WO2020110213A1 - Climatiseur - Google Patents

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Publication number
WO2020110213A1
WO2020110213A1 PCT/JP2018/043684 JP2018043684W WO2020110213A1 WO 2020110213 A1 WO2020110213 A1 WO 2020110213A1 JP 2018043684 W JP2018043684 W JP 2018043684W WO 2020110213 A1 WO2020110213 A1 WO 2020110213A1
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WIPO (PCT)
Prior art keywords
heat exchange
exchange section
refrigerant
heat exchanger
flow path
Prior art date
Application number
PCT/JP2018/043684
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English (en)
Japanese (ja)
Inventor
森田　敦
中村　伸
前田　剛志
暁 八柳
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/043684 priority Critical patent/WO2020110213A1/fr
Priority to JP2020557445A priority patent/JP7210609B2/ja
Publication of WO2020110213A1 publication Critical patent/WO2020110213A1/fr

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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
    • F25B39/00—Evaporators; 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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

Definitions

  • the present invention relates to an air conditioner.
  • the outdoor heat exchanger functions as an evaporator during heating operation.
  • the outdoor heat exchanger has a plurality of fins and a pipe penetrating the plurality of fins.
  • frost forms on the surfaces of the plurality of fins of the outdoor heat exchanger depending on the outside air conditions. If this frost is stuck between the plurality of fins, the heating capacity of the air conditioner is reduced. Therefore, the defrosting operation is performed in order to suppress a decrease in heating capacity due to frost formation.
  • the defrosting operation is performed, for example, by detecting the state of frost formation for a certain period of time or the outside air temperature or the change of the refrigeration cycle temperature.
  • the cooling operation cycle is performed by switching the four-way valve during the heating operation.
  • high-temperature refrigerant flows into the outdoor heat exchanger, thereby melting the frost attached to the plurality of fins of the outdoor heat exchanger.
  • the indoor blower and the outdoor blower of the air conditioner are stopped, and the heating operation is interrupted. Since the heating operation is interrupted during the defrosting operation, the room temperature drops. Therefore, if the defrosting operation is frequently performed, the user who causes the air conditioner to perform the heating operation feels uncomfortable.
  • Patent Document 1 Japanese Unexamined Patent Publication No. 2009-30852 (Patent Document 1) describes an air conditioner capable of suppressing frost formation in an outdoor heat exchanger.
  • the third heat exchanger which functions as a condenser during the heating operation, is arranged on the windward side of the outdoor heat exchanger. Since the high-temperature and high-pressure refrigerant flows through the third heat exchanger, the temperature of the air passing through the third heat exchanger becomes higher than that of the outside air. Therefore, since the temperature of the air flowing into the outdoor heat exchanger becomes higher than the temperature of the outside air, it becomes possible to suppress the frost formation in the outdoor heat exchanger.
  • the refrigerant is basically allowed to flow to the bypass circuit without flowing to the third heat exchanger during the cooling operation.
  • the refrigerant is caused to flow through the third heat exchanger, and the third heat exchanger functions as an evaporator.
  • the third heat exchanger In cooling operation, if the refrigerant is flowed to the bypass circuit without flowing to the third heat exchanger, the third heat exchanger will not function as a heat exchanger. Further, in the cooling operation, when the third heat exchanger functions as an evaporator, the third heat exchanger does not function as a condenser. Therefore, the condensing capacity cannot be improved by the third heat exchanger during the cooling operation.
  • the present invention has been made in view of the above problems, and an object thereof is to be able to suppress frost formation of the outdoor heat exchanger during heating operation, and to improve the condensation capacity of the outdoor heat exchanger during cooling operation. It is to provide an air conditioner capable of
  • the air conditioner of the present invention includes a compressor, a flow path switching valve, an outdoor heat exchanger, a flow path guiding device, an expansion valve, and an indoor heat exchanger.
  • the compressor compresses and discharges the refrigerant.
  • the flow path switching valve is connected to the compressor.
  • the outdoor heat exchanger includes a first heat exchange unit connected to the flow path switching valve and a second heat exchange unit.
  • the flow channel guide device is connected to the first heat exchange section and the second heat exchange section.
  • the expansion valve is connected to the second heat exchange section and the flow path guide device.
  • the indoor heat exchanger is connected to the flow path switching valve and the flow path guide device.
  • the flow path switching valve switches the refrigerant flow so that the refrigerant discharged from the compressor flows to the indoor heat exchanger during the heating operation and the refrigerant discharged from the compressor flows to the outdoor heat exchanger during the cooling operation. It is configured.
  • the flow path guiding device causes the refrigerant flowing from the indoor heat exchanger during the heating operation to flow into the second heat exchange section, and causes the refrigerant flowing from the expansion valve via the second heat exchange section to flow into the first heat exchange section, During the cooling operation, the refrigerant flowing from the first heat exchange section is caused to flow to the second heat exchange section, and the refrigerant flow is guided so that the refrigerant flowing from the expansion valve via the second heat exchange section is caused to flow to the indoor heat exchanger. Is configured.
  • the refrigerant that has flowed from the indoor heat exchanger during the heating operation is caused to flow to the second heat exchange section and also flowed from the expansion valve via the second heat exchange section.
  • Refrigerant flowing into the first heat exchange section, refrigerant flowing from the first heat exchange section during cooling operation is caused to flow into the second heat exchange section, and refrigerant flowing from the expansion valve via the second heat exchange section is exchanged with indoor heat.
  • It is configured to guide the flow of the refrigerant so as to flow into the container. Therefore, it is possible to suppress frost formation on the outdoor heat exchanger by causing the refrigerant to flow through the second heat exchange unit during the heating operation. Further, the condensing capacity of the outdoor heat exchanger can be improved by causing the refrigerant to flow through the second heat exchange section during the cooling operation.
  • FIG. 3 is an example of a Mollier diagram in the cooling operation of the air conditioner according to Embodiment 1 of the present invention. It is a figure which shows schematically the structure of the outdoor heat exchanger of the air conditioner which concerns on Embodiment 2 of this invention. It is a figure which shows schematically the structure of the modification of the outdoor heat exchanger of the air conditioner which concerns on Embodiment 2 of this invention.
  • FIG. 1 is a refrigerant circuit diagram showing the configuration of an air conditioner 300 according to Embodiment 1 of the present invention.
  • the air conditioner 300 mainly includes an outdoor unit 100, an indoor unit 200, a gas side extension pipe 10, and a liquid side extension pipe 20.
  • the gas side extension pipe 10 is a pipe that connects the outdoor unit 100 and the indoor unit 200, and a large amount of gas single-phase refrigerant flows during operation.
  • the liquid-side extension pipe 20 is a pipe that connects the outdoor unit 100 and the indoor unit 200, and a large amount of liquid single-phase refrigerant flows during operation.
  • the outdoor unit 100 mainly includes a compressor 1, a flow path switching valve 2, an outdoor heat exchanger 3, an outdoor blower 4, a flow path guiding device 5, and an expansion valve 6.
  • a compressor 1, a flow path switching valve 2, an outdoor heat exchanger 3, an outdoor blower 4, a flow path guiding device 5, and an expansion valve 6 are housed in the outdoor unit 100.
  • the indoor unit 200 mainly includes an indoor heat exchanger 7 and an indoor blower 8. The indoor heat exchanger 7 and the indoor blower 8 are housed in the indoor unit 200.
  • a refrigerant circuit is configured by connecting the compressor 1, the flow path switching valve 2, the outdoor heat exchanger 3, the flow path guiding device 5, the expansion valve 6, and the indoor heat exchanger 7 by piping. ing.
  • the compressor 1 is configured to compress the drawn refrigerant and discharge it.
  • the compressor 1 may have a variable capacity.
  • the compressor 1 may be configured so that the capacity changes by adjusting the rotation speed of the compressor 1 based on an instruction from a control device (not shown).
  • the flow path switching valve 2 is connected to the compressor 1, the outdoor heat exchanger 3, and the indoor heat exchanger 7.
  • the flow path switching valve 2 is configured to switch the flow of the refrigerant flowing through the refrigerant circuit between the heating operation and the cooling operation.
  • the flow path switching valve 2 allows the refrigerant discharged from the compressor 1 to flow into the indoor heat exchanger 7 during the heating operation, and the refrigerant discharged from the compressor 1 to flow into the outdoor heat exchanger 3 during the cooling operation. It is configured to switch the flow.
  • the outdoor heat exchanger 3 is for exchanging heat between the refrigerant flowing in the outdoor heat exchanger 3 and the outdoor air.
  • the outdoor heat exchanger 3 includes a first heat exchange section 3a and a second heat exchange section 3b.
  • the first heat exchange section 3a is connected to the flow path switching valve 2.
  • the second heat exchange unit 3b is connected to the first heat exchange unit 3a via the flow path guiding device 5.
  • the first heat exchange section 3a and the second heat exchange section 3b are in a positional relationship of being adjacent to each other.
  • the second heat exchange section 3b adds the heat of the refrigerant flowing through the second heat exchange section 3b and the heat of the air warmed by passing through the second heat exchange section 3b to the first heat exchange section 3a.
  • the 1st heat exchange part 3a is arrange
  • the second heat exchange section 3b may be in contact with the first heat exchange section 3a, and the second heat exchange section 3b may not be in contact with the first heat exchange section 3a.
  • the first heat exchange section 3a functions as an evaporator that evaporates the refrigerant during heating operation, and functions as a condenser that condenses the refrigerant during cooling operation.
  • the second heat exchange unit 3b functions as a condenser that condenses cooling during both heating operation and cooling operation.
  • the second heat exchange unit 3b is arranged between the indoor heat exchanger 7 that functions as a condenser and the expansion valve 6 in the refrigerant circuit during the heating operation.
  • the second heat exchange section 3b is disposed between the expansion valve 6 and the first heat exchange section 3a which functions as a condenser in the refrigerant circuit during the cooling operation.
  • the first heat exchange section 3a and the second heat exchange section 3b are plate fin tube type heat exchangers each having a plurality of fins and a circular tube or a flat tube heat transfer tube penetrating the plurality of fins.
  • An outdoor blower 4 is attached to the outdoor heat exchanger 3.
  • the outdoor blower 4 is configured to supply the air flowing around the outdoor heat exchanger 3.
  • the outdoor blower 4 adjusts the amount of air flowing around the outdoor heat exchanger 3 by adjusting the number of rotations of the outdoor blower 4 based on an instruction from a control device (not shown), and thereby the outdoor air and the refrigerant are separated from each other. It is configured to adjust the amount of heat exchange between them.
  • the flow path guide device 5 is connected to the first heat exchange section 3a and the second heat exchange section 3b.
  • the flow path guide device 5 is arranged between the first heat exchange section 3a and the second heat exchange section 3b in the refrigerant circuit.
  • the flow passage guide device 5 has a function of changing the direction of the refrigerant flow in the refrigerant circuit between the heating operation and the cooling operation.
  • the refrigerant circuit becomes a path for the refrigerant from the second heat exchange section 3b to the first heat exchange section 3a via the expansion valve 6 during the heating operation, and the cooling circuit is provided.
  • the refrigerant has a path from the first heat exchange section 3a to the expansion valve 6 via the second heat exchange section 3b.
  • the flow path guide device 5 is configured to guide the flow of the refrigerant as follows during the heating operation and the cooling operation, respectively. That is, the flow path guiding device 5 causes the refrigerant flowing from the indoor heat exchanger 7 during the heating operation to flow to the second heat exchange section 3b and to transfer the refrigerant flowing from the expansion valve 6 via the second heat exchange section 3b to the first heat exchange section 3b. It is configured to guide the flow of the refrigerant so as to flow to the first heat exchange section 3a.
  • the flow path guiding device 5 causes the refrigerant flowing from the first heat exchange section 3a during the cooling operation to flow to the second heat exchange section 3b, and at the same time, to flow the refrigerant flowing from the expansion valve 6 via the second heat exchange section 3b. It is configured to guide the flow of the refrigerant so as to flow to the indoor heat exchanger 7.
  • the flow path guiding device 5 is a four-way valve 5a. Further, referring to FIG. 2, the flow path guiding device 5 may be a check valve bridge circuit 5b.
  • the check valve bridge circuit 5b is composed of four check valves.
  • the check valve bridge circuit 5b shown in FIG. 2 is configured to function similarly to the four-way valve 5a shown in FIG.
  • the expansion valve 6 is connected to the second heat exchange section 3b and the flow path guide device 5.
  • the expansion valve 6 is configured to reduce the pressure by expanding the refrigerant condensed in the condenser.
  • the expansion valve 6 serves as a throttle device that reduces the pressure of the refrigerant condensed by the indoor heat exchanger 7 and the second heat exchange section 3b during the heating operation, and during the cooling operation, the outdoor heat exchanger 3 (the first heat exchange section 3a and the second heat exchange section 3a).
  • the expansion device reduces the pressure of the refrigerant condensed by the heat exchange section 3b).
  • the expansion valve 6 is, for example, an electronic control valve.
  • the indoor heat exchanger 7 is for exchanging heat between the refrigerant flowing in the indoor heat exchanger 7 and the indoor air.
  • the indoor heat exchanger 7 is connected to the flow path switching valve 2 and the flow path guide device 5.
  • the indoor heat exchanger 7 functions as a condenser that condenses the refrigerant during the heating operation, and functions as an evaporator that evaporates the refrigerant during the cooling operation.
  • the indoor heat exchanger 7 is a plate fin tube type heat exchanger having a plurality of fins and a circular or flat heat transfer tube penetrating the plurality of fins.
  • An indoor blower 8 is installed alongside the indoor heat exchanger 7.
  • the indoor blower 8 is configured to supply air flowing around the indoor heat exchanger 7.
  • the indoor blower 8 adjusts the amount of air flowing around the indoor heat exchanger 7 by adjusting the number of revolutions of the indoor blower 8 based on an instruction from a control device (not shown), and thereby the indoor air and the refrigerant are separated from each other. It is configured to adjust the amount of heat exchange between them.
  • the air conditioner 300 according to the present embodiment can selectively perform the heating operation and the cooling operation.
  • the solid line arrow in FIG. 1 indicates the refrigerant flow during the heating operation, and the broken line arrow in the figure indicates the refrigerant flow during the cooling operation. Note that this point is the same in the refrigerant circuit diagrams in the following figures.
  • the heating operation of the air conditioner 300 will be described.
  • the compressor 1, the flow path switching valve 2, the gas side extension pipe 10, the indoor heat exchanger 7, the liquid side extension pipe 20, the flow path guiding device 5, the second heat exchange section 3b, the expansion valve 6, the flow Refrigerant circulates through the refrigerant circuit in the order of the path guide device 5, the first heat exchange section 3a, and the flow path switching valve 2.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 1 is discharged from the compressor 1, passes through the flow path switching valve 2 and the gas side extension pipe 10, reaches the indoor heat exchanger 7, and is blown by the indoor blower 8. It radiates heat to the stored indoor air to condense and become high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant reaches the second heat exchange section 3b via the liquid-side extension pipe 20 and the flow path guiding device 5, and is further condensed by radiating heat to the room air.
  • the high-pressure liquid refrigerant is decompressed by expanding in the expansion valve 6, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • This low-temperature low-pressure gas-liquid two-phase refrigerant reaches the first heat exchange section 3a via the flow path guiding device 5, and absorbs heat from the outdoor air blown by the outdoor blower 4 in the first heat exchange section 3a. This evaporates and becomes a low-pressure vapor refrigerant.
  • the low-pressure vapor refrigerant returns to the compressor 1 via the flow path switching valve 2 and is compressed by the compressor 1. In this way, the refrigerant circulates in the refrigerant circuit during the heating operation.
  • the cooling operation of the air conditioner 300 will be described.
  • the refrigerant circulates through the refrigerant circuit in the order of the indoor heat exchanger 7, the gas side extension pipe 10, and the flow path switching valve 2.
  • the high-temperature and high-pressure gas refrigerant compressed in the compressor 1 is discharged from the compressor 1, passes through the flow path switching valve 2, reaches the first heat exchange section 3 a, and becomes the outdoor air blown by the outdoor blower 4. On the other hand, it radiates heat to condense and become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant reaches the second heat exchange section 3b via the flow path guiding device 5 and radiates heat to the outdoor air to be further condensed.
  • the high-pressure liquid refrigerant is decompressed by being expanded by the expansion valve 6, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature low-pressure gas-liquid two-phase refrigerant reaches the indoor heat exchanger 7 via the liquid side extension pipe 20 and evaporates by absorbing heat from the indoor air blown by the indoor blower 8 to form a low-pressure vapor refrigerant.
  • the low-pressure vapor refrigerant returns to the compressor 1 via the gas side extension pipe 10 and the flow path switching valve 2, and is compressed in the compressor 1. In this way, in the cooling operation, the refrigerant circulates in the refrigerant circuit.
  • FIG. 3 is an example of a Mollier diagram in the heating operation of the air conditioner 300.
  • an indoor temperature isotherm IA and an outdoor temperature isotherm OA are shown.
  • the dashed arrows in FIG. 3 indicate the direction of heat dissipation or heat absorption in each heat exchanger.
  • the refrigerant in a relatively high temperature and high pressure state flows through the second heat exchange section 3b, causing condensation of the refrigerant or supercooling of the liquid refrigerant.
  • Refrigerant in a relatively low temperature and low pressure state flows through the first heat exchange section 3a, and the refrigerant evaporates.
  • frost may occur in the first heat exchange section 3a.
  • the second heat exchange section 3b and the first heat exchange section 3a are adjacent to each other, the heat of the refrigerant flowing through the second heat exchange section 3b and the heat of the second heat exchange section 3b are heated. It becomes possible to suppress the frost formation of the 1st heat exchange part 3a by the heat of air.
  • the refrigerant exchanges heat with the air having an outdoor temperature lower than the indoor temperature, so that the temperature difference between the refrigerant and the air becomes large. Therefore, it is possible to increase the heat exchange amount as compared with the configuration without the second heat exchange portion 3b.
  • FIG. 4 is an example of a Mollier diagram in the cooling operation of the air conditioner 300. Also in FIG. 4, the isotherm IA of the indoor temperature and the isotherm OA of the outdoor temperature are shown. As shown in FIG. 4, in the cooling operation as well, as in the heating operation, the refrigerant in a relatively high temperature and high pressure state flows in the second heat exchange section 3b, and the refrigerant is condensed or the liquid refrigerant is supercooled. Therefore, the second heat exchange section 3b plays a role of assisting the first heat exchange section 3a which functions as a condenser.
  • the flow passage guide device 5 causes the second heat exchanging unit 3b to cool the high-temperature high-pressure refrigerant to the outside air in both the heating operation and the cooling operation. Function as. Therefore, in the heating operation, it is possible to suppress frost formation on the first heat exchange section 3a by the heat of the air warmed by passing through the second heat exchange section 3b or the second heat exchange section 3b. Moreover, in the cooling operation, the second heat exchange section 3b can promote the condensation and supercooling of the refrigerant.
  • the flow path guiding device 5 causes the refrigerant flowing from the indoor heat exchanger 7 during the heating operation to flow to the second heat exchange section 3b and to cause the second heat exchange section 3b to operate.
  • the refrigerant that has flowed in from the expansion valve 6 via the first heat exchange section 3a is caused to flow, and the refrigerant that has flowed in from the first heat exchange section 3a during the cooling operation is caused to flow to the second heat exchange section 3b and the second heat exchange section 3b.
  • the refrigerant flow is configured so that the refrigerant flowing from the expansion valve 6 via the indoor heat exchanger 7 is guided.
  • the refrigerant when the refrigerant is caused to flow through the second heat exchange section 3b during the heating operation, the heat of the refrigerant flowing through the second heat exchange section 3b and the heat of the air warmed by passing through the second heat exchange section 3b generate the first heat.
  • the frost formation of the 1 heat exchange part 3a can be suppressed. Therefore, frost formation on the outdoor heat exchanger 3 can be suppressed.
  • the refrigerant is condensed in the second heat exchange section 3b by flowing the refrigerant through the second heat exchange section 3b during the cooling operation. Therefore, the condensation capacity of the outdoor heat exchanger 3 can be improved. This enables highly efficient operation of the air conditioner 300.
  • the flow path guiding device 5 is the four-way valve 5a. Therefore, the flow of the refrigerant can be accurately guided by the four-way valve 5a.
  • the flow path guiding device 5 may be the check valve bridge circuit 5b. Since the check valve bridge circuit 5b does not require the control mechanism of the flow channel guide device 5, the flow channel guide device 5 is less likely to malfunction. Further, since the check valve bridge circuit 5b does not require the control mechanism of the flow channel guiding device 5, programming for the flow channel guiding device 5 is unnecessary. Therefore, the design cost of the flow channel guide device 5 is reduced.
  • Embodiment 2 An air conditioner 300 according to Embodiment 2 of the present invention will be described with reference to FIG. Note that the air conditioner 300 according to Embodiments 2 to 5 of the present invention has the same configuration, operation, and effect as the air conditioner 300 according to Embodiment 1 of the present invention described above, unless otherwise specified. ing.
  • the second heat exchange section 3b is in contact with the lower portion of the first heat exchange section 3a.
  • the second heat exchange section 3b is arranged vertically below the first heat exchange section 3a.
  • the second heat exchange section 3b is arranged directly below the first heat exchange section 3a.
  • the first heat exchange section 3a and the second heat exchange section 3b are configured integrally. That is, the first heat exchange section 3a and the second heat exchange section 3b are not separated from each other. The first heat exchange section 3a and the second heat exchange section 3b are connected to each other.
  • the flow path guiding device 5 is a four-way valve 5a. Further, referring to FIG. 6, the flow path guiding device 5 may be a check valve bridge circuit 5b. The check valve bridge circuit 5b shown in FIG. 6 is configured to function similarly to the four-way valve 5a shown in FIG.
  • the air conditioner 300 of the present embodiment since the second heat exchanging portion 3b is in contact with the lower portion of the first heat exchanging portion 3a, the refrigerant is allowed to flow to the second heat exchanging portion 3b during the heating operation. As a result, it becomes possible to suppress freezing of the condensed water that has accumulated below the outdoor heat exchanger 3.
  • the first heat exchanging unit 3a and the second heat exchanging unit 3b are integrally configured, so that the first heat exchanging unit 3a and the second heat exchanging unit are used. Manufacturing of 3b becomes easy.
  • Embodiment 3 An air conditioner 300 according to Embodiment 3 of the present invention will be described with reference to FIG. 7. As shown in FIG. 7, in the air conditioner 300 according to the present embodiment, the second heat exchange section 3b is in contact with the lower portion of the first heat exchange section 3a. The 1st heat exchange part 3a and the 2nd heat exchange part 3b are comprised by the integral structure. Therefore, the air conditioner 300 according to the present embodiment has the same effect as the air conditioner 300 according to the second embodiment of the present invention described above.
  • the outdoor blower 4 shown in FIG. 1 causes air to flow into the outdoor heat exchanger 3 as indicated by the white arrow in FIG. 7.
  • the second heat exchange unit 3b is arranged on the windward side of the first heat exchange unit 3a in the flow direction of the air flowing through the outdoor heat exchanger 3.
  • the second heat exchange section 3b is arranged below the first heat exchange section 3a so as to cover a part of the windward side of the first heat exchange section 3a.
  • the second heat exchange section 3b only needs to be arranged so as to include the lower portion of the first heat exchange section 3a, and is arranged so as to cover the entire windward side (entire surface) of the first heat exchange section 3a. May be.
  • the second heat exchange section 3b is arranged on the upwind side of the first heat exchange section 3a in the flow direction of the air flowing through the outdoor heat exchanger 3. Therefore, during the heating operation, the air that has passed through the second heat exchange section 3b flows into the first heat exchange section 3a.
  • the temperature of the air that has passed through the second heat exchange section 3b becomes higher than the outside air temperature. Therefore, the temperature of the air flowing from the second heat exchange section 3b into the first heat exchange section 3a becomes higher than the outside air temperature. This makes it possible to suppress frost formation in the first heat exchange section 3a.
  • FIG. 9 shows pipes PI of the first heat exchange section 3a, the second heat exchange section 3b, and the indoor heat exchanger 7.
  • the equivalent flow path diameter of the second heat exchange section 3b is equal to the internal flow path of the first heat exchange section 3a or the indoor heat exchanger 7. Less than equivalent diameter.
  • Each of the first heat exchange section 3a, the second heat exchange section 3b, and the indoor heat exchanger 7 includes a pipe PI provided with an in-pipe flow passage FP through which a refrigerant flows.
  • the first equivalent diameter D1 of the in-pipe flow passage FP provided in the pipe P1 of the second heat exchange section 3b is the second equivalent diameter D2 of the in-pipe flow passage FP provided in the pipe P2 of the first heat exchange section 3a.
  • D3 of the in-pipe flow passages FP provided in the pipe P3 of the indoor heat exchanger 7.
  • the refrigerant in a relatively high temperature and high pressure state flows through the second heat exchange unit 3b during both the cooling operation and the heating operation. Therefore, in the second heat exchange section 3b, the refrigerant is condensed or the liquid refrigerant is supercooled. Therefore, in the second heat exchange section 3b, a large amount of the refrigerant in the liquid state occupies a state in which the density of the refrigerant is high and the flow velocity is low as compared with other places on the refrigerant circuit. Therefore, the amount of refrigerant in the refrigerant circuit can be reduced by reducing the equivalent diameter of the in-tube flow path of the second heat exchange section 3b. Further, by reducing the equivalent diameter of the second heat exchange portion 3b in the pipe, the flow velocity in the pipe is increased, so that heat transfer in the pipe can be promoted.
  • the first equivalent diameter D1 of the second heat exchange section 3b is the second equivalent diameter D2 of the first heat exchange section 3a and the second equivalent diameter D1 of the indoor heat exchanger 7. 3 is smaller than at least one of the equivalent diameters D3. Therefore, the amount of refrigerant in the refrigerant circuit can be reduced. Further, it becomes possible to promote heat transfer in the pipe PI of the second heat exchange section 3b.
  • Embodiment 5 An air conditioner 300 according to Embodiment 5 of the present invention will be described with reference to FIG. 10. As shown in FIG. 10, in the air conditioner 300 according to the present embodiment, the pressure drop portion 9 is provided between the indoor heat exchanger 7 and the flow passage guide device 5 on the refrigerant circuit.
  • the air conditioner 300 includes a connection pipe CP that connects the flow passage guide device 5 and the indoor heat exchanger 7.
  • the connection pipe CP includes a liquid side extension pipe 20.
  • the connection pipe CP includes a pressure drop unit 9.
  • the pressure drop unit 9 is, for example, a capillary tube.
  • the flow path guiding device 5 is a four-way valve 5a. Further, with reference to FIG. 11, the flow path guiding device 5 may be a check valve bridge circuit 5b. The check valve bridge circuit 5b shown in FIG. 11 is configured to function similarly to the four-way valve 5a shown in FIG.
  • connection pipe CP includes the liquid side extension pipe 20 and connects the indoor unit 200 and the outdoor unit 100, so that the length of the pipe is long and the internal volume of the pipe is large. That is, in the connection pipe CP, the amount of refrigerant present is larger than that in other places on the refrigerant circuit.
  • connection pipe CP since the connection pipe CP includes the pressure drop unit 9, the refrigerant flowing through the connection pipe CP can be decompressed to be in the two-phase state. Since the density of the refrigerant in the connection pipe CP is reduced by setting the refrigerant in the two-phase state, the amount of the refrigerant present in the connection pipe CP can be reduced.
  • the pressure drop section 9 is provided in the configuration of the conventional air conditioner, the refrigerant in the two-phase state flows into the expansion valve 6 from the pressure drop section 9, so that the expansion valve 6 cannot be controlled normally. .. Further, when the refrigerant passes through the expansion valve 6, a sound of the refrigerant flowing is generated.
  • the air conditioner 300 it is possible to recondense the two-phase refrigerant depressurized by the pressure lowering section 9 by the second heat exchange section 3b and return it to the liquid refrigerant in the heating operation. Becomes That is, since it becomes the liquid refrigerant immediately before flowing into the expansion valve 6, it is possible to prevent the refrigerant in the two-phase state from flowing into the expansion valve 6 from preventing normal control of the expansion valve 6. Further, it is possible to suppress the generation of the sound of the refrigerant flowing when the refrigerant passes through the expansion valve 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un climatiseur (300) étant pourvu : d'un compresseur (1) ; d'une valve de commutation de passage (2) ; d'un échangeur de chaleur extérieur (3) ; d'un dispositif de guidage de passage (5) ; d'un détendeur (6) ; et d'un échangeur de chaleur intérieur (7). L'échangeur de chaleur extérieur (3) comprend une première partie d'échange de chaleur (3a) et une seconde partie d'échange de chaleur (3b). Le dispositif de guidage de passage (5) est configuré pour guider l'écoulement d'un fluide frigorigène de façon à fournir le fluide frigorigène qui s'est écoulé depuis l'échangeur de chaleur intérieur (7) jusqu'à la seconde partie d'échange de chaleur (3b), et fournir le fluide frigorigène qui s'est écoulé depuis le détendeur (6) par l'intermédiaire de la seconde partie d'échange de chaleur (3b) vers la première partie d'échange de chaleur (3a) pendant une opération de chauffage, et de façon à fournir le fluide frigorigène qui s'est écoulé depuis la première partie d'échange de chaleur (3a) vers la seconde partie d'échange de chaleur (3b), et fournir le fluide frigorigène qui s'est écoulé depuis le détendeur (6) par l'intermédiaire de la seconde partie d'échange de chaleur (3b) vers l'échangeur de chaleur intérieur (7) pendant une opération de refroidissement.
PCT/JP2018/043684 2018-11-28 2018-11-28 Climatiseur WO2020110213A1 (fr)

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PCT/JP2018/043684 WO2020110213A1 (fr) 2018-11-28 2018-11-28 Climatiseur
JP2020557445A JP7210609B2 (ja) 2018-11-28 2018-11-28 空気調和機

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PCT/JP2018/043684 WO2020110213A1 (fr) 2018-11-28 2018-11-28 Climatiseur

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0285647A (ja) * 1988-09-20 1990-03-27 Sanyo Electric Co Ltd 空気調和機
JP3177302U (ja) * 2012-05-17 2012-07-26 株式会社Ｂ．Ｔ．Ｐ 冷暖房空調装置
WO2015059832A1 (fr) * 2013-10-25 2015-04-30 三菱電機株式会社 Échangeur thermique et dispositif à cycle de réfrigération utilisant ledit échangeur thermique
JP2016095094A (ja) * 2014-11-14 2016-05-26 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4845987B2 (ja) 2009-03-16 2011-12-28 日本軽金属株式会社 冷暖房空調システム
JP5873768B2 (ja) * 2012-06-28 2016-03-01 株式会社コロナ 空気調和機
WO2016002111A1 (fr) 2014-06-30 2016-01-07 正 岡本 Système de climatisation à refroidissement et chauffage

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0285647A (ja) * 1988-09-20 1990-03-27 Sanyo Electric Co Ltd 空気調和機
JP3177302U (ja) * 2012-05-17 2012-07-26 株式会社Ｂ．Ｔ．Ｐ 冷暖房空調装置
WO2015059832A1 (fr) * 2013-10-25 2015-04-30 三菱電機株式会社 Échangeur thermique et dispositif à cycle de réfrigération utilisant ledit échangeur thermique
JP2016095094A (ja) * 2014-11-14 2016-05-26 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置

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