WO2010038382A1 - 漏洩診断装置、漏洩診断方法、及び冷凍装置 - Google Patents
漏洩診断装置、漏洩診断方法、及び冷凍装置 Download PDFInfo
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- WO2010038382A1 WO2010038382A1 PCT/JP2009/004824 JP2009004824W WO2010038382A1 WO 2010038382 A1 WO2010038382 A1 WO 2010038382A1 JP 2009004824 W JP2009004824 W JP 2009004824W WO 2010038382 A1 WO2010038382 A1 WO 2010038382A1
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- Prior art keywords
- refrigerant
- leakage
- index value
- amount
- exergy
- Prior art date
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- 238000000034 method Methods 0.000 title claims description 89
- 239000003507 refrigerant Substances 0.000 claims abstract description 965
- 238000003745 diagnosis Methods 0.000 claims abstract description 87
- 230000008569 process Effects 0.000 claims description 77
- 238000004364 calculation method Methods 0.000 claims description 73
- 239000007788 liquid Substances 0.000 claims description 73
- 238000005057 refrigeration Methods 0.000 claims description 72
- 230000007246 mechanism Effects 0.000 claims description 17
- 238000004781 supercooling Methods 0.000 claims description 16
- 230000017525 heat dissipation Effects 0.000 claims description 9
- 230000009467 reduction Effects 0.000 claims description 6
- 230000008859 change Effects 0.000 description 73
- 238000001514 detection method Methods 0.000 description 33
- 230000007423 decrease Effects 0.000 description 30
- 238000012986 modification Methods 0.000 description 29
- 230000004048 modification Effects 0.000 description 26
- 238000001816 cooling Methods 0.000 description 23
- 238000010586 diagram Methods 0.000 description 17
- 238000010438 heat treatment Methods 0.000 description 15
- 239000002826 coolant Substances 0.000 description 12
- 238000007906 compression Methods 0.000 description 10
- 230000006835 compression Effects 0.000 description 8
- 238000004378 air conditioning Methods 0.000 description 7
- 238000005259 measurement Methods 0.000 description 5
- 238000012545 processing Methods 0.000 description 5
- 230000006837 decompression Effects 0.000 description 4
- 230000005494 condensation Effects 0.000 description 3
- 238000009833 condensation Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000002250 progressing effect Effects 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
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- 238000004891 communication Methods 0.000 description 2
- 238000013523 data management Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 239000011555 saturated liquid Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 239000003463 adsorbent Substances 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 235000013367 dietary fats Nutrition 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 235000013305 food Nutrition 0.000 description 1
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- 239000010520 ghee Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012932 thermodynamic analysis Methods 0.000 description 1
Images
Classifications
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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
- F25B49/005—Arrangement or mounting of control or safety devices of 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/005—Outdoor unit expansion valves
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
- F25B2500/222—Detecting refrigerant leaks
-
- 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
- F25B2600/00—Control issues
- F25B2600/19—Refrigerant outlet condenser temperature
-
- 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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Definitions
- the present invention relates to a leakage diagnosis apparatus, a leakage diagnosis method, and a refrigeration apparatus including a leakage diagnosis apparatus for diagnosing the presence or absence of refrigerant leakage from a refrigerant circuit.
- Patent Document 1 describes an abnormality detection system as this type of leakage diagnosis apparatus.
- This abnormality detection system is configured to detect refrigerant leakage by utilizing the degree of supercooling, superheat, low pressure, high pressure, outside air temperature, room temperature and compressor speed of the refrigeration cycle of the air conditioner. Has been.
- Patent Document 2 describes an analyzer for a refrigeration apparatus that analyzes refrigerant exergy in a circuit configuration device (for example, a compressor) of a refrigerant circuit and diagnoses a failure of the circuit configuration device.
- a circuit configuration device for example, a compressor
- JP 2006-275411 A Japanese Patent No. 4039462
- the present invention has been made in view of the above points, and an object of the present invention is to provide a leakage diagnosis apparatus for diagnosing the presence or absence of refrigerant leakage in a refrigerant circuit that performs a refrigeration cycle.
- the purpose is to realize refrigerant leakage diagnosis using the amount of loss of ghee.
- a compressor (30), a radiator (34, 37), a pressure reduction mechanism (36), and an evaporator (34, 37) are provided as circuit components, and a refrigerant is circulated to perform a refrigeration cycle.
- a leakage diagnosis device (50) for diagnosing the presence or absence of refrigerant leakage in the refrigerant circuit (20) to be performed is an object.
- this leak diagnostic apparatus (50) is an index that calculates a leak index value that changes according to the amount of refrigerant leaked from the refrigerant circuit (20), based on the amount of refrigerant exergy loss in the circuit-constituting equipment.
- a leakage determination means (53) for determining whether or not refrigerant leakage has occurred in the refrigerant circuit (20) And.
- the leakage index value that changes in accordance with the refrigerant amount leaked from the refrigerant circuit (20) based on the amount of refrigerant exergy loss in the circuit components such as the radiator (34, 37). Calculated. Then, based on the leakage index value, it is determined whether refrigerant leakage has occurred in the refrigerant circuit (20).
- refrigerant leakage occurs in the refrigerant circuit (20)
- a predetermined change appears in the amount of refrigerant exergy loss in the circuit component device.
- a leakage index value that changes in accordance with the refrigerant amount leaked from the refrigerant circuit (20) can be calculated.
- the leakage index value changes in a predetermined manner when refrigerant leakage occurs. For this reason, in the first invention, based on the amount of loss of refrigerant exergy in the circuit component device, a leakage index value that changes in a predetermined manner when refrigerant leakage occurs in the refrigerant circuit (20) is calculated. Diagnosis of refrigerant leakage is performed based on the value.
- Exergy is the maximum work that can be converted into mechanical energy when a substance at a certain pressure and temperature is changed to an environmental state, and is also called “effective energy”.
- the amount of refrigerant exergy loss in the circuit component equipment is “energy that is extra required in the actual refrigeration cycle relative to the theoretical cycle (reverse Carnot cycle) in the circuit component equipment”. Means the amount of exergy lost in the circuit component device. “Exergy loss” can also be expressed as “exergy loss”. The amount of refrigerant exergy loss in the circuit component device will be specifically described.
- the temperature and pressure of the refrigerant are constant during the heat dissipation process of the theoretical cycle.
- the refrigerant exchanges heat with a fluid such as air with a temperature difference, and a friction loss occurs in the pipe. Therefore, extra energy is required for the theoretical cycle. Become.
- the amount of refrigerant exergy loss in the radiator (34, 37) corresponds to the energy required for the theoretical cycle, and represents the amount of loss generated in the radiator (34, 37).
- the temperature and pressure of the refrigerant are constant.
- the refrigerant exchanges heat with a fluid such as air with a temperature difference, and a friction loss occurs in the pipe. Therefore, extra energy is required for the theoretical cycle. Become.
- the amount of refrigerant exergy loss in the evaporator (34, 37) corresponds to the energy required for the theoretical cycle, and represents the magnitude of the loss generated in the evaporator (34, 37).
- the index value calculation means (31) uses the radiator as a leakage index value based on a loss amount of refrigerant exergy in the radiator (34, 37).
- the side index value is calculated, and the leakage determination means (53) determines whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the radiator side index value.
- the radiator side index value is calculated based on the amount of refrigerant exergy loss in the radiator (34, 37).
- the loss of refrigerant exergy in the radiator (34, 37) decreases as the high pressure of the refrigeration cycle decreases. That is, when refrigerant leakage occurs, a predetermined change appears in the amount of refrigerant exergy loss in the radiator (34, 37). For this reason, the diagnosis of the refrigerant leakage is performed based on the radiator side index value calculated based on the amount of loss of refrigerant exergy in the radiator (34, 37).
- the radiator (34, 37) cools and condenses the gas refrigerant, while the index value calculation means (31) includes the radiator (34, 37). ),
- the radiator side index value is calculated without using the amount of loss of exergy in the process in which the refrigerant is in the gas single phase state.
- the radiator side index value is calculated without using the amount of loss of exergy in the process in which the refrigerant is in the gas single phase state in the radiator (34, 37).
- a fourth invention is the loss of exergy in the third invention, wherein the index value calculation means (31) is in a process in which the refrigerant is in a gas-liquid two-phase state in the radiator (34, 37).
- the ratio of the other of the amount and the amount of loss of exergy in the process in which the refrigerant is in the liquid single-phase state in the radiator (34, 37) is calculated as the radiator-side index value.
- the ratio of the other to the “exergy loss amount in the process of being in the state” is calculated as the radiator side index value.
- the latter of “the amount of exergy loss during the process” is greatly reduced. Therefore, when refrigerant leakage occurs, a predetermined change appears in the radiator side index value. For this reason, “the amount of exergy loss in the process where the refrigerant is in the gas-liquid two-phase state in the radiator (34, 37)” and “the refrigerant is in the liquid single-phase state in the radiator (34, 37)”.
- the ratio of the other to one of “the amount of exergy loss in the process” is used as the radiator side index value, and the refrigerant leakage is diagnosed based on the radiator side index value.
- the decompression mechanism (36) is constituted by an expansion valve (36) having a variable opening, and the opening of the expansion valve (36)
- the leakage determination means (53) is based on the radiator side index value. Even if it is not possible to determine that refrigerant leakage has occurred in the circuit (20), refrigerant leakage occurs in the refrigerant circuit (20) when the opening of the expansion valve (36) falls below a predetermined determination opening. It is determined that
- the opening of the expansion valve (36) changes before the radiator side index value.
- the opening degree of the expansion valve (36) is determined as the opening degree. When it becomes below, it determines with the refrigerant
- the index value calculation means (31) is configured such that the amount of refrigerant exergy loss in the radiator (34, 37) and the radiator (34, 37) The other ratio with respect to one of the refrigerant heat dissipation in 37) is calculated as the radiator side index value.
- the ratio of the other of “the amount of refrigerant exergy loss in the radiator (34, 37)” and “the amount of refrigerant released in the radiator (34, 37)” to the radiator side Calculated as an index value.
- the “exhaust loss of refrigerant in the radiator (34,37)” and “radiator (34,37) are accompanied by a decrease in the high pressure of the refrigeration cycle.
- the amount of heat released from the refrigerant in) decreases by substantially the same amount.
- the former and the latter are considerably larger values. For this reason, when refrigerant leakage occurs, a predetermined change appears in the radiator side index value.
- the ratio of the other of “the amount of refrigerant exergy in the radiator (34, 37)” and “the amount of refrigerant released in the radiator (34, 37)” to the other is used as the radiator side index value. Diagnosis of refrigerant leakage is performed based on the radiator side index value.
- the index value calculation means (31) is configured such that the refrigerant exergy loss amount in the radiator (34, 37) and the compressor (30) The ratio of the other to one of the inputs is calculated as the radiator side index value.
- the ratio of the other of “the amount of refrigerant exergy loss in the radiator (34, 37)” and “the input of the compressor (30)” to the other is calculated as the radiator side index value.
- the loss of refrigerant exergy in the radiator (34,37) and the compressor (30) "Input" decreases by approximately the same amount.
- the former and the latter are considerably larger values. For this reason, when refrigerant leakage occurs, a predetermined change appears in the radiator side index value.
- the ratio of the other of “exhaust loss of refrigerant in the radiator (34, 37)” and “input of the compressor (30)” to the other is used as the radiator side index value, and the radiator side index Diagnosis of refrigerant leakage is performed based on the value.
- the refrigerant circuit (20) is controlled so that the low pressure of the refrigeration cycle becomes a constant value, while the index value calculating means ( 31) calculates an evaporator-side index value based on the amount of refrigerant exergy loss in the evaporator (34, 37), and the leakage determination means (53) is based on the evaporator-side index value. It is determined whether or not refrigerant leakage in the refrigerant circuit (20) has progressed to a predetermined level.
- refrigerant leakage it is determined whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the radiator side index value, and refrigerant leakage in the refrigerant circuit (20) is determined based on the evaporator side index value. It is determined whether or not has progressed to a predetermined level.
- the radiator (34, 37) is in a state where the amount of refrigerant leaked from the refrigerant circuit (20) is relatively small.
- the refrigerant exergy loss amount in () changes relatively large, whereas the refrigerant exergy loss amount in the evaporator (34, 37) hardly changes.
- the amount of refrigerant exergy loss in the evaporator (34, 37) changes relatively greatly when the amount of refrigerant leaked from the refrigerant circuit (20) is relatively large.
- the index value calculating means (31) uses the refrigerant index exergy loss amount in the evaporator (34, 37) as the leakage index value.
- the side index value is calculated, and the leakage determination means (53) determines whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the evaporator side index value.
- the evaporator-side index value is calculated based on the loss of refrigerant exergy in the evaporator (34, 37) as the leakage index value.
- the loss of refrigerant exergy in the evaporator (34, 37) decreases as the low pressure of the refrigeration cycle decreases. That is, when refrigerant leakage occurs, a predetermined change appears in the amount of refrigerant exergy loss in the evaporators (34, 37). Therefore, the refrigerant leakage diagnosis is performed based on the evaporator-side index value calculated based on the refrigerant exergy loss amount in the evaporators (34, 37).
- the index value calculation means (31) loses exergy during a process in which the refrigerant is in a gas-liquid two-phase state in the evaporator (34, 37).
- the ratio of the other to one of the amount and the loss of exergy in the process in which the refrigerant is in the gas single phase state in the evaporator (34, 37) is calculated as the evaporator-side index value.
- the ratio of the other to the “exergy loss amount in the process of being in the state” is calculated as the evaporator-side index value.
- the amount of exergy loss in the process of being in the phase state increases.
- the “exergy loss amount in the process in which the refrigerant is in the gas-liquid two-phase state in the evaporators (34, 37)” does not change so much. Therefore, when refrigerant leakage occurs, a predetermined change appears in the radiator side index value. For this reason, “the amount of exergy loss in the process in which the refrigerant is in the gas-liquid two-phase state in the evaporator (34, 37)” and “the refrigerant is in the gas single-phase state in the evaporator (34, 37)”.
- the ratio of the other to “the amount of exergy loss during the process” is used as the evaporator side index value, and the refrigerant leakage is diagnosed based on the evaporator side index value.
- the decompression mechanism (36) is constituted by an expansion valve (36) having a variable opening, and the opening of the expansion valve (36).
- the leakage determination means (53) is based on the evaporator side index value and the refrigerant circuit Even if it is not possible to determine that a refrigerant leak has occurred in (20), if the opening of the expansion valve (36) exceeds a predetermined determination opening, a refrigerant leak will occur in the refrigerant circuit (20). It is determined that
- the opening of the expansion valve (36) exceeds the determination opening, the refrigerant leaks. It is determined that
- the opening degree of the expansion valve (36) is adjusted so that the degree of superheat of the refrigerant flowing out of the evaporator (34, 37) becomes a constant value, the amount of refrigerant leaking from the refrigerant circuit (20) In a relatively small state, the degree of superheat of the refrigerant flowing out of the evaporator (34, 37) hardly changes.
- the ratio of one to the other is almost unchanged. That is, the evaporator side index value hardly changes.
- the opening of the expansion valve (36) increases so that the degree of superheat of the refrigerant flowing out of the evaporator (34, 37) does not increase. Go.
- the opening degree of the expansion valve (36) is determined as the determination opening degree even if it is not possible to determine that refrigerant leakage has occurred based on the evaporator side index value. If it becomes above, it will determine with the refrigerant
- the index value calculation means (31) uses the compressor-side index as the leakage index value based on the loss of refrigerant exergy in the compressor (30). The value is calculated, and the leakage determination means (53) determines whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the compressor side index value.
- the compressor-side index value is calculated based on the amount of refrigerant exergy loss in the compressor (30).
- the amount of refrigerant exergy in the compressor (30) increases as the degree of superheat of the refrigerant sucked into the compressor (30) increases. . That is, when refrigerant leakage occurs, a predetermined change appears in the amount of refrigerant exergy loss in the compressor (30). Therefore, the refrigerant leakage diagnosis is performed based on the compressor-side index value calculated based on the refrigerant exergy loss amount in the compressor (30).
- the index value calculation means (31) uses the refrigerant exergy loss amount in the radiator (34, 37) as the leakage index value and the evaporator (The ratio of the other to the amount of refrigerant exergy loss in 34, 37) is calculated.
- the ratio of the other of “the amount of refrigerant exergy loss in the radiator (34,37)” and “the amount of refrigerant exergy loss in the evaporator (34,37)” to the other is: Calculated as a leakage index value.
- the radiator (34,37) While the amount of refrigerant exergy loss in the refrigerant decreases, the amount of refrigerant exergy loss in the evaporator (34, 37) hardly changes. For this reason, a predetermined change appears in the leakage index value.
- the refrigerant circuit (20) is controlled so that the high pressure of the refrigeration cycle becomes a constant value, for example, when refrigerant leakage occurs, a predetermined change appears in the leakage index value. For this reason, the ratio of the other of “the amount of refrigerant exergy loss in the radiator (34,37)” and “the amount of refrigerant exergy loss in the evaporator (34,37)” to the other is used as the leakage index value.
- the refrigerant leakage is diagnosed based on the leakage index value.
- the refrigerant circuit (20) includes an accumulator for separating the liquid refrigerant from the refrigerant sucked into the compressor (30). 38) is provided, and the accumulator (38) is configured so that the leakage determination means (53) can determine that the refrigerant leakage has occurred in the refrigerant circuit (20) based on the leakage index value. If the difference between the superheat degree of the refrigerant flowing into the refrigerant and the superheat degree of the refrigerant flowing out of the accumulator (38) is greater than or equal to a predetermined suction side reference value, refrigerant leakage has occurred in the refrigerant circuit (20) Do not judge.
- the degree of superheat of the refrigerant flowing into the accumulator (38) and the degree of superheat of the refrigerant flowing out of the accumulator (38) If the difference from the reference value is greater than or equal to the suction side reference value, it is not determined that refrigerant leakage has occurred.
- the difference in the degree of superheat at the inlet / outlet of the accumulator (38) is greater than or equal to the suction side reference value, a relatively large amount of refrigerant has accumulated in the accumulator (38).
- refrigerant leakage has occurred when a relatively large amount of refrigerant has accumulated in the accumulator (38). Not determined.
- a compressor (30), a radiator (34, 37), a pressure reducing mechanism (36), and an evaporator (34, 37) are provided as circuit components, and a refrigerant is circulated to perform a refrigeration cycle.
- the leakage diagnosis device (50) for diagnosing the presence or absence of refrigerant leakage in the refrigerant circuit (20) to be performed is targeted.
- this leak diagnostic apparatus (50) is an index that calculates a leak index value that changes according to the amount of refrigerant leaked from the refrigerant circuit (20), based on the amount of refrigerant exergy loss in the circuit-constituting equipment.
- a value calculating means (31) and a display means (56) for displaying information for leakage diagnosis based on the leakage index value calculated by the index value calculating means (31).
- a leakage index value that changes in accordance with the amount of refrigerant leaked from the refrigerant circuit (20) is calculated based on the amount of refrigerant exergy loss in the circuit configuration device. Then, information for leakage diagnosis based on the leakage index value is displayed on the display means (56). For this reason, it is possible to diagnose the refrigerant leakage by a person who has seen the leakage diagnosis information displayed on the display means (56).
- a compressor (30), a radiator (34, 37), a pressure reducing mechanism (36), and an evaporator (34, 37) are provided as circuit components, and a refrigerant is circulated to perform a refrigeration cycle.
- the refrigeration apparatus (10) includes a leakage diagnosis apparatus (50) that calculates a leakage index value using the amount of refrigerant exergy loss in the circuit component device.
- a compressor (30), a radiator (34, 37), a pressure reduction mechanism (36), and an evaporator (34, 37) are provided as circuit components, and a refrigerant is circulated to perform a refrigeration cycle.
- a leakage diagnosis method for diagnosing the presence or absence of refrigerant leakage with respect to the refrigerant circuit (20) to be performed is targeted.
- this leakage diagnosis method is an index value calculation step for calculating a leakage index value that changes according to the amount of refrigerant leaked from the refrigerant circuit (20) based on the amount of refrigerant exergy loss in the circuit configuration device.
- a leakage determination step of determining whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the leakage index value calculated in the index value calculation step.
- the leakage index value that changes in accordance with the amount of refrigerant leaked from the refrigerant circuit (20) using the amount of refrigerant exergy loss in the circuit components such as the radiator (34, 37). Calculated. Then, based on the leakage index value, it is determined whether refrigerant leakage has occurred in the refrigerant circuit (20).
- a leakage index value that changes in a predetermined manner when refrigerant leakage occurs in the refrigerant circuit (20) is calculated using the amount of loss of refrigerant exergy in the circuit configuration device, and is based on the leakage index value. The refrigerant leakage is diagnosed.
- a leakage index value that changes in a predetermined manner when refrigerant leakage occurs in the refrigerant circuit (20) is calculated.
- a leak diagnosis is performed.
- the refrigerant leakage in the refrigerant circuit (20) can be detected by monitoring the change of the leakage index value, for example. Therefore, the diagnosis of refrigerant leakage using the amount of refrigerant exergy loss in the circuit configuration device of the refrigerant circuit (20) can be realized.
- the refrigerant leakage diagnosis is performed based on the radiator side index value calculated based on the loss amount of the exergy of the refrigerant. Accordingly, it is possible to realize refrigerant leakage diagnosis using the amount of refrigerant exergy loss in the radiator (34, 37).
- the conventional leakage detection method can detect a state in which the refrigerant leakage has progressed to some extent, but in a state where the refrigerant leakage is small, the physical quantity used for detecting the refrigerant leakage (for example, the low pressure of the refrigeration cycle) is Since it hardly changed, it was not possible to detect a state where the degree of refrigerant leakage was small.
- the amount of refrigerant exergy in the radiator (34, 37) appears to some extent even when the amount of refrigerant leaked from the refrigerant circuit (20) is relatively small. Therefore, refrigerant leakage can be detected at a stage where the amount of refrigerant leaked from the refrigerant circuit (20) is relatively small. Therefore, the amount of refrigerant leaking from the refrigerant circuit (20) can be reduced, and when a refrigerant that affects the global environment is used, the influence on the global environment can be reduced.
- the radiator side index value is calculated without using the amount of loss of exergy in the process in which the refrigerant is in the gas single phase state in the radiator (34, 37).
- the amount of refrigerant exergy loss in the entire radiator (34, 37) is represented by the area of the region (c) in FIG.
- the coordinate value of the point B in FIG. 2 is required.
- the coordinate value of point B consists of the temperature and entropy of the refrigerant after the end of the compression stroke in the compressor (30).
- the radiator side index value is an accurate value due to the error in the coordinate value of point B.
- the radiator side index value is calculated without using the amount of loss of exergy in the process in which the refrigerant is in the gas single phase state in the radiator (34, 37).
- the calculation of the radiator side index value does not require the refrigerant temperature and entropy after the end of the compression stroke. Therefore, the radiator side index value can be calculated using only relatively accurate values.
- the radiator side index value is non-dimensional, even if the refrigerant circuits (20) having different rated capacities are compared with each other, the radiator side index value is not much. There is no difference.
- refrigerant leakage without considering the rated capacity of the refrigerant circuit (20). For example, when it is determined whether refrigerant leakage has occurred by comparing the radiator side index value with a predetermined reference value, a common reference value is used between refrigerant circuits (20) having different rated capacities. Diagnosis of refrigerant leakage can be performed.
- the opening degree of the expansion valve (36) when the opening degree of the expansion valve (36) is adjusted so that the degree of supercooling of the refrigerant flowing out of the radiator (34, 37) becomes a constant value, refrigerant leakage occurs. Since the change in the opening degree of the expansion valve (36) appears before the radiator side index value, if the opening degree of the expansion valve (36) is equal to or less than the determination opening degree, it is determined that a refrigerant leak has occurred. ing. Therefore, refrigerant leakage can be detected at a stage where the amount of refrigerant leaking from the refrigerant circuit (20) is small.
- the ratio of the ratio as the radiator side index value is used to diagnose refrigerant leakage based on the radiator side index value.
- This radiator-side index value is a ratio of exergy loss amounts as in the fourth aspect of the invention, and thus is a dimensionless value. For this reason, it is possible to diagnose refrigerant leakage without considering the rated capacity of the refrigerant circuit (20).
- the “heat dissipation amount of the refrigerant in the radiator (34, 37)” is a value reflecting the operating state of the refrigerant circuit (20) (for example, the circulation amount of the refrigerant).
- the amount of refrigerant exergy loss in the radiator (34, 37) varies not only when refrigerant leakage occurs but also depending on the operating state of the refrigerant circuit (20) (for example, the amount of refrigerant circulation). .
- the amount of refrigerant exergy loss in the radiator (34, 37) as it is for diagnosis of refrigerant leakage, it is necessary to consider the operating state of the refrigerant circuit (20).
- the refrigerant leakage diagnosis is performed by comparing the radiator side index value with a predetermined reference value
- the operating state of the refrigerant circuit (20) when the reference value is determined is reproduced, and the heat dissipation in that state is reproduced. It is necessary to compare the vessel index value with the reference value.
- the radiator side index value reflecting the operation state of the refrigerant circuit (20) is used, the refrigerant leakage diagnosis is performed without taking the operation state of the refrigerant circuit (20) into consideration. It can be carried out.
- the refrigerant leakage diagnosis is performed based on the radiator-side index value with this ratio as the radiator-side index value.
- This radiator-side index value is a ratio of exergy loss amounts as in the fourth aspect of the invention, and thus is a dimensionless value. For this reason, it is possible to diagnose refrigerant leakage without considering the rated capacity of the refrigerant circuit (20).
- “input of the compressor (30)” is a value reflecting the operating state of the refrigerant circuit (20) (for example, the circulation amount of the refrigerant).
- the radiator side index value reflecting the operating state of the refrigerant circuit (20) is used for diagnosis of refrigerant leakage. Therefore, similar to the sixth aspect, the refrigerant leakage can be diagnosed without much consideration of the operating state of the refrigerant circuit (20).
- the refrigerant circuit (20) it is determined based on the radiator side index value whether refrigerant leakage has occurred in the refrigerant circuit (20), and based on the evaporator side index value, the refrigerant circuit (20). It is determined whether or not the refrigerant leakage at has progressed to a predetermined level. Therefore, it is possible to detect not only whether or not refrigerant leakage has occurred, but also whether or not refrigerant leakage in the refrigerant circuit (20) has progressed to a predetermined level.
- the refrigerant leakage diagnosis is performed on the basis of the evaporator-side index value calculated based on the refrigerant exergy loss amount. Therefore, the refrigerant leakage diagnosis using the refrigerant exergy loss amount in the evaporator (34, 37) can be realized.
- the opening degree of the expansion valve (36) when the opening degree of the expansion valve (36) is adjusted so that the degree of superheat of the refrigerant flowing out of the evaporator (34, 37) becomes a constant value, the evaporator-side index value Since the change appears in the opening degree of the expansion valve (36) earlier than that, if the opening degree of the expansion valve (36) is equal to or larger than the determination opening degree, it is determined that the refrigerant leaks. Therefore, refrigerant leakage can be detected at a stage where the amount of refrigerant leaking from the refrigerant circuit (20) is small.
- the leakage is diagnosed based on the leakage index value using this ratio as the leakage index value. Since this leakage index value is a ratio between the loss amounts of exergy, it is a dimensionless value. For this reason, similarly to the fourth aspect of the invention, it is possible to diagnose refrigerant leakage without considering the rated capacity of the refrigerant circuit (20).
- refrigerant leakage even if it can be determined that refrigerant leakage has occurred based on the leakage index value, if a relatively large amount of refrigerant has accumulated in the accumulator (38), refrigerant leakage will occur. Not determined to have occurred.
- the air conditioning load decreases, the amount of refrigerant circulating in the refrigerant circuit (20) decreases, and the amount of refrigerant accumulated in the accumulator (38) increases.
- the operating capacity of the compressor (30) increases after the amount of refrigerant accumulated in the accumulator (38) increases, it takes time for the amount of refrigerant in the accumulator (38) to decrease.
- the refrigerant circuit (20) has a short circulation amount of the refrigerant, and thus this state may be erroneously determined as refrigerant leakage.
- the degree of superheat of the refrigerant flowing into the accumulator (38) even when it is determined that the refrigerant leakage has occurred based on the leakage index value.
- the superheat degree of the refrigerant flowing out of the accumulator (38) is equal to or greater than a predetermined suction side reference value, it is determined that a relatively large amount of refrigerant has accumulated in the accumulator (38) Do not judge. Therefore, it is possible to suppress erroneous determination of a state where a relatively large amount of refrigerant is accumulated in the accumulator (38) as refrigerant leakage.
- FIG. 6 is a Ts diagram (temperature-entropy diagram) showing a region used for calculating a leak index value in the leak diagnosis apparatus according to the embodiment.
- FIG. 4 is a Ts diagram showing a region used for calculating a leakage index value in the leakage diagnosis apparatus according to the embodiment, (A) is a diagram of a reference state, and (B) is a diagram of a first progress state. .
- It is a Ts diagram which shows the field used for calculation of a leak index value in a leak diagnostic device concerning an embodiment, (A) is a figure of a standard state, and (B) is a figure of the 2nd progress state. .
- FIG. 1 It is a schematic block diagram of the air conditioning apparatus which concerns on the modification 1 of embodiment. It is a Ts diagram which shows the field used for calculation of a leak index value in a leak diagnostic device concerning modification 1 of an embodiment, (A) is a figure of a standard state, and (B) is the 1st progress state. FIG. It is a Ts diagram which shows the area
- This embodiment is a refrigeration apparatus (10) provided with a leakage diagnosis apparatus (50) according to the present invention.
- the refrigeration apparatus (10) is an air conditioner (10) including an outdoor unit (11) and an indoor unit (13), and performs switching between a cooling operation and a heating operation. It is configured as follows.
- the outdoor unit (11) is provided with an outdoor circuit (21).
- the indoor unit (13) is provided with an indoor circuit (22).
- an outdoor circuit (21) and an indoor circuit (22) are connected by a liquid side connection pipe (23) and a gas side connection pipe (24), thereby performing a refrigerant circuit ( 20) is configured.
- the refrigerant circuit (20) is filled with, for example, a fluorocarbon refrigerant. The amount of refrigerant charged in the refrigerant circuit (20) is determined from the necessary amount of refrigerant during heating operation.
- the outdoor circuit (21) of the outdoor unit (11) includes a compressor (30), an outdoor heat exchanger (34) that constitutes a heat source side heat exchanger, and an expansion valve (36) that constitutes a pressure reducing mechanism. Is provided as a circuit configuration device.
- the outdoor circuit (21) includes a four-way switching valve (33) to which the compressor (30) is connected, a liquid side shut-off valve (25) to which the liquid side communication pipe (23) is connected, and a gas side.
- a gas-side stop valve (26) to which the communication pipe (24) is connected is provided.
- the compressor (30) is a high-pressure dome type compressor in which the inside of a sealed container-like casing is filled with a compressed refrigerant.
- the discharge side of the compressor (30) is connected to the first port (P1) of the four-way switching valve (33) via the discharge pipe (40).
- the suction side of the compressor (30) is connected to the third port (P3) of the four-way switching valve (33) via the suction pipe (41).
- the suction pipe (41) is provided with an airtight container-like accumulator (38).
- the outdoor heat exchanger (34) is a cross-fin type fin-and-tube heat exchanger. Outdoor air is supplied to the outdoor heat exchanger (34) by an outdoor fan (12) provided in the vicinity of the outdoor heat exchanger (34). In the outdoor heat exchanger (34), heat is exchanged between the outdoor air and the refrigerant.
- the outdoor fan (12) can adjust the air volume in multiple stages.
- the outdoor heat exchanger (34) is connected to the fourth port (P4) of the four-way selector valve (33).
- the other end of the outdoor heat exchanger (34) is connected to the liquid side shut-off valve (25) via the liquid pipe (42).
- the liquid pipe (42) is provided with an expansion valve (36) having a variable opening and a receiver (39) in a sealed container shape.
- the second port (P2) of the four-way switching valve (33) is connected to the gas side shut-off valve (26).
- the four-way selector valve (33) is in a first state in which the first port (P1) and the second port (P2) communicate with each other and the third port (P3) and the fourth port (P4) communicate with each other (FIG. 1). And a second state (FIG. 1) in which the first port (P1) and the fourth port (P4) communicate with each other and the second port (P2) and the third port (P3) communicate with each other.
- the state indicated by a broken line) can be switched.
- a pair of suction temperature sensors (45a) and a suction pressure sensor (46a) are provided on the suction side of the compressor (30).
- a pair of discharge temperature sensors (45b) and a discharge pressure sensor (46b) are provided on the discharge side of the compressor (30).
- An outdoor gas temperature sensor (45c) is provided on the gas side of the outdoor heat exchanger (34).
- An outdoor liquid temperature sensor (45d) is provided on the liquid side of the outdoor heat exchanger (34).
- An outdoor temperature sensor (18) is provided upstream of the outdoor fan (12).
- an indoor heat exchanger (37) that constitutes a use side heat exchanger is provided as a circuit component device.
- the indoor heat exchanger (37) is configured by a cross fin type fin-and-tube heat exchanger.
- Indoor air is supplied to the indoor heat exchanger (37) by an indoor fan (14) provided in the vicinity of the indoor heat exchanger (37).
- the indoor fan (14) can adjust the air volume in multiple stages.
- an air filter is provided between the air inlet opening in the room and the indoor fan (14) (not shown).
- an indoor liquid temperature sensor (45e) is provided on the liquid side of the indoor heat exchanger (37).
- An indoor gas temperature sensor (45f) is provided on the gas side of the indoor heat exchanger (37).
- An indoor temperature sensor (19) is provided upstream of the indoor fan (14).
- the various sensors (18, 45, 46) of the outdoor unit (11) and the various sensors (19, 45, 46) of the indoor unit (13) described above calculate index values of the leak diagnosis device (50) described later. It may be considered as a part of the means (31) or may be considered as a part of the refrigeration apparatus (10).
- the refrigeration apparatus (10) of the present embodiment includes a leakage diagnosis apparatus (50) according to the present invention.
- the leak diagnosis device (50) is configured to perform a leak detection operation for detecting whether or not a refrigerant leak has occurred in the refrigerant circuit (20).
- the leakage detection operation is an operation for detecting that the refrigerant is decreasing from the reference state in which no refrigerant leakage occurs in the refrigerant circuit (20).
- the leakage diagnosis device (50) includes a refrigerant state detection unit (51), an exergy calculation unit (52), and a leakage determination unit (53).
- the refrigerant state detection unit (51) and the exergy calculation unit (52) constitute an index value calculation unit (31), and the leak determination unit (53) constitutes a leak determination unit (53). .
- the refrigerant state detection unit (51) includes the refrigerant temperature and entropy (coordinate values of point A in FIG. 2) at the inlet of the compressor (30) (the outlet of the evaporator (34, 37)), and the compressor (30). Temperature and entropy (the coordinate value of point B in FIG. 2) at the outlet of the condenser (the inlet of the condenser (34,37)) and the inlet of the expansion valve (36) (the outlet of the condenser (34,37)) Refrigerant temperature and entropy (coordinate value of point E in FIG. 2) and refrigerant temperature and entropy (coordinate value of point G in FIG.
- the exergy calculation unit (52) uses the refrigerant temperature and entropy obtained by the refrigerant state detection unit (51) to use the compressor (30), the condenser (34, 37), and the evaporator (34, 37). ) Is detected, and a leakage index value that changes in accordance with the refrigerant amount leaked from the refrigerant circuit (20) is calculated using the exergy loss amount.
- the exergy calculation unit (52) uses, as the leakage index value, the radiator side index value using the amount of refrigerant exergy loss in the condenser (34, 37) and the refrigerant excel in the evaporator (34, 37). An evaporator-side index value using the amount of lost energy and a compressor-side index value using the amount of loss of refrigerant exergy in the compressor (30) are calculated.
- exergy analysis thermodynamic analysis
- the loss amount of the exergy of the refrigerant in the circuit component device represents the magnitude of the loss generated in the circuit component device (loss value in the circuit component device).
- the exergy calculation unit (52) uses the refrigerant temperature and entropy obtained by the refrigerant state detection unit (51) to use the refrigerant exergy loss amount ⁇ E (in the condenser (34, 37). c), a refrigerant exergy loss amount ⁇ E (e) in the evaporator (34, 37), and a refrigerant exergy loss amount ⁇ E (b) in the compressor (30).
- the exergy calculation unit (52) uses the refrigerant temperature and entropy obtained by the refrigerant state detection unit (51) to input the input (input power) ⁇ E (a) of the compressor (30) and the condenser The refrigerant heat release amount ⁇ E (a + g) at (34, 37) is detected.
- the compressor (30) the exergy of the refrigerant increases due to the input ⁇ E (a) of the compressor (30), but the exergy of the refrigerant is lost due to mechanical loss and heat dissipation loss.
- the exergy calculation unit (52) uses, as the first radiator side index value, the amount of refrigerant exergy loss in the condenser (34, 37) with respect to the “input ⁇ E (a) of the compressor (30)”.
- the exergy calculation unit (52) uses, as the second radiator side index value, “the refrigerant heat release amount ⁇ E (a + g) in the condenser (34,37)” to “the refrigerant in the condenser (34,37)”.
- the exergy calculation unit (52) outputs the refrigerant exergy loss ⁇ E (e) in the evaporator (34, 37) as an evaporator-side index value.
- the exergy calculating unit (52) outputs the refrigerant exergy loss ⁇ E (b) in the compressor (30) as it is as the compressor-side index value.
- the exergy loss ⁇ E (e) in the process in which the refrigerant is in the gas single-phase state in the evaporator (34, 37) can be used as the evaporator-side index value.
- the leakage determination unit (53) determines whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the leakage index value calculated by the exergy calculation unit (52). Specifically, the leakage determination unit (53) uses the leakage index value output from the exergy calculation unit (52) and the value of the reference state (reference value) where no refrigerant leakage occurs in the refrigerant circuit (20). Thus, it is determined whether or not refrigerant leakage has occurred in the refrigerant circuit (20).
- the leakage determination unit (53) determines whether or not refrigerant leakage has occurred based on the radiator-side index value, and based on the evaporator-side index value, the refrigerant leakage is at a predetermined level (circuit due to insufficient refrigerant). It is determined whether or not it has progressed to a level at which the component equipment may be damaged.
- the leakage determination unit (53) includes a memory for storing a reference value of each leakage index value.
- the reference state value of the ratio of “loss of refrigerant exergy in the condenser (34, 37)” to “input of the compressor (30)” is stored as the first reference value R1 (0).
- the value of the reference state of the ratio of “the amount of refrigerant exergy loss in the condenser (34,37)” to the “heat dissipation amount of the refrigerant in the condenser (34,37)” is the second reference value R2 (0)
- the reference value of the refrigerant exergy loss amount in the evaporator (34, 37) is stored as the third reference value, and the reference value of the refrigerant exergy loss amount in the compressor (30) Is stored as the fourth reference value.
- the leakage determination unit (53) determines whether or not refrigerant leakage has occurred based on a change in which the refrigerant exergy loss ⁇ E (c) in the condenser (34, 37) is smaller than that in the reference state. judge. Specifically, the leakage determination unit (53) determines whether the refrigerant leakage is based on the rate of change of the first radiator side index value from the reference state and the rate of change of the second radiator side index value from the reference state. Determine whether it has occurred. In this determination, only one of the change rate from the reference state of the first radiator side index value and the change rate from the reference state of the second radiator side index value may be used.
- the leakage determination unit (53) detects that the refrigerant exergy loss ⁇ E (e) in the evaporator (34, 37) is larger than that in the reference state and the refrigerant exergy in the compressor (30). It is determined whether or not the refrigerant leakage has progressed to a predetermined level on the basis of both of the change in which the loss amount ⁇ E (b) becomes larger than that in the reference state. Specifically, the leakage determination unit (53) sets the refrigerant leakage to a predetermined level based on the rate of change of the evaporator-side index value from the reference state and the rate of change of the compressor-side index value from the reference state. It is determined whether it is progressing to.
- the refrigeration apparatus (10) is configured to be able to switch between cooling operation and heating operation by a four-way switching valve (33).
- the four-way switching valve (33) is set to the second state.
- the outdoor heat exchanger (34) serves as a condenser and the indoor heat exchanger (37) serves as an evaporator.
- a compression refrigeration cycle is performed.
- the operating frequency of the compressor (30) is controlled so that the value of the low pressure of the refrigeration cycle (detected value of the suction pressure sensor (46a)) becomes a constant value, and the indoor heat exchanger (37)
- the opening degree of the expansion valve (36) is adjusted so that the degree of superheat (superheat) of the refrigerant at the outlet becomes a predetermined target value (for example, 5 ° C.).
- the refrigerant compressed by the compressor (30) is condensed by exchanging heat with outdoor air in the outdoor heat exchanger (34).
- the refrigerant condensed in the outdoor heat exchanger (34) is depressurized when passing through the expansion valve (36), and then is evaporated by exchanging heat with indoor air in the indoor heat exchanger (37).
- the refrigerant evaporated in the indoor heat exchanger (37) is compressed again by the compressor (30).
- the four-way switching valve (33) is set to the first state.
- the outdoor heat exchanger (34) serves as an evaporator and the indoor heat exchanger (37) serves as a condenser.
- a compression refrigeration cycle is performed.
- the operating frequency of the compressor (30) is controlled so that the value of the high pressure of the refrigeration cycle (detected value of the discharge pressure sensor (46b)) becomes a constant value, and the indoor heat exchanger (37)
- the opening degree of the expansion valve (36) is adjusted so that the degree of subcooling of the refrigerant at the outlet (subcool) becomes a predetermined target value (for example, 5 ° C).
- the refrigerant compressed by the compressor (30) is condensed by exchanging heat with indoor air in the indoor heat exchanger (37).
- the refrigerant condensed in the indoor heat exchanger (37) is decompressed when passing through the expansion valve (36), and thereafter evaporates by exchanging heat with outdoor air in the outdoor heat exchanger (34).
- the refrigerant evaporated in the outdoor heat exchanger (34) is compressed again by the compressor (30).
- the leak diagnosis device (50) performs a leak detection operation during cooling operation or heating operation.
- the leak diagnosis apparatus (50) performs a leak detection operation at a predetermined control cycle, for example.
- the leakage detection operation during the cooling operation will be described.
- a first step of detecting the temperature and entropy of the refrigerant at a predetermined position of the refrigerant circuit (20) is performed.
- the predetermined positions of the refrigerant circuit (20) are the inlet and outlet of the compressor (30) and the inlet and outlet of the expansion valve (36).
- the refrigerant state detector (51) detects the measured value of the suction temperature sensor (45a) as the temperature of the refrigerant at the inlet of the compressor (30). Further, the refrigerant state detection unit (51) calculates the entropy of the refrigerant at the inlet of the compressor (30) using the measurement value of the suction temperature sensor (45a) and the measurement value of the suction pressure sensor (46a). Thereby, the coordinate value of the point A in the Ts diagram shown in FIG. 2 is obtained.
- the refrigerant state detection unit (51) detects the measured value of the discharge temperature sensor (45b) as the refrigerant temperature at the outlet of the compressor (30). Further, the refrigerant state detection unit (51) calculates the entropy of the refrigerant at the outlet of the compressor (30) using the measurement value of the discharge temperature sensor (45b) and the measurement value of the discharge pressure sensor (46b). Thereby, the coordinate value of the point B in the Ts diagram shown in FIG. 2 is obtained.
- the refrigerant state detection unit (51) detects the measured value of the outdoor liquid temperature sensor (45d) as the refrigerant temperature at the inlet of the expansion valve (36). Further, the refrigerant state detection unit (51) calculates the entropy of the refrigerant at the inlet of the expansion valve (36) using the measured value of the outdoor liquid temperature sensor (45d) and the measured value of the discharge pressure sensor (46b). In calculating the entropy of the refrigerant at the inlet of the expansion valve (36), the measured value of the discharge pressure sensor (46b) is assumed that the pressure at the inlet of the expansion valve (36) is equal to the pressure at the outlet of the compressor (30). Is used. Thereby, the coordinate value of the point E in the Ts diagram shown in FIG. 2 is obtained.
- the refrigerant state detector (51) detects the measured value of the indoor liquid temperature sensor (45e) as the refrigerant temperature at the outlet of the expansion valve (36).
- the refrigerant state detector (51) calculates the entropy of the refrigerant at the outlet of the expansion valve (36) using the measured value of the indoor liquid temperature sensor (45e) and the measured value of the suction pressure sensor (46a).
- the measured value of the suction pressure sensor (46a) assumes that the pressure at the outlet of the expansion valve (36) is equal to the pressure at the inlet of the compressor (30). Is used.
- the enthalpy of the refrigerant at the inlet of the expansion valve (36) is calculated so that entropy can be calculated from the temperature and pressure of the refrigerant. It is assumed that it is equal to the refrigerant enthalpy at the outlet of the expansion valve (36). Thereby, the coordinate value of the point G on the Ts diagram shown in FIG. 2 is obtained.
- the second step constitutes an index value calculation step together with the first step.
- the exergy calculation unit (52) performs the refrigerant exergy loss ⁇ E (c) in the outdoor heat exchanger (34) operating as a condenser and the indoor heat exchanger ( 37) refrigerant exergy loss ⁇ E (e), refrigerant exergy loss ⁇ E (b) in compressor (30), compressor (30) input ⁇ E (a), outdoor heat A refrigerant heat release amount ⁇ E (a + g) in the exchanger (34) is calculated.
- circuit components compressor (30), condenser (34, 37), the amount of refrigerant exergy loss in the expansion valve (36) and the evaporator (34, 37)) can be obtained.
- Th is the temperature of the air sent to the condenser (34, 37) (in the cooling operation, the measured value of the outside air temperature sensor (18)), and Tc is the air sent to the evaporator (34, 37). (In the cooling operation, the measured value of the indoor temperature sensor (19)).
- point A is a point determined from the refrigerant temperature and entropy at the inlet of the compressor (30) (the outlet of the evaporator (34, 37)).
- Point B is a point determined from the refrigerant temperature and entropy at the outlet of the compressor (30) (inlet of the condenser (34, 37)).
- Point E is a point determined from the refrigerant temperature and entropy at the inlet of the expansion valve (36) (outlet of the condenser (34, 37)).
- Point G is a point determined from the refrigerant temperature and entropy at the outlet of the expansion valve (36) (inlet of the evaporators (34, 37)).
- point C is a point where the isobaric line passing through the point B and the saturated vapor line intersect.
- Point D is a point where an isotherm passing through point C and a saturated liquid line intersect.
- Point F is a point where an isoenthalpy line passing through point E intersects with a saturated liquid line.
- Point H is a point where an isotherm passing through point G intersects with a saturated vapor line.
- Point I is a point at which the temperature becomes Tc on an isentropic line passing through point A.
- Point J is a point at which the temperature becomes Th on an isentropic line passing through point A.
- Point K is a point at which the temperature becomes Th on an isentropic line passing through point G.
- Point L is a point at which the temperature becomes Tc on an isentropic line passing through point G.
- Point M is a point at which the temperature becomes Th on an isentropic line passing through point B.
- the point C, the point B, the point E, and the point G, the measured value of the outdoor air temperature sensor (18), and the measured value of the indoor temperature sensor (19) are used to generate the point C.
- D, F, H, I, J, K, L, and M are calculated.
- the input ⁇ E (a) of the compressor (30) is represented by the area of the region (a).
- the refrigerant exergy loss amount ⁇ E (b) in the compressor (30) is represented by the area of the region (b).
- the refrigerant exergy loss amount ⁇ E (c) in the condenser (34, 37) is expressed by the area of the region (c).
- the amount of refrigerant exergy loss ⁇ E (d) in the expansion valve (36) is represented by the area of the region (d).
- the amount of refrigerant exergy loss ⁇ E (e) in the evaporator (34, 37) is represented by the area of the region (e).
- the area (a) is an area obtained by subtracting the area (g) from the entire hatched area.
- the work ⁇ E (f) of the reverse Carnot cycle is represented by the area of the region (f).
- the refrigerant heat release ⁇ E (a + g) in the condenser (34, 37) is in the region below the line from point B to point E through point C and point D, that is, the region (a) (g ) Area is added to the area (total area hatched in FIG. 2).
- the refrigerant endothermic amount ⁇ E (g) in the evaporator (34, 37) is expressed by the area of the area below the line extending from point G to point A to point A, that is, the area of (g).
- the exergy calculation unit (52) uses the coordinate values of the points B, C, D, and E and the measured value Th of the outdoor air temperature sensor (18) to determine the refrigerant in the outdoor heat exchanger (34). The amount of exergy loss ⁇ E (c) is calculated.
- the exergy calculation unit (52) uses the coordinate values of the points A, G, and H and the measured value Tc of the indoor temperature sensor (19) to determine the exergy of the refrigerant in the indoor heat exchanger (37).
- the loss amount ⁇ E (e) is calculated.
- the exergy calculation unit (52) uses the coordinate values of the points A and B and the measured value Th of the outside air temperature sensor (18) to reduce the amount of refrigerant exergy ⁇ E (b in the compressor (30). ) Is calculated.
- the exergy calculation unit (52) calculates the input ⁇ E (a) of the compressor (30) using the coordinate values of the points A, B, C, D, E, G, and H. .
- the exergy calculation unit (52) calculates the heat release amount ⁇ E (a + g) of the refrigerant in the outdoor heat exchanger (34) using the coordinate values of the points B, C, D, and E.
- the exergy calculation unit (52) calculates the area of the area below the line segment connecting the points A and B as the refrigerant exergy loss ⁇ E (b) in the compressor (30). It may be configured.
- the refrigerant exergy loss ⁇ E (b) in the compressor (30) is the change in refrigerant temperature from the inlet to the outlet of the compressor (30), and the refrigerant entropy at the inlet of the compressor (30).
- the exergy calculation unit (52) calculates the amount of refrigerant exergy loss in the outdoor heat exchanger (34) relative to the refrigerant heat release amount ⁇ E (a + g) in the outdoor heat exchanger (34).
- the exergy calculation unit (52) outputs the refrigerant exergy loss ⁇ E (e) in the evaporator (34, 37) as an evaporator-side index value, and the refrigerant exergy loss in the compressor (30).
- the quantity ⁇ E (b) is output as the compressor side index value.
- the third step constitutes a leakage determination step.
- the leakage determination unit (53) reads the first reference value R1 (0) and the second reference value R2 (0) from the memory.
- the leakage determining unit (53) divides the first radiator side index value R1 by the first reference value R1 (0), thereby changing the rate of change (R1 / R) of the first radiator side index value from the reference state. R1 (0)) is calculated.
- the leakage determination unit (53) determines whether or not a first determination condition is satisfied in which the rate of change of the first radiator-side index value from the reference state is equal to or less than a predetermined first decrease determination value.
- the leakage determination unit (53) divides the second radiator-side index value R2 by the second reference value R2 (0), thereby changing the second radiator-side index value from the reference state (R2 / R2 (0)) is calculated.
- the leakage determination unit (53) determines whether or not a second determination condition is satisfied in which the rate of change of the second radiator-side index value from the reference state is equal to or less than a predetermined second decrease determination value.
- the leakage determination unit (53) determines that refrigerant leakage has occurred in the refrigerant circuit (20) when at least one of the first determination condition and the second determination condition is satisfied. On the other hand, the leakage determination unit (53) determines that no refrigerant leakage has occurred in the refrigerant circuit (20) when both the first determination condition and the second determination condition are not satisfied.
- the condensation temperature of the refrigerant in the condenser (34) is lower than that in the reference state. . Since the difference between the refrigerant condensing temperature and the outdoor air temperature in the condenser (34) becomes smaller, the refrigerant temperature at the outlet of the condenser (34) becomes higher than the reference state, and at the outlet of the condenser (34). The degree of supercooling of the refrigerant is smaller than that in the reference state. The entropy of the refrigerant at the inlet and outlet of the expansion valve (36) is greater than that in the reference state.
- the high pressure in the refrigeration cycle is lower than the reference state, but the low pressure in the refrigeration cycle is not much different from the reference state.
- the degree of superheat of the refrigerant at the outlet of the evaporator (37) is not so different from the reference state.
- the change in the refrigerant exergy loss amount ⁇ E (c) in the condenser (34) from the reference state is particularly large.
- the refrigerant exergy loss ⁇ E (c) in the condenser (34) changes. In this case, the refrigerant exergy in the condenser (34) is also changed. Loss amount ⁇ E (c) increases. Therefore, in the present embodiment, it is determined whether or not refrigerant leakage has occurred based on a change in the amount of refrigerant exergy ⁇ E (c) in the condenser (34) that decreases from the reference state.
- the refrigerant exergy loss ⁇ E (c) in the condenser (34) is smaller than that in the reference state because the degree of refrigerant supercooling at the outlet of the condenser (34) is small. This is because in the effective flow path length of the condenser (34), the ratio of the gas-liquid two-phase region with good heat exchange efficiency increases, and the heat exchange efficiency as a whole increases.
- the refrigerant exergy loss amount ⁇ E (e) in the evaporator (37) is slightly smaller than the reference state, and the refrigerant exergy loss amount ⁇ E in the compressor (30). Both (b) and the exergy loss amount ⁇ E (d) of the refrigerant in the expansion valve (36) do not change so much from the reference state.
- the loss amount of refrigerant exergy in the condenser (34, 37) may be used as the radiator side index value as it is.
- coolant leakage has arisen based on the radiator side index value it is not restricted to the above-mentioned method. For example, you may determine with the refrigerant
- the leakage determination unit (53) reads out the third reference value and the fourth reference value from the memory. Then, the leakage determination unit (53) calculates the rate of change of the evaporator-side index value from the reference state by dividing the evaporator-side index value ⁇ E (e) by the third reference value. The leakage determination unit (53) determines whether or not a third determination condition is satisfied in which the rate of change of the evaporator-side index value from the reference state is equal to or greater than a predetermined first increase determination value.
- the leakage determination unit (53) calculates the rate of change of the compressor-side index value from the reference state by dividing the compressor-side index value ⁇ E (b) by the fourth reference value. The leakage determination unit (53) determines whether or not a fourth determination condition is satisfied in which the rate of change of the compressor-side index value from the reference state is equal to or greater than a predetermined second increase determination value.
- the leakage determination unit (53) determines that the refrigerant leakage has occurred based on the radiator side index value, and when both the third determination condition and the fourth determination condition are satisfied, the refrigerant leakage is detected. It determines with progressing to the predetermined level (the level which may damage a circuit structure apparatus by lack of refrigerant
- the condensation temperature of the refrigerant in the condenser (34) is higher than that in the first traveling state. Further lower.
- the refrigerant temperature at the outlet of the condenser (34) becomes higher than that in the first progress state, and the degree of supercooling of the refrigerant at the outlet of the condenser (34) becomes lower than that in the first progress state.
- the entropy of the refrigerant at the inlet and outlet of the expansion valve (36) is further increased compared to the first progress state.
- the high pressure in the refrigeration cycle is further lower than that in the first progress state, and the low pressure in the refrigeration cycle is lower than that in the first progress state.
- the degree of superheat of the refrigerant at the outlet of the evaporator (37) becomes larger than that in the first progress state.
- the amount of refrigerant exergy loss ⁇ E (c) in the condenser (34) is larger than that in the first progress state.
- the refrigerant exergy loss ⁇ E (e) in the evaporator (37) does not change so much.
- the refrigerant circuit (20) is controlled so that the low pressure of the refrigeration cycle becomes a constant value, the refrigerant exergy loss ⁇ E (e) in the evaporator (37) hardly changes.
- the compressor (30) is deteriorated, the refrigerant circuit (20) is controlled so that the degree of superheat of the refrigerant flowing out of the evaporator (37) becomes a constant value.
- the amount of refrigerant exergy loss ⁇ E (b) does not change so much.
- the refrigerant exergy loss amount ⁇ E (e) in the evaporator (37) increases from the reference state, and the refrigerant exergy loss amount ⁇ E (b in the compressor (30). ) Is increased from the reference state, it is determined whether or not the refrigerant leakage has progressed to a predetermined level.
- the method for determining whether or not refrigerant leakage has occurred based on the respective leakage index values of the evaporator-side index value and the compressor-side index value is not limited to the above-described method. For example, when the condition that the leakage index value exceeds a predetermined determination threshold is satisfied, it may be determined that the refrigerant leakage has progressed to a predetermined level. Further, when the condition that the average value of the leakage index values in a predetermined period (for example, one month) exceeds a predetermined determination threshold is satisfied, it may be determined that the refrigerant leakage has progressed to a predetermined level. .
- a leakage index value that changes in a predetermined manner when refrigerant leakage occurs in the refrigerant circuit (20) is calculated, and based on the leakage index value Diagnosis of refrigerant leakage is performed.
- the refrigerant leakage in the refrigerant circuit (20) can be detected by monitoring the change of the leakage index value, for example. Therefore, the diagnosis of refrigerant leakage using the amount of refrigerant exergy loss in the circuit configuration device of the refrigerant circuit (20) can be realized.
- the condenser (34, 37) even in a state where the amount of refrigerant leaked from the refrigerant circuit (20) is relatively small.
- the condenser (34, 37) Shows a large change in the amount of refrigerant exergy loss. For this reason, refrigerant leakage can be detected at a stage where the amount of refrigerant leaked from the refrigerant circuit (20) is small. Then, the amount of refrigerant leaking from the refrigerant circuit (20) can be reduced, and when a refrigerant that affects the global environment is used, the influence on the global environment can be reduced.
- the change from the reference state of the refrigerant exergy loss in the evaporator (34, 37) and the change from the reference state of the refrigerant exergy loss in the compressor (30) Based on both, it is determined whether or not the refrigerant leakage has progressed to a predetermined level. Therefore, it can be more accurately determined whether or not the refrigerant leakage has progressed to a predetermined level.
- refrigerant leakage has occurred in the refrigerant circuit (20) based on the radiator side index value, and the refrigerant is determined based on the evaporator side index value and the compressor side index value. It is determined whether the refrigerant leak in the circuit (20) has progressed to a predetermined level. Therefore, it is possible to detect not only whether or not refrigerant leakage has occurred, but also whether or not refrigerant leakage has progressed to a predetermined level.
- the ratio of the “exhaust loss of refrigerant in the condenser (34, 37)” to the “input of the compressor (30)” is predetermined. Therefore, this ratio is used as the radiator side index value, and the refrigerant leakage is diagnosed based on the radiator side index value.
- the ratio of “the amount of refrigerant exergy loss in the condenser (34, 37)” to “the amount of refrigerant heat released in the condenser (34, 37)” is predetermined.
- radiator side index value is used as the radiator side index value, and the refrigerant leakage is diagnosed based on the radiator side index value. Since these radiator side index values are the ratios between the loss amounts of exergy, they are non-dimensionalized values. For this reason, it is possible to diagnose refrigerant leakage without considering the rated capacity of the refrigerant circuit (20).
- “input of the compressor (30)” is a value reflecting the operating state of the refrigerant circuit (20) (for example, the circulation amount of the refrigerant and the temperature of the outdoor air).
- the “heat dissipation amount of refrigerant in the condenser (34, 37)” is a value reflecting the operating state of the refrigerant circuit (20).
- the radiator side index value reflecting the operating state of the refrigerant circuit (20) is used for diagnosis of refrigerant leakage. Therefore, it is possible to diagnose refrigerant leakage without taking into account the operating state of the refrigerant circuit (20).
- a leakage diagnosis device (50) that uses the amount of loss of refrigerant exergy in the circuit component device is provided to determine whether or not refrigerant leakage has occurred in the refrigerant circuit (20). Yes. Therefore, it is possible to provide a refrigeration apparatus (10) that can perform refrigerant leakage diagnosis using the amount of refrigerant exergy loss in the circuit configuration device of the refrigerant circuit (20).
- FIG. 5 shows the schematic block diagram of the air conditioning apparatus (10) of this modification 1, only one indoor unit (13) is described, and description of other indoor units (13) is omitted.
- an outdoor expansion valve (36a) is provided in the outdoor circuit (21), and each indoor circuit (22) An expansion valve (36b) is provided.
- the leak detection operation of the first modification can also be applied to an air conditioner (10) having one indoor unit (13) as shown in FIG.
- the indoor expansion valve (36b) and the outdoor expansion valve (36a) are constituted by variable-opening electric expansion valves.
- an electric expansion valve having a maximum control pulse value of 480 pulses is used as the outdoor expansion valve (36a).
- the outdoor expansion valve (36a) is set to fully open, and the opening degree of the indoor expansion valve (36b) is a constant value (for example, 5 ° C.) of the superheat of the refrigerant flowing out of the indoor heat exchanger (37). Adjusted to be.
- the opening of the outdoor expansion valve (36a) is adjusted so that the degree of superheat of the refrigerant flowing out of the outdoor heat exchanger (34) becomes a constant value (for example, 5 ° C.).
- the opening degree of (36b) is adjusted so that the degree of supercooling of the refrigerant flowing out from the indoor heat exchanger (37) becomes a constant value (for example, 5 ° C.).
- the leak detection operation during the cooling operation will be described.
- the same first step as in the above embodiment is performed.
- the exergy calculation unit (52) calculates an exergy loss amount ⁇ E (c2) in a process in which the refrigerant is in a gas-liquid two-phase state in the outdoor heat exchanger (34).
- the exergy loss amount ⁇ E (c2) in the process in which the refrigerant is in the gas-liquid two-phase state in the outdoor heat exchanger (34) is represented by the area of the region (c2).
- the exergy calculation unit (52) calculates the area of the area (c2) using the coordinate values of the points C and D and the measured value Th of the outside air temperature sensor (18), thereby exchanging the outdoor heat.
- the amount of exergy loss ⁇ E (c2) in the process in which the refrigerant is in the gas-liquid two-phase state in the vessel (34) is calculated.
- the exergy calculation unit (52) calculates an exergy loss amount ⁇ E (c3) in a process in which the refrigerant is in a liquid single phase state in the outdoor heat exchanger (34). 6 and 7, the exergy loss amount ⁇ E (c3) in the process in which the refrigerant is in the liquid single-phase state in the outdoor heat exchanger (34) is represented by the area of the region (c3). .
- the exergy calculation unit (52) calculates the area of the area (c3) using the coordinate values of the points D and E and the measured value Th of the outside air temperature sensor (18), thereby exchanging the outdoor heat.
- the amount of exergy loss ⁇ E (c3) in the process in which the refrigerant is in the liquid single phase state is calculated in the vessel (34).
- the exergy calculation unit (52) calculates an exergy loss amount ⁇ E (e1) in the process in which the refrigerant is in a gas-liquid two-phase state in the indoor heat exchanger (37). 6 and 7, the exergy loss amount ⁇ E (e1) in the process in which the refrigerant is in the gas-liquid two-phase state in the indoor heat exchanger (37) is represented by the area of the region (e1).
- the exergy calculating unit (52) calculates the area of the area (e1) using the coordinate values of the G point and the H point and the measured value Tc of the indoor temperature sensor (19), thereby exchanging the indoor heat.
- the amount of exergy loss ⁇ E (e1) in the process in which the refrigerant is in the gas-liquid two-phase state in the container (37) is calculated.
- the exergy calculation unit (52) calculates an exergy loss amount ⁇ E (e2) in the process in which the refrigerant is in a gas single phase state in the indoor heat exchanger (37). 6 and 7, the amount of exergy loss ⁇ E (e2) in the process in which the refrigerant is in the gas single-phase state in the indoor heat exchanger (37) is represented by the area of the region (e2). .
- the exergy calculation unit (52) calculates the area of the area (e2) using the coordinate values of the points H and A and the measured value Tc of the indoor temperature sensor (19), thereby exchanging the indoor heat.
- the amount of exergy loss ⁇ E (e2) in the process in which the refrigerant is in the gas single-phase state in the vessel (37) is calculated.
- the exergy loss ⁇ E (c2) in the process in which the refrigerant is in the gas-liquid two-phase state is the loss generated when the refrigerant in the gas-liquid two-phase state flows. Represents size.
- the amount of exergy loss ⁇ E (c3) in the process in which the refrigerant is in the liquid single-phase state represents the amount of loss that occurs when the liquid single-phase refrigerant flows. ing.
- the amount of exergy loss ⁇ E (e1) in the process in which the refrigerant is in the gas-liquid two-phase state in the indoor heat exchanger (37) is the magnitude of the loss that occurs when the gas-liquid two-phase refrigerant flows. Represents.
- the amount of exergy loss ⁇ E (e1) in the process in which the refrigerant is in the gas single-phase state in the indoor heat exchanger (37) represents the amount of loss that occurs when the gas single-phase refrigerant flows. ing.
- the memory of the leakage determination unit (53) includes “outdoor energy loss” for “the amount of loss of exergy in the process in which the refrigerant is in a gas-liquid two-phase state in the outdoor heat exchanger (34)” during the cooling operation.
- the reference value of the ratio of the “exergy loss amount in the process in which the refrigerant is in the liquid single-phase state in the heat exchanger (34)” is stored as the fifth reference value.
- this memory has “in the indoor heat exchanger (37) the amount of loss of exergy in the process in which the refrigerant is in a gas-liquid two-phase state in the indoor heat exchanger (37)” during the cooling operation.
- the value of the reference state of the ratio of the “exergy loss amount in the process in which the refrigerant is in the gas single phase state” is stored as the sixth reference value.
- the leakage determination unit (53) reads out the fifth reference value and the sixth reference value from the memory. Then, the leakage determination unit (53) calculates the rate of change of the radiator side index value from the reference state by dividing the radiator side index value by the fifth reference value. The leakage determination unit (53) determines whether or not a fifth determination condition is satisfied in which the rate of change of the radiator side index value from the reference state is equal to or less than a predetermined first determination value. The leakage determination unit (53) determines that refrigerant leakage has occurred in the refrigerant circuit (20) when the fifth determination condition is satisfied. On the other hand, when the fifth determination condition is not satisfied, the leakage determination unit (53) determines that no refrigerant leakage has occurred in the refrigerant circuit (20).
- the leakage determination unit (53) calculates the rate of change from the reference state of the evaporator-side index value by dividing the evaporator-side index value by the sixth reference value.
- the leakage determination unit (53) determines whether or not a sixth determination condition is satisfied in which the rate of change of the evaporator-side index value from the reference state is equal to or greater than a predetermined second determination value.
- the leakage determination unit (53) determines that the refrigerant leakage has progressed to a predetermined level (a level at which the circuit component device may be damaged due to insufficient refrigerant).
- the operation frequency of the compressor (30) is controlled so that the value of the low pressure of the refrigeration cycle (the detection value of the suction pressure sensor (46a)) becomes a constant value. Since the control is performed, in the first progress state in which the amount of refrigerant leaked from the refrigerant circuit (20) is relatively small, there is almost no change in the amount of refrigerant exergy loss in the evaporator (34, 37). In the first traveling state, a relatively large change appears in the amount of refrigerant exergy loss in the condensers (34, 37).
- high-pressure constant control is performed to control the operating frequency of the compressor (30) so that the high-pressure value of the refrigeration cycle (detected value of the discharge pressure sensor (46b)) becomes a constant value.
- the amount of refrigerant exergy in the condenser (34, 37) is relatively large. Change appears. And if a refrigerant
- refrigerant leakage it is determined whether or not refrigerant leakage has occurred in the refrigerant circuit (20) based on the evaporator side index value, and refrigerant leakage in the refrigerant circuit (20) is determined based on the radiator side index value. It is possible to determine whether or not the level has progressed to the level.
- the exergy calculation unit (52) calculates an exergy loss amount ⁇ E (e1) in the process in which the refrigerant is in a gas-liquid two-phase state in the outdoor heat exchanger (34). To do.
- the exergy calculation unit (52) calculates an exergy loss amount ⁇ E (e2) in the process in which the refrigerant is in a gas single-phase state in the outdoor heat exchanger (34).
- the exergy calculation unit (52) uses, as the evaporator-side index value, “the amount of exergy loss ⁇ E (e1) in the process in which the refrigerant is in a gas-liquid two-phase state in the outdoor heat exchanger (34)”.
- R3 (R3 ⁇ E (e2) / ⁇ E (e1)) of the “exergy loss amount ⁇ E (e2) in the process where the refrigerant is in a single-phase state in the outdoor heat exchanger (34)”
- the ratio R3 is output.
- the memory of the leakage determination unit (53) includes “outdoor energy loss amount in the process in which the refrigerant is in a gas-liquid two-phase state in the outdoor heat exchanger (34)” during the heating operation.
- the value of the reference state of the ratio of the “exergy loss amount in the process in which the refrigerant is in the gas single phase state in the heat exchanger (34)” is stored as the seventh reference value.
- the leakage determination unit (53) reads the seventh reference value from the memory. And the leak determination part (53) calculates the rate of change from the reference state of the evaporator side index value by dividing the evaporator side index value calculated in the second step by the seventh reference value. The leakage determination unit (53) determines whether or not a seventh determination condition is satisfied in which the rate of change of the evaporator-side index value from the reference state is equal to or greater than a predetermined third determination value. The leakage determination unit (53) determines that refrigerant leakage has occurred in the refrigerant circuit (20) when the seventh determination condition is satisfied. On the other hand, the leakage determination unit (53) determines that no refrigerant leakage has occurred in the refrigerant circuit (20) when the seventh determination condition is not satisfied.
- the radiator side index value is calculated without using the amount of loss of exergy in the process in which the refrigerant is in the gas single-phase state in the condenser (34, 37). For this reason, the temperature and entropy of the refrigerant after the end of the compression stroke are not required for calculating the radiator side index value. Therefore, the radiator side index value can be calculated using only relatively accurate values.
- the radiator side index value is calculated without using the amount of exergy loss in the process in which the refrigerant is in the gas single phase state in the condenser (34, 37). Also good.
- the amount of exergy loss in the process in which the refrigerant is in a gas-liquid two-phase state in the condenser (34, 37) A predetermined change appears in the ratio of the “loss of exergy in the process where the refrigerant is in a liquid single phase state in the condenser (34, 37)”.
- the refrigerant leakage is diagnosed based on the vessel side index value.
- the “evaporator (34, 37) in the process in which the refrigerant is in a gas-liquid two-phase state in the evaporator (34, 37)” 37) a predetermined change appears in the ratio of the “exergy loss amount in the process in which the refrigerant is in the gas single phase state”. Based on the evaporator-side index value, this ratio is used as the evaporator-side index value.
- the refrigerant leakage is diagnosed.
- the radiator-side index value and the evaporator-side index value are ratios between exergy loss amounts, and thus become dimensionless values. For this reason, it is possible to diagnose refrigerant leakage without considering the rated capacity of the refrigerant circuit (20).
- the fifth to seventh reference values can be shared among the refrigeration apparatuses (10) having different rated capacities.
- the leakage determination unit (53) causes the first opening of the indoor expansion valve (36b) to be greater than or equal to a predetermined first determination opening (for example, 1500 pulses). It is determined whether or not the opening condition is satisfied.
- the leakage determination unit (53) satisfies the first opening condition even when the sixth determination condition is not satisfied (when it is not possible to determine that refrigerant leakage has occurred based on the evaporator-side index value). In this case, it is determined that refrigerant leakage has occurred in the refrigerant circuit (20).
- the first determination opening is a value larger than the opening of the indoor expansion valve (36b) (a value around 500 pulses) assumed in a state where no refrigerant leaks, and no refrigerant leaks. Then, it is a value that cannot be.
- the refrigerant circuit (20) When the amount of refrigerant leaked from the refrigerant is relatively small, the degree of superheat of the refrigerant flowing out of the indoor heat exchanger (37) hardly changes. For this reason, the evaporator side index value hardly changes.
- the opening of the indoor expansion valve (36b) is increased so that the degree of superheat of the refrigerant flowing out of the indoor heat exchanger (37) does not increase. It will become. That is, when refrigerant leakage occurs, the opening of the expansion valve (36) changes before the evaporator-side index value. In the second modification, paying attention to such points, even if it is not possible to determine that refrigerant leakage has occurred based on the evaporator-side index value, the opening of the indoor expansion valve (36b) is the first. If it is equal to or greater than the determination opening, it is determined that refrigerant leakage has occurred. Therefore, refrigerant leakage can be detected at a stage where the amount of refrigerant leaking from the refrigerant circuit (20) is small.
- the leakage determination unit (53) determines that the opening of the outdoor expansion valve (36a) is greater than or equal to a predetermined second determination opening (for example, 400 pulses). It is determined whether or not the 2 opening condition is satisfied.
- the leakage determination unit (53) satisfies the second opening condition even when the seventh determination condition is not satisfied (when it is not possible to determine that refrigerant leakage has occurred based on the evaporator-side index value). In this case, it is determined that refrigerant leakage has occurred in the refrigerant circuit (20).
- the second determination opening is larger than the opening (50-100 pulses) of the outdoor expansion valve (36a) assumed in a state where no refrigerant leaks, and in a state where no refrigerant leaks. It is a value that cannot be.
- the opening degree of the indoor expansion valve (36b) can be used to determine whether or not refrigerant leakage has occurred during heating operation.
- the exergy calculation unit (52) sets the value of the exergy in the process in which the refrigerant is in a gas-liquid two-phase state in the indoor heat exchanger (37) as the radiator side index value.
- the ratio of “the amount of loss of exergy in the process in which the refrigerant is in the liquid single phase state in the indoor heat exchanger (37)” to the “loss amount” is calculated.
- a leak determination part (53) determines whether the 8th determination conditions from which the change rate from the reference
- the leakage determination unit (53) determines that refrigerant leakage has occurred in the refrigerant circuit (20) when the eighth determination condition is satisfied.
- the leakage determination unit (53) determines whether or not a third opening condition is established in which the opening of the indoor expansion valve (36b) is equal to or smaller than a predetermined third determination opening (for example, 100 pulses). Determine whether.
- the leakage determination unit (53) satisfies the third opening degree condition even when the eighth determination condition is not satisfied (when it is not possible to determine that refrigerant leakage has occurred based on the radiator side index value). In this case, it is determined that refrigerant leakage has occurred in the refrigerant circuit (20).
- the third determination opening is a value smaller than the opening of the indoor expansion valve (36b) (a value around 500 pulses) assumed in a state where no refrigerant leaks, and no refrigerant leaks. Then, it is a value that cannot be.
- the refrigerant circuit (20) When supercooling control is performed to adjust the opening of the indoor expansion valve (36b) so that the supercooling degree of the refrigerant flowing out of the indoor heat exchanger (37) becomes a constant value, the refrigerant circuit (20) When the amount of the leaked refrigerant is relatively small, the degree of supercooling of the refrigerant flowing out from the indoor heat exchanger (37) hardly changes. For this reason, the radiator side index value hardly changes. On the other hand, when the refrigerant flowing through the indoor heat exchanger (37) decreases due to refrigerant leakage, the opening of the indoor expansion valve (36b) is set so that the degree of supercooling of the refrigerant flowing out of the indoor heat exchanger (37) does not decrease. It gets smaller.
- the opening degree of the indoor expansion valve (36b) is third. If it is less than the determination opening, it is determined that refrigerant leakage has occurred. Therefore, refrigerant leakage can be detected at a stage where the amount of refrigerant leaking from the refrigerant circuit (20) is small.
- Modification 3 of Embodiment A modification 3 of the embodiment will be described.
- the leakage diagnosis device (50) of the second modification the method for determining whether or not the refrigerant leakage in the refrigerant circuit (20) has progressed to a predetermined level is different from the above embodiment.
- the exergy calculation unit (52) uses the “outdoor heat exchanger as a leakage index value for the refrigerant exergy loss ⁇ E (e) in the indoor heat exchanger (37)”.
- the leakage determination unit (53) includes the amount of refrigerant exergy in the outdoor heat exchanger (34) relative to the amount of refrigerant exergy in the indoor heat exchanger (37) during the cooling operation. ”Ratio reference state value is stored as the eighth reference value.
- the leakage determination unit (53) reads the eighth reference value from the memory. Then, the leakage determination unit (53) calculates the rate of change of the leakage index value from the reference state by dividing the leakage index value calculated in the second step by the eighth reference value.
- the leakage determination unit (53) determines whether or not an eighth determination condition is satisfied in which the rate of change of the leakage index value from the reference state is equal to or less than a predetermined fifth determination value.
- the leakage determination unit (53) determines that the refrigerant leakage in the refrigerant circuit (20) has progressed to a predetermined level when the eighth determination condition is satisfied.
- the ratio of the “exhaust loss of refrigerant in the condenser (34, 37)” to the “exhaust loss of refrigerant in the evaporator (34, 37)” is set as the leakage index value.
- the refrigerant leakage is diagnosed based on the leakage index value. Since this leakage index value is a ratio between the loss amounts of exergy, it is a dimensionless value. For this reason, it is possible to diagnose refrigerant leakage without considering the rated capacity of the refrigerant circuit (20).
- the amount of refrigerant accumulated in the accumulator (38) increases.
- the operating capacity of the compressor (30) increases after the amount of refrigerant accumulated in the accumulator (38) increases, it takes time for the amount of refrigerant in the accumulator (38) to decrease. Therefore, until the refrigerant amount in the accumulator (38) decreases, the refrigerant circuit (20) has a short circulation amount of the refrigerant, and thus this state may be erroneously determined as refrigerant leakage.
- the degree of superheat of the refrigerant flowing into the accumulator (38) If the difference between the superheat of the refrigerant flowing out of the accumulator (38) exceeds the specified suction side reference value, it is judged that a relatively large amount of refrigerant has accumulated in the accumulator (38), and the refrigerant is judged to be leaking. do not do. Therefore, it is possible to suppress erroneous determination of a state where a relatively large amount of refrigerant is accumulated in the accumulator (38) as refrigerant leakage.
- the refrigerant circuit (20) is provided with an inlet temperature sensor (17) in the refrigerant pipe connected to the inlet of the accumulator (38) as shown in FIG. If the leakage determination unit (53) is in the cooling operation, for example, the refrigerant that flows into the accumulator (38) by subtracting the measured value of the intake temperature sensor (45a) from the measured value of the inlet temperature sensor (17) And the difference between the degree of superheat of the refrigerant from the accumulator (38) to the compressor (30).
- the leak diagnosis apparatus (50) may be provided with the data processing part (55) which averages the leak index value which the exergy calculation part (52) output, as shown in FIG. .
- the leakage diagnosis device (50) is installed at a position away from the refrigeration device (10).
- the leakage diagnosis apparatus (50) is connected to a control board provided in the refrigeration apparatus (10) through, for example, a network line (57).
- the leak diagnosis device (50) receives the measured values of all temperature sensors (16-19, 45, 63) and pressure sensors (46) provided in the refrigeration device (10) via the control board.
- the data management unit (54) is provided.
- the refrigerant state detection unit (51) uses the measurement values of the temperature sensors (16-19, 45, 63) and the pressure sensor (46) input to the data management unit (54), as in the above embodiment, The refrigerant temperature and entropy are detected at each position of the inlet of the compressor (30), the outlet of the compressor (30), the inlet of the expansion valve (36), and the outlet of the expansion valve (36).
- the exergy calculation unit (52) calculates the leakage index value as in the above embodiment.
- the exergy calculation unit (52) calculates the leakage index value once a day, for example, and outputs it to the data processing unit (55).
- the exergy calculation unit (52) for example, “an outdoor heat exchanger (34) for an exergy loss ⁇ E (c2) in a process in which the refrigerant is in a gas-liquid two-phase state” In 34), the ratio of the exergy loss amount ⁇ E (c3) in the process in which the refrigerant is in the liquid single-phase state is calculated as the leakage index value.
- Data of the leakage index value is accumulated in the data processing unit (55).
- the data processing unit (55) averages the accumulated leakage index values, for example, on a monthly basis, and creates the chart shown in FIG.
- the monitor (56) of the leakage diagnosis apparatus (50) displays a chart created by the data processing unit (55) as leakage diagnosis information.
- the leakage index value averaged on a monthly basis (hereinafter referred to as “monthly average index value”) is visualized.
- the leakage determination unit (53) compares the trend of the monthly average index value of a certain year with the trend of the monthly average index value of the previous year. In addition, it may be determined whether or not refrigerant leakage has occurred in the refrigerant circuit (20).
- the leakage determination unit (53) may determine whether or not refrigerant leakage has occurred in the refrigerant circuit (20) by comparing the monthly average index value with a predetermined reference value. In this case, as shown in FIG. 10, since the monthly average index value varies depending on the month, the reference value may be set to a larger value as the month in which the monthly average index value is expected to increase.
- the monthly average index value may be lower than the reference value from the beginning of the installation of the refrigeration apparatus (10).
- the refrigerant is insufficient because the refrigerant circuit (20) is not filled with a sufficient amount of refrigerant when the refrigeration apparatus (10) is installed, instead of refrigerant leakage. .
- the refrigeration apparatus (10) is not only an air conditioner (10), but also a refrigeration apparatus (10) that cools the inside of a refrigerator for refrigeration or freezing food, indoor air conditioning and cooling, A refrigeration apparatus (10) that performs heating, a refrigeration apparatus (10) with a humidity control function that uses the heat of the refrigerant flowing through the heat exchanger to heat or cool the adsorbent, or a hot water supply function that heats water with a high-pressure refrigerant It may be a refrigeration apparatus (10).
- the refrigeration apparatus (10) may be configured to perform a supercritical cycle in which the high pressure of the refrigeration cycle is higher than the critical pressure of the refrigerant.
- a heat exchanger that serves as a condenser operates as a radiator (gas cooler).
- carbon dioxide is used as the refrigerant.
- the present invention is useful for a leakage diagnosis apparatus, a leakage diagnosis method, and a refrigeration apparatus including the leakage diagnosis apparatus for diagnosing the presence or absence of refrigerant leakage from the refrigerant circuit.
- Air conditioning equipment (refrigeration equipment) 20 Refrigerant circuit 30 Compressor 34 Outdoor heat exchanger (heat radiator, evaporator) 36 Expansion valve (pressure reduction mechanism) 37 Indoor heat exchangers (radiators, evaporators) 50 Leakage diagnosis device 51 Refrigerant state detection unit (index value calculation means) 52 Exergy calculation unit (index value calculation means) 53 Leakage determination unit (leakage determination means)
Abstract
Description
室外ユニット(11)には、室外回路(21)が設けられている。室内ユニット(13)には、室内回路(22)が設けられている。この冷凍装置(10)では、室外回路(21)と室内回路(22)を液側連絡配管(23)及びガス側連絡配管(24)で接続することによって、蒸気圧縮冷凍サイクルを行う冷媒回路(20)が構成されている。冷媒回路(20)には、例えばフロン系の冷媒が充填されている。冷媒回路(20)に充填された冷媒量は、暖房運転時における冷媒の必要量から決められている。
室外ユニット(11)の室外回路(21)には、圧縮機(30)と、熱源側熱交換器を構成する室外熱交換器(34)と、減圧機構を構成する膨張弁(36)とが、回路構成機器として設けられている。また、室外回路(21)には、圧縮機(30)が接続される四路切換弁(33)と、液側連絡配管(23)が接続される液側閉鎖弁(25)と、ガス側連絡配管(24)が接続されるガス側閉鎖弁(26)とが設けられている。
室内ユニット(13)の室内回路(22)には、利用側熱交換器を構成する室内熱交換器(37)が回路構成機器として設けられている。室内熱交換器(37)は、クロスフィン式のフィン・アンド・チューブ型熱交換器により構成されている。室内熱交換器(37)には、室内熱交換器(37)の近傍に設けられた室内ファン(14)によって室内空気が供給される。室内熱交換器(37)では、室内空気と冷媒との間で熱交換が行われる。なお、室内ファン(14)は、風量を複数段階に調節できる。また、室内ユニット(13)では、室内に開口する吸込口と室内ファン(14)との間にエアフィルタが設けられている(図示省略)。
本実施形態の冷凍装置(10)は、本発明に係る漏洩診断装置(50)を備えている。漏洩診断装置(50)は、冷媒回路(20)において冷媒漏れが生じているか否かを検出するための漏洩検出動作を行うように構成されている。漏洩検出動作は、冷媒回路(20)において冷媒漏れが生じていない基準状態から冷媒が減っていることを検出するための動作である。
冷凍装置(10)の運転動作について説明する。この冷凍装置(10)は、四路切換弁(33)によって冷房運転と暖房運転の切り換えを行うことができるように構成されている。
冷房運転では、四路切換弁(33)が第2状態に設定される。そして、この状態で圧縮機(30)の運転が行われると、冷媒回路(20)では、室外熱交換器(34)が凝縮器となって室内熱交換器(37)が蒸発器となる蒸気圧縮冷凍サイクルが行われる。
暖房運転では、四路切換弁(33)が第1状態に設定される。そして、この状態で圧縮機(30)の運転が行われると、冷媒回路(20)では、室外熱交換器(34)が蒸発器となって室内熱交換器(37)が凝縮器となる蒸気圧縮冷凍サイクルが行われる。
漏洩診断装置(50)の動作について説明する。漏洩診断装置(50)は、冷房運転中や暖房運転中に漏洩検出動作を行う。漏洩診断装置(50)は、例えば所定の制御周期で漏洩検出動作を行う。以下では、冷房運転中の漏洩検出動作について説明する。
本実施形態では、回路構成機器における冷媒のエクセルギーの損失量に基づいて、冷媒回路(20)において冷媒漏れが生じると所定の変化をする漏洩指標値が算出され、その漏洩指標値に基づいて冷媒漏れの診断が行われる。冷媒回路(20)における冷媒漏れは、例えば、漏洩指標値の変化を監視することにより検知することが可能である。従って、冷媒回路(20)の回路構成機器における冷媒のエクセルギーの損失量を用いた冷媒漏れの診断を実現することができる。
実施形態の変形例1について説明する。この変形例1の漏洩診断装置(50)は、漏洩検出動作が上記実施形態とは異なっている。なお、この変形例1では、互いに並列に接続された複数台の室内ユニット(13)を備えた空気調和装置(10)を例に説明する。但し、この変形例1の空気調和装置(10)の概略構成図を示す図5では、室内ユニット(13)を1台のみ記載し、他の室内ユニット(13)の記載は省略している。複数台の室内ユニット(13)を備えた空気調和装置(10)では、図5に示すように、室外回路(21)に室外膨張弁(36a)が設けられ、各室内回路(22)に室内膨張弁(36b)が設けられる。なお、この変形例1の漏洩検出動作は、図1に示すような室内ユニット(13)が1台の空気調和装置(10)にも適用可能である。
実施形態の変形例2について説明する。この変形例2の漏洩診断装置(50)は、冷媒漏れが生じているか否かを判定するのに、漏洩指標値に加えて、室内膨張弁(36b)の開度及び室外膨張弁(36a)の開度を利用している。以下では、上記実施形態の変形例1と異なる点について説明する。
実施形態の変形例3について説明する。この変形例2の漏洩診断装置(50)は、冷媒回路(20)における冷媒漏れが所定のレベルにまで進行しているか否かを判定する方法が、上記実施形態とは異なっている。
上記実施形態は、以下の変形例のように構成してもよい。
上記実施形態について、漏洩指標値に基づけば冷媒回路(20)において冷媒漏れが生じていると判定できる場合であっても、アキュームレータ(38)に流入する冷媒の過熱度とアキュームレータ(38)から流出した冷媒の過熱度との差が所定の吸入側基準値以上になる場合は、冷媒回路(20)において冷媒漏れが生じていると判定しないように、漏洩判定部(53)を構成してもよい。
上記実施形態について、漏洩診断装置(50)が、図8に示すように、エクセルギー算出部(52)が出力した漏洩指標値を平均化処理するデータ処理部(55)を備えていてもよい。第2変形例では、漏洩診断装置(50)が、冷凍装置(10)とは離れた位置に設置されている。漏洩診断装置(50)は、例えばネットワーク回線(57)を通じて、冷凍装置(10)に設けられた制御基板に接続されている。漏洩診断装置(50)には、制御基板を介して、冷凍装置(10)に設けられた全ての温度センサ(16-19,45,63)と圧力センサ(46)の計測値が入力されるデータ管理部(54)が設けている。
上記実施形態について、冷凍装置(10)が、空気調和装置(10)だけでなく、食品を冷蔵又は冷凍するための庫内を冷却する冷凍装置(10)、室内の冷暖房と庫内の冷却とを行う冷凍装置(10)、熱交換器を流通する冷媒の熱を吸着剤の加熱又は冷却に用いる調湿機能付きの冷凍装置(10)、或いは、高圧冷媒により水を加熱する給湯機能を有する冷凍装置(10)であってもよい。
上記実施形態について、冷凍装置(10)が、冷凍サイクルの高圧が冷媒の臨界圧力よりも高くなる超臨界サイクルを行うように構成されていてもよい。この場合、冷凍サイクルの高圧が冷媒の臨界圧力よりも低くなる通常の冷凍サイクルでは凝縮器となる熱交換器が、放熱器(ガスクーラ)として動作する。冷媒としては、例えば二酸化炭素が用いられる。
20 冷媒回路
30 圧縮機
34 室外熱交換器(放熱器、蒸発器)
36 膨張弁(減圧機構)
37 室内熱交換器(放熱器、蒸発器)
50 漏洩診断装置
51 冷媒状態検出部(指標値算出手段)
52 エクセルギー算出部(指標値算出手段)
53 漏洩判定部(漏洩判定手段)
Claims (17)
- 圧縮機(30)、放熱器(34,37)、減圧機構(36)、及び蒸発器(34,37)が回路構成機器として設けられ、冷媒を循環させて冷凍サイクルを行う冷媒回路(20)における冷媒漏れの有無を診断する漏洩診断装置であって、
上記回路構成機器における冷媒のエクセルギーの損失量に基づいて、上記冷媒回路(20)から漏れた冷媒量に応じて変化する漏洩指標値を算出する指標値算出手段(31)と、
上記指標値算出手段(31)が算出した漏洩指標値に基づいて、上記冷媒回路(20)において冷媒漏れが生じているか否かを判定する漏洩判定手段(53)とを備えていることを特徴とする漏洩診断装置。 - 請求項1において、
上記指標値算出手段(31)は、上記漏洩指標値として、上記放熱器(34,37)における冷媒のエクセルギーの損失量に基づいて放熱器側指標値を算出し、
上記漏洩判定手段(53)は、上記放熱器側指標値に基づいて、上記冷媒回路(20)において冷媒漏れが生じているか否かを判定することを特徴とする漏洩診断装置。 - 請求項2において、
上記放熱器(34,37)では、ガス冷媒が冷却されて凝縮する一方、
上記指標値算出手段(31)は、上記放熱器(34,37)において冷媒がガス単相状態になっている過程でのエクセルギーの損失量を用いずに、上記放熱器側指標値を算出することを特徴とする漏洩診断装置。 - 請求項2において、
上記指標値算出手段(31)は、上記放熱器(34,37)において冷媒が気液二相状態になっている過程でのエクセルギーの損失量と、上記放熱器(34,37)において冷媒が液単相状態になっている過程でのエクセルギーの損失量との一方に対する他方の比率を、上記放熱器側指標値として算出することを特徴とする漏洩診断装置。 - 請求項4において、
上記冷媒回路(20)では、上記減圧機構(36)が開度可変の膨張弁(36)により構成され、上記膨張弁(36)の開度が、上記放熱器(34,37)から流出した冷媒の過冷却度が一定値になるように調節される一方、
上記漏洩判定手段(53)は、上記放熱器側指標値に基づけば上記冷媒回路(20)において冷媒漏れが生じていると判定できない場合であっても、上記膨張弁(36)の開度が所定の判定開度以下になると、上記冷媒回路(20)において冷媒漏れが生じていると判定することを特徴とする漏洩診断装置。 - 請求項2又は3において、
上記指標値算出手段(31)は、上記放熱器(34,37)における冷媒のエクセルギーの損失量と、上記放熱器(34,37)における冷媒の放熱量との一方に対する他方の比率を、上記放熱器側指標値として算出することを特徴とする漏洩診断装置。 - 請求項2又は3において、
上記指標値算出手段(31)は、上記放熱器(34,37)における冷媒のエクセルギーの損失量と、上記圧縮機(30)の入力との一方に対する他方の比率を、上記放熱器側指標値として算出することを特徴とする漏洩診断装置。 - 請求項2において、
上記冷媒回路(20)は、冷凍サイクルの低圧が一定値になるように制御される一方、
上記指標値算出手段(31)は、上記蒸発器(34,37)における冷媒のエクセルギーの損失量に基づいて蒸発器側指標値を算出し、
上記漏洩判定手段(53)は、上記蒸発器側指標値に基づいて上記冷媒回路(20)における冷媒漏れが所定のレベルにまで進行しているか否かを判定することを特徴とする漏洩診断装置。 - 請求項1において、
上記指標値算出手段(31)は、上記漏洩指標値として、上記蒸発器(34,37)における冷媒のエクセルギーの損失量に基づいて蒸発器側指標値を算出し、
上記漏洩判定手段(53)は、上記蒸発器側指標値に基づいて、上記冷媒回路(20)において冷媒漏れが生じているか否かを判定することを特徴とする漏洩診断装置。 - 請求項9において、
上記指標値算出手段(31)は、上記蒸発器(34,37)において冷媒が気液二相状態になっている過程でのエクセルギーの損失量と、上記蒸発器(34,37)において冷媒がガス単相状態になっている過程でのエクセルギーの損失量との一方に対する他方の比率を、上記蒸発器側指標値として算出することを特徴とする漏洩診断装置。 - 請求項10において、
上記冷媒回路(20)では、上記減圧機構(36)が開度可変の膨張弁(36)により構成され、上記膨張弁(36)の開度が、上記蒸発器(34,37)から流出した冷媒の過熱度が一定値になるように調節される一方、
上記漏洩判定手段(53)は、上記蒸発器側指標値に基づけば上記冷媒回路(20)において冷媒漏れが生じていると判定できない場合であっても、上記膨張弁(36)の開度が所定の判定開度以上になると、上記冷媒回路(20)において冷媒漏れが生じていると判定することを特徴とする漏洩診断装置。 - 請求項1において、
上記指標値算出手段(31)は、上記漏洩指標値として、上記圧縮機(30)における冷媒のエクセルギーの損失量に基づいて圧縮機側指標値を算出し、
上記漏洩判定手段(53)は、上記圧縮機側指標値に基づいて、上記冷媒回路(20)において冷媒漏れが生じているか否かを判定することを特徴とする漏洩診断装置。 - 請求項1において、
上記指標値算出手段(31)は、上記漏洩指標値として、上記放熱器(34,37)における冷媒のエクセルギーの損失量と、上記蒸発器(34,37)における冷媒のエクセルギーの損失量との一方に対する他方の比率を算出することを特徴とする漏洩診断装置。 - 請求項1において、
上記冷媒回路(20)には、上記圧縮機(30)に吸入される冷媒から液冷媒を分離するためのアキュームレータ(38)が設けられる一方、
上記漏洩判定手段(53)は、上記漏洩指標値に基づけば上記冷媒回路(20)において冷媒漏れが生じていると判定できる場合であっても、上記アキュームレータ(38)に流入する冷媒の過熱度と上記アキュームレータ(38)から流出した冷媒の過熱度との差が所定の吸入側基準値以上になる場合は、上記冷媒回路(20)において冷媒漏れが生じていると判定しないことを特徴とする漏洩診断装置。 - 圧縮機(30)、放熱器(34,37)、減圧機構(36)、及び蒸発器(34,37)が回路構成機器として設けられ、冷媒を循環させて冷凍サイクルを行う冷媒回路(20)における冷媒漏れの有無を診断するための漏洩診断装置であって、
上記回路構成機器における冷媒のエクセルギーの損失量に基づいて、上記冷媒回路(20)から漏れた冷媒量に応じて変化する漏洩指標値を算出する指標値算出手段(31)と、
上記指標値算出手段(31)が算出した漏洩指標値に基づく漏洩診断用の情報を表示する表示手段(56)とを備えていることを特徴とする漏洩診断装置。 - 圧縮機(30)、放熱器(34,37)、減圧機構(36)、及び蒸発器(34,37)が回路構成機器として設けられ、冷媒を循環させて冷凍サイクルを行う冷媒回路(20)と、
請求項1又は15に記載の漏洩診断装置(50)とを備えていることを特徴とする冷凍装置。 - 圧縮機(30)、放熱器(34,37)、減圧機構(36)、及び蒸発器(34,37)が回路構成機器として設けられ、冷媒を循環させて冷凍サイクルを行う冷媒回路(20)における冷媒漏れの有無を診断する漏洩診断方法であって、
上記回路構成機器における冷媒のエクセルギーの損失量に基づいて、上記冷媒回路(20)から漏れた冷媒量に応じて変化する漏洩指標値を算出する指標値算出ステップと、
上記指標値算出ステップで算出した漏洩指標値に基づいて、上記冷媒回路(20)において冷媒漏れが生じているか否かを判定する漏洩判定ステップとを備えていることを特徴とする漏洩診断方法。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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EP09817425.3A EP2333461B1 (en) | 2008-09-30 | 2009-09-24 | Leakage diagnosing device, leakage diagnosing method, and refrigerating device |
CN200980135214.7A CN102149990B (zh) | 2008-09-30 | 2009-09-24 | 泄漏诊断装置、泄漏诊断方法及制冷装置 |
AU2009299329A AU2009299329B2 (en) | 2008-09-30 | 2009-09-24 | Leakage diagnosis apparatus, leakage diagnosis method, and refrigeration apparatus |
US13/121,448 US8555703B2 (en) | 2008-09-30 | 2009-09-24 | Leakage diagnosis apparatus, leakage diagnosis method, and refrigeration apparatus |
ES09817425.3T ES2676541T3 (es) | 2008-09-30 | 2009-09-24 | Aparato de diagnóstico de fuga, procedimiento de diagnóstico de fuga y aparato de refrigeración |
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JP (2) | JP5040975B2 (ja) |
CN (1) | CN102149990B (ja) |
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- 2009-09-24 EP EP09817425.3A patent/EP2333461B1/en active Active
- 2009-09-24 CN CN200980135214.7A patent/CN102149990B/zh active Active
- 2009-09-24 WO PCT/JP2009/004824 patent/WO2010038382A1/ja active Application Filing
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EP2333461A4 (en) | 2015-04-15 |
AU2009299329B2 (en) | 2013-03-21 |
CN102149990A (zh) | 2011-08-10 |
JP5040975B2 (ja) | 2012-10-03 |
JP5234167B2 (ja) | 2013-07-10 |
CN102149990B (zh) | 2013-10-23 |
JP2010107187A (ja) | 2010-05-13 |
AU2009299329A1 (en) | 2010-04-08 |
ES2676541T3 (es) | 2018-07-20 |
EP2333461B1 (en) | 2018-06-06 |
US8555703B2 (en) | 2013-10-15 |
JP2012047447A (ja) | 2012-03-08 |
EP2333461A1 (en) | 2011-06-15 |
US20110174059A1 (en) | 2011-07-21 |
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