which are load units that heat or cool the load, and multiple outdoor units, which are heat source units that supply capacity to the indoor units, with refrigerant piping (see, for example, Patent Document 1).
  • operation control may be performed by stopping some of the heat source units, such as single-lung operation. In this case, the heat source unit that is stopped will close its valve to prevent refrigerant from flowing in.
  • gas refrigerant flows into the heat exchanger of the stopped heat source unit and dissipates heat, causing stagnation and the accumulation of liquid refrigerant (hereinafter referred to as liquid refrigerant).
  • liquid refrigerant liquid refrigerant
  • the objective is to obtain a refrigeration cycle device and a refrigeration cycle operation control method that performs operation control to eliminate refrigerant shortages.
  • the disclosed refrigeration cycle device includes a refrigerant circuit configured by piping multiple heat source units each having a compressor and a condenser to one or more load units each having a load throttling device and an evaporator, and a control device that operates a stopped heat source unit when there is a shortage of refrigerant used for operation when any of the multiple heat source units is stopped.
  • the disclosed refrigeration cycle operation control method is a refrigeration cycle operation control method for controlling the operation of a refrigeration cycle device that configures a refrigerant circuit that circulates refrigerant by connecting multiple heat source units having compressors and condensers to one or multiple load units through piping, and includes a step of determining whether or not there is a shortage of refrigerant used for operation when any of the multiple heat source units is stopped, and a step of operating the stopped heat source unit when it is determined that there is a shortage of refrigerant.
  • the control device when multiple heat source units are connected to a refrigerant circuit by piping, if a refrigerant shortage occurs during operation of a stopped heat source unit, the control device operates the stopped heat source unit.
  • the stopped heat source unit By operating the stopped heat source unit, the refrigerant accumulated in the stopped heat source unit can be used for operation, correcting the uneven distribution of refrigerant and resolving the refrigerant shortage. This makes it possible to prevent the load unit from being insufficiently cooled.
  • FIG. 1 is a diagram showing a configuration of an air conditioning device 1 according to a first embodiment.
  • 1 is a diagram showing a configuration of a load machine 200 according to a first embodiment.
  • FIG. 1 is a diagram showing a configuration of a heat source device 100 according to a first embodiment.
  • FIG. 4 is a diagram illustrating a process flow for resolving a refrigerant shortage according to the first embodiment.
  • FIG. 1 is a diagram showing the configuration of an air conditioner 1 according to the first embodiment.
  • the air conditioner 1 is a device that adjusts the air in an indoor space that is a thermal load, and performs heating and cooling.
  • the air conditioner 1 will be described as an example of a refrigeration cycle device.
  • the air conditioner 1 connects a plurality of heat source units 100 and a plurality of load units 200 to be in the same system by a liquid refrigerant piping 300 and a gas refrigerant piping 400.
  • the equipment in the heat source unit 100 and the equipment in the load unit 200 are connected by piping to form a refrigerant circuit in which the refrigerant circulates.
  • heat source unit 100A and heat source unit 100B heat source unit 100A and heat source unit 100B
  • load unit 200A and load unit 200B load unit 200A and load unit 200B
  • the air conditioner 1 may have three or more heat source units 100 and load units 200.
  • FIG 2 is a diagram showing the configuration of the load machine 200 according to embodiment 1.
  • the load machine 200 is an indoor unit that is installed indoors and supplies conditioned air.
  • the load machine 200 according to embodiment 1 has a load heat exchanger 210 and a load throttling device 220 as devices that constitute a refrigerant circuit.
  • the load machine 200 also has a load fan 230.
  • the load heat exchanger 210 exchanges heat between the refrigerant and the air to be conditioned.
  • the load heat exchanger 210 functions as a condenser during heating operation, condensing and liquefying the refrigerant.
  • the load heat exchanger 210 also functions as an evaporator during cooling operation, evaporating and vaporizing the refrigerant.
  • the load throttling device 220 is a device having a pressure reducing valve or an expansion valve that reduces the pressure and expands the refrigerant.
  • the subcooling throttling device 170 has an electronic expansion valve that opens and closes at a degree of opening based on instructions from the control device 500 described below.
  • the load fan 230 sends the air to be conditioned to the load heat exchanger 210, promoting heat exchange between the air and the refrigerant.
  • FIG. 3 is a diagram showing the configuration of the heat source unit 100 according to the first embodiment.
  • the heat source unit 100 is installed, for example, outside a room that is a space to be air-conditioned, and serves as an outdoor unit that supplies the capacity (horsepower) for air-conditioning the indoor space to the load unit 200.
  • the heat source unit 100 has, for example, a compressor 110, a flow switching device 120, a heat source heat exchanger 130, a heat source throttling device 140, an accumulator 150, a bypass piping 160, a supercooling throttling device 170, and a supercooling heat exchanger 180.
  • the heat source unit 100 is equipped with a heat source fan 190 that blows air to the heat source heat exchanger 130.
  • the compressor 110 draws in the refrigerant, compresses it, and discharges it in a high-temperature, high-pressure state.
  • the compressor 110 in the first embodiment is, for example, configured as an inverter compressor whose capacity can be controlled.
  • the compressor 110 is driven at a drive frequency F based on instructions from the control device 500, which will be described later.
  • the flow path switching device 120 is a device that switches between the refrigerant flow path in cooling operation and the refrigerant flow path in heating operation.
  • the flow path switching device 120 has, for example, a four-way valve.
  • the heat source heat exchanger 130 exchanges heat between the outdoor air and the refrigerant.
  • the heat source heat exchanger 130 is, for example, a fin-and-tube type heat exchanger having multiple heat transfer tubes and multiple fins.
  • the heat source heat exchanger 130 functions as a condenser during cooling operation and as an evaporator during heating operation.
  • the heat source fan 190 supplies outdoor air to the heat source heat exchanger 130.
  • the outdoor air becomes the heat source fluid that is the subject of heat exchange with the refrigerant in the heat source heat exchanger 130.
  • the heat source fluid may be water or the like.
  • the heat source throttling device 140 is a device having a pressure reducing valve or expansion valve that reduces the pressure of the refrigerant and expands it.
  • the heat source throttling device 140 has an electronic expansion valve that opens and closes the valve at an opening degree based on instructions from the control device 500, which will be described later.
  • the heat source throttling device 140 has the valve fully open during cooling operation.
  • the heat source throttling device 140 closes the valve when the heat source unit 100 is stopped to prevent the inflow of the refrigerant.
  • the accumulator 150 is provided in the suction section, which is the suction side of the compressor 110.
  • the accumulator 150 stores excess refrigerant in the refrigerant circulation circuit.
  • the amount of refrigerant required for air conditioning differs between heating operation and cooling operation.
  • the accumulator 150 stores excess refrigerant that occurs due to differences in operation.
  • the accumulator 150 stores excess refrigerant that occurs transiently when the operation changes.
  • the accumulator 150 stores excess refrigerant, but this is not limited to this.
  • a receiver that stores high-pressure liquid refrigerant may be installed.
  • the bypass pipe 160 is a pipe that allows some of the high-temperature and high-pressure refrigerant to bypass and flow into the suction section of the compressor 110.
  • the bypass pipe 160 is provided with a supercooling throttle device 170.
  • the supercooling throttle device 170 is a device that has a pressure reducing valve or an expansion valve that reduces the pressure and expands the refrigerant based on instructions from the control device 500, which will be described later.
  • the supercooling throttle device 170 has an electronic expansion valve that opens and closes the valve at an opening degree based on instructions from the control device 500, which will be described later.
  • the supercooling heat exchanger 180 exchanges heat between the medium-temperature and high-pressure refrigerant flowing between the heat source heat exchanger 130 and the heat source throttle device 140 and the low-temperature and low-pressure refrigerant flowing through the bypass pipe 160 that has flowed out of the supercooling throttle device 170.
  • the control device 500 which is a refrigeration cycle operation control device, controls the equipment of the air conditioning device 1 based on the operation content performed by the air conditioning device 1.
  • the control device 500 has a control processing device 501, a storage device 502, and a timing device 503.
  • the control processing device 501 is a device that performs processing such as calculations and judgments based on physical quantity data such as temperature sent from various sensors installed in the air conditioning device 1, and controls the equipment of the air conditioning device 1 such as the compressor 110. Therefore, in embodiment 1, the processing described as being performed by the control device 500 is actually processed by the control processing device 501. In embodiment 1, the control processing device 501 performs processing particularly related to correcting a shortage of refrigerant used for operation.
  • the storage device 502 is a device that stores data required for the control processing device 501 to perform processing.
  • the timing device 503 is a device that has a timer or the like that measures time when used for judgments by the control processing device 501. In the first embodiment, the timing device 503 particularly measures the time related to the non-cooling detection timer, which is the time during which the load is not cooled due to a shortage of refrigerant. There are no particular limitations on the location where the control device 500 is installed.
  • control processing device 501 of the control device 500 is usually configured with a device that performs control and arithmetic processing, such as a microcomputer centered on a CPU (Central Processing Unit).
  • the control processing device 501 programs the processing procedures performed by each part in advance and executes the program to realize the processing of each part.
  • the storage device 502 has the program data.
  • the realization of the processing is not limited to the execution of the program, and each part may be configured with a dedicated device separately.
  • the storage device 502 also has a volatile storage device (not shown) such as a random access memory (RAM) that can temporarily store data, and a hard disk, a non-volatile auxiliary storage device (not shown) such as a flash memory that can store data for the long term.
  • RAM random access memory
  • flash memory non-volatile auxiliary storage device
  • the air conditioning device 1 has various sensors as detection devices that detect physical quantities for the control device 500 to perform control.
  • the compressor discharge temperature sensor 510 installed in the heat source device 100 is a sensor that detects the temperature of the refrigerant discharged by the compressor 110.
  • the high-pressure pressure sensor 520 is a sensor that detects the pressure of the refrigerant discharged by the compressor 110.
  • the discharge superheat degree TdSH can be obtained based on the temperature detected by the compressor discharge temperature sensor 510 and the pressure detected by the high-pressure pressure sensor 520.
  • the two heat source heat exchanger temperature sensors 530 each detect the temperature of the refrigerant flowing into or out of the heat source heat exchanger 130.
  • the subcooling degree SCO during cooling operation can be obtained based on the refrigerant outflow temperature of the refrigerant flowing out of the heat source heat exchanger 130 detected by the heat source heat exchanger temperature sensor 530.
  • the two load heat exchanger temperature sensors 540 installed in the load device 200 each detect the temperature of the refrigerant flowing into or out of the load heat exchanger 210.
  • each device of the air conditioning device 1 will be described based on the flow of the refrigerant.
  • the control device 500 adjusts the supercooling throttling device 170 to pass a portion of the refrigerant passing through the main refrigerant circuit through the bypass piping 160.
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 110 passes through the flow switching device 120 and flows into the heat source heat exchanger 130.
  • the refrigerant then passes through the heat source heat exchanger 130 and exchanges heat with the outdoor air supplied by the heat source fan 190, causing it to condense and become liquefied.
  • the liquefied refrigerant passes through the load throttling device 220.
  • the refrigerant is depressurized as it passes through the load throttling device 220, and becomes a two-phase gas-liquid state.
  • the refrigerant that has been depressurized by the load throttling device 220 and becomes a two-phase gas-liquid state passes through the load heat exchanger 210. Then, in the load heat exchanger 210, for example, the refrigerant evaporates by exchanging heat with the air in the space to be air-conditioned, and the gasified refrigerant passes through the flow switching device 120 and is sucked back into the compressor 110. In this manner, the refrigerant in the air conditioning device 1 circulates, and air conditioning related to cooling is performed.
  • the control device 500 closes the supercooling throttling device 170.
  • the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 110 passes through the flow path switching device 120 and flows into the load heat exchanger 210. While passing through the load heat exchanger 210, the gas refrigerant condenses and liquefies, for example, by exchanging heat with the air in the space to be air-conditioned.
  • the condensed and liquefied refrigerant passes through the load throttling device 220.
  • the refrigerant is depressurized when passing through the load throttling device 220.
  • the refrigerant that has been depressurized by the load throttling device 220 and has become a gas-liquid two-phase state passes through the supercooling heat exchanger 180 and the heat source heat exchanger 130.
  • the supercooling throttling device 170 is closed, no heat exchange occurs between the refrigerants in the supercooling heat exchanger 180.
  • the refrigerant evaporates by exchanging heat with the outdoor air sent from the heat source fan 190, and the gasified refrigerant passes through the flow path switching device 120 and the accumulator 150 and is sucked back into the compressor 110. In this way, the refrigerant in the air conditioning device 1 circulates and performs air conditioning related to heating.
  • FIG. 4 is a diagram explaining the flow of processing for resolving a refrigerant shortage in embodiment 1.
  • the steps of the refrigerant shortage resolving processing explained in FIG. 4 are performed by the control device 500 (particularly the control processing device 501).
  • the control device 500 determines whether the air conditioning device 1 is performing cooling operation (step S1). If the control device 500 determines that cooling operation is not being performed, it ends the processing.
  • control device 500 determines whether cooling operation is being performed, it determines whether any heat source units 100 are stopped (step S2). When the control device 500 determines that no heat source units 100 are stopped, it returns to step S1 and continues processing.
  • control device 500 determines whether there is a heat source unit 100 that is stopped, it determines whether there is a refrigerant shortage (step S3). If the control device 500 determines that there is no refrigerant shortage, it determines whether an arbitrary set uncooling detection timer reset condition is satisfied (step S4). If the control device 500 determines that the uncooling detection timer reset condition is satisfied, it resets the uncooling detection timer to 0 (step S5). Then, the control device 500 returns to step S1 to continue processing. Furthermore, if the control device 500 determines that the uncooling detection timer reset condition is not satisfied, it stops timing the uncooling detection timer (step S6).
  • control device 500 determines a refrigerant shortage from the degree of subcooling SCO of the refrigerant flowing out of the heat source heat exchanger 130, the drive frequency F of the compressor 110 in the operating heat source unit 100, and the discharge superheat TdSH of the refrigerant discharged by the compressor 110.
  • the control device 500 calculates the discharge superheat TdSH, which is the difference between the discharge temperature detected by the compressor discharge temperature sensor 510 and the saturation temperature Tc converted from the high-pressure pressure detected by the high-pressure pressure sensor 520.
  • the control device 500 also calculates the subcooling degree SCO, which is the difference between the saturation temperature Tc and the refrigerant outflow temperature detected by the heat source heat exchanger temperature sensor 530.
  • the control device 500 determines whether or not there is a refrigerant shortage based on the refrigerant shortage determination conditions.
  • the refrigerant shortage determination conditions are conditions (1) to (3), and when all of (1) to (3) are satisfied, the control device 500 determines that there is a refrigerant shortage.
  • the set values set for each condition are merely examples, and are not limited to these, and any value can be set.
  • the drive frequency F is smaller than the target drive frequency Ft required to obtain the target capacity for the current load machine (for example, F ⁇ Ft).
  • the non-coldness detection timer reset condition in step S4 is, for example, the conditions shown in (4) to (6).
  • the control device 500 determines that the non-coldness detection timer reset condition is satisfied if any of the conditions shown in (4) to (6) is satisfied.
  • the degree of supercooling SCO is greater than the set degree of supercooling SCOt by 2 [K] or more (for example, SCO>SCOt+2 [K]).
  • the drive frequency F is higher than 1.2 times the target drive frequency Ft (for example, the drive frequency F is higher than 120% of the target drive frequency Ft. F>1.2Ft)
  • the discharge superheat degree TdSH is smaller than the set discharge superheat degree TdSHt by 10 [K] or more (for example, TdSH ⁇ TdSHt-10 [K]).
  • step S7 the timing device 503 starts timing the non-cooling detection timer.
  • the control device 500 determines, for example, whether the time counted by the non-cooling detection timer has counted to a set time of 300 seconds or more (step S8). If the control device 500 determines that the time counted by the non-cooling detection timer is not 300 seconds or more, it returns to step S1 and continues processing.
  • the set time is set to 300 seconds, but this is not limited to this and can be set arbitrarily.
  • the control device 500 determines whether the load Ht in the load unit 200 is equal to or greater than the load setting value A (step S9).
  • the load Ht is the total load.
  • the control device 500 determines that the load Ht is equal to or greater than the load setting value A based on the comparison, it starts the operation of the stopped heat source unit 100 (step S10). Then, the control device 500 controls the opening degree of the load throttling device 220 of the load unit 200 to be equal to or greater than the maximum opening degree that can be achieved in normal operation.
  • the opening degree of the load throttling device 220 is not controlled to be larger than necessary, but by starting the operation of the stopped heat source unit 100, the total drive frequency F of the multiple compressors 110 increases, the amount of refrigerant circulating in the refrigerant circuit increases, and the pressure of the suction section, which is the suction side of the compressor 110, decreases. Therefore, in order to suppress the pressure drop in the suction section, the control device 500 temporarily expands the opening of the load throttling device 220 to an opening larger than the maximum opening that can be expanded in normal operation based on performance. The control device 500 also controls the heat source throttling device 140 to be fully open (step S11). After temporarily expanding the opening of the load throttling device 220, the control device 500 controls the adjustment of the opening of the load throttling device 220 during normal operation.
  • control device 500 determines in step S9 based on the comparison that the load Ht of the load unit 200 is not equal to or greater than the load setting value A, it stops one of the heat source units 100 that is in operation. Then, the control device 500 starts operation of the one heat source unit 100 that is stopped (step S12).
  • the control device 500 determines whether there is one heat source unit 100 in operation (step S13). If the control device 500 determines that there is one heat source unit 100 in operation, it drives the compressor 110 at the minimum drive frequency possible in normal operation. In addition, the control device 500 drives the heat source fan 190 at the maximum drive frequency possible in normal operation (step S14). After driving the compressor 110 at the minimum drive frequency and the heat source fan 190 at the maximum drive frequency, the control device 500 performs control to adjust the drive frequencies of the compressor 110 and the heat source fan 190 during normal operation.
  • step S13 if the control device 500 determines that there is more than one heat source unit 100 in operation, it controls the opening degree of the load throttling device 220 of the load unit 200 to an opening degree equal to or greater than the maximum opening degree possible in normal operation. Furthermore, the control device 500 controls the heat source throttling device 140 to be fully open (step S11). The control device 500 performs the above refrigerant shortage resolution process at regular intervals.
  • the control device 500 determines that there is a shortage of refrigerant to be used for operation when there is a stopped heat source unit 100, it operates the stopped heat source unit 100.
  • the refrigerant that had accumulated in the stopped heat source unit 100 is circulated in the refrigerant circuit and used for operation, correcting the uneven distribution of refrigerant and resolving the refrigerant shortage related to operation. Therefore, it is possible to prevent the load unit 200 from being insufficiently cooled.
  • the control device 500 determines a refrigerant shortage from the degree of subcooling SCO of the refrigerant flowing out of the heat source heat exchanger 130, the drive frequency F of the compressor 110 in the operating heat source unit 100, and the discharge superheat TdSH of the refrigerant discharged by the compressor 110. This allows the control device 500 to accurately determine a refrigerant shortage.
  • the control device 500 determines that the time measured by the non-cooling detection timer measured by the timing device 503 is equal to or greater than the set detection time, it operates the stopped heat source unit 100, thereby making an even more accurate determination.
  • the control device 500 when the load Ht in the load unit 200 is less than the load setting value A, the control device 500 starts one of the heat source units 100 that is stopped and stops one of the heat source units 100 that is in operation. This prevents the combined heat source units from supplying excessive capacity, enabling efficient operation.
  • the control device 500 controls the load throttling device 220 to an opening degree greater than the normal maximum opening degree. This allows the refrigerant that has accumulated in the heat source heat exchanger 130 to be quickly circulated through the refrigerant circuit.
  • the heat source heat exchanger 130 is a heat exchanger that functions as a condenser or an evaporator depending on the refrigerant flow path, but is not limited thereto.
  • the heat source heat exchanger 130 may be a condenser that only performs condensation.
  • the valve that closes the flow path to prevent refrigerant from flowing in when the heat source device 100 is stopped is described as the heat source throttling device 140 whose opening degree can be changed as desired, but this is not limited to this.
  • the heat source heat exchanger 130 is a condenser, it may be an on-off valve.
  • the air conditioner 1 has been described as an example of a refrigeration cycle device, but this is not limiting.
  • the present invention can be applied to other refrigeration cycle devices, such as a refrigeration device (where the load unit 200 is a cooling unit) in which the heat source heat exchanger 130 of the heat source unit 100 serves as a condenser, or a refrigeration device (where the load unit 200 is a refrigeration unit).
  • 1 air conditioning device 100, 100A, 100B heat source device, 110 compressor, 120 flow switching device, 130 heat source heat exchanger, 140 heat source throttling device, 150 accumulator, 160 bypass piping, 170 supercooling throttling device, 180 supercooling heat exchanger, 190 heat source fan, 200, 200A, 200B load device, 210 load heat exchanger, 220 load throttling device, 230 load fan, 300 liquid refrigerant piping, 400 gas refrigerant piping, 500 control device, 501 control processing device, 502 storage device, 503 timing device, 510 compressor discharge temperature sensor, 520 high pressure pressure sensor, 530 heat source heat exchanger temperature sensor, 540 load heat exchanger temperature sensor.

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

Abstract

La présente invention comprend : un circuit de fluide frigorigène configuré en reliant, par l'intermédiaire de tuyaux, une pluralité de sources de chaleur ayant des compresseurs et des condenseurs et une ou une pluralité de charges ayant des dispositifs d'étranglement de charge et des évaporateurs ; et un dispositif de commande configuré de telle sorte que si une pénurie de fluide frigorigène utilisé pour le fonctionnement se produit lorsque, parmi la pluralité de sources de chaleur, il y a une source de chaleur qui s'est arrêtée, le dispositif de commande redémarre la source de chaleur qui s'est arrêtée.
PCT/JP2023/029390 2023-08-14 2023-08-14 Dispositif à cycle de réfrigération et procédé de commande de fonctionnement de cycle de réfrigération Pending WO2025037358A1 (fr)

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JP2025540529A JPWO2025037358A1 (fr) 2023-08-14 2023-08-14
PCT/JP2023/029390 WO2025037358A1 (fr) 2023-08-14 2023-08-14 Dispositif à cycle de réfrigération et procédé de commande de fonctionnement de cycle de réfrigération

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Application Number Priority Date Filing Date Title
PCT/JP2023/029390 WO2025037358A1 (fr) 2023-08-14 2023-08-14 Dispositif à cycle de réfrigération et procédé de commande de fonctionnement de cycle de réfrigération

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04217765A (ja) * 1990-12-18 1992-08-07 Japan Electron Control Syst Co Ltd 空調装置
JP2006194552A (ja) * 2005-01-17 2006-07-27 Matsushita Electric Ind Co Ltd 空気調和機
JP2007315750A (ja) * 2007-08-27 2007-12-06 Sanyo Electric Co Ltd 空気調和装置
JP2013224784A (ja) * 2012-04-20 2013-10-31 Mitsubishi Electric Corp 冷凍サイクル装置
US20150176848A1 (en) * 2013-12-24 2015-06-25 Lg Electronics Inc. Air conditioning system and method of controlling an air conditioning system
JP2021156532A (ja) * 2020-03-27 2021-10-07 株式会社富士通ゼネラル 空気調和機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04217765A (ja) * 1990-12-18 1992-08-07 Japan Electron Control Syst Co Ltd 空調装置
JP2006194552A (ja) * 2005-01-17 2006-07-27 Matsushita Electric Ind Co Ltd 空気調和機
JP2007315750A (ja) * 2007-08-27 2007-12-06 Sanyo Electric Co Ltd 空気調和装置
JP2013224784A (ja) * 2012-04-20 2013-10-31 Mitsubishi Electric Corp 冷凍サイクル装置
US20150176848A1 (en) * 2013-12-24 2015-06-25 Lg Electronics Inc. Air conditioning system and method of controlling an air conditioning system
JP2021156532A (ja) * 2020-03-27 2021-10-07 株式会社富士通ゼネラル 空気調和機

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