WO2017179210A1 - 冷凍装置 - Google Patents

冷凍装置 Download PDF

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Publication number
WO2017179210A1
WO2017179210A1 PCT/JP2016/062177 JP2016062177W WO2017179210A1 WO 2017179210 A1 WO2017179210 A1 WO 2017179210A1 JP 2016062177 W JP2016062177 W JP 2016062177W WO 2017179210 A1 WO2017179210 A1 WO 2017179210A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
temperature
amount
heat source
refrigeration apparatus
Prior art date
Application number
PCT/JP2016/062177
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English (en)
French (fr)
Japanese (ja)
Inventor
佐多　裕士
齊藤　信
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
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2018511869A priority Critical patent/JP6588626B2/ja
Priority to CN201680084454.9A priority patent/CN109073304B/zh
Priority to PCT/JP2016/062177 priority patent/WO2017179210A1/ja
Publication of WO2017179210A1 publication Critical patent/WO2017179210A1/ja

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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
    • 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
    • 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 a refrigeration apparatus for determining the amount of refrigerant in a refrigerant circuit.
  • an air conditioner such as a refrigeration system
  • the capacity of the refrigeration system may be reduced or the components may be damaged. Therefore, in order to prevent the occurrence of such a problem, some have a function of determining whether the amount of refrigerant filled in the refrigeration apparatus is excessive or insufficient.
  • the average temperature efficiency ⁇ A of the temperature efficiency ⁇ of the supercooling heat exchanger is used.
  • the determination threshold value ⁇ line of the temperature efficiency ⁇ is determined to be a constant value of 0.4 (see Patent Document 1).
  • the temperature efficiency is generally expressed by the following (Formula 1).
  • Patent Document 1 in the case of an air supercooling heat exchanger in which the high temperature side is a refrigerant and the low temperature side is an air fluid, the temperature efficiency is such that the supercooling degree of the refrigerant at the outlet of the supercooling heat exchanger is supercooled.
  • the value is divided by the maximum temperature difference of the heat exchanger.
  • the degree of supercooling of the refrigerant at the outlet of the supercooling heat exchanger is a value obtained by subtracting the subcooling heat exchanger outlet temperature from the condenser outlet temperature, and the maximum temperature of the supercooling heat exchanger. It is described that the difference is a value obtained by subtracting the outside air temperature from the condenser outlet temperature.
  • the condenser outlet temperature is TH5
  • the supercooling heat exchanger outlet temperature is TH8
  • the outside air temperature is TH6
  • the temperature efficiency ⁇ of the supercooling heat exchanger is expressed by the following (Formula 2).
  • the extent to which refrigerant shortage can be determined is roughly determined by the "temperature efficiency value when the refrigerant amount is properly sealed” and “temperature efficiency ⁇ determination threshold. It changes depending on the difference of “ ⁇ line”. That is, if the difference between “the value of temperature efficiency when the amount of refrigerant is properly sealed” and “the determination threshold value ⁇ line of temperature efficiency ⁇ ” is large, it is not possible to determine the lack of refrigerant unless a large amount of refrigerant leaks.
  • the refrigerant shortage can be determined with a small refrigerant leakage amount. it can.
  • the “temperature efficiency value when the refrigerant amount is properly sealed” is 0.45, and the “temperature efficiency ⁇ determination threshold value”. Since the value ⁇ line ”(“ threshold value ”indicated by a broken line in the graph of FIG. 14) is 0.40, the difference is as small as 0.05, and the refrigerant shortage can be detected with a small amount of refrigerant leakage. On the other hand, under the conditions of a fan air volume of 100 m 3 / min and an operating frequency of 30 Hz, “temperature efficiency value when refrigerant amount is properly sealed” is 0.80, and “temperature efficiency ⁇ determination threshold ⁇ line” is 0. Therefore, the difference is as large as 0.40, and the refrigerant shortage cannot be detected unless a large amount of refrigerant leaks.
  • the change due to the operating condition of the refrigeration apparatus is smaller than the determination of the lack of the refrigerant amount using the change in the degree of supercooling, but the difference in the temperature efficiency due to the above operating condition occurs.
  • the temperature range in the cabinet for showcases, unit coolers, etc. is about -50 to + 23 ° C, and the temperature range in the cabinet is larger than the temperature range for air conditioners +15 to + 30 ° C. .
  • Not having the condition fixing mode like the refrigerant shortage determination mode is also a reason why the conditions at the time of refrigerant shortage determination change greatly.
  • the present invention has been made against the background of the above-described problems, and it is an object of the present invention to determine whether or not refrigerant is insufficient by determining the shortage of refrigerant and the amount of leakage, and to shorten the time required for determining whether or not refrigerant is insufficient. .
  • a refrigeration apparatus includes a compressor, a heat source side heat exchanger, a heat source side fan that blows air to the heat source side heat exchanger, a heat source side unit having a supercooler, a use side expansion valve, And a refrigeration apparatus having a refrigerant circuit that circulates a refrigerant, and is connected to at least one usage side unit having a usage side heat exchanger, and the degree of supercooling of the refrigerant on the outlet side of the subcooler, Refrigerant for determining the shortage of the amount of refrigerant charged in the refrigerant circuit using the temperature efficiency of the subcooler, which is a value divided by the maximum temperature difference between the high temperature side fluid and the low temperature side fluid exchanged by the subcooler.
  • a shortage determination unit is provided, and the refrigerant shortage determination unit compares the temperature efficiency of the subcooler with the temperature efficiency threshold value that is changed according to the operating state of the refrigeration apparatus, and determines the shortage of the refrigerant amount.
  • the temperature efficiency threshold value is changed according to the operating state, and this temperature efficiency threshold value is used for comparison with the temperature efficiency of the subcooler to determine the shortage of the refrigerant amount. ing. Therefore, it is possible to determine the shortage of the refrigerant amount according to the operating state of the refrigeration apparatus, and it is possible to determine the shortage of the refrigerant amount with a small refrigerant leakage amount.
  • FIG. 2 is an example of a ph diagram when the refrigerant amount is appropriate in the refrigeration apparatus shown in FIG.
  • FIG. 2 is an example of a ph diagram when the refrigerant amount is insufficient in the refrigeration apparatus shown in FIG.
  • FIG. 1 is a figure explaining the relationship between the refrigerant
  • a diagram illustrating an example of a temperature change of the refrigerant when the refrigerant flows in the order of the heat source side heat exchanger, the receiver, and the air supercooler. is there. It is a figure explaining the relationship between the refrigerant
  • FIG. 1 is a diagram schematically illustrating an example of a refrigerant circuit of a refrigeration apparatus according to an embodiment of the present invention.
  • the refrigeration apparatus 1 illustrated in FIG. 1 performs, for example, room cooling such as a room, a warehouse, a showcase, or a refrigerator by performing a vapor compression refrigeration cycle operation.
  • the refrigeration apparatus 1 includes, for example, one heat source side unit 2 and two usage side units 4 connected in parallel to the heat source side unit 2.
  • the heat source side unit 2 and the use side unit 4 are connected by the liquid refrigerant extension pipe 6 and the gas refrigerant extension pipe 7, whereby the refrigerant circuit 10 for circulating the refrigerant is formed.
  • the refrigerant charged in the refrigerant circuit 10 of this embodiment is, for example, R410A, which is an HFC mixed refrigerant.
  • R410A which is an HFC mixed refrigerant.
  • one heat source side unit 2 and two usage side units 4 are described.
  • two or more heat source side units 2 may be used. May be one or three or more.
  • the capacities of the plurality of heat source side units 2 may be the same or different.
  • the capacity of the plurality of usage-side units 4 may be the same or different.
  • the refrigeration apparatus 1 in which the refrigerant exchanges heat with air will be described.
  • the refrigerant may be a refrigeration apparatus that exchanges heat with a fluid such as water, refrigerant, or brine.
  • the use side unit 4 is an indoor unit that is installed indoors, for example, and includes a use side refrigerant circuit 10 a and a use side control unit 32 that constitute a part of the refrigerant circuit 10.
  • the use side refrigerant circuit 10 a includes a use side expansion valve 41 and a use side heat exchanger 42.
  • the use side expansion valve 41 adjusts the flow rate of the refrigerant flowing through the use side refrigerant circuit 10a, and is configured by, for example, an electronic expansion valve or a temperature type expansion valve.
  • the use side expansion valve 41 may be disposed in the heat source side unit 2, and in this case, the use side expansion valve 41 is, for example, the first subcooler 22 and the liquid side of the heat source side unit 2.
  • the use-side heat exchanger 42 is, for example, a fin and tube heat exchanger configured to include a heat transfer tube and a large number of fins, and functions as an evaporator that evaporates the refrigerant.
  • a use side fan 43 that blows air to the use side heat exchanger 42 is disposed.
  • the use-side fan 43 includes, for example, a centrifugal fan or a multi-blade fan, and is driven by a motor not shown.
  • the use side fan 43 can adjust the amount of air blown to the use side heat exchanger 42.
  • the heat source side unit 2 includes, for example, a heat source side refrigerant circuit 10b, a first injection circuit 71, and a heat source side control unit 31 that constitute a part of the refrigerant circuit 10.
  • the heat source side refrigerant circuit 10 b includes a compressor 21, a heat source side heat exchanger 23, a receiver 25, a first subcooler 22, a liquid side closing valve 28, a gas side closing valve 29, and an accumulator 24.
  • the first injection circuit 71 branches a part of the refrigerant sent from the heat source side heat exchanger 23 to the use side heat exchanger 42 from the heat source side refrigerant circuit 10b and returns it to the intermediate pressure part of the compressor 21.
  • the injection amount adjusting valve 72 is included.
  • the compressor 21 is, for example, an inverter compressor that is controlled by an inverter, and can change the capacity (the amount of refrigerant sent out per unit time) by arbitrarily changing the operating frequency.
  • the compressor 21 may be a constant speed compressor that operates at 50 Hz or 60 Hz.
  • FIG. 1 shows an example having one compressor 21, but two or more compressors 21 are connected in parallel according to the load size of the usage-side unit 4. May be.
  • the heat source side heat exchanger 23 is, for example, a fin and tube heat exchanger configured to include a heat transfer tube and a large number of fins, and functions as a condenser that condenses the refrigerant.
  • a heat source side fan 27 for blowing air to the heat source side heat exchanger 23 is disposed.
  • the heat source side fan 27 blows outside air sucked from the outside of the heat source side unit 2 to the heat source side heat exchanger 23.
  • the heat source side fan 27 includes, for example, a centrifugal fan or a multiblade fan, and is driven by a motor not shown.
  • the heat source side fan 27 can adjust the amount of air blown to the heat source side heat exchanger 23.
  • the receiver 25 is disposed between the heat source side heat exchanger 23 and the first subcooler 22 and stores excess liquid refrigerant.
  • the receiver 25 is a container for storing excess liquid refrigerant.
  • the surplus liquid refrigerant is generated in the refrigerant circuit 10 in accordance with, for example, the load size of the usage-side unit 4, the refrigerant condensing temperature, the outside air temperature, the evaporation temperature, or the capacity of the compressor 21. .
  • the first subcooler 22 exchanges heat between the refrigerant and the air, and is formed integrally with the heat source side heat exchanger 23. That is, in the example of this embodiment, a part of the heat exchanger is configured as the heat source side heat exchanger 23, and the other part of the heat exchanger is configured as the first subcooler 22.
  • the first subcooler 22 corresponds to the “supercooler” of the present invention.
  • the 1st subcooler 22 and the heat source side heat exchanger 23 may be comprised separately. In that case, a fan (not shown) that blows air to the first subcooler 22 is disposed in the vicinity of the first subcooler 22.
  • the liquid side closing valve 28 and the gas side closing valve 29 are constituted by valves that open and close such as a ball valve, an on-off valve, or an operation valve, for example.
  • the inlet of the first injection circuit 71 is connected between the first subcooler 22 and the liquid side closing valve 28, but the inlet of the first injection circuit 71 is It may be connected between the receiver 25 and the first subcooler 22, may be connected to the receiver 25, or may be connected between the heat source side heat exchanger 23 and the receiver 25. .
  • the heat source side unit 2 includes a heat source side control unit 31 that controls the entire refrigeration apparatus 1.
  • the heat source side control unit 31 includes a microcomputer and a memory.
  • the usage side unit 4 includes a usage side control unit 32 that controls the usage side unit 4.
  • the use side control unit 32 includes a microcomputer and a memory.
  • the use side control unit 32 and the heat source side control unit 31 can communicate and exchange control signals.
  • the use side control unit 32 receives an instruction from the heat source side control unit 31. In response, the user side unit 4 is controlled.
  • the refrigeration apparatus 1 includes an intake temperature sensor 33a, a discharge temperature sensor 33b, a suction outside air temperature sensor 33c, a supercooler high pressure side outlet temperature sensor 33d, a use side heat exchange inlet temperature sensor 33e, and a use side heat exchange. It includes an outlet temperature sensor 33f, a suction air temperature sensor 33g, a suction pressure sensor 34a, and a discharge pressure sensor 34b.
  • the suction temperature sensor 33a, the discharge temperature sensor 33b, the suction outside air temperature sensor 33c, the supercooler high pressure side outlet temperature sensor 33d, the suction pressure sensor 34a, and the discharge pressure sensor 34b are disposed in the heat source side unit 2 and are controlled by the heat source. Connected to the unit 31.
  • the use side heat exchange inlet temperature sensor 33e, the use side heat exchange outlet temperature sensor 33f, and the intake air temperature sensor 33g are provided in the use side unit 4 and connected to the use side control unit 32.
  • the suction temperature sensor 33a detects the temperature of the refrigerant sucked by the compressor 21.
  • the discharge temperature sensor 33b detects the temperature of the refrigerant discharged from the compressor 21.
  • the subcooler high pressure side outlet temperature sensor 33d detects the temperature of the refrigerant that has passed through the first subcooler 22.
  • the use side heat inlet temperature sensor 33e detects the evaporation temperature of the gas-liquid two-phase refrigerant flowing into the use side heat exchanger.
  • the use-side heat exchange outlet temperature sensor 33f detects the temperature of the refrigerant that has flowed out of the use-side heat exchanger 42.
  • the above-mentioned sensor for detecting the temperature of the refrigerant is disposed, for example, in contact with the refrigerant pipe or inserted into the refrigerant pipe, and detects the temperature of the refrigerant.
  • the suction outside air temperature sensor 33c detects the ambient temperature outside the room by detecting the temperature of the air before passing through the heat source side heat exchanger 23.
  • the intake air temperature sensor 33g detects the ambient temperature in the room where the use side heat exchanger 42 is installed by detecting the temperature of the air before passing through the use side heat exchanger 42.
  • the suction pressure sensor 34 a is disposed on the suction side of the compressor 21 and detects the pressure of the refrigerant sucked into the compressor 21.
  • the suction pressure sensor 34 a may be disposed between the gas side closing valve 29 and the compressor 21.
  • the discharge pressure sensor 34b is disposed on the discharge side of the compressor 21 and detects the pressure of the refrigerant discharged from the compressor 21.
  • the condensation temperature of the heat source side heat exchanger 23 is obtained by converting the pressure of the discharge pressure sensor 34b into the saturation temperature, but the condensation temperature of the heat source side heat exchanger 23 is obtained. Can also be obtained by arranging a temperature sensor in the heat source side heat exchanger 23.
  • FIG. 2 is a control block diagram of the refrigeration apparatus according to the embodiment of the present invention.
  • the control unit 3 controls the entire refrigeration apparatus 1, and the control unit 3 of the present embodiment is included in the heat source side control unit 31.
  • the control unit 3 corresponds to the “refrigerant lack determination unit” of the present invention.
  • the control unit 3 includes an acquisition unit 3a, a calculation unit 3b, a storage unit 3c, and a drive unit 3d.
  • the acquisition unit 3a, the calculation unit 3b, and the drive unit 3d are configured to include, for example, a microcomputer, and the storage unit 3c is configured to include, for example, a semiconductor memory.
  • the acquisition unit 3a acquires information such as temperature and pressure detected by sensors such as a pressure sensor and a temperature sensor.
  • the calculation unit 3b performs processing such as calculation, comparison, and determination using the information acquired by the acquisition unit 3a.
  • the drive unit 3d performs drive control of the compressor 21, valves, fans, and the like using the results calculated by the calculation unit 3b.
  • the storage unit 3c stores physical property values (saturation pressure, saturation temperature, etc.) of the refrigerant, data for the calculation unit 3b to perform calculations, and the like.
  • the calculation unit 3b can refer to or update the storage content of the storage unit 3c as necessary.
  • the control unit 3 includes an input unit 3e and an output unit 3f.
  • the input unit 3e inputs operation input from a remote controller or switches (not shown) or communication data from communication means (not shown) such as a telephone line or a LAN line.
  • the output unit 3f outputs the processing result of the control unit 3 to a display unit (not shown) such as an LED or a monitor, and outputs it to a notification unit (not shown) such as a speaker, or a telephone line or a LAN line.
  • a communication means not shown.
  • the calculation unit 3b calculates the temperature efficiency ⁇ of the first subcooler 22 using the information acquired by the acquisition unit 3a, and the output unit 3f calculates the temperature efficiency calculated by the calculation unit 3b.
  • the remote device is provided with a refrigerant shortage determining means (not shown) for determining the shortage of the refrigerant amount, and determines the shortage of the refrigerant amount using the temperature efficiency ⁇ .
  • control unit 3 is included in the heat source side control unit 31
  • control unit 3 may be included in the use side control unit 32 or the heat source
  • the side control unit 31 and the use side control unit 32 may be configured separately.
  • FIG. 3 is an example of a ph diagram when the refrigerant amount is appropriate in the refrigeration apparatus shown in FIG.
  • the compressor 21 illustrated in FIG. 1 compresses the refrigerant.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 21 in FIG. 1 is heat-exchanged by the heat source side heat exchanger 23 functioning as a condenser to be condensed and liquefied.
  • the refrigerant that has been heat-exchanged by the heat source side heat exchanger 23 and condensed and liquefied flows into the receiver 25 and is temporarily stored in the receiver 25.
  • the amount of the refrigerant stored in the receiver 25 varies depending on the operation load, the outside air temperature, the condensation temperature, and the like of the usage-side unit 4.
  • the liquid refrigerant stored in the receiver 25 in FIG. 1 is supercooled by the first subcooler 22.
  • the degree of supercooling at the outlet of the first supercooler 22 is calculated by subtracting the temperature of the supercooler high-pressure side outlet temperature sensor 33d from the condensation temperature.
  • the liquid refrigerant supercooled by the first subcooler 22 in FIG. 1 from the point N to the point O in FIG. 3 passes through the liquid side closing valve 28 and the liquid refrigerant extension pipe 6 to the usage side unit 4. It is sent and decompressed by the use side expansion valve 41 to become a low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant decompressed by the use side expansion valve 41 in FIG. 1 is gasified in the use side heat exchanger 42 functioning as an evaporator.
  • the degree of superheat of the refrigerant is calculated by subtracting the evaporation temperature of the refrigerant detected by the use side heat exchange inlet temperature sensor 33e from the temperature detected by the use side heat exchange outlet temperature sensor 33f.
  • the gas refrigerant gasified by the use side heat exchanger 42 returns to the compressor 21 via the gas refrigerant extension pipe 7, the gas side closing valve 29, and the accumulator 24.
  • the first injection circuit 71 is for lowering the refrigerant temperature of the discharge part of the compressor 21.
  • the inlet of the first injection circuit 71 is connected between the outlet of the first subcooler 22 and the liquid side shut-off valve 28, and a part of the high-pressure liquid refrigerant subcooled by the first subcooler 22 is Then, the pressure is reduced by the injection amount adjusting valve 72 to become a two-phase refrigerant having an intermediate pressure, and flows into the injection portion of the compressor 21.
  • FIG. 4 is an example of a ph diagram when the refrigerant amount is insufficient in the refrigeration apparatus shown in FIG.
  • the refrigeration apparatus 1 operates in the same manner as when the refrigerant amount is appropriate, as shown in FIG.
  • the enthalpy at the outlet of the heat source side heat exchanger 23 functioning as a condenser increases as shown by a point M1 in FIG.
  • the refrigerant state at the outlet of the heat exchanger 23 becomes a two-phase state.
  • the first subcooler 22 performs the condensing and supercooling of the two-phase refrigerant, so that the point N1 indicates The enthalpy at the outlet of the first subcooler 22 is also increased.
  • the refrigerant amount is determined using the degree of supercooling of the refrigerant. For example, when the amount of refrigerant is insufficient due to leakage of the refrigerant, the degree of supercooling decreases as shown in FIG. Therefore, in the comparative example, it is determined that the refrigerant amount is insufficient when the degree of supercooling becomes smaller than a preset threshold value.
  • FIG. 5 is a diagram illustrating the relationship between the refrigerant amount of the refrigeration apparatus illustrated in FIG. 1, the degree of supercooling of the first subcooler, and the operating conditions of the refrigeration apparatus.
  • the degree of supercooling of the first subcooler 22 varies greatly depending on the operating conditions of the refrigeration apparatus 1 (outside air temperature, heat exchange amount, refrigerant circulation amount, evaporation temperature, etc.). For this reason, as in the comparative example, when determining the shortage of the refrigerant amount using the supercooling degree, it is necessary to set the supercooling degree threshold value S low so as not to make an erroneous determination.
  • the supercooling degree threshold value S since the supercooling degree threshold value S must be set low, it takes a long time to determine whether the refrigerant amount is insufficient. For example, when the refrigerant is leaking, The amount of leakage will increase.
  • the refrigerant amount is determined using the temperature efficiency ⁇ of the first subcooler 22 that has a smaller variation with respect to changes in the operating conditions of the refrigeration apparatus 1 than the degree of supercooling.
  • determination of the refrigerant amount using temperature efficiency will be described.
  • FIG. 6 is an example of the temperature change of the refrigerant when the refrigerant flows in the order of the heat source side heat exchanger, the receiver, and the air supercooler in the refrigeration apparatus shown in FIG. It is a figure explaining.
  • the vertical axis indicates the temperature, and the temperature is higher at the top.
  • the horizontal axis indicates the refrigerant path of the heat source side heat exchanger 23, the receiver 25, and the first subcooler 22.
  • s1 is the refrigerant condensation temperature
  • s2 is the refrigerant temperature at the outlet of the first subcooler 22
  • s3 is the outside air temperature.
  • the temperature efficiency ⁇ of the first subcooler 22 indicates the efficiency of the first subcooler 22, and the maximum temperature difference A is taken as the denominator and the actual temperature difference B is taken as the numerator. .
  • the maximum possible temperature difference A is the difference between the refrigerant condensing temperature s1 and the outside air temperature s3
  • the actually possible temperature difference B is the refrigerant condensing temperature s1 and the first subcooling. This is the difference from the temperature s2 at the outlet of the vessel 22.
  • the temperature efficiency ⁇ is expressed by the following (Formula 3).
  • FIG. 7 is a diagram illustrating the relationship between the refrigerant amount of the refrigeration apparatus illustrated in FIG. 1, the temperature efficiency of the first subcooler, and the operating conditions of the refrigeration apparatus.
  • the horizontal axis represents the refrigerant amount of the refrigerant
  • the vertical axis represents the temperature efficiency ⁇ of the first subcooler 22.
  • the temperature efficiency of a heat exchanger is expressed by the following (Formula 4).
  • the first subcooler 22 of the present embodiment exchanges heat between the refrigerant and the air, and the high temperature side fluid is refrigerant and the low temperature side fluid is air. Therefore, K: heat passage rate (W / (m 2 ⁇ K)) varies depending on the air flow rate and the refrigerant circulation rate. The temperature efficiency decreases as the air flow rate decreases or the refrigerant circulation rate increases.
  • High-temperature side fluid density (kg / m 3 ) ⁇ High-temperature side fluid volume flow rate (m 3 / h) is refrigerant circulation amount G (kg / h). descend. The refrigerant circulation amount varies depending on the compressor frequency, the refrigerant compressor intake gas pressure, and the compressor intake gas temperature. Ch: The high temperature side fluid specific heat (KJ / kg) fluctuates depending on the high pressure of the refrigerant, and the temperature efficiency decreases as the high pressure increases. Vm: The low-temperature side fluid volume flow rate (m 3 / h) is the air volume on the air side, and varies depending on the air volume of the heat source side fan 27.
  • the heat transfer area (m 2 ) is a constant value unique to the refrigeration apparatus 1.
  • ⁇ m Low-temperature side fluid density (kg / m 3 )
  • Cm Low-temperature side fluid specific heat (KJ / kg) is the density of air and specific heat, but has a substantially constant value.
  • the heat transfer area (A), the low temperature side fluid density ( ⁇ m), and the low temperature side fluid specific heat (Cm) of the refrigeration apparatus 1 are constant values. Further, the temperature efficiency varies depending on the refrigerant circulation amount that varies the heat passage rate (K), the high pressure that varies the high-temperature side fluid specific heat (Ch), and the air flow rate that varies depending on the air volume of the heat source side fan 27.
  • the refrigerant circulation amount varies depending on the compressor frequency, the refrigerant compressor intake gas pressure, and the compressor intake gas temperature.
  • the refrigerant circulation amount that is, the compressor frequency, the compressor intake gas pressure of the refrigerant, the compressor intake gas temperature, the air flow rate, and the high pressure pressure are set. And set.
  • the temperature efficiency which is an index for determining the refrigerant shortage
  • the threshold value varies less depending on the operating conditions than the supercooling value, but varies depending on the operating conditions as described above. Therefore, changing the threshold value according to the operating conditions can reduce the difference between the "temperature efficiency value when the refrigerant amount is properly sealed" and the "temperature efficiency ⁇ judgment threshold value ⁇ line", and the amount of refrigerant It is possible to determine the refrigerant shortage by the leakage amount.
  • a threshold setting method according to operating conditions will be described below.
  • FIG. 8 is a diagram illustrating an example of the relationship between the temperature efficiency value of the refrigeration apparatus according to the embodiment of the present invention, the fan output, and the operating frequency. Specifically, as shown in FIG. 8, the temperature efficiency threshold is set to be smaller as the fan output decreases. As a result, the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is about 0.05 to 0.10 under the condition where the fan air volume is 40%. Become.
  • FIG. 14 is a diagram for explaining an example of the relationship between the temperature efficiency value, the fan air volume, and the operating frequency according to the prior art.
  • the value of temperature efficiency when the refrigerant amount is properly sealed is 0.45
  • the “threshold value shown by a broken line” "The determination threshold value ⁇ line of the temperature efficiency ⁇ " is 0.40, so the difference is as small as 0.05, and the refrigerant shortage can be detected with a small amount of refrigerant leakage.
  • the difference is improved as compared with the case where “the determination threshold ⁇ line of the temperature efficiency ⁇ ” is a constant value as shown in FIG.
  • the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is about 0.20 to 0.30 under the condition of the fan air volume of 100%.
  • the difference is improved as compared with the case where “the determination threshold value ⁇ line of the temperature efficiency ⁇ ” in FIG. 14 is a constant value, but the difference is larger than the condition of the fan air volume 40%.
  • FIG. 9 is a diagram for explaining an example of the relationship between the temperature efficiency value of the refrigeration apparatus according to the embodiment of the present invention, the high-temperature side refrigerant circulation rate, and the fan air volume. Specifically, as shown in FIG. 9, the temperature efficiency threshold is set to be smaller as the refrigerant circulation rate increases.
  • the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is about 0.05 to 0.10 when the fan air volume is 40%.
  • the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ are determined more than the“ temperature efficiency ⁇ determination threshold value ⁇ line ” is a constant value.
  • the difference of the “threshold value ⁇ line” is improved.
  • the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is about 0.20 to 0.30 under the condition of the fan air volume of 100%.
  • the difference is improved as compared with the case where “the determination threshold value ⁇ line of the temperature efficiency ⁇ ” in FIG. 14 is a constant value, but the difference is larger than the condition of the fan air volume 40%.
  • the amount of refrigerant circulation is the amount of refrigerant circulation
  • Compressor suction refrigerant density is determined by compressor suction pressure and compressor suction temperature
  • f () represents a function using the value in () as a parameter. Therefore, the refrigerant density is calculated by the intake temperature sensor 33a and the intake pressure sensor 34a of the refrigeration apparatus 1, and the refrigerant circulation amount is calculated by the compressor operating frequency and the constant 2. When there are a plurality of compressors, the total value of the refrigerant circulation amount of each compressor is calculated.
  • the threshold value may be determined using the refrigerant circulation amount based on the saturated suction refrigerant density calculated using only the suction pressure sensor 34a and the compressor operating frequency. Although the accuracy is further lowered, the threshold value may be determined simply based on only the total value of the compressor operating frequencies, or the threshold value may be changed only based on the low pressure. Even in these cases, the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ judgment threshold value”, compared with the case where the “temperature efficiency ⁇ judgment threshold value ⁇ line” is a constant value. The difference in “ ⁇ line” is improved.
  • FIG. 10 is a diagram for explaining an example of the relationship between the temperature efficiency value, the high pressure, and the operating frequency of the refrigeration apparatus according to the embodiment of the present invention. Specifically, as shown in FIG. 10, the temperature efficiency threshold is set to be smaller as the high pressure is decreased. As a result, under the condition of the compressor operating frequency of 100 Hz, the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is about 0.05 to 0.10. Thus, as shown in FIG.
  • the difference is improved as compared with the case where “the determination threshold value ⁇ line of the temperature efficiency ⁇ ” is a constant value.
  • the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is about 0.20 to 0.30.
  • the difference is improved as compared with the case where the “threshold value ⁇ line for temperature efficiency ⁇ ” of 14 is a constant value, but the difference is larger than the condition of the compressor operating frequency of 100 Hz.
  • FIG. 15 is a diagram for explaining an example of the relationship between the temperature efficiency value and ⁇ T of the refrigeration apparatus according to the embodiment of the present invention. Specifically, as shown in FIG. 15, the temperature efficiency threshold is set to be smaller as ⁇ T increases. As a result, even if the fan output and the operating frequency fluctuate, the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is 0.05 to 0. 0. 0. As shown in FIG. 14, the difference is greatly improved as compared with the case where “the determination threshold value ⁇ line of the temperature efficiency ⁇ ” is a constant value as shown in FIG.
  • the difference between the “temperature efficiency value when the refrigerant amount is properly sealed” and the “temperature efficiency ⁇ determination threshold ⁇ line” is the largest. Therefore, the shortage of refrigerant can be detected with the most appropriate amount of refrigerant leakage.
  • FIG. 11 is a flowchart showing the procedure of the refrigerant quantity determination operation in the present embodiment.
  • the refrigerant amount determination operation shown in FIG. 11 is executed by the heat source side control unit 31 of the refrigeration apparatus 1.
  • the refrigeration apparatus 1 determines the refrigerant amount using the temperature efficiency ⁇ of the first subcooler 22. Note that the determination of the refrigerant amount described below can also be applied to a refrigerant charging operation when the refrigeration apparatus 1 is installed or a refrigerant charging operation when the refrigeration apparatus 1 is maintained.
  • the refrigerant amount determination operation may be executed when an instruction from a remote device (not shown) is received.
  • Step ST1 Normal operation control is started in step ST1.
  • the heat source side control unit 31 acquires operation data such as the pressure and temperature of the refrigerant circuit 10 detected by the sensors, and uses the operation data to condense the condensation temperature, the evaporation temperature, and the like.
  • the control values such as target value and deviation are calculated to control the actuators.
  • the operation of the actuators will be described.
  • the heat source side control unit 31 controls the operating frequency of the compressor 21 so that the evaporation temperature of the refrigeration cycle of the refrigeration apparatus 1 matches the target temperature (for example, 0 ° C.).
  • the evaporation temperature of the refrigeration cycle can also be obtained by converting the pressure detected by the suction pressure sensor 34a into a saturation temperature.
  • the heat source side control unit 31 increases the operation frequency of the compressor 21 when the current evaporation temperature is higher than the target temperature, and operates the compressor 21 when the current evaporation temperature is lower than the target value. Reduce the frequency.
  • the heat source side control unit 31 blows air to the heat source side heat exchanger 23 so that the condensation temperature of the refrigeration cycle of the refrigeration apparatus 1 matches a target temperature (for example, 45 ° C.). Control the number of revolutions.
  • the condensation temperature of the refrigeration cycle of the refrigeration apparatus 1 can also be obtained by converting the pressure detected by the discharge pressure sensor 34b into a saturation temperature.
  • the heat source side control unit 31 increases the rotational speed of the heat source side fan 27 when the current condensing temperature is higher than the target temperature, and the heat source side fan 27 when the current condensing temperature is lower than the target temperature. Reduce the rotation speed.
  • the heat source side control unit 31 adjusts the opening degree of the injection amount adjusting valve 72 of the first injection circuit 71 using a signal obtained from the sensors. For example, the heat source side control unit 31 opens the injection amount adjustment valve 72 when the current discharge temperature of the compressor 21 is high, and sets the injection amount adjustment valve 72 when the current discharge temperature of the compressor 21 is low. Close. Further, for example, the heat source side control unit 31 controls the rotation speed of the use side fan 43 that blows air to the use side unit 4.
  • step ST2 the heat source side control unit 31, for example, the outlet temperature of the heat source side heat exchanger 23, the temperature of the outlet of the first subcooler 22, the outside air temperature detected by the suction outside air temperature sensor 33c and the discharge pressure sensor 34b. Is used to calculate the temperature efficiency ⁇ of the first subcooler 22.
  • the heat source side control unit 31 acquires the operating state of the refrigeration apparatus 1.
  • the heat source side control unit 31 determines whether or not the current operation state corresponds to an exception condition for refrigerant amount determination.
  • exception conditions for this refrigerant quantity determination for example, the following conditions are set in advance. When it corresponds to any one of these, it judges that it corresponds to the exceptional condition of refrigerant
  • ⁇ When the compressor 21 is stopped. -30 minutes after startup (because temperature efficiency ⁇ is not stable). -In the case of low outside air temperature (at low outside air temperature, the fan air volume is reduced because it tries to maintain high pressure. Therefore, the temperature efficiency ⁇ also decreases, which may cause false detection). ⁇ At high outside temperatures that are outside the operating range.
  • step ST1 When the operating state of the refrigeration apparatus 1 corresponds to the “exception condition for refrigerant amount determination”, the process returns to step ST1, and the operating state of the refrigeration apparatus 1 corresponds to the “exception condition for refrigerant amount determination”. If not, the process proceeds to step ST4.
  • step ST4 the heat source side control unit 31 determines whether or not the operation control of the refrigeration apparatus 1 started in step ST1 is stably executed.
  • FIG. 12 is a conceptual diagram for explaining stability determination conditions in the embodiment of the present invention.
  • the stability determination condition is set such that the plurality of temperature efficiencies ⁇ calculated in step ST2 and the operation frequency at that time do not vary greatly. For example, as the stability determination condition, it is determined that the stability determination condition is satisfied when the frequency of the compressor 21 satisfies the following condition (8) and when the temperature efficiency ⁇ satisfies the following condition (9). . That is, as shown in FIG. 12A, when all the changes from the average value of the target data fall within the predetermined value ( ⁇ ) (open circles), it is determined that the stability determination condition is satisfied.
  • step ST1 When the operation control of the refrigeration apparatus 1 is not stable, the process returns to step ST1, and when the operation control of the refrigeration apparatus 1 is stable, the process proceeds to step ST5.
  • the temperature efficiency ⁇ of the first subcooler 22 is preferably a moving average of a plurality of temperature efficiencies ⁇ that are temporally different from each other, rather than using an instantaneous value.
  • the determination threshold value Tm may be stored in advance in the storage unit 3c of the heat source side control unit 31, for example, or may be set by input from a remote controller or a switch, or from a remote device (not shown). May be set according to the instruction.
  • step ST6 the heat source side control unit 31 outputs in step ST6 that the refrigerant amount is suitable.
  • the amount of refrigerant is appropriate, the fact that the amount of refrigerant is appropriate is displayed, for example, on a display unit (not shown) such as an LED or a liquid crystal disposed in the refrigeration apparatus 1, or the amount of refrigerant is appropriate. Is transmitted to a remote device (not shown).
  • step ST7 the heat source side control unit 31 outputs in step ST7 that the refrigerant amount is insufficient.
  • the refrigerant amount is insufficient, for example, an alarm indicating that the refrigerant amount is insufficient is displayed on a display unit (not shown) such as an LED or a liquid crystal provided in the refrigeration apparatus 1, or A signal indicating that the amount of refrigerant is insufficient is transmitted to a remote device (not shown).
  • a display unit such as an LED or a liquid crystal provided in the refrigeration apparatus 1
  • a signal indicating that the amount of refrigerant is insufficient is transmitted to a remote device (not shown).
  • an emergency may be required when the amount of refrigerant is insufficient, it may be configured to notify the service person directly of the occurrence of an abnormality through a telephone line or the like.
  • step ST3 after calculating the temperature efficiency ⁇ in step ST2, it is determined in step ST3 whether or not the operating state of the refrigeration apparatus 1 satisfies the exceptional condition, and in step ST4, the refrigeration apparatus.
  • Step ST2 may be executed after step ST3 and step ST4.
  • the temperature efficiency ⁇ is used to determine whether or not the refrigerant circuit 10 of the refrigeration apparatus 1 has a shortage of refrigerant. Even in this case, leakage of the refrigerant can be detected at an early stage.
  • the operating state of the refrigeration apparatus 1 is acquired, and the temperature efficiency threshold for determining the refrigerant shortage using the temperature efficiency ⁇ of the refrigeration apparatus 1 is the operation of the refrigeration apparatus 1. It changes according to the state. Therefore, the determination can be made with as little refrigerant shortage and leakage as possible, and the refrigerant shortage determination is performed earlier than the conventional method. As a result, the rise in the internal temperature can be reduced as much as possible, and the deterioration of the global environment can be reduced, the damage to the stored items due to the increase in the internal temperature when the refrigerant leaks, and the recovery cost after the refrigerant leaks. Further, since the temperature efficiency threshold value can be changed and determined with a small number of parameters, the determination can be made with as little refrigerant shortage and leakage as possible with simpler control.
  • control for specifying the condensation temperature and the evaporation temperature is not performed.
  • the control may be performed so that the condensation temperature and the evaporation temperature are constant.
  • it is not necessary to control the condensing temperature and the evaporating temperature by setting the operating frequency of the compressor 21 and the rotation speed of the heat source side fan 27 of the heat source side unit 2 as constant values.
  • the control may be performed so that one of the condensation temperature and the evaporation temperature becomes a target value.
  • the degree of subcooling of the first subcooler 22 and the fluctuation of the operating state quantity that varies according to the degree of subcooling are reduced, and the threshold value is determined. It becomes easy, and it becomes easy to determine whether the amount of refrigerant is insufficient.
  • the refrigerant amount determination operation of the present embodiment is applied to the refrigerant charging operation at the initial stage of installation of the refrigeration apparatus 1 or the refrigerant charging operation when the refrigerant is once discharged and charged again at the time of maintenance. It is possible to reduce the time required for the operator and reduce the load on the worker.
  • FIG. 13 is a diagram schematically illustrating a refrigerant circuit of a refrigeration apparatus according to a modification of the present invention.
  • the heat source side unit 2A of the refrigeration apparatus 1A of the modification has a second subcooler 26 instead of the first subcooler 22 as shown in FIG. is doing.
  • the second subcooler 26 corresponds to the “supercooler” of the present invention.
  • the second subcooler 26 includes, for example, a double-tube subcooler or a plate heat exchanger, and includes a high-pressure refrigerant flowing in the heat source side refrigerant circuit 10b and an intermediate pressure flowing in the first injection circuit 71A. Heat exchange with the other refrigerant.
  • a part of the refrigerant that has passed through the second subcooler 26 is expanded by the injection amount adjustment valve 72 to become an intermediate-pressure refrigerant, and exchanges heat with the refrigerant that has passed through the second subcooler 26. Further, the intermediate-pressure refrigerant that flows in from the injection amount adjustment valve 72 and exchanges heat with the second subcooler 26 becomes a refrigerant having a high dryness, so that the discharge temperature of the compressor 21 is lowered in order to lower the discharge temperature of the compressor 21. Injection into the suction side. The refrigerant determination operation in the modification is performed using the temperature efficiency of the second subcooler 26.
  • the temperature efficiency is the refrigerant at the outlet of the second subcooler 26. Is a value obtained by dividing the degree of supercooling (condenser outlet temperature-subcooling heatr outlet temperature) by the maximum temperature difference of the second supercooler 26 (condenser outlet temperature-intermediate pressure (injection circuit) saturation temperature). .
  • the temperature efficiency is expressed by the following (Formula 10).
  • the 1st subcooler 22 can be added and the refrigerant
  • FIG. 1st subcooler 22 can be added and the refrigerant
  • the modified second subcooler 26 exchanges heat between the refrigerant and the refrigerant, and the high-temperature side fluid is the refrigerant, and the low-temperature side fluid is also the refrigerant. Therefore, K: heat passage rate (W / (m 2 ⁇ K)) varies depending on the refrigerant circulation amount. The temperature efficiency decreases as the refrigerant circulation rate increases.
  • Low temperature side fluid density (kg / m 3 ) ⁇ Low temperature side fluid volume flow rate (m 3 / h) is the low temperature side refrigerant circulation amount Gm (kg / h) flowing through the first injection circuit 71A, When the refrigerant circulation amount Gm increases, the temperature efficiency decreases.
  • the refrigerant circulation amount Gm flowing through the first injection circuit 71A varies depending on the opening degree of the injection amount adjusting valve 72 and the differential pressure upstream and downstream of the injection amount adjusting valve 72.
  • A heat transfer area
  • the temperature efficiency is defined as the high-temperature side refrigerant circulation amount that fluctuates the heat transfer rate (K), the low-temperature side refrigerant circulation amount that flows through the first injection circuit 71A, It fluctuates depending on the high-pressure pressure that changes the high-temperature side fluid specific heat (Ch) and the intermediate pressure. Therefore, when the temperature efficiency threshold value is changed according to the operating conditions, the temperature efficiency threshold value, the low temperature side refrigerant circulation rate, the high pressure pressure, and the intermediate pressure are set.
  • the high-temperature side refrigerant circulation amount varies depending on the compressor frequency, the refrigerant compressor intake gas pressure, and the compressor intake gas temperature.
  • the low-temperature side refrigerant circulation amount varies depending on the opening degree of the injection amount adjusting valve 72 and the differential pressure between the upstream and downstream of the injection amount adjusting valve 72.
  • the threshold value is changed according to the low-temperature side refrigerant circulation amount as “threshold value setting method 5 based on operating conditions”. Specifically, as in FIG. 9, the temperature efficiency threshold is set to be smaller as the low-temperature-side refrigerant circulation rate increases. Thereby, as shown in FIG. 14, the difference is improved as compared with the case where “the determination threshold value ⁇ line of the temperature efficiency ⁇ ” is a constant value.
  • the low-temperature side refrigerant circulation amount is obtained from the following (Formula 11).
  • the control unit 3 outputs the opening degree of the injection amount adjusting valve 72, the differential pressure between the upstream and downstream of the injection amount adjusting valve 72, and the injection amount adjustment.
  • the low-temperature side refrigerant circulation amount is calculated from the pressure and temperature upstream of the valve 72. If there is no pressure sensor at 71A downstream of the injection amount adjusting valve 72, the pressure may be calculated from the suction pressure sensor 34a and the discharge pressure sensor 34b.
  • the refrigerant circulation amount it is necessary to perform complicated calculations with the controller. Therefore, although the accuracy is slightly reduced, for simplicity, either a value for outputting the opening degree of the injection amount adjusting valve 72, a differential pressure between the upstream and downstream of the injection amount adjusting valve 72, or a pressure upstream of the injection amount adjusting valve 72 is used.
  • the threshold may be determined using one or more of the parameters.
  • suction pressure sensor 34a and the discharge pressure sensor 34b are simply used in place of the differential pressure between the upstream and downstream of the injection amount adjusting valve 72, and the suction pressure and discharge pressure of the compressor expressed by the following formula 12 are used.
  • the threshold value may be changed using the compression ratio as a parameter.
  • the threshold value may be changed using the temperature difference between the upstream and downstream of the injection amount adjusting valve 72 or the pressure ratio between the upstream and downstream of the injection amount adjusting valve 72 as a parameter. Further, the threshold value may be changed using the density upstream of the injection amount adjusting valve 72 as a parameter.
  • the threshold value may be changed using any one of the temperatures upstream of the regulating valve 72 as a parameter, or the threshold value may be changed using a plurality of these as parameters.
  • the present invention is not limited to the above embodiment, and various modifications can be made within the scope of the present invention. That is, the configuration of the above embodiment may be improved as appropriate, or at least a part of the configuration may be replaced with another configuration. Further, the configuration requirements that are not particularly limited with respect to the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at a position where the function can be achieved.

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