WO2023042268A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2023042268A1 WO2023042268A1 PCT/JP2021/033771 JP2021033771W WO2023042268A1 WO 2023042268 A1 WO2023042268 A1 WO 2023042268A1 JP 2021033771 W JP2021033771 W JP 2021033771W WO 2023042268 A1 WO2023042268 A1 WO 2023042268A1
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- Prior art keywords
- heat exchanger
- refrigerant
- flow path
- temperature
- compressor
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- 239000003507 refrigerant Substances 0.000 claims abstract description 139
- 239000002826 coolant Substances 0.000 claims description 8
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical group CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 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 49
- 238000001816 cooling Methods 0.000 description 32
- 238000010586 diagram Methods 0.000 description 15
- 238000010438 heat treatment Methods 0.000 description 15
- 238000005057 refrigeration Methods 0.000 description 11
- 230000007423 decrease Effects 0.000 description 8
- 238000012545 processing Methods 0.000 description 8
- 230000001105 regulatory effect Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 7
- 238000001704 evaporation Methods 0.000 description 6
- 230000008020 evaporation Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000006870 function Effects 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 239000008399 tap water Substances 0.000 description 3
- 235000020679 tap water Nutrition 0.000 description 3
- 230000008901 benefit 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
- 238000010792 warming Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000008859 change 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
- 230000001276 controlling effect Effects 0.000 description 1
- 239000003673 groundwater Substances 0.000 description 1
- 239000001282 iso-butane Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229910000679 solder Inorganic materials 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
Definitions
- the present 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.
- a first heat exchanger having a second flow path for heat exchange between the refrigerant passing through the first flow path and the refrigerant passing through the second flow path, and the refrigerant directed from the outlet of the second flow path to the compressor.
- a second heat exchanger having a third flow path through which the gas flows and a fourth flow path through which the heat medium flows, and for exchanging heat between the refrigerant passing through the third flow path and the heat medium passing through the fourth flow path;
- a flow control device that adjusts the amount of medium supplied to the second heat exchanger, a temperature sensor that detects the temperature of the heat medium, and a control device that controls the flow control device according to the output of the temperature sensor.
- 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 of a refrigeration cycle using R290 refrigerant with an internal heat exchanger and an external heat exchanger in the configuration of Embodiment 1;
- 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 cross-section F1 of FIG. 6; 4 is a perspective view showing the appearance of an external heat exchanger 400.
- FIG. FIG. 9 is a cross-sectional view of the external heat exchanger 400 in cross-section F2 of FIG. 8; 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. 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.
- the air conditioner 1000 shown in FIG. 1 includes a refrigerant circuit 500, an internal heat exchanger 250, an external heat exchanger 400, 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 includes a flow path R1 and a flow path R2.
- the high-pressure, high-temperature refrigerant that has passed through the condenser (outdoor heat exchanger 210) flows through the flow path R1.
- the low-pressure, low-temperature refrigerant sucked by the compressor 200 flows through the flow path R2.
- 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 compressor 200.
- the external heat exchanger 400 includes a flow path R3 and a flow path R4.
- the refrigerant flowing toward the compressor 200 from the outlet of the second flow path R2 of the internal heat exchanger flows through the flow path R3.
- An external cooling heat medium conveyed from the flow path 410 flows through the flow path R4.
- External heat exchanger 400 is configured to perform heat exchange between the refrigerant passing through flow path R3 and the external cooling heat medium passing through flow path R4.
- 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.
- external heat exchanger 400 may be cooled by sprinkling water from the outside.
- the flow rate adjusting device 420 adjusts the amount of heat medium such as water for cooling the external heat exchanger 400 supplied to the external heat exchanger 400 .
- 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 260-263 and 411.
- a temperature sensor 260 is arranged in a suction pipe of the compressor 200 and measures a refrigerant suction temperature T260.
- the temperature sensor 261 is arranged in a pipe connecting the flow path R2 of the internal heat exchanger 250 and the flow path R3 of the external heat exchanger 400, and measures 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 temperature of the low-pressure refrigerant at the inlet of the external heat exchanger 400 obtained by the temperature sensor 261, it can be cooled by water. As a result, the temperature of the low-pressure refrigerant whose temperature has risen due to heat exchange with the high-pressure refrigerant in the internal heat exchanger 250 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 in FIG. 1 includes the external heat exchanger 400 that can be cooled with water, but the air conditioner 2000 differs from the air conditioner 1000 in that the external heat exchanger 400 is not provided.
- 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 of a refrigeration cycle using R290 refrigerant with an internal heat exchanger and an external 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. 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 refrigerant sucked into compressor 200 is cooled by external heat exchanger 400 .
- the compressor suction point is shifted to the right across the isothermal line, but this shift can be eliminated. Therefore, a reduction in inhalation density can be avoided.
- 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).
- 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 taken along section F1 in FIG.
- the internal heat exchanger 250 shown in FIGS. 6 and 7 has a double tube structure including an inner tube 251 and an outer tube 252 .
- 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 outer tube 252 serves as a flow path R2 through which the high-pressure refrigerant flowing out from the outlet of the outdoor heat exchanger 210 flows during cooling.
- the coolant flowing through the flow path R1 and the coolant flowing through the flow path R2 have a countercurrent relationship.
- FIG. 8 is a perspective view showing the external appearance of the external heat exchanger 400.
- FIG. FIG. 9 is a cross-sectional view of external heat exchanger 400 taken along section F2 in FIG.
- the external heat exchanger 400 shown in FIGS. 8 and 9 has a double tube structure including an inner tube 401 and an outer tube 402 .
- the inner pipe 401 serves as a flow path R3 through which the low-pressure refrigerant returning to the suction portion of the compressor 200 flows.
- Flow path R3 is located between flow path R2 and the suction port of compressor 200 .
- the outer pipe 402 serves as a channel R4 through which water transported from the outside flows through the channel 410 .
- the coolant flowing through the flow path R3 and the water flowing through the flow path R4 have a countercurrent relationship.
- the external heat exchanger 400 has the flow path R4, water is used as the cooling medium flowing through the flow path R4, and the external heat exchanger 400 is a double pipe.
- the cooling medium does not have to be water.
- the external heat exchanger 400 may not be a double tube, and may be a plate heat exchanger or the like.
- the flow path through which the cooling medium such as water flows does not have to be a closed space.
- the flow path R3 of the internal heat exchanger 250 may be a tube, and the tube may be immersed in a grooved water path to cool the refrigerant flowing through the flow path R3.
- water may be sprayed to cool the piping to the suction of the compressor 200 .
- the internal heat exchanger 250 is installed so as to function during cooling, there is no problem if it is installed so as to function during heating.
- the internal heat exchanger 250 may not be a double pipe, but may be, for example, a plate heat exchanger or the like, or may have a form in which the low-pressure pipe and the high-pressure pipe are brought into contact with each other using solder or the like to exchange heat.
- the suction temperature may be estimated from the amount of heat exchange on the water side by acquiring the outlet temperature on the water side.
- 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. 10 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 flow path R ⁇ b>2 of the internal heat exchanger 250 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 .
- the control device 100 turns off the flow rate adjusting device 420 in step S13. It is controlled to be fully closed so that water does not flow to the external heat exchanger 400 .
- 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. 11 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 gas-liquid two phases, so it is desirable to control the state of the refrigerant in the evaporator so that the amount of gaseous refrigerant is reduced as much as possible. be.
- 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. 11 is temporarily exited.
- the flow regulating device 420 is fully closed (YES in S23)
- the external heat exchanger 400 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. 12 is a diagram showing the configuration of an air conditioner 1001 to which a sensor used for heating is added. Specifically, air conditioner 1001 further includes temperature sensors 264 and 265 in addition to the configuration of air conditioner 1000 shown in FIG.
- FIG. 13 is a flowchart for explaining control of the flow rate adjusting device 420 during heating.
- step S31 the control device 100 acquires the outlet refrigerant temperature T261 of the flow path R2 of the internal heat exchanger 250 from the temperature sensor 261, and acquires the water temperature T411 from the temperature sensor 411.
- step S ⁇ b>32 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 .
- the control device 100 switches the flow rate adjusting device 420 to step S33. It is controlled to be fully closed so that water does not flow to the external heat exchanger 400 .
- 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).
- the suction SH is calculated by subtracting the evaporation temperature T264 obtained by temperature sensor 264 from the suction temperature T260 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.
- evaporator outlet SH is calculated by subtracting the evaporating temperature obtained by temperature sensor 264 from the value of temperature sensor 265 .
- 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. 14 is a diagram showing the configuration of an air conditioner 1002 according to Embodiment 2. As shown in FIG. 14
- outdoor heat exchanger 210 in FIG. 14 is configured to exchange heat with water, which is a cooling source from the outside.
- the water may be circulated and cooled, for example, in a cooling tower, and then resupplied from a water supply pipe.
- tap water or the like may be newly supplied.
- 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 external heat exchanger 400 may be used in a cooling-only air conditioner without 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 external heat exchanger 400 shown in FIG. 1 uses an external cooling source to suppress the decrease in the density of the sucked refrigerant, so that the performance of the air conditioner can be improved even when the R32 refrigerant is used.
- 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). , a first flow path R1 through which the refrigerant that has passed through the condenser (outdoor heat exchanger 210) flows, and a second flow path R2 through which the refrigerant sucked into the compressor 200 flows, and the refrigerant passing through the first flow path R1 and a first heat exchanger (internal heat exchanger 250) that exchanges heat with the refrigerant passing through the second flow path R2, and a third flow path R3 through which refrigerant flows from the outlet of the second flow path R2 toward the compressor 200 and a fourth flow path R4 through which a heat medium flows, and a second heat exchanger (external heat exchanger 400 ), a flow rate adjusting device 420 for adjusting the amount of heat medium supplied to the second heat exchanger (external heat exchanger 400),
- the control device 100 controls the second heat exchanger (external heat exchanger 400) when the temperature T411 of the heat medium is lower than the temperature T261 of the refrigerant flowing into the second heat exchanger (external heat exchanger 400).
- the flow control device 420 is controlled so that the heat medium is supplied to the heat exchanger (external heat exchanger 400).
- Control device 100 transfers heat to the second heat exchanger (external heat exchanger 400) when the temperature T411 of the heat medium is higher than the temperature T261 of the refrigerant flowing into the second heat exchanger (external heat exchanger 400). Control the flow regulator 420 so that no medium is supplied.
- the second heat exchanger (external heat exchanger 400) is a double-tube heat exchanger in which an inner tube 401 and an outer tube 402 are arranged.
- the inner tube 401 is the third flow path R3 through which the refrigerant passes
- the outer tube 402 is the fourth flow path R4 through which the heat medium passes.
- the condenser (outdoor heat exchanger 270) 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, 325, 400, 550 heat exchanger, 120 indoor fan, 200 compressor, 220 outdoor fan, 230 expansion valve, 240 four-way valve, 251, 401 Inner tube, 252, 402 Outer tube, 260 to 265, 411 Temperature sensor, 410, R1 to R4 Flow path, 420 Flow control device, 500 Refrigerant circuit, 1000, 1001, 1002, 2000 Air conditioner, P1 to 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、外部熱交換器400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、外部熱交換器400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 (5)
- 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が流れる第1流路および前記圧縮機に吸入される前記冷媒が流れる第2流路を有し、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を熱交換させる第1熱交換器と、
前記第2流路の出口から前記圧縮機に向かう前記冷媒が流れる第3流路および熱媒体が流れる第4流路を有し、前記第3流路を通過する前記冷媒と前記第4流路を通過する前記熱媒体とを熱交換させる第2熱交換器と、
前記熱媒体を前記第2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、前記第2熱交換器に流入す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、前記第2熱交換器に前記熱媒体が供給されるように前記流量調整装置を制御し、
前記制御装置は、前記第2熱交換器に流入する前記冷媒の温度よりも前記熱媒体の温度が高い場合に、前記第2熱交換器に前記熱媒体が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に記載の空気調和装置。 - 前記第2熱交換器は、内管と外管が配置された2重管式熱交換器であり、
前記内管は、前記冷媒が通過する前記第3流路であり、
前記外管は、前記熱媒体が通過する前記第4流路である、請求項1または2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1~3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1~4のいずれか1項に記載の空気調和装置。
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2006194518A (ja) * | 2005-01-13 | 2006-07-27 | Daikin Ind Ltd | 冷凍装置 |
JP2009162403A (ja) | 2007-12-28 | 2009-07-23 | Toshiba Carrier Corp | 空気調和機 |
JP2013249988A (ja) * | 2012-05-31 | 2013-12-12 | Sanden Corp | ヒートポンプ装置 |
JP2016125714A (ja) * | 2014-12-26 | 2016-07-11 | ダイキン工業株式会社 | 蓄熱式空気調和機 |
WO2019155614A1 (ja) * | 2018-02-09 | 2019-08-15 | 三菱電機株式会社 | 空気調和装置、空調システム及び熱交換ユニット |
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JP2006194518A (ja) * | 2005-01-13 | 2006-07-27 | Daikin Ind Ltd | 冷凍装置 |
JP2009162403A (ja) | 2007-12-28 | 2009-07-23 | Toshiba Carrier Corp | 空気調和機 |
JP2013249988A (ja) * | 2012-05-31 | 2013-12-12 | Sanden Corp | ヒートポンプ装置 |
JP2016125714A (ja) * | 2014-12-26 | 2016-07-11 | ダイキン工業株式会社 | 蓄熱式空気調和機 |
WO2019155614A1 (ja) * | 2018-02-09 | 2019-08-15 | 三菱電機株式会社 | 空気調和装置、空調システム及び熱交換ユニット |
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