EP3770535A1 - Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation - Google Patents

Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation Download PDF

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Publication number
EP3770535A1
EP3770535A1 EP18911206.3A EP18911206A EP3770535A1 EP 3770535 A1 EP3770535 A1 EP 3770535A1 EP 18911206 A EP18911206 A EP 18911206A EP 3770535 A1 EP3770535 A1 EP 3770535A1
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EP
European Patent Office
Prior art keywords
heat exchanger
heat transfer
transfer tubes
refrigerant
heat
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP18911206.3A
Other languages
German (de)
English (en)
Other versions
EP3770535A4 (fr
Inventor
Yuki UGAJIN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3770535A1 publication Critical patent/EP3770535A1/fr
Publication of EP3770535A4 publication Critical patent/EP3770535A4/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F25B39/02—Evaporators
    • 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
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present disclosure relates to a heat exchanger for heat exchange, a refrigeration cycle apparatus, and an air-conditioning apparatus. More specifically, the present disclosure relates to a heat exchanger that includes a heat transfer tube having an inner surface provided with grooves.
  • heat transfer tubes each having an inner surface provided with grooves are provided to extend through through-holes formed in fins arranged at predetermined intervals.
  • the heat transfer tubes serve as part of a refrigerant circuit in the refrigeration cycle apparatus, and fluid, such as refrigerant, flows in the heat transfer tubes.
  • fluid such as refrigerant
  • the refrigerant that flows in such heat transfer tubes as described above exchanges heat with, for example, air that flows outside the transfer pipes to change in phase (condense or evaporate).
  • grooves are formed based on set parameters, and the heat transfer performance of the heat transfer tubes is improved by an increase in a surface area in the pipes, an effect of string fluid with grooves, and an effect of holding a liquid film between the grooves because of capillary action (see, for example, Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2004-301495
  • the present disclosure is applied to solve the above problem, and relates to a heat exchanger, a refrigeration cycle apparatus, and an air-conditioning apparatus that are formed suitable for flow passages of heat transfer tubes.
  • a heat exchanger includes heat transfer tubes each of which allow fluid to flow therethrough and has an inner surface provided with grooves that are recessed parts spirally extending in a direction along a tube axis of each heat transfer tube; and heat exchanger bodies including fins that are in contact with the heat transfer tubes to promote heat exchange of the fluid.
  • the grooves of the inner surface of each of those heat transfer tubes are formed such that a lead angle ⁇ between the tube axis and an extending direction of the grooves falls within a range of 25 degrees to 45 degrees, and in the case where the heat transfer tubes that allow the fluid to flow from the inlet of the heat exchanger to the outlet of the heat exchanger have a flow passage length L of greater than 10 m, the grooves of the inner surface of each of those heat transfer tubes are formed such that the lead angle ⁇ is 5 degrees or more and less than 25 degrees.
  • grooves are formed such that the lead angle is set to a value that varies in accordance with the flow passage length L from the inlet of the heat exchanger to the outlet of the heat exchanger.
  • the heat exchanger is formed suitable for the length of a flow passage. It is therefore possible to increase heat exchange efficiency and increase an annual performance factor (APF) of an air-conditioning apparatus.
  • the levels of temperature, pressure, etc. are not determined in relation to absolute values, that is, they are relatively determined in accordance with the state and operation of the apparatus, for example.
  • the suffixes may be omitted.
  • Fig. 1 schematically illustrates a configuration of a heat exchanger 1 according to Embodiment 1 of the present disclosure.
  • the heat exchanger 1 is a fin-tube heat exchanger that includes a plurality of heat exchanger bodies 10 and a flow passage pipe 20.
  • refrigerant that flows from a heat exchanger inlet 1A passes through heat transfer tubes 12 in each of the heat exchanger bodies 10 and exchanges heat with air that flows between fins 11.
  • the refrigerant that has exchanged heat with the air flows out from a heat exchanger outlet 1B.
  • the flow passage pipe 20 connects the plurality of heat exchanger bodies 10 and serve as a flow passage through which refrigerant flows.
  • the flow passage pipe 20 has branches such as a single pipe, a T pipe, and a bulge three-way pipe.
  • Fig. 2 schematically illustrates a configuration of a heat exchanger body 10 according to Embodiment 1 of the present disclosure.
  • the heat exchanger body 10 includes a plurality of fins 11 and a plurality of heat transfer tubes 12.
  • the fins 11 are substantially rectangular plate-like fins that are arranged at regular intervals.
  • the fins 11 have through-holes that are formed such that the heat transfer tubes 12 inserted through the through-holes intersect the fins 11 in contact with the fins 12.
  • the heat transfer tubes 12 are part of a flow passage in a refrigerant circuit of a refrigeration cycle apparatus, and refrigerant flows in the heat transfer tubes 12.
  • the fins 11 receive heat of refrigerant that flows in the heat transfer tubes 12 and heat of air that flows outside the heat transfer tubes 12. Because of provision of the fins 11, a heat transfer area is increased, and heat exchange is efficiently performed between the refrigerant and the air.
  • Fig. 3 is a view for explaining an inner surface of part of a heat transfer tube 12 that extends in a direction parallel to a tube axis 15 in the heat exchanger 1 according to Embodiment 1 of the present disclosure.
  • Fig. 4 is a view for explaining an inner surface of part of the heat transfer tube 12 that extends in a direction perpendicular to the tube axis 15 in the heat exchanger 1 according to Embodiment 1 of the present disclosure.
  • the heat transfer tubes 12 of the heat exchanger 1 according to Embodiment 1 each have an inner surface provided with a plurality of grooves 14 that are recesses extending spirally.
  • the grooves 14 serve as part of a flow passage for refrigerant, which is fluid. Because of provision of the grooves 14, for example, a surface area of the inner surface of the heat transfer tube 12 is increased, the fluid is stirred, and a liquid film is held by capillary action, thereby promoting heat transfer between the heat transfer tube 12 and refrigerant that flows in the heat transfer tube 12.
  • the grooves 14 are formed in the inner surface of the heat transfer tube 12 such that an imaginary line that extends in the direction along the tube axis 15 and an imaginary line that extends in a direction in which the grooves 14 spirally extend form a certain angle. This angle will be hereinafter referred to as a lead angle ⁇ . Also, because of provision of the grooves 14, recessed parts and raised parts are formed at the inner surface of the heat transfer tube 12. Although the recessed parts correspond to the grooves 14, the height of the raised parts corresponds to the height h of the grooves 14 in Embodiment 1 as described later.
  • the flow passage length L is the length of heat transfer tubes 12 that extends from the heat exchanger inlet 1A to the heat exchanger outlet 1B to allow refrigerant to flow from the heat exchanger inlet 1A to the heat exchanger outlet 1B.
  • the sum of lengths L1, L2, and L3 of heat transfer tubes 12 of heat exchanger bodies 10 located on a path of the flow passage pipe 20 indicated by solid lines in Fig. 1 is the flow passage length L.
  • Fig. 5 indicates a correlation between the lead angle ⁇ at the heat transfer tube 12 and the performance of the heat transfer tube 12 according to Embodiment 1 of the present disclosure.
  • the performance of the heat transfer tube 12 is expressed by in-pipe heat transfer coefficient ⁇ i.
  • in-pipe heat transfer coefficient ⁇ i increases while the value by which the in-pipe heat transfer coefficient ⁇ i increases decreases.
  • in-pipe refrigerant pressure loss ⁇ Pref monotonically increases.
  • the greater the in-pipe heat transfer coefficient ⁇ i and the smaller the in-pipe refrigerant pressure loss ⁇ Pref the higher the efficiency of the heat exchange. Therefore, the optimum shape of the grooves 14 depends on the type of the heat exchanger 1.
  • Fig. 6 schematically indicates a correlation between the lead angle ⁇ at the heat transfer tube 12 and an annual performance factor (APF) in Embodiment 1 of the present disclosure.
  • the annual performance factor (APF) is an indicator indicative of annual performance of an air conditioner.
  • the greater the flow passage length L the greater the influence of the in-pipe refrigerant pressure loss ⁇ Pref.
  • the in-pipe refrigerant pressure loss ⁇ Pref is small.
  • the lead angle ⁇ is reduced, the APF tends to be improved.
  • the smaller the flow passage length L the greater the influence of the in-pipe heat transfer coefficient ⁇ i.
  • the in-pipe heat transfer coefficient ⁇ i is also great.
  • the lead angle ⁇ tends to be improved.
  • a test of a room air conditioner was conducted regarding the case where the flow passage length L is 10 m or less (L ⁇ 10 m) and the case where the flow passage length L is greater than 10 m (L>10 m). According to the result of the test, it was found that a threshold value of the APF lies at a lead angle ⁇ of 25 degrees, as illustrated in Fig. 6 .
  • the above associated heat transfer tubes 12 should be formed to have grooves 14 having a lead angle ⁇ that falls within the range of 25 degrees to 45 degrees (25° ⁇ ⁇ 45°), and in the case where the flow passage length L is more than 10 m (L>10 m), preferably, the heat transfer tubes 12 should be formed to have grooves 14 having a lead angle ⁇ that is 5 degrees or more and less than 25 degrees (5° ⁇ 25°).
  • a heat transfer tube 12 tends to be formed such that the smaller the outside diameter, the smaller the inside diameter. Therefore, as the outside diameter of the heat transfer tube 12 decreases, the inside diameter decreases, as a result of which the in-pipe refrigerant pressure loss ⁇ Pref increases.
  • many room air conditioners employ heat transfer tubes each having an outside diameter of ⁇ 7.0 or ⁇ 6.35.
  • the outside diameter and the inside diameter can be made smaller while maintaining the in-pipe refrigerant pressure loss ⁇ Pref.
  • a heat transfer tube 12 having an outside diameter of ⁇ 5.0 or less in which the in-pipe refrigerant pressure loss ⁇ Pref is approximately two or more times greater than in a heat transfer tube having an outside diameter of ⁇ 7.0.
  • an in-pipe volume thereof can be reduced. It is therefore possible to reduce the amount of refrigerant that is required for the entire refrigerant circuit.
  • the safety of the apparatus can be further improved by reducing the amount of the refrigerant.
  • the heat exchange 1 As described above, in the heat exchange 1 according to Embodiment 1, regarding associated ones of the heat transfer tubes 12 through which refrigerant passes, in the case where the flow passage length L is 10 m or less (L ⁇ 10 m), grooves 14 are formed such that the lead angle ⁇ falls within the range of 25 degrees to 45 degrees (25° ⁇ 45°), and in the case where the flow passage length L is greater than 10 m (L>10 m), the grooves 14 are formed such that the lead angle ⁇ is 5 degrees or more and less than 25 degrees (5 ⁇ 25). It is therefore possible to increase the APF of an air-conditioning apparatus.
  • Embodiment 2 will be described by referring manly to the differences between the heat transfer tubes 12 according to Embodiments 1 and 2.
  • the heat transfer tubes 12 according to Embodiment 2 basically have a similar configuration to the heat transfer tubes 12 according to Embodiment 1, and each have an inner surface in which a plurality of spiral grooves 14 are formed. It should be noted that regarding Embodiment 1, the groove height h of the grooves 14 is not described above in detail.
  • the heat transfer tube 12 is formed such that in the case where the flow passage length L is 10 m or less (L ⁇ 10 m), the grooves 14 are formed in the inner surface to have a groove height h of 0.06 mm or more (h ⁇ 0.06 mm), and in the case where the flow passage length L is more than 10 m (L>10 m), the grooves 14 are formed in the inner surface to have a groove height h of more than 0.06 mm (0.06 ⁇ h).
  • Fig. 7 indicates a correlation between the groove height h of the heat transfer tube 12 and the performance of the heat transfer tube 12 according to Embodiment 2 of the present disclosure.
  • the performance of the heat transfer tube 12 is expressed by in-pipe heat transfer coefficient ⁇ i.
  • the in-pipe heat transfer coefficient ⁇ i increases while the value by which the in-pipe heat transfer coefficient ⁇ i increases decreases.
  • the in-pipe refrigerant pressure loss ⁇ Pref monotonically increases.
  • the greater the in-pipe heat transfer coefficient ⁇ i and the smaller the in-pipe refrigerant pressure loss ⁇ Pref the higher the efficiency of the heat exchange.
  • Fig. 8 schematically indicates a correlation between the groove height h of the heat transfer tube 12 and the APF in Embodiment 2 of the present disclosure.
  • the greater the flow passage length L the greater the influence of the in-pipe refrigerant pressure loss ⁇ Pref. Therefore, in this case, when the groove height h is small, the APF tends to be improved.
  • the smaller the flow passage length L the greater the influence of the in-pipe heat transfer coefficient ⁇ i. Therefore, in this case, when the groove height h is great, the APF tends to be improved.
  • a test of the room air conditioner was conducted regarding the case where the flow passage length L is 10 m or less (L ⁇ 10 m) and the case where the flow passage length L is greater than 10 m (L>10 m). According to the result of the test, it was found that a threshold value of the APF lies at a groove height h of 0.06 mm, as illustrated in Fig. 8 .
  • grooves 14 should be formed such that the groove height h is 0.06 mm or more (h ⁇ 0.06 mm), and in the case where the flow passage length L is greater than 10 m (L>10 m), preferably, the grooves 14 should be formed such that the groove height h is greater than 0.06 mm (0.06 ⁇ h).
  • the amount of refrigerant that is required for the entire refrigerant circuit can be reduced by reducing the diameter of the heat transfer tube 12 and also reducing the in-pipe volume of the heat transfer tube 12.
  • the safety of the apparatus can be further improved by reducing the amount of the refrigerant.
  • the grooves 14 may be formed in such a manner as to satisfy both the conditions concerning the lead angle ⁇ as described regarding Embodiment 1 and the conditions concerning the groove height h of the grooves 14 regarding Embodiment 2.
  • Fig. 9 illustrates a configuration of a refrigeration cycle apparatus according to Embodiment 3 of the present disclosure.
  • An air-conditioning apparatus 50 that cools or heats an air-conditioned space will be described as an example of the refrigeration cycle apparatus.
  • the air-conditioning apparatus is an apparatus that air-conditions the air-conditioned space by circulating refrigerant while changing in phase the refrigerant from liquid refrigerant to gas refrigerant and from gas refrigerant to liquid refrigerant through steps of evaporation, compression, condensation, and expansion and thus transferring heat to and from the refrigerant.
  • the air-conditioning apparatus 50 as illustrated in Fig. 9 includes an outdoor unit 200 and an indoor unit 100.
  • a compressor 210, a four-way valve 220, a heat-source-side heat exchanger 230, and an expansion device 240 of the outdoor unit 200, and a load-side heat exchanger 110 of the indoor unit 100 are connected by a gas refrigerant pipe 300 and a liquid refrigerant pipe 400, whereby a refrigerant cycle circuit is formed.
  • the flow of refrigerant during cooling operation is indicated by solid line arrows
  • flow of refrigerant during heating operation is indicated by dotted line arrows.
  • the outdoor unit 200 includes the compressor 210, the four-way valve 220, the heat-source-side heat exchanger 230, the expansion device 240, and a heat-source-side fan 250.
  • the compressor 210 compresses sucked refrigerant and discharges the compressed refrigerant.
  • the compressor 210 may be, but is not limited to, a compressor whose capacity (the amount of refrigerant to be fed per unit time) is changed by causing, for example, an inverter circuit to change an operating frequency of the compressor.
  • the four-way valve 220 is a valve that switches the flow of refrigerant, for example, in accordance with whether an operation mode is the cooling operation or the heating operation.
  • the heat-source-side heat exchanger 230 causes heat exchange to be performed between refrigerant and air (outdoor air).
  • the heat-source-side heat exchanger 230 operates as an evaporator that evaporates and gasifies refrigerant.
  • the heat-source-side heat exchanger 230 operates as a condenser that condenses and liquefies refrigerant.
  • the heat-source-side fan 250 sends air to the heat-source-side heat exchanger 230.
  • the heat-source-side fan 250 is controlled by a controller 60A.
  • the expansion device 240 such as an expansion valve (flow-amount control unit) reduces refrigerant in pressure to expand the refrigerant.
  • the expansion device 240 is an electronic expansion valve
  • the opening degree of the expansion device 240 is adjusted in response to an instruction from the controller 60A.
  • the indoor unit 100 includes the load-side heat exchanger 110 and a load-side fan 120.
  • the load-side heat exchanger 110 causes heat exchange to be performed between air to be air-conditioned and refrigerant.
  • the load-side heat exchanger 110 operates as a condenser that condenses and liquefies refrigerant.
  • the load-side heat exchanger 110 operates as an evaporator that evaporates and gasifies refrigerant.
  • the heat exchanger 1 according to Embodiment 1 or Embodiment 2 is used as the load-side heat exchanger 110. This, however, is not limiting.
  • the heat exchanger 1 according to Embodiment 1 or Embodiment 2 may be used as the heat-source-side heat exchanger 230. That is, the heat exchanger 1 according to Embodiment 1 or Embodiment 2 is used as at least one of a heat exchanger that operates as a condenser and a heat exchanger that operates as an evaporator.
  • the heat exchanger 1 is used as the load-side heat exchanger 110, an air conditioner having a high heat exchange efficiency and high performance can be provided.
  • the load-side fan 120 sends air to the load-side heat exchanger 110.
  • the load-side fan 120 is controlled by a controller 60A.
  • the controller 60A and the controller 60B are connected to the compressor 210, the four-way valve 220, the expansion device 240, the heat-source-side fan 250, the load-side fan 120, various sensors, etc.
  • the controller 60A and the controller 60B control operation of devices such as the compressor 210 in response to signals supplied from the various sensors.
  • the controller 60A and the controller 60B switch the operation between the cooling operation and the heating operation by switching the flow passage of the four-way valve 220.
  • High-pressure, high-temperature gas refrigerant discharged from the compressor 210 flows into the heat-source-side heat exchanger 230 through the four-way valve 220 and exchanges heat with outside air supplied by the heat-source-side fan 250 to condense and change into high-pressure liquid refrigerant, and the high-pressure liquid refrigerant then flows out from the heat-source-side heat exchanger 230.
  • the high-pressure liquid refrigerant that has flowed out of the heat-source-side heat exchanger 230 flows into the expansion device 240 and changes into low-pressure two-phase gas-liquid refrigerant.
  • the low-pressure two-phase gas-liquid refrigerant that has flowed out of the expansion device 240 flows into the load-side heat exchanger 110 and exchanges with indoor air supplied by the load-side fan 120 to evaporate and change into low-pressure gas refrigerant, and the low-pressure gas refrigerant then flows out of the load-side heat exchanger 110.
  • the low-pressure gas refrigerant that has flowed out of the load-side heat exchanger 110 is sucked into the compressor 210 through the four-way valve 220.
  • High-pressure, high-temperature gas refrigerant discharged from the compressor 210 flows into the load-side heat exchanger 110 through the four-way valve 220.
  • the refrigerant exchanges heat with indoor air supplied by the load-side fan 120 to condense and change into high-pressure liquid refrigerant, and the high-pressure liquid refrigerant then flows out of the load-side heat exchanger 110.
  • the high-pressure liquid refrigerant that has flowed out of the load-side heat exchanger 110 flows into the expansion device 240 and change into low-pressure two-phase gas-liquid refrigerant.
  • the low-pressure two-phase gas-liquid refrigerant flows into the heat-source-side heat exchanger 230 and exchanges heat with outdoor air supplied by the heat-source-side fan 250 to evaporate and change into low-pressure gas refrigerant, and the low-pressure gas refrigerant then flows out of the heat-source-side heat exchanger 230.
  • the low-pressure gas refrigerant that has flowed out of the heat-source-side heat exchanger 230 is sucked into the compressor 210 through the four-way valve 220.
  • immiscible oil such as HAB oil should be used in terms of solubility of refrigerant in the refrigerating machine oil and replacement of a unit with a new one.
  • HAB oil should be used in terms of solubility of refrigerant in the refrigerating machine oil and replacement of a unit with a new one.
  • an air-conditioning apparatus 50 employing the heat exchanger 1 according to either Embodiment 1 or Embodiment 2 can have high performance and high quality.
  • R32 is used as refrigerant for use in the air-conditioning apparatus 50.
  • refrigerant having lower GWP global warming potential
  • R290 can be applied.
  • the in-pipe refrigerant pressure loss ⁇ Pref is larger than in the case of using R32.
  • R290 is highly flammable refrigerant, and thus if a large amount of 290 is applied, it may burn.
  • the heat exchanger 1 according to Embodiment 1 or Embodiment 2 is advantageous, that is, can compensate for the in-pipe refrigerant pressure loss ⁇ Pref of R290. Furthermore, the in-pipe volume of the heat exchanger 1 can be reduced, and the amount of the refrigerant can thus be reduced. It is therefore possible to provide a refrigeration cycle apparatus having high performance and high quality.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
EP18911206.3A 2018-03-20 2018-03-20 Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation Withdrawn EP3770535A4 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/011044 WO2019180817A1 (fr) 2018-03-20 2018-03-20 Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation

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EP3770535A1 true EP3770535A1 (fr) 2021-01-27
EP3770535A4 EP3770535A4 (fr) 2021-01-27

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EP (1) EP3770535A4 (fr)
JP (1) JP6925508B2 (fr)
CN (1) CN111886459A (fr)
WO (1) WO2019180817A1 (fr)

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CN116249870A (zh) 2020-10-12 2023-06-09 三菱电机株式会社 制冷循环装置、空调机和热交换器

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JPWO2019180817A1 (ja) 2021-01-07
WO2019180817A1 (fr) 2019-09-26
EP3770535A4 (fr) 2021-01-27
CN111886459A (zh) 2020-11-03
JP6925508B2 (ja) 2021-08-25

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