WO2016135904A1 - Appareil frigorifique - Google Patents

Appareil frigorifique Download PDF

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Publication number
WO2016135904A1
WO2016135904A1 PCT/JP2015/055476 JP2015055476W WO2016135904A1 WO 2016135904 A1 WO2016135904 A1 WO 2016135904A1 JP 2015055476 W JP2015055476 W JP 2015055476W WO 2016135904 A1 WO2016135904 A1 WO 2016135904A1
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WIPO (PCT)
Prior art keywords
refrigerant
heat source
amount
temperature
refrigeration apparatus
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.)
Ceased
Application number
PCT/JP2015/055476
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English (en)
Japanese (ja)
Inventor
佐多　裕士
齊藤　信
久登 森田
洋貴 佐藤
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
Original Assignee
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 JP2017501756A priority Critical patent/JP6449979B2/ja
Priority to PCT/JP2015/055476 priority patent/WO2016135904A1/fr
Priority to CN201580072558.3A priority patent/CN107110586B/zh
Publication of WO2016135904A1 publication Critical patent/WO2016135904A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the present invention relates to a refrigeration apparatus for determining the amount of refrigerant in a refrigerant circuit.
  • a temperature difference between the inlet refrigerant temperature and the outlet refrigerant temperature of the subcooler is calculated, and it is determined that the refrigerant is leaking when the temperature difference is smaller than a set value.
  • a temperature difference between the inlet refrigerant temperature and the outlet refrigerant temperature of the subcooler is calculated, and it is determined that the refrigerant is leaking when the temperature difference is smaller than a set value.
  • Patent Document 1 uses the change in the degree of supercooling to determine the shortage of the refrigerant amount, erroneous determination is likely to occur in the refrigerant leakage determination. This is because the degree of supercooling varies greatly depending on the operating conditions of the refrigeration apparatus.
  • the present invention has been made against the background of the above-described problems, and an object thereof is to obtain a refrigeration apparatus capable of accurately determining the amount of refrigerant.
  • a refrigeration apparatus includes a heat source side unit having a heat source side heat exchanger and a supercooler functioning as a compressor and a condenser, and a usage side heat exchanger functioning as a usage side expansion valve and an evaporator.
  • a refrigerating apparatus having a refrigerant circuit that is connected by piping and circulates a refrigerant, the degree of supercooling of the refrigerant at the outlet of the subcooler being a maximum temperature difference of the subcooler.
  • a refrigerant amount determination unit that determines the amount of refrigerant charged in the refrigerant circuit using the temperature efficiency of the subcooler, which is a value obtained by dividing, and the refrigerant amount determination unit acquires the operating state of the refrigeration apparatus, If the determination of the refrigerant amount is likely to be an erroneous determination, the refrigerant amount is not determined.
  • the refrigerant amount can be accurately determined.
  • FIG. 2 is an example of a ph diagram when the amount of refrigerant in the refrigeration apparatus shown in FIG. 1 is appropriate.
  • FIG. 2 is an example of a ph diagram when the refrigerant amount of the refrigeration apparatus shown in FIG. 1 is insufficient. It is a figure explaining the relationship between the refrigerant
  • FIG. 1 is a diagram for explaining an example of a temperature change of a refrigerant when the refrigerant flows in the order of a heat source side heat exchanger, a receiver, and an air supercooler when the refrigerant amount is an appropriate amount in the refrigeration apparatus illustrated in FIG. 1. It is. It is a figure explaining the relationship between the refrigerant
  • FIG. [Refrigeration equipment] 1 is a diagram schematically illustrating an example of a refrigerant circuit of a refrigeration apparatus according to Embodiment 1 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, a second injection circuit 73, and a heat source side control unit 31 that constitute a part of the refrigerant circuit 10.
  • a heat source side refrigerant circuit 10b includes, for example, a heat source side refrigerant circuit 10b, a first injection circuit 71, a second injection circuit 73, and a heat source side control unit 31 that constitute a part of the refrigerant circuit 10.
  • the refrigeration apparatus 1 is one of the first injection circuit 71 and the second injection circuit 73.
  • the structure which has one side may be sufficient.
  • 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 second injection circuit 73 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 flows into the suction portion of the compressor 21.
  • a capillary tube 74 and a solenoid valve 75 for suction injection.
  • 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 size of the load on the use side unit 4, the refrigerant condensing temperature, the outside air temperature, the capacity of the compressor 21, or the like.
  • 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 capillary tube 74 may be configured with a valve capable of adjusting the flow rate.
  • the inlets of the first injection circuit 71 and the second injection circuit 73 are connected between the first subcooler 22 and the liquid side shut-off valve 28, but the first injection
  • the inlets of the circuit 71 and the second injection circuit 73 may be connected between the receiver 25 and the first subcooler 22, may be connected to the receiver 25, or may be connected to the heat source side heat exchanger 23. It may be connected between 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 diagram schematically illustrating an example of the configuration of the refrigeration apparatus according to Embodiment 1 of the present invention.
  • the control unit 3 controls the entire refrigeration apparatus 1, and the control unit 3 in the example of this embodiment is included in the heat source side control unit 31.
  • the control unit 3 corresponds to the “refrigerant amount 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 T 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.
  • T is sent to the remote device.
  • 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 T.
  • 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 of the refrigeration apparatus shown in FIG. 1 when the amount of refrigerant is appropriate.
  • 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.
  • the second injection circuit 73 is for lowering the refrigerating machine oil inside the compressor 21, the temperature of the motor, and the refrigerant temperature of the discharge part.
  • the inlet of the second injection circuit 73 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 in the capillary tube 74 to become a low-pressure two-phase refrigerant and flows into the suction 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 refrigerant amount is insufficient due to leakage of the refrigerant, the degree of supercooling is reduced as shown in FIG. Therefore, in Comparative Example 1, when the degree of supercooling becomes smaller than a preset threshold value, it is determined that the refrigerant amount is insufficient.
  • 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, etc.). Therefore, as in Comparative Example 1, when using the degree of supercooling to determine whether the amount of refrigerant is insufficient, it is necessary to set the degree of supercooling threshold S low so as not to make an erroneous determination.
  • the refrigerant amount is determined by using the temperature efficiency T 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. This will be described below.
  • 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 when the refrigerant amount is an appropriate amount in the refrigeration apparatus illustrated in FIG. FIG.
  • 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 T 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 condensation temperature s1 and the outside air temperature s3
  • the actually possible temperature difference B is the condensation temperature s1 and the outlet of the first subcooler 22. Is the difference from the temperature s2.
  • 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 T of the first subcooler 22.
  • the temperature efficiency T indicates the performance of the supercooling heat exchanger 5, and since the fluctuation due to the operating conditions of the refrigeration apparatus 1 is smaller than the degree of supercooling, a threshold is set for each operating condition of the refrigeration apparatus 1. Therefore, it is possible to improve the determination accuracy of the refrigerant amount shortage.
  • an exception condition for refrigerant amount determination is provided, and when the refrigerant amount determination corresponds to an exception condition that may be erroneously determined, the temperature efficiency T of the first subcooler 22 is set. The amount of refrigerant used is not determined. This will be described below.
  • Exception condition 1 is a case where user-side fan delay control is performed.
  • the use-side fan delay control is performed to prevent warm air generated during the defrosting operation from being blown out into the cooling space.
  • the time until the temperature of the use side heat exchanger 42 decreases after the defrosting operation is completed is, for example, several minutes, and the use side fan 43 operates before the temperature of the use side heat exchanger 42 decreases. Then, since warm air is blown out into the cooling space, the operation of the use side fan 43 is stopped until the temperature of the use side heat exchanger 42 decreases. And after the temperature of the use side heat exchanger 42 falls, the operation
  • the refrigerant amount determination using the temperature efficiency T may be erroneously determined. Therefore, at the time of use-side fan delay control, the refrigerant amount determination using the temperature efficiency T is not performed.
  • the use-side fan delay control is completed and the use-side fan 43 is operated, the refrigerant flowing from the use-side heat exchanger 42 to the compressor 21 is in a gas state, and the shortage of refrigerant on the high-pressure side is resolved.
  • the control unit 3 determines that the refrigeration apparatus 1 is performing the use-side fan delay control by acquiring the operation state of the refrigeration apparatus 1. Then, the control unit 3 determines that the refrigerant flowing from the use side heat exchanger 42 to the compressor 21 is in the gas state during the use side fan delay control or during the use side fan delay control and after the use side fan delay control.
  • the refrigerant shortage determination is not performed for a certain period of time. Even when the use-side fan delay control is not performed, when the operation of the use-side fan 43 is stopped, the refrigerant amount determination using the temperature efficiency T may be erroneously determined as described above. There is. Therefore, when the operation of the use-side fan 43 is stopped, the refrigerant amount determination using the temperature efficiency T may not be performed.
  • the temperature efficiency T exceeds the preset set time and falls below the temperature efficiency threshold value T1
  • the maximum time of the use side fan delay control is, for example, about 10 minutes
  • Exception condition 2 is when the evaporation temperature is high during pull-down.
  • the operation may be performed in a state where the pressure on the low pressure side of the refrigerant circuit 10 is higher than usual although it is a short time. In this case, the pressure from the use side expansion valve 41 to the suction portion of the compressor 21 increases, and the refrigerant density increases.
  • the required amount of refrigerant is expressed by density ⁇ volume, the required amount of refrigerant on the low pressure side temporarily increases, and the high pressure side such as the receiver 25, the first subcooler 22, the heat source side heat exchanger 23, etc. A refrigerant shortage state occurs. Therefore, at the time of pull-down, when the evaporation temperature is high, the refrigerant amount determination using the temperature efficiency T is not performed.
  • FIG. 8 is a diagram for explaining that, in the refrigerant amount determination of this embodiment, when the compressor is an inverter compressor, the refrigerant amount determination is not performed according to the magnitude of the low pressure.
  • FIG. 9 is a diagram for explaining that, in the refrigerant amount determination according to this embodiment, when the compressor is a constant speed compressor, the refrigerant amount determination is not performed according to the magnitude of the low pressure. .
  • the compressor 21 is an inverter compressor, the operating frequency of the compressor 21 is increased so that the actual low pressure approaches the target low pressure P1 set in advance. It has been reduced. Further, as shown in FIG.
  • a low pressure cut ON value P4 is set to operate the compressor 21 when the low pressure increases, and when the low pressure decreases.
  • a low pressure cut OFF value P3 for stopping the compressor 21 is set, and the compressor 21 is operated. That is, when the compressor 21 is an inverter compressor, the low pressure pressure during the operation of the compressor 21 is operated at a substantially target low pressure, and when the compressor 21 is a constant speed compressor, the compression is performed. Most of operations are less than the low pressure cut ON value for operating the machine 21. Therefore, if the current low pressure is higher than the target low pressure or the value obtained by adding a margin to the low pressure cut ON value as described below, the refrigerant shortage determination is not performed. That is, as shown in FIG.
  • the refrigerant shortage determination is not performed when the current low pressure is larger than the target low pressure P1 + the pressure P2 of the margin ⁇ .
  • the refrigerant shortage determination is performed when the current low pressure is higher than the low pressure cut ON value P4 + the pressure P5 of the margin ⁇ . Absent.
  • Exception condition 3 is a case where the electromagnetic valve 75 for suction injection shown in FIG. 1 is open.
  • the electromagnetic valve 75 for suction injection When the electromagnetic valve 75 for suction injection is opened, a part of the high-pressure liquid refrigerant is decompressed by the capillary tube 74 and flows into the suction portion of the compressor 21.
  • the high pressure side such as the first subcooler 22 and the heat source side heat exchanger 23 is in a refrigerant shortage state.
  • the case where the electromagnetic valve 75 for suction injection is opened is a rare situation, for example, when the intake gas temperature of the compressor 21 abnormally rises during pull-down after a long-term stop.
  • the electromagnetic valve 75 for suction injection is used.
  • the gas-liquid two-phase state up to the suction portion of the compressor 21 is temporarily increased, the amount of refrigerant temporarily increases to the low pressure side, and the high pressure side such as the receiver 25, the first subcooler 22 and the heat source side heat exchanger 23 is in a refrigerant shortage state. Therefore, the refrigerant shortage determination is not performed.
  • the example in which the refrigerant shortage determination is not performed when performing the injection in the second injection circuit 73 has been described.
  • the refrigerant shortage is not performed. You may be comprised so that determination may not be performed. In that case, it is only necessary to determine whether or not to determine whether the refrigerant is insufficient by using the opening degree of the injection amount adjusting valve 72 or the like.
  • Exception condition 4 (when the air volume of the heat source fan is low)]
  • the air volume of the heat source side fan 27 is reduced.
  • the air volume of the heat source side fan 27 is reduced, for example, when the outside air is reduced, if the high pressure is too low, the differential pressure of the use side expansion valve 41 becomes small and the flow rate of the refrigerant cannot be secured.
  • the air volume of the heat source side fan 27 is reduced in order to keep it high. For example, in order to reduce the noise of the heat source side fan 27, the air volume of the heat source side fan 27 may be reduced.
  • the condensing temperature increases as the air volume of the heat source side fan 27 decreases, so that the maximum possible temperature difference A, which is the difference between the condensing temperature and the outside air temperature, increases.
  • the actual possible temperature difference B which is the difference between the condensation temperature and the outlet temperature of the first subcooler 22, is the maximum possible temperature difference A because the air volume of the heat source side fan 27 is reduced. Does not become large compared to. Therefore, when the air volume of the heat source side fan 27 is decreased, the temperature efficiency T is decreased. In particular, when the ambient temperature is low, such as -15 ° C., it is necessary to turn on / off the heat source side fan 27.
  • the maximum temperature difference A that is normally about 7K to 15K is 30K to 50K.
  • the temperature efficiency T decreases. Therefore, when the air volume of the heat source side fan 27 is decreased, the difference between the outside air temperature and the condensation temperature is increased, or when the outside air temperature is lower than a certain temperature, the refrigerant shortage determination is not performed.
  • FIG. 10 is a diagram showing an example of the relationship between the air volume of the heat source side fan and the temperature efficiency threshold. As shown in FIG. 10, by setting the temperature efficiency threshold T2 when the air volume of the heat source side fan 27 is reduced to a small value, compared to the temperature efficiency threshold T3 when the air volume of the heat source side fan 27 is large. In addition, the risk of erroneous determination of refrigerant amount determination using temperature efficiency T can be suppressed.
  • the condensation temperature is 25.0 ° C.
  • the outside air temperature is 24.9 ° C.
  • the outlet temperature of the first subcooler 22 is 24.8 ° C.
  • the temperature efficiency T varies greatly due to sensor variations or the like during a long-term stop of the compressor 21.
  • the temperature efficiency T is stabilized at a value between 0.0 and 1.0 at time m2.
  • the time from time m1 to time m2 is, for example, about 30 seconds to 1 minute.
  • the temperature efficiency T is unstable for a certain time after the compressor 21 is started after the compressor 21 is stopped. For example, the compressor 21 is repeatedly stopped and operated in a short time. In such a case, the situation where the temperature efficiency T is low continues. As a result, even if the refrigerant is not leaking, the refrigerant determination using the temperature efficiency T may be insufficient. Therefore, the refrigerant shortage is not determined for a certain period of time after the compressor 21 is started after the compressor 21 is stopped.
  • FIG. 12 is a diagram illustrating an example of the refrigerant amount determination operation of the refrigeration apparatus illustrated in FIG.
  • the refrigeration apparatus 1 uses the temperature efficiency T of the first subcooler 22 to determine the refrigerant amount. 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 of FIG. 12 the refrigeration apparatus 1 shown in FIG.
  • 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 number of rotations of the heat source side fan 27 when the current condensing temperature is higher than the target temperature, and increases the rotational speed of 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 adjustment valve 72 of the first injection circuit 71 using the signals obtained from the sensors, or for the suction injection of the second injection circuit 73.
  • the opening degree of the electromagnetic valve 75 is adjusted. For example, when the current discharge temperature of the compressor 21 is high, the heat source side control unit 31 opens the injection amount adjusting valve 72 or the suction injection electromagnetic valve 75 and the current discharge temperature of the compressor 21 is low. Closes the injection amount adjusting valve 72 or the electromagnetic valve 75 for suction injection. 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 T of the first subcooler 22.
  • step ST3 the heat source side control unit 31 acquires the operation state of the refrigeration apparatus 1.
  • the process returns to step ST1
  • 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 the operation control of the refrigeration apparatus 1 performed in step ST1 is stable. If the operation control of the refrigeration apparatus 1 is not stable, the process returns to step ST1, and if the operation control of the refrigeration apparatus 1 is stable, the process proceeds to step ST5.
  • the temperature efficiency T of the first subcooler 22 is preferably a moving average of a plurality of temperature efficiencies T 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 an input from a remote controller or a switch, or an instruction from a remote device (not shown). May be set.
  • 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).
  • the heat source side control unit 31 outputs in step ST7 that the refrigerant amount is abnormal.
  • the refrigerant amount is abnormal, for example, an alarm indicating that the refrigerant amount is abnormal is displayed on a display unit (not shown) such as an LED or a liquid crystal provided in the refrigeration apparatus 1, or the refrigerant amount 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
  • the refrigerant amount Is transmitted to a remote device not shown.
  • an emergency since an emergency may be required when the amount of refrigerant is abnormal, it may be configured to notify the service person of the occurrence of abnormality directly through a telephone line or the like.
  • the temperature efficiency T is calculated in step ST2, and it is determined whether or not the refrigerant amount is determined in steps ST3 and ST4.
  • step ST3 and step ST4 are used.
  • step ST2 may be executed. By performing the calculation of the temperature efficiency T after determining whether or not to determine the refrigerant amount, the amount of processing that the heat source side control unit 31 performs the calculation can be reduced.
  • the temperature efficiency T is used to determine the amount of refrigerant flowing in the refrigerant circuit 10 of the refrigeration apparatus 1, so that even if the refrigerant leaks, The refrigerant leakage can be detected at an early stage.
  • the refrigerant amount using the temperature efficiency T Since the determination is not performed, the risk of erroneous determination of the refrigerant amount is suppressed.
  • the amount of refrigerant can be set to an appropriate amount, the cost of the refrigerant can be reduced.
  • the amount of refrigerant is an appropriate amount, even if the refrigerant leaks, the amount of refrigerant released into the atmosphere can be reduced.
  • the refrigeration apparatus 1 of this embodiment since the amount of refrigerant is an appropriate amount, even if the operation of the expansion valve or the like becomes abnormal and liquid back occurs, the amount of liquid back to the compressor 21 is reduced. Can be reduced. Therefore, the refrigeration apparatus 1 of this embodiment has improved reliability.
  • 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 variable that varies according to the degree of subcooling are reduced, and the threshold value can be easily determined. This makes it easier to determine whether the refrigerant amount is insufficient.
  • the refrigerant amount determination operation of this 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 refilled 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 shows a first modification of FIG. Compared with the refrigeration apparatus 1 described in FIG. 1, the heat source side unit 2 ⁇ / b> A of the refrigeration apparatus 1 ⁇ / b> A according to the first modification has a second subcooler 26 downstream of the first subcooler 22, as shown in FIG. 13. It has further.
  • the second subcooler 26 corresponds to the “supercooler” of the present invention.
  • the second subcooler 26 includes, for example, a double pipe or a plate-type heat exchanger, and has 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 refrigerant is performed.
  • 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.
  • the high-pressure refrigerant flowing from the receiver 25 and heat-exchanged by the second subcooler 26 is further subcooled.
  • 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 first modification is performed using the temperature efficiency of the first subcooler 22, the temperature efficiency of the second subcooler 26, or the temperature efficiency of the first subcooler 22 and the second subcooler 26. It's fine.
  • the first subcooler 22 may be omitted, and the refrigerant that has flowed out from the receiver 25 may flow into the second subcooler 26.
  • the present invention is not limited to the above embodiment, and can be variously modified 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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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un appareil frigorifique (1) comprenant un circuit de fluide frigorigène (10) qui est constitué d'une unité côté source de chaleur (2) et d'au moins une unité côté utilisation (4) qui sont raccordées par tuyauterie et font circuler un fluide frigorigène dans cette dernière. L'unité côté source de chaleur (2) comprend un compresseur (21), un échangeur de chaleur côté source de chaleur (23) servant de condenseur et un sur-refroidisseur (22). L'unité côté utilisation (4) comprend une soupape de détente côté utilisation (41) et un échangeur de chaleur côté utilisation (42) servant d'évaporateur. L'appareil frigorifique (1) est pourvu d'une unité de détermination de quantité de fluide frigorigène (3) qui détermine la quantité du fluide frigorigène chargé dans le circuit de fluide frigorigène (10) au moyen de l'efficacité thermique T du sur-refroidisseur (22), qui est une valeur obtenue par division du degré de surfusion du fluide frigorigène à la sortie du sur-refroidisseur (22) par la différence de température maximale du sur-refroidisseur (22). L'unité de détermination de quantité de fluide frigorigène (3) acquiert l'état de fonctionnement de l'appareil frigorifique (1) et, si la quantité de fluide frigorigène est susceptible d'être déterminée de manière erronée, la détermination de la quantité de fluide frigorigène n'est pas effectuée.
PCT/JP2015/055476 2015-02-25 2015-02-25 Appareil frigorifique Ceased WO2016135904A1 (fr)

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JP2017501756A JP6449979B2 (ja) 2015-02-25 2015-02-25 冷凍装置
PCT/JP2015/055476 WO2016135904A1 (fr) 2015-02-25 2015-02-25 Appareil frigorifique
CN201580072558.3A CN107110586B (zh) 2015-02-25 2015-02-25 制冷装置

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WO2021111561A1 (fr) 2019-12-04 2021-06-10 三菱電機株式会社 Unité extérieure et dispositif à cycle frigorifique
CN118463450A (zh) * 2024-04-09 2024-08-09 比亚迪股份有限公司 制冷剂泄漏检测方法、电子设备、计算机可读存储介质及计算机程序产品

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CN118463450A (zh) * 2024-04-09 2024-08-09 比亚迪股份有限公司 制冷剂泄漏检测方法、电子设备、计算机可读存储介质及计算机程序产品

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