WO2022230034A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2022230034A1 WO2022230034A1 PCT/JP2021/016709 JP2021016709W WO2022230034A1 WO 2022230034 A1 WO2022230034 A1 WO 2022230034A1 JP 2021016709 W JP2021016709 W JP 2021016709W WO 2022230034 A1 WO2022230034 A1 WO 2022230034A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- temperature
- flow path
- air conditioner
- Prior art date
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- 238000004378 air conditioning Methods 0.000 title abstract description 3
- 239000003507 refrigerant Substances 0.000 claims abstract description 145
- 238000001816 cooling Methods 0.000 claims abstract description 35
- 230000001105 regulatory effect Effects 0.000 claims description 10
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical group CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 claims description 6
- 239000002826 coolant Substances 0.000 claims description 6
- 239000001294 propane Substances 0.000 claims description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 47
- 238000010586 diagram Methods 0.000 description 16
- 238000010438 heat treatment Methods 0.000 description 15
- 238000005057 refrigeration Methods 0.000 description 11
- 230000007423 decrease Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 3
- 230000006870 function Effects 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- NNPPMTNAJDCUHE-UHFFFAOYSA-N isobutane Chemical compound CC(C)C NNPPMTNAJDCUHE-UHFFFAOYSA-N 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 239000008399 tap water Substances 0.000 description 2
- 235000020679 tap water Nutrition 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000003673 groundwater Substances 0.000 description 1
- 239000001282 iso-butane Substances 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000013589 supplement Substances 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
- 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
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2103—Temperatures near a heat exchanger
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
-
- 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
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
Definitions
- the present disclosure relates to an air conditioner.
- Patent Document 1 discloses an air conditioner using an HC refrigerant with a low GWP, namely propane (R290) or isobutane, as a refrigerant in a refrigerant circuit. This air conditioner uses an internal heat exchanger to increase efficiency.
- the present disclosure has been made to solve the above problems, and is an air conditioner that can achieve further performance improvement of a refrigeration cycle using an internal heat exchanger while keeping the size of the internal heat exchanger small.
- the purpose is to disclose an apparatus.
- An air conditioner includes at least a compressor, a condenser, an expansion valve, and an evaporator, and heat exchange is performed between a refrigerant circuit in which refrigerant circulates, and the refrigerant that has passed through the condenser and the refrigerant sucked into the compressor.
- a heat medium for cooling the heat exchanger a flow rate adjusting device for adjusting the amount of heat medium supplied to the heat exchanger, a temperature sensor for detecting the temperature of the heat medium, and a flow rate adjusting device according to the output of the temperature sensor.
- a control device for controlling the
- the air conditioner of the present disclosure makes it possible to obtain the effect of increasing the enthalpy difference of the evaporator without reducing the density of refrigerant drawn into the compressor. This allows further performance improvements in refrigeration cycles using internal heat exchangers.
- FIG. 1 is a diagram showing the configuration of an air conditioner 1000 according to Embodiment 1.
- FIG. It is a figure which shows the structure of the air conditioning apparatus 2000 of the example of examination.
- FIG. 4 is a PH diagram of a refrigeration cycle using R290 refrigerant without an internal heat exchanger in the configuration of the study example.
- FIG. 4 is a PH diagram in the case of a refrigeration cycle using R290 refrigerant with an internal heat exchanger in the configuration of the study example.
- FIG. 4 is a PH diagram for a refrigeration cycle using R290 refrigerant with an internal heat exchanger in the configuration of Embodiment 1.
- FIG. 3 is a perspective view showing the appearance of an internal heat exchanger 250;
- FIG. 3 is a perspective view showing the appearance of an internal heat exchanger 250;
- FIG. 7 is a cross-sectional view of the internal heat exchanger 250 in section F of FIG. 6.
- FIG. 4 is a flow chart for explaining control of the flow regulating device 420 during cooling.
- 4 is a flowchart for explaining control of expansion valve 230 during cooling.
- FIG. 10 is a diagram showing the configuration of an air conditioner 1001 to which a sensor used for heating is added; 4 is a flowchart for explaining control of the flow rate adjusting device 420 during heating.
- FIG. 10 is a diagram showing the configuration of an air conditioner 1002 according to Embodiment 2.
- FIG. 1 is a diagram showing the configuration of an air conditioner 1000 according to Embodiment 1. As shown in FIG. The air conditioner 1000 shown in FIG. 1 includes a refrigerant circuit 500, an internal heat exchanger 250, a flow rate adjusting device 420, and a control device 100.
- the refrigerant circuit 500 includes at least a compressor 200, an outdoor heat exchanger 210, an expansion valve 230, and an indoor heat exchanger 110, and is configured to circulate refrigerant.
- the refrigerant uses, for example, R290.
- the refrigerant circuit 500 is composed of a compressor 200 , an outdoor heat exchanger 210 , an outdoor fan 220 , an expansion valve 230 , a four-way valve 240 , an indoor heat exchanger 110 and an indoor fan 120 .
- the four-way valve 240 has ports P1-P4.
- As the expansion valve 230 for example, an electronic expansion valve (LEV: Linear Expansion Valve) can be used.
- LEV Linear Expansion Valve
- the compressor 200 is configured to change the operating frequency according to a control signal received from the control device 100 .
- the compressor 200 incorporates an inverter-controlled drive motor whose rotational speed is variable, and the rotational speed of the drive motor changes when the operating frequency is changed.
- the output of compressor 200 is adjusted.
- Various types such as rotary type, reciprocating type, scroll type, and screw type can be adopted for the compressor 200 .
- the four-way valve 240 is controlled by a control signal received from the control device 100 to be in either the cooling operation state or the heating operation state.
- the cooling operation state as indicated by broken lines, the ports P1 and P4 are in communication, and the ports P2 and P3 are in communication.
- the heating operation state as indicated by solid lines, the port P1 and the port P3 are in communication, and the port P2 and the port P4 are in communication.
- the internal heat exchanger 250 exchanges heat between the high-pressure, high-temperature refrigerant that has passed through the condenser (outdoor heat exchanger 210) and the low-pressure, low-temperature refrigerant sucked by the compressor 200 during cooling.
- Internal heat exchanger 250 is additionally configured to exchange heat with an external cooling heat medium conveyed from flow path 410 .
- water is used as the heat medium for cooling.
- the water may, for example, be circulated such that it is cooled in a cooling tower or the like after passing through the internal heat exchanger 250 and then re-supplied through the flow path 410 .
- drain water from the evaporator, tap water, groundwater, or the like may flow without being circulated. It is sufficient that the internal heat exchanger can be cooled by the heat medium, and it is not always necessary to provide a flow path for passing the heat medium inside.
- the internal heat exchanger 250 may be cooled by spraying water from the outside.
- the flow rate adjusting device 420 adjusts the amount of heat medium such as water for cooling the internal heat exchanger 250 supplied to the internal heat exchanger 250 .
- a control valve whose opening varies from 0 to 100% according to a control signal can be used.
- the air conditioner 1000 further includes temperature sensors 260 to 263 and 411.
- a temperature sensor 260 is arranged in a suction pipe of the compressor 200 and measures a refrigerant suction temperature T260.
- a temperature sensor 261 is arranged in a pipe connecting the outdoor heat exchanger 210 and the internal heat exchanger 250 to measure the refrigerant temperature T261.
- the temperature sensor 262 is arranged in the indoor heat exchanger 110 and measures a refrigerant temperature T262 which is an evaporation temperature during cooling and a condensation temperature during heating.
- the temperature sensor 263 is arranged in a pipe connecting the indoor heat exchanger 110 and the port P3 of the four-way valve 240, and measures the refrigerant temperature T263.
- a temperature sensor 411 detects a temperature T411 of a heat medium such as water. If the water temperature is lower than the high-pressure refrigerant inlet temperature of the internal heat exchanger 250 obtained by the temperature sensor 261, the water can cool the high-pressure refrigerant. can be lowered.
- the control device 100 is configured to control the flow rate adjusting device 420 according to the output of the temperature sensor 411 . Further, the control device 100 controls the opening degree of the expansion valve 230 so as to adjust the SH (superheat: degree of heating) of the refrigerant at the outlet of the evaporator.
- SH superheat: degree of heating
- the control device 100 includes a CPU (Central Processing Unit) 101, a memory 102 (ROM (Read Only Memory) and RAM (Random Access Memory)), an input/output buffer (not shown), and the like.
- the CPU 101 develops a program stored in the ROM into a RAM or the like and executes it.
- the program stored in the ROM is a program in which processing procedures of the control device 100 are described.
- the control device 100 controls each device in the air conditioner 1000 according to these programs. This control is not limited to processing by software, and processing by dedicated hardware (electronic circuit) is also possible.
- FIG. 2 is a diagram showing the configuration of the air conditioner 2000 of the study example.
- the air conditioner 1000 of FIG. 1 includes a water-coolable internal heat exchanger 250 , but instead of this, the air conditioner 2000 includes a general internal heat exchanger 550 .
- the internal heat exchanger 550 shown in FIG. 2 exchanges heat between the high-temperature, high-pressure refrigerant flowing out from the outlet of the outdoor heat exchanger 210 and the low-temperature, low-pressure refrigerant sucked into the compressor 200 during cooling.
- FIGS. 3 to 5 we will explain how the PH diagram changes due to such a difference in the internal heat exchanger.
- FIG. 3 is a PH diagram of a refrigeration cycle using R290 refrigerant without an internal heat exchanger in the configuration of the study example.
- FIG. 4 is a PH diagram in the case of a refrigeration cycle using R290 refrigerant with an internal heat exchanger in the configuration of the study example.
- FIG. 5 is a PH diagram for a refrigeration cycle using R290 refrigerant with an internal heat exchanger in the configuration of the first embodiment.
- the COP of the air conditioner will increase.
- the increase in the evaporator enthalpy difference ⁇ he acts more than the decrease in the suction density ⁇ s, so the use of an internal heat exchanger improves the COP of the air conditioner. It is possible.
- the compressor suction point shifts to the right across the isothermal line, causing the gas temperature to rise and the suction density to decrease. For this reason, the effect of increasing the evaporator enthalpy difference cannot be maximized.
- refrigerants such as R32 and R410
- the reduction in suction density and the increase in enthalpy difference in the evaporator cancel each other out, so the effect of the internal heat exchanger cannot be obtained.
- the enthalpy at the high pressure side refrigerant outlet of the internal heat exchanger 250 is smaller than when a normal internal heat exchanger 550 is used, and the evaporator enthalpy difference is h(D3)-h( A3).
- the reason for the expansion is that while the temperature of the refrigerant at the high-pressure outlet of the normal internal heat exchanger 550 is 28.2°C, in the present embodiment, the temperature of the cooling source from the outside is 22°C. This is because the temperature of the refrigerant at the high-pressure outlet of the internal heat exchanger 250 drops to the temperature (22° C.).
- FIG. 6 is a perspective view showing the appearance of the internal heat exchanger 250.
- FIG. FIG. 7 is a cross-sectional view of internal heat exchanger 250 at section F in FIG.
- the internal heat exchanger 250 shown in FIGS. 6 and 7 has a triple tube structure comprising an inner tube 251 , a middle tube 252 and an outer tube 253 .
- the inner pipe 251 serves as a flow path R1 through which the low-pressure refrigerant returning to the suction portion of the compressor 200 flows.
- the middle pipe 252 serves as a flow path R2 through which the high-pressure refrigerant that has flowed out from the outlet of the outdoor heat exchanger 210 flows.
- the outer tube 253 serves as a channel R3 through which water transported from the outside flows through the channel 410 .
- the refrigerant flowing through the flow path R1 and the refrigerant flowing through the flow path R2 have a counter-current relationship
- the refrigerant flowing through the flow path R2 and the water flowing through the flow path R3 also have a counter-current relationship. becomes.
- the reason for configuring the internal heat exchanger 250 as shown in FIGS. 6 and 7 will be described below. Since the temperature of the water flowing into the internal heat exchanger 250 is lower than the temperature of the high-pressure refrigerant at the inlet of the internal heat exchanger 250, the temperature of the high-pressure refrigerant flowing out of the outlet of the outdoor heat exchanger 210 is higher than the temperature of the internal heat exchanger 250. It has the highest temperature among the passing fluids. Therefore, by flowing the high-pressure refrigerant through the middle tube 252, both the low-pressure refrigerant flowing through the inner tube 251 and the water flowing through the outer tube 253 can be heat-exchanged with the high-pressure refrigerant, which is efficient.
- the internal heat exchanger 250 has a flow path 410, the cooling medium flowing through the flow path 410 is water, and the internal heat exchanger 250 is a triple tube.
- the cooling medium does not have to be water.
- the internal heat exchanger 250 may not be a triple tube, and may not form a flow path for a cooling medium such as water.
- the internal heat exchanger 250 may be made of a double tube, and the internal heat exchanger 250 may be cooled by spraying water from above.
- the internal heat exchanger 250 is installed so as to function during cooling, it may be installed so as to function during heating.
- the flow of refrigerant during heating is indicated by solid arrows
- the flow of refrigerant during cooling is indicated by broken arrows.
- the control device 100 changes the frequency of the compressor 200 so that the indoor temperature reaches the target (set) temperature, as in a normal air conditioner. Further, the control device 100 controls the flow rate adjusting device 420 during cooling as follows.
- FIG. 8 is a flowchart for explaining the control of the flow regulating device 420 during cooling.
- the control device 100 acquires the outlet refrigerant temperature T ⁇ b>261 of the outdoor heat exchanger 210 from the temperature sensor 261 and acquires the water temperature T ⁇ b>411 from the temperature sensor 411 .
- control device 100 determines whether temperature T ⁇ b>261 obtained from temperature sensor 261 is higher than temperature T ⁇ b>411 obtained from temperature sensor 411 .
- T261>T411 does not hold (NO in S12)
- the control device 100 fully closes the flow regulating device 420 in step S13. to prevent water from flowing through the internal heat exchanger 250 .
- T261>T411 is satisfied (YES in S12)
- the control device 100 controls the flow regulating device 420 to fully open in step S14.
- step S15 the control device 100 determines whether the degree of superheat of the sucked refrigerant (hereinafter referred to as suction SH) is smaller than the judgment value ⁇ (>0).
- the suction SH is calculated by subtracting the evaporation temperature obtained by the temperature sensor 262 from the suction temperature obtained by the temperature sensor 260 .
- the judgment value ⁇ is set to a value, for example, 5K, at which it can be judged that the refrigerant sucked into the compressor 200 is sufficiently gasified.
- the flow rate adjusting device 420 is used to adjust the flow rate of water to the internal heat exchanger 250, but a pump may be used to control the flow rate of water.
- FIG. 9 is a flowchart for explaining control of expansion valve 230 during cooling.
- Evaporator outlet SH is calculated by subtracting evaporation temperature T262 obtained by temperature sensor 262 from evaporator outlet temperature T263 obtained by temperature sensor 263 .
- the judgment value ⁇ is assumed to be smaller than the judgment value ⁇ . For example, when the judgment value ⁇ is 5K, the judgment value ⁇ is set to 2K.
- the reason why the judgment value ⁇ is set smaller than the judgment value ⁇ is that the heat exchange efficiency of the evaporator is good when it is used in two gas-liquid phases, so it is desirable to control the state of the refrigerant in the evaporator so that the amount of gas refrigerant is reduced as much as possible. be.
- the control device 100 performs step In S23, it is determined whether or not the flow control device 420 is fully closed.
- flow rate adjusting device 420 controls intake SH to an appropriate value as shown in steps S15 and S16 of FIG. , the processing of the flow chart of FIG. 9 is temporarily exited.
- the flow regulating device 420 is fully closed (YES in S23)
- the internal heat exchanger 250 does not exchange heat with the water supplied from the outside, so the evaporator outlet SH ⁇ suction SH. .
- the suction SH ⁇ ⁇ ( ⁇ ) the refrigerant sucked into the compressor 200 is not properly heated. Therefore, in step S24, the control device 100 increases the value of the intake SH by closing the opening of the expansion valve 230 by a constant value, and then executes the determination processing in step S25.
- the device 100 closes the opening of the expansion valve 230 by a constant value in step S26. By controlling the opening degree of the expansion valve 230 in this manner, the value of the suction SH can be increased. After that, the process of step S25 is executed again.
- the control flow of the flow control device 420 and the expansion valve 230 during cooling has been described above.
- the flow regulating device 420 may be fully closed and controlled in the same manner as a normal air conditioner, but the flow regulating device 420 may be controlled as follows.
- FIG. 10 is a diagram showing the configuration of an air conditioner 1001 to which a sensor used for heating is added.
- FIG. 11 is a flowchart for explaining control of the flow rate adjusting device 420 during heating.
- step S31 the control device 100 acquires the inlet refrigerant temperature T264 of the internal heat exchanger 250 from the temperature sensor 264, and acquires the water temperature T411 from the temperature sensor 411.
- step S ⁇ b>32 control device 100 determines whether or not temperature T ⁇ b>264 obtained from temperature sensor 264 is higher than temperature T ⁇ b>411 obtained from temperature sensor 411 .
- T264>T411 does not hold (NO in S32)
- the control device 100 controls the flow regulating device 420 to fully close in step S33. and keep water out of the internal heat exchanger 250 .
- T264>T411 holds (YES in S32)
- the control device 100 controls the flow rate adjusting device 420 to fully open in step S34.
- step S35 the control device 100 determines whether the degree of superheat of the suctioned refrigerant (suction SH) is smaller than the determination value ⁇ (>0).
- Suction SH is calculated by subtracting the evaporating temperature obtained by temperature sensor 265 from the suction temperature obtained by temperature sensor 260 .
- the judgment value ⁇ is set to a value, for example, 5K, at which it can be judged that the refrigerant sucked into the compressor 200 is sufficiently gasified.
- SH ⁇ YES in S35
- the controller 100 closes the flow control device 420 by a certain degree of opening in step S36.
- a pump may be used to control the flow rate of water.
- the same processing as during cooling shown in FIG. 9 may be executed.
- the evaporator outlet SH is calculated by subtracting the temperature sensor 265 value from the temperature sensor 266 value.
- the air conditioner of Embodiment 1 it is possible to improve the coefficient of performance COP of an air conditioner that uses R290 as a refrigerant and an internal heat exchanger. Also, the refrigerant is most effective when using R290, but even when using R32 or R410 as the refrigerant, the suction density changes from that shown in FIG. , and the COP can be improved.
- the difference in evaporator enthalpy increases in the same way as during cooling, and performance improvement can be expected.
- outdoor heat exchanger 210 is an air heat exchanger in consideration of the situation where the cooling source of the refrigeration cycle cannot always be used. For example, tap water may not be usable due to a water outage. Therefore, in order to ensure that the refrigerating cycle functions, it is appropriate that the heat exchange target of the outdoor heat exchanger 210 is outside air that can be used at any time. In addition, in order to use the outdoor heat exchanger 210 as a water-refrigerant heat exchanger, it is also necessary to route water pipes.
- FIG. 12 is a diagram showing the configuration of an air conditioner 1002 according to Embodiment 2. As shown in FIG. 12
- outdoor heat exchanger 210 in FIG. 12 is configured to exchange heat with water, which is a cooling source from the outside.
- the water is circulated and cooled in a cooling tower or the like, and then resupplied from the water supply pipe.
- Heat exchanger 270 is, for example, a plate heat exchanger.
- the water used in heat exchanger 270 and internal heat exchanger 250 is supplied from the same water supply pipe.
- the amount of heat exchanged by water is increased compared to the configuration shown in Embodiment 1, so the return of water is reduced.
- the plate heat exchanger 270 is used as the outdoor heat exchanger, the heat exchange performance is improved.
- the refrigerant circuit is provided with a four-way valve, but the internal heat exchanger 250 may be used in a cooling-only air conditioner that does not have a four-way valve.
- the R290 refrigerant is used as the refrigerant circulating in the refrigerant circuit, but other refrigerants such as R32 and R410 may be used.
- R32 refrigerant for example, there is no advantage in introducing the internal heat exchanger 550 shown in the example of study in FIG. 2 because the effect of the increase in the enthalpy difference in the evaporator and the effect of the decrease in the density of the sucked refrigerant cancel each other out.
- the internal heat exchanger 250 shown in FIG. 1 uses an external cooling source to suppress the reduction in the density of the sucked refrigerant, thereby improving the performance of the air conditioner even when using the R32 refrigerant.
- the air conditioner 1000 shown in FIG. 1 includes at least a compressor 200, a condenser (outdoor heat exchanger 210), an expansion valve 230, and an evaporator (indoor heat exchanger 110). , an internal heat exchanger 250 that exchanges heat between the refrigerant that has passed through the condenser (outdoor heat exchanger 210) and the refrigerant sucked into the compressor 200, and a heat medium that cools the internal heat exchanger 250.
- a flow control device 420 that adjusts the amount supplied to the exchanger, a temperature sensor 411 that detects the temperature of the heat medium, and a control device 100 that controls the flow control device 420 according to the output of the temperature sensor 411 .
- the control device 100 supplies the heat medium to the internal heat exchanger 250.
- Control the flow regulator 420 .
- control device 100 controls flow control device 420 so that the heat medium is supplied to internal heat exchanger 250 when temperature T411 of the heat medium is lower than temperature T260 of the refrigerant sucked into compressor 200. Control.
- the control device 100 prevents the heat medium from being supplied to the internal heat exchanger 250. Control the flow regulator 420 .
- the internal heat exchanger 250 passes through a first flow path R1 through which the refrigerant sucked into the compressor 200 passes, and the condenser (outdoor heat exchanger 210). It has a second flow path R2 through which the refrigerant passes and a third flow path R3 through which the heat medium passes.
- the refrigerant passing through the first flow path R1 and the refrigerant passing through the second flow path R2 have a countercurrent relationship, and the refrigerant passing through the second flow path R2 and the heat medium passing through the third flow path R3 are in a countercurrent relationship.
- the internal heat exchanger 250 passes through a first flow path R1 through which the refrigerant sucked into the compressor 200 passes, and the condenser (outdoor heat exchanger 210). It has a second flow path R2 through which the refrigerant passes and a third flow path R3 through which the heat medium passes.
- the second flow path R2 and the third flow path R3 are arranged adjacent to each other so as to exchange heat.
- the internal heat exchanger 250 is a triple-tube heat exchanger in which an inner tube 251, a middle tube 252, and an outer tube 253 are arranged in order from the inside to the outside. is.
- the inner tube 251 is the first flow path R1.
- a second flow path R2 is formed between the middle tube 252 and the inner tube 251 .
- a third flow path R3 is formed between the middle tube 252 and the outer tube 253 .
- the condenser heat exchanger 270
- the condenser is configured such that heat is exchanged between the heat medium and the refrigerant.
- the refrigerant is propane.
- the embodiments disclosed this time should be considered as examples and not restrictive in all respects.
- the scope of the present disclosure is indicated by the scope of the claims rather than the description of the above-described embodiments, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.
- 100 control device 101 CPU, 102 memory, 110, 210, 250, 270, 550 heat exchanger, 120 indoor fan, 200 compressor, 220 outdoor fan, 230 expansion valve, 240 four-way valve, 251 inner pipe, 252 middle pipe , 253 outer tube, 260 to 266, 411 temperature sensor, 410, R1, R2, R3 flow path, 420 flow rate regulator, 500 refrigerant circuit, 1000, 1001, 1002, 2000 air conditioner, P1, P2, P3, P4 port.
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Abstract
Description
図1は、実施の形態1に係る空気調和装置1000の構成を示す図である。図1に示す空気調和装置1000は、冷媒回路500と、内部熱交換器250と、流量調整装置420と、制御装置100とを備える。
暖房時は、流量調整装置420を全閉とし、通常の空気調和装置と同様に制御してもよいが、以下のように流量調整装置420を制御しても良い。
実施の形態1で説明した図1の構成では、冷凍サイクルの冷却源が常に使用できる状況にない場合も考慮し、室外熱交換器210を空気熱交換器とした。たとえば、水道水などでは断水などで使えない場合などがある。したがって、冷凍サイクルとして必ず機能させるためには、室外熱交換器210の熱交換対象をいつでも利用できる外気とすることが適切である。また、室外熱交換器210を水―冷媒熱交換器とするには水配管を引き回す必要もあり、シンプルな構成とするため図1のように構成した。
以上説明した実施の形態1、2では、四方弁を備えた冷媒回路としたが、四方弁がない冷房専用の空気調和装置に、内部熱交換器250を用いてもよい。
以下に、本実施の形態について再び図面を参照しながら総括する。なお、括弧内については、冷房時に該当するユニットを記載している。
今回開示された実施の形態は、すべての点で例示であって制限的なものではないと考えられるべきである。本開示の範囲は、上記した実施の形態の説明ではなくて請求の範囲によって示され、請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。
Claims (9)
- 少なくとも圧縮機、凝縮器、膨張弁、および蒸発器を含み、冷媒が循環する冷媒回路と、
前記凝縮器を通過した前記冷媒と前記圧縮機に吸入される前記冷媒とを熱交換させる熱交換器と、
前記熱交換器を冷却するための熱媒体を前記熱交換器に供給する量を調整する流量調整装置と、
前記熱媒体の温度を検出する温度センサと、
前記温度センサの出力に応じて前記流量調整装置を制御する制御装置とを備える、空気調和装置。 - 前記制御装置は、前記凝縮器を通過した前記冷媒の温度よりも前記熱媒体の温度が低い場合に、前記熱媒体が前記熱交換器に供給されるように前記流量調整装置を制御する、請求項1に記載の空気調和装置。
- 前記制御装置は、前記圧縮機に吸入される前記冷媒の温度よりも前記熱媒体の温度が低い場合に、前記熱媒体が前記熱交換器に供給されるように前記流量調整装置を制御する、請求項1に記載の空気調和装置。
- 前記制御装置は、前記凝縮器を通過した前記冷媒の温度よりも前記熱媒体の温度が高い場合には、前記熱媒体が前記熱交換器に供給されないように前記流量調整装置を制御する、請求項1~3のいずれか1項に記載の空気調和装置。
- 前記熱交換器は、
前記圧縮機に吸入される前記冷媒が通過する第1流路と、
前記凝縮器を通過した前記冷媒が通過する第2流路と、
前記熱媒体が通過する第3流路とを備え、
前記第1流路を通過する前記冷媒と前記第2流路を通過する前記冷媒とは、対向流の関係にあり、
前記第2流路を通過する前記冷媒と前記第3流路を通過する前記熱媒体とは、対向流の関係にある、請求項1~4のいずれか1項に記載の空気調和装置。 - 前記熱交換器は、
前記圧縮機に吸入される前記冷媒が通過する第1流路と、
前記凝縮器を通過した前記冷媒が通過する第2流路と、
前記熱媒体が通過する第3流路とを備え、
前記第2流路と前記第3流路は、熱交換するように隣接して配置される、請求項1~4のいずれか1項に記載の空気調和装置。 - 前記熱交換器は、内側から外側に向けて内管、中管、外管が順に配置された3重管式熱交換器であり、
前記内管は、前記第1流路であり、
前記中管と前記内管との間に、前記第2流路が形成され、
前記中管と前記外管との間に、前記第3流路が形成される、請求項6に記載の空気調和装置。 - 前記凝縮器は、前記熱媒体と前記冷媒とが熱交換するように構成される、請求項1~7のいずれか1項に記載の空気調和装置。
- 前記冷媒は、プロパンである、請求項1~8のいずれか1項に記載の空気調和装置。
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