WO2022180821A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2022180821A1 WO2022180821A1 PCT/JP2021/007500 JP2021007500W WO2022180821A1 WO 2022180821 A1 WO2022180821 A1 WO 2022180821A1 JP 2021007500 W JP2021007500 W JP 2021007500W WO 2022180821 A1 WO2022180821 A1 WO 2022180821A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- range
- operating frequency
- temperature
- refrigerant circuit
- Prior art date
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 33
- 239000003507 refrigerant Substances 0.000 claims abstract description 148
- 238000001704 evaporation Methods 0.000 claims abstract description 72
- 230000008020 evaporation Effects 0.000 claims abstract description 29
- 230000007423 decrease Effects 0.000 claims description 10
- 239000003570 air Substances 0.000 description 30
- 239000007788 liquid Substances 0.000 description 14
- 230000006870 function Effects 0.000 description 12
- 238000010586 diagram Methods 0.000 description 9
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 8
- 230000005494 condensation Effects 0.000 description 8
- 238000009833 condensation Methods 0.000 description 8
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 4
- 229910002092 carbon dioxide Inorganic materials 0.000 description 4
- 230000001737 promoting effect Effects 0.000 description 3
- 229910021529 ammonia Inorganic materials 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- CDOOAUSHHFGWSA-OWOJBTEDSA-N (e)-1,3,3,3-tetrafluoroprop-1-ene Chemical compound F\C=C\C(F)(F)F CDOOAUSHHFGWSA-OWOJBTEDSA-N 0.000 description 1
- FXRLMCRCYDHQFW-UHFFFAOYSA-N 2,3,3,3-tetrafluoropropene Chemical compound FC(=C)C(F)(F)F FXRLMCRCYDHQFW-UHFFFAOYSA-N 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
-
- 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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
-
- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/17—Speeds
- F25B2700/171—Speeds of the compressor
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
Definitions
- the present disclosure relates to a refrigeration cycle device.
- the refrigeration cycle device described in International Publication No. 2015/132964 includes a low temperature side refrigeration cycle and a high temperature side refrigeration cycle.
- the low-side refrigeration cycle includes a low-side compressor, a heat source-side heat exchanger, a low-side condenser, a low-side expansion valve, and a utilization-side heat exchanger.
- the high temperature side refrigeration cycle includes a high temperature side compressor, a high temperature side condenser, a high temperature side expansion valve, and a high temperature side evaporator.
- the low temperature side condenser exchanges heat with the high temperature side evaporator.
- a heat source side heat exchanger and a high temperature side condenser are arranged in the housing of the outdoor unit.
- the heat source side heat exchanger and the high temperature side condenser are air-cooled heat exchangers
- the heat source side heat exchanger and the high temperature side condenser are mutually affected by the blower.
- the evaporation temperature decreases in the high pressure side refrigeration cycle, and a phenomenon (liquid backflow) in which the liquid refrigerant is sucked into the high pressure side compressor may occur.
- Liquid bag causes compressor failure.
- An object of the present disclosure is to provide a refrigeration cycle apparatus having two refrigerant circuits that can suppress the occurrence of compressor failure due to liquid backflow.
- a refrigeration cycle device of the present disclosure includes a first refrigerant circuit and a second refrigerant circuit.
- the first refrigerant circuit includes a first compressor, an air-cooled first heat exchanger, a first condenser, a first expansion device, and a first evaporator.
- a first refrigerant is circulated through the first condenser, the first expansion device, and the first evaporator in that order.
- the second refrigerant circuit includes a second compressor, a second air-cooled condenser, a second expansion device, and a second evaporator, wherein the second compressor, the second condenser, the second expansion device, and the second A second refrigerant is circulated in order of the evaporator.
- the refrigeration cycle device includes a second heat exchanger that exchanges heat between the first refrigerant of the first evaporator and the second refrigerant of the second condenser, and a control device.
- the control device stops the operation of the second refrigerant circuit when the values of the evaporation temperature of the first refrigerant in the first evaporator and the operating frequency of the first compressor are within the first range.
- the first range includes the lower limit of the evaporating temperature and the lower limit of the operating frequency.
- the first range which includes the lower limit of the evaporating temperature and the lower limit of the operating frequency, is a range with a lower load than the remaining ranges.
- the control device stops the operation of the second refrigerant circuit when the values of the evaporation temperature of the first refrigerant in the first evaporator and the operating frequency of the first compressor are within the first range. This suppresses the occurrence of liquid backflow in the second refrigerant circuit.
- FIG. 1 is a diagram showing the configuration of a refrigeration cycle apparatus according to Embodiment 1; FIG. It is a figure which shows the flow of the air in an outdoor unit.
- FIG. 1 is a diagram showing the configuration of a refrigeration cycle apparatus 100 according to Embodiment 1.
- FIG. 1 includes a low-side refrigerant circuit RC1, a high-side refrigerant circuit RC2, a heat exchanger 30, a control device 40, and sensors 50 and 51.
- the refrigerant circuit RC1 includes a compressor 10, an air-cooled auxiliary heat exchanger 11, a condenser 12, an expansion device 13, and an evaporator .
- Refrigerant circuit RC1 circulates the first refrigerant through compressor 10, auxiliary heat exchanger 11, condenser 12, expansion device 13, and evaporator 14 in this order.
- the refrigerant circuit RC2 includes a compressor 20, an air-cooled condenser 21, an expansion device 22, and an evaporator 23.
- Refrigerant circuit RC2 circulates the second refrigerant through compressor 20, air-cooled condenser 21, expansion device 22, and evaporator 23 in this order.
- the expansion device 13 and the evaporator 14 are arranged inside the indoor unit 2 such as a supermarket showcase.
- the compressor 20 , the condenser 21 and the expansion device 22 of the refrigerant circuit RC ⁇ b>1 and the refrigerant circuit RC ⁇ b>2 are arranged inside the outdoor unit 1 .
- the outdoor unit 1 and the indoor unit 2 are connected by pipes 3 and 4 . Therefore, when the connection of the pipes 3 and 4 is changed in order to rearrange the indoor units 2, the refrigerant circuit RC1 can be opened. At this time, leakage of the first refrigerant may occur.
- the refrigerant circuit RC2 is generally not opened.
- the CO2 refrigerant or the mixed refrigerant containing CO2 which has a small impact on global warming, is used as the first refrigerant charged in the refrigerant circuit RC1 in consideration of refrigerant leakage.
- HFO hydrofluoroolefin refrigerant
- HC refrigerant CO 2
- ammonia water
- Heat exchanger 30 exchanges heat between the first refrigerant of the condenser 12 and the second refrigerant of the evaporator 23 .
- Heat exchanger 30 is, for example, a cascade heat exchanger such as a plate type.
- Compressor 10 sucks in the first refrigerant flowing through the refrigerant circuit RC1, compresses the first refrigerant, and discharges the first refrigerant in a high-temperature, high-pressure state.
- Compressor 10 is, for example, a positive displacement compressor equipped with an inverter and driven by a motor (not shown) controlled by the inverter.
- Various types of compressors such as a reciprocating type, a rotary type, a scroll type, and a screw type can be employed as the compressor 10 .
- the auxiliary heat exchanger 11 cools the gaseous first refrigerant discharged from the compressor 10 by exchanging heat with outdoor air (outside air) as a heat source.
- the auxiliary heat exchanger 11 has a blower 15 for promoting heat exchange.
- the blower 15 is a fan of the type whose air volume can be adjusted.
- the condenser 12 gives the heat of the first refrigerant that has passed through the auxiliary heat exchanger 11 to the second refrigerant flowing through the evaporator 23 of the refrigerant circuit RC2, thereby condensing and liquefying the first refrigerant (condensing and liquefying). ).
- the expansion device 13 decompresses and expands the first refrigerant that has passed through the condenser 12 .
- the expansion device 13 is composed of, for example, an electronic expansion valve, a capillary, a temperature-sensitive expansion valve, or the like.
- the evaporator 14 evaporates the first refrigerant that has passed through the expansion device 13 into a gas (evaporates) in order to maintain the cooling target at the set utilization temperature through heat exchange with the cooling target.
- the object to be cooled is directly or indirectly cooled by heat exchange with the first refrigerant.
- Compressor 20 sucks the second refrigerant flowing through the refrigerant circuit RC2, compresses the second refrigerant, and discharges the second refrigerant in a high-temperature and high-pressure state.
- Compressor 20 is, for example, a positive displacement compressor equipped with an inverter and driven by a motor (not shown) controlled by the inverter.
- Various types of compressors such as a reciprocating type, a rotary type, a scroll type, and a screw type can be employed as the compressor 20 .
- the condenser 21 exchanges heat between the second refrigerant discharged from the compressor 20 and the outside air to condense and liquefy the second refrigerant.
- the condenser 21 has a blower 24 for promoting heat exchange.
- the air blower 24 is also configured by a fan whose air volume can be adjusted.
- the expansion device 22 decompresses and expands the second refrigerant that has passed through the condenser 21 .
- the expansion device 22 is composed of, for example, an electronic expansion valve, a capillary, a temperature-sensitive expansion valve, or the like.
- the evaporator 23 evaporates and gasifies the second refrigerant that has passed through the expansion device 22 by heat exchange with the first refrigerant flowing through the condenser 12 .
- the sensor 50 measures the temperature of the outside air.
- a sensor 51 measures the pressure of the first refrigerant that has passed through the evaporator 14 .
- the sensors 50 and 51 output measurement results to the control device 40 .
- the control device 40 includes a processor, memory, and a communication interface.
- the processor determines the operating frequency (rotational speed) of the compressors 10, 20 and the air volume of the fans 15, 24 according to the data stored in the memory and the information obtained via the communication interface (for example, the measurement results of the sensors 50, 51). etc. to control.
- the memory includes, for example, ROM (Read Only Memory), RAM (Random Access Memory), and flash memory.
- the flash memory stores an operating system, application programs, and various data.
- the controller 40 is implemented by a processor executing an operating system and application programs stored in memory. Various data stored in the memory are referenced when the application program is executed.
- FIG. 2 is a diagram showing the flow of air inside the outdoor unit 1.
- the auxiliary heat exchanger 11 and the condenser 21 are arranged side by side. With such an arrangement, the flow of ambient air generated by the blower 24 to promote heat exchange in the condenser 21 also affects the auxiliary heat exchanger 11 . Similarly, the flow of outside air generated by blower 15 to promote heat exchange in auxiliary heat exchanger 11 also affects condenser 21 .
- the control device 40 according to Embodiment 1 performs the following control in order to suppress the excessive decrease in the evaporation temperature and the occurrence of liquid backflow in the refrigerant circuit RC2.
- the controller 40 controls the operation of the refrigerant circuit RC2 based on the outside air temperature measured by the sensor 50, the evaporation temperature of the first refrigerant converted from the pressure measured by the sensor 51, and the operating frequency of the compressor 10. do.
- a plurality of two-dimensional maps are preset in the control device 40 .
- the two-dimensional map is a map whose axes are the evaporation temperature of the first refrigerant in the refrigerant circuit RC1 and the operating frequency of the compressor 10 .
- a plurality of two-dimensional maps are created in advance corresponding to different outside air temperatures.
- FIG. 3 is a diagram showing an example of the two-dimensional map 60 preset in Embodiment 1.
- FIG. FIG. 4 is a diagram showing another example of the two-dimensional map 60 preset in the first embodiment.
- the two-dimensional map 60 shown in FIG. 3 is a map used when the outside air temperature is the temperature T1.
- a two-dimensional map 60 shown in FIG. 4 is a map used when the outside air temperature is the temperature T2.
- the temperature T1 is the lower limit of the temperature range that the outside air can take.
- the temperature T2 is higher than the temperature T1 and slightly lower than the target value of the condensation temperature of the first refrigerant in the refrigerant circuit RC1.
- the two-dimensional map 60 includes a first range 61 including the lower limit of the evaporating temperature of the first refrigerant in the refrigerant circuit RC1 and the lower limit of the operating frequency of the compressor 10, and the evaporating temperature and a second range 62 including an upper limit of and an upper limit of the operating frequency.
- the first range 61 and the second range 62 are separated by a boundary line 63 .
- the first range 61 includes a point 64 indicating the lower limit of the evaporating temperature and the lower limit of the operating frequency, a point 65 indicating the upper limit of the evaporating temperature and the lower limit of the operating frequency, and the upper limit of the evaporating temperature and the operating frequency. a point 66 indicating a value selected from the lower limit to the upper limit of the evaporating temperature; a point 68 indicating a value selected from the lower limit to the upper limit of the evaporating temperature and the upper limit of the operating frequency; and a point 69 indicating the upper limit of the operating frequency.
- the first range 61 includes a line connecting the points 64 and 65, a line connecting the points 65 and 66, a boundary line 63 connecting the points 66 and 68, a line connecting the points 68 and 69, and the area surrounded by the line connecting the points 69 and 64 .
- the second range 62 is the remaining area. That is, a point 66 indicating the upper limit of the evaporating temperature and a value selected from the lower limit to the upper limit of the operating frequency; a point 67 indicating the upper limit of the evaporating temperature and the upper limit of the operating frequency; and a point 68 representing the upper limit of the operating frequency.
- the second range 62 is an area surrounded by a line connecting points 66 and 67 , a line connecting points 67 and 68 , and a boundary line 63 connecting points 68 and 66 .
- the upper and lower limits of the operating frequency, the upper and lower limits of the evaporating temperature, the operating frequency value at point 66, the evaporating temperature value at point 68, and the boundary line 63 are determined by the test performed in advance. determined according to the results of Boundary line 63 is represented by an arbitrary function.
- the control device 40 selects one two-dimensional map 60 corresponding to the outside air temperature measured by the sensor 50 from among the multiple two-dimensional maps 60 . Specifically, the control device 40 selects the two-dimensional map 60 corresponding to the temperature closest to the ambient temperature measured by the sensor 50 .
- the control device 40 uses the selected two-dimensional map 60 to determine whether to operate the refrigerant circuit RC2.
- control device 40 detects that the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are within the second range 62 of the selected two-dimensional map 60, and the refrigerant circuit Run RC2. That is, the control device 40 operates the compressor 20 to circulate the second refrigerant in the refrigerant circuit RC2. Furthermore, the control device 40 operates the air blower 24 .
- the control device 40 stops the operation of the refrigerant circuit RC2 when the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are within the first range 61 of the selected two-dimensional map 60. Let That is, the control device 40 stops the operation of the compressor 20 and stops the circulation of the second refrigerant in the refrigerant circuit RC2. Furthermore, the control device 40 stops the operation of the blower 24 .
- control device 40 operates the blower 15 regardless of whether the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are within the first range 61 or the second range 62 .
- the first range 61 including the lower limit of the evaporating temperature and the lower limit of the operating frequency is the remaining area (that is, the second range 62 including the upper limit of the evaporating temperature and the upper limit of the operating frequency).
- the control device 40 stops the operation of the refrigerant circuit RC ⁇ b>2 when the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are within the first range 61 .
- the power consumption required for the refrigerant circuit RC2 is reduced, and the operating noise is reduced. Furthermore, the occurrence of liquid backflow in the refrigerant circuit RC2 is suppressed.
- the control device 40 operates the refrigerant circuit RC ⁇ b>2 according to the fact that the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are within the second range 62 . Thereby, the condensing temperature of the first refrigerant in the refrigerant circuit RC1 is adjusted to be equal to or lower than the upper limit value.
- the first range 61 is set to increase as the outside air temperature decreases.
- the second range 62 is set in the two-dimensional map 60 so as to become smaller as the outside air temperature becomes lower. That is, the boundary line 63 between the first range 61 and the second range 62 is set so as to approach the point 67 indicating the upper limit of the evaporating temperature and the upper limit of the operating frequency as the outside air temperature decreases.
- the condensation capacity of the auxiliary heat exchanger 11 increases and the amount of heat exchanged in the heat exchanger 30 decreases. Therefore, in the refrigerant circuit RC2, an excessive drop in the evaporation temperature or liquid backflow in the compressor 20 may occur. Therefore, by setting the first range 61 to be larger as the outside air temperature becomes lower, the frequency of stopping the operation of the refrigerant circuit RC2 increases. This suppresses the occurrence of liquid backflow in the refrigerant circuit RC2.
- Embodiment 2 differs from refrigeration cycle apparatus 100 according to Embodiment 1 in that a two-dimensional map 60 including the third range is used.
- FIG. 5 is a diagram showing an example of a two-dimensional map 60 preset in Embodiment 2.
- two-dimensional map 60 includes third range 70 in addition to first range 61 and second range 62 .
- the third range 70 is located between the first range 61 and the second range 62 on the two-dimensional map 60 .
- the first range 61 includes a point 64 indicating the lower limit of the evaporating temperature and the lower limit of the operating frequency, a point 65 indicating the upper limit of the evaporating temperature and the lower limit of the operating frequency, and the upper limit of the evaporating temperature and the operating frequency.
- a point 66a indicating a first value selected from the lower limit to the upper limit of the evaporating temperature
- a point 68a indicating the second value selected from the lower limit to the upper limit of the evaporating temperature and the upper limit of the operating frequency.
- a point 69 indicating the lower limit of the evaporation temperature and the upper limit of the operating frequency.
- the first range 61 includes a line connecting the points 64 and 65, a line connecting the points 65 and 66a, a boundary line 63a connecting the points 66a and 68a, a line connecting the points 68a and 69, and the area surrounded by the line connecting the points 69 and 64 .
- the second range 62 indicates a point 66b indicating the upper limit of the evaporating temperature and a third value selected from the lower limit to the upper limit of the operating frequency, and the upper limit of the evaporating temperature and the upper limit of the operating frequency.
- This is an area formed by a point 67 and a point 68b indicating a fourth value selected from between the lower limit value and the upper limit value of the evaporating temperature and the upper limit value of the operating frequency.
- the second range 62 is an area surrounded by a line connecting points 66b and 67, a line connecting points 67 and 68b, and a boundary line 63b connecting points 68b and 66b. Note that the boundary line 63b is closer to the point 67 than the boundary line 63a. That is, the third value of the operating frequency at point 66b is greater than the first value of the operating frequency at point 66a.
- the fourth value of evaporating temperature at point 68b is greater than the second value of evaporating
- the third range 70 is an area formed by points 66a, 66b, 68b, and 68a. That is, the second range 62 includes a line connecting the points 66a and 66b, a boundary line 63b connecting the points 68b and 66b, a line connecting the points 68b and 68a, and a boundary connecting the points 68a and 66a. This is the area surrounded by line 63a.
- the first to fourth values and boundary lines 63a and 63b are determined according to the results of pre-implemented tests.
- the boundary lines 63a and 63b are represented by arbitrary functions.
- a plurality of two-dimensional maps 60 are preset in the control device 40 .
- the first range 61 is set to increase as the outside air temperature decreases.
- the second range 62 is set in the two-dimensional map 60 so as to become smaller as the outside air temperature becomes lower.
- a two-dimensional map 60 shown in FIG. 5 is a map used when the outside air temperature is the temperature T1.
- control device 40 selects one two-dimensional map 60 corresponding to the outside air temperature measured by the sensor 50 from among the plurality of two-dimensional maps 60 .
- control device 40 If the evaporation temperature measured by sensor 51 and the current operating frequency of compressor 10 are within second range 62 of selected two-dimensional map 60, control device 40 operates refrigerant circuit RC2 and , blower 15 is operated. That is, the control device 40 circulates the second refrigerant in the refrigerant circuit RC ⁇ b>2 and promotes heat exchange in the auxiliary heat exchanger 11 . As a result, the condensing temperature of the first refrigerant in the refrigerant circuit RC1 is adjusted to be equal to or lower than the upper limit value under heavy load conditions.
- the control device 40 stops the operation of the refrigerant circuit RC2 when the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are within the first range 61 of the selected two-dimensional map 60. and blower 15 is operated. As a result, the power consumption required for the refrigerant circuit RC2 is reduced, and the operating noise is reduced. Furthermore, the occurrence of liquid backflow in the refrigerant circuit RC2 is suppressed.
- control device 40 operates refrigerant circuit RC2 and , the operation of the blower 15 is stopped.
- the operation of the blower 15 is stopped.
- the number of times the refrigerant circuit RC2 is started and stopped is reduced, and deterioration and failure of the refrigerant circuit RC2 are suppressed.
- stable operation is possible while maintaining the condensation temperature of the first refrigerant at the target value.
- the controller 40 uses the two-dimensional map 60 to determine whether the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are in the first range 61 and the second range 62. It was decided to judge whether it belongs to any of the above.
- control device 40 may use a function indicating boundary line 63 instead of two-dimensional map 60 .
- x indicates the operating frequency
- y indicates the evaporating temperature.
- the control device 40 determines the evaporating temperature and It is only necessary to determine that the operating frequency belongs to the second range 62 .
- the controller 40 uses the two-dimensional map 60 to determine whether the evaporation temperature measured by the sensor 51 and the current operating frequency of the compressor 10 are in the first range 61, the It was decided to determine which one of the second range 62 and the third range 70 belongs.
- the control device 40 may use functions indicating the boundary lines 63a and 63b.
- x indicates the operating frequency
- y indicates the evaporating temperature.
- the control device 40 When substituting the current operating frequency of the compressor 10 and the evaporating temperature measured by the sensor 51 into the function, the control device 40 changes the evaporating temperature and operating frequency according to y ⁇ fa(x). It is only necessary to make a determination that it belongs to the first range 61 .
- the control device 40 evaporates according to satisfying fa(x) ⁇ y ⁇ fb(x). It may be determined that the temperature and operating frequency belong to the third range 70 .
- the control device 40 When substituting the current operating frequency of the compressor 10 and the evaporating temperature measured by the sensor 51 into the function, the control device 40 changes the evaporating temperature and operating frequency according to y ⁇ fb(x). A determination that belongs to the second range 62 may be made.
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Abstract
Description
<冷凍サイクル装置の構成>
図1は、実施の形態1に係る冷凍サイクル装置100の構成を示す図である。図1に示されるように、は、低元側の冷媒回路RC1と、高元側の冷媒回路RC2と、熱交換器30と、制御装置40と、センサ50,51と、を備える。
図2は、室外機1内の空気の流れを示す図である。図2に示されるように、室外機1内において、補助熱交換器11と凝縮器21とが並んで配置される。このような配置の場合、凝縮器21の熱交換を促すための送風機24によって生成される外気の流れは、補助熱交換器11にも影響を及ぼす。同様に、補助熱交換器11の熱交換を促すための送風機15によって生成される外気の流れは、凝縮器21にも影響を及ぼす。
制御装置40は、センサ50によって計測された外気温度、センサ51によって計測された圧力から換算される第1冷媒の蒸発温度、および圧縮機10の運転周波数に基づいて、冷媒回路RC2の運転を制御する。
実施の形態2に係る冷凍サイクル装置は、実施の形態1に係る冷凍サイクル装置100と比較して、第3範囲を含む二次元マップ60を用いる点で相違する。
上記の実施の形態1の説明では、制御装置40は、二次元マップ60を用いて、センサ51によって計測された蒸発温度および現在の圧縮機10の運転周波数が第1範囲61および第2範囲62のいずれに属するかを判断するものとした。しかしながら、制御装置40は、二次元マップ60の代わりに境界線63を示す関数を用いてもよい。たとえば、制御装置40は、境界線63を示す関数y=f(x)を用いる。なお、xは運転周波数を示し、yは蒸発温度を示す。制御装置40は、現在の圧縮機10の運転周波数およびセンサ51によって計測された蒸発温度を当該関数に代入したときに、y<f(x)を満たすことに応じて、蒸発温度および運転周波数が第1範囲61に属する判断すればよい。同様に、制御装置40は、現在の圧縮機10の運転周波数およびセンサ51によって計測された蒸発温度を当該関数に代入したときに、y≧f(x)を満たすことに応じて、蒸発温度および運転周波数が第2範囲62に属する判断すればよい。
Claims (7)
- 冷凍サイクル装置であって、
第1圧縮機、空冷式の第1熱交換器、第1凝縮器、第1膨張装置、および第1蒸発器を含み、前記第1圧縮機、前記第1熱交換器、前記第1凝縮器、前記第1膨張装置、および前記第1蒸発器の順に第1冷媒を循環させる第1冷媒回路と、
第2圧縮機、空冷式の第2凝縮器、第2膨張装置、および第2蒸発器を含み、前記第2圧縮機、前記第2凝縮器、前記第2膨張装置、および前記第2蒸発器の順に第2冷媒を循環させる第2冷媒回路と、
前記第1凝縮器の前記第1冷媒と前記第2蒸発器の前記第2冷媒との間で熱交換を行なう第2熱交換器と、
制御装置と、を備え、
前記制御装置は、前記第1冷媒回路における前記第1冷媒の蒸発温度および前記第1圧縮機の運転周波数の値が第1範囲内であることに応じて、前記第2冷媒回路の運転を停止し、
前記第1範囲は、前記蒸発温度の下限値および前記運転周波数の下限値を含む、冷凍サイクル装置。 - 前記第1熱交換器と前記第2凝縮器とは、室外機の筐体内に配置される、請求項1に記載の冷凍サイクル装置。
- 前記制御装置は、前記蒸発温度および前記運転周波数の値が第2範囲内であることに応じて、前記第2冷媒回路を運転させ、
前記第2範囲は、前記蒸発温度の上限値および前記運転周波数の上限値を含む、請求項1または2に記載の冷凍サイクル装置。 - 前記第1範囲は、外気温度が低くなるほど大きくなるように設定され、
前記第2範囲は、外気温度が低くなるほど小さくなるように設定される、請求項3に記載の冷凍サイクル装置。 - 前記第1熱交換器に外気を送る送風機をさらに備え、
前記制御装置は、
前記蒸発温度および前記運転周波数の値が前記第1範囲または前記第2範囲内であることに応じて、前記送風機を運転させ、
前記蒸発温度および前記運転周波数の値が第3範囲内であることに応じて、前記第2冷媒回路を運転させるとともに、前記送風機の運転を停止し、
前記第3範囲は、前記第1範囲と前記第2範囲との間に位置する、請求項3または4に記載の冷凍サイクル装置。 - 前記第1範囲は、前記蒸発温度の下限値と前記運転周波数の下限値とを示す第1点と、前記蒸発温度の上限値と前記運転周波数の下限値とを示す第2点と、前記蒸発温度の上限値と前記運転周波数の下限値から上限値の間から選択される値とを示す第3点と、前記蒸発温度の下限値から上限値の間から選択された値と前記運転周波数の上限値とを示す第4点と、前記蒸発温度の下限値と前記運転周波数の上限値とを示す第5点と、によって形成される領域である、請求項1から5のいずれか1項に記載の冷凍サイクル装置。
- 前記第1冷媒は、CO2冷媒またはCO2を含む混合冷媒である、請求項1から6のいずれか1項に記載の冷凍サイクル装置。
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WO2015132964A1 (ja) * | 2014-03-07 | 2015-09-11 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2018008129A1 (ja) * | 2016-07-07 | 2018-01-11 | 三菱電機株式会社 | 冷凍サイクル装置 |
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JP2009210133A (ja) * | 2008-02-29 | 2009-09-17 | Mitsubishi Electric Corp | ヒートポンプ給湯機 |
WO2015132964A1 (ja) * | 2014-03-07 | 2015-09-11 | 三菱電機株式会社 | 冷凍サイクル装置 |
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