WO2021176651A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2021176651A1
WO2021176651A1 PCT/JP2020/009421 JP2020009421W WO2021176651A1 WO 2021176651 A1 WO2021176651 A1 WO 2021176651A1 JP 2020009421 W JP2020009421 W JP 2020009421W WO 2021176651 A1 WO2021176651 A1 WO 2021176651A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
heat
heat exchanger
refrigerant
transfer tube
Prior art date
Application number
PCT/JP2020/009421
Other languages
English (en)
Japanese (ja)
Inventor
幹 佐藤
拓未 西山
健太 村田
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.)
Filing date
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 US17/790,299 priority Critical patent/US20230043875A1/en
Priority to JP2022504883A priority patent/JP7414951B2/ja
Priority to PCT/JP2020/009421 priority patent/WO2021176651A1/fr
Priority to EP20923061.4A priority patent/EP4116642A4/fr
Publication of WO2021176651A1 publication Critical patent/WO2021176651A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features

Definitions

  • the present invention relates to a heat exchanger of an air conditioner.
  • the mixed refrigerant of HFC refrigerant and HFO refrigerant is excellent in terms of refrigerating capacity, theoretical COP, flammability, toxicity, etc., and may be applicable to a wide range of refrigerating and air-conditioning equipment.
  • a so-called non-azeotropic mixed refrigerant is obtained, and the characteristics are different from those of a pure refrigerant and an azeotropic mixed refrigerant.
  • the low boiling point component evaporates preferentially, and then the high boiling point component evaporates. Further boiling of the ingredients is suppressed.
  • a non-azeotropic mixed refrigerant it is necessary to recover from such deterioration of heat transfer of evaporation.
  • an auxiliary heat exchanger is arranged on the refrigerant inlet side when the heat exchanger is used as an evaporator, the number of refrigerant flow paths of the auxiliary heat exchanger is reduced, and a pipe is used.
  • a method of increasing the diameter is known (for example, Patent Document 1).
  • the auxiliary heat exchanger when used as a condenser, the auxiliary heat exchanger having an enlarged pipe diameter is located on the refrigerant outlet side. Since the supercooled liquid flows on the refrigerant outlet side of the condenser, there is a problem that the amount of refrigerant required for this refrigeration cycle increases due to the expansion of the pipe diameter, and the amount of refrigerant used increases.
  • the present invention has been made to solve the above problems without deteriorating the heat transfer performance when used as an evaporator in a heat exchanger of an air conditioner using a non-co-boiling mixed refrigerant. , A heat exchanger capable of reducing the required amount of refrigerant is obtained.
  • the heat exchangers are A first heat transfer tube in which a heat medium circulates inside and a plurality of grooves are formed on the inner peripheral surface, One end is connected to one end of the first heat transfer tube to form one heat medium flow path, the diameter of the tube is smaller than that of the first heat transfer tube, and the pressure loss per unit length is the first transfer. It is composed of a second heat transfer tube having an inner surface shape smaller than that of the heat tube.
  • the required amount of refrigerant can be reduced without deteriorating the heat exchange heat performance.
  • the manufacturing cost can be reduced.
  • FIG. 1 It is a refrigerant circuit diagram of the air conditioner including the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a front view of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is sectional drawing of the heat transfer tube used for the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a characteristic figure which shows an example of the heat transfer performance with respect to the dryness of a refrigerant of a general grooved pipe. It is a characteristic figure which shows an example of the pressure loss with respect to the dryness of a refrigerant of a general grooved pipe.
  • It is a Ph diagram which shows the refrigerating cycle operation of the air conditioner equipped with the heat exchanger which concerns on Embodiment 1.
  • FIG. 1 It is a refrigerating cycle operation of the air conditioner equipped with the heat exchanger which concerns on Embodiment 1.
  • FIG. 5 is an external view of an air conditioner to which the heat exchanger according to the first or second embodiment is applied.
  • FIG. 1 is a refrigerant circuit diagram showing an example of an air conditioner including a heat exchanger according to the first embodiment. The flow direction of the refrigerant is also shown by a solid line and a broken line.
  • 100 is an air conditioner, and the outdoor unit 1 and the indoor unit 2 are connected by a gas pipe 3 and a liquid pipe 4 to form one refrigerant circuit.
  • This refrigerant circuit is filled with a mixed refrigerant composed of two or more types of refrigerants having different boiling points.
  • the outdoor unit 1 is equipped with a compressor 5, an outdoor heat exchanger 6, an expansion valve 7, and a four-way valve 9, and the indoor unit 2 is equipped with an indoor heat exchanger 8.
  • the indoor heat exchanger 8 acts as an evaporator
  • the refrigerant discharged from the compressor 5 flows into the outdoor heat exchanger 6 through the four-way valve 9, is depressurized by the expansion valve 7, and is decompressed by the expansion valve 7.
  • Outflow The refrigerant that has flowed into the indoor unit 2 through the liquid pipe 4 evaporates in the indoor heat exchanger 8 and flows out of the indoor unit 2.
  • the refrigerant that has returned to the outdoor unit 1 through the gas pipe 3 is sucked into the compressor 5 again.
  • the refrigerant discharged from the compressor 5 flows into the indoor unit 2 from the gas pipe 3 by setting the flow path of the four-way valve 9.
  • the refrigerant condensed in the indoor heat exchanger 8 returns to the outdoor unit 1 through the liquid pipe 4, and is depressurized by the expansion valve 7.
  • the low-pressure refrigerant exchanges heat with the outdoor air in the outdoor heat exchanger 6 and evaporates, and is sucked into the compressor 5 again via the four-way valve 9.
  • the outdoor heat exchanger 6 and the indoor heat exchanger 8 are provided with fans, respectively, to forcibly force the outdoor and indoor air into the outdoor heat exchanger 6 and the indoor heat exchanger 8. By blowing air, the heat exchange efficiency between the refrigerant and air is improved.
  • the fan for example, a cross flow fan, a propeller fan, a turbo fan, or a sirocco fan can be used. Further, a plurality of fans may be provided for one heat exchanger, or one fan may be provided for a plurality of heat exchangers.
  • the air conditioner 100 has a minimum configuration capable of cooling operation and heating operation, and devices such as a gas-liquid separator, a receiver, an accumulator, and an internal heat exchanger are appropriately added to the refrigerant circuit. You may.
  • FIG. 2 is a front view showing an example of the outdoor heat exchanger 6 according to the first embodiment.
  • the outdoor heat exchanger 6 is composed of a plurality of fins 11 laminated at intervals of about 1.5 mm, and heat transfer tubes 31 to 38 penetrating the fins 11.
  • the heat transfer tubes 31 to 38 are formed in a hairpin shape and are heat-transferredly closely fitted to the fins 11.
  • One end or both ends of the heat transfer tubes 31 to 38 are connected by a plurality of U-shaped tubes 14 to form one refrigerant flow path having 12 as a gas side inlet / outlet and 13 as a liquid side inlet / outlet.
  • the liquid side inlet / outlet 13 corresponds to the inlet of the refrigerant flow path, and the gas side inlet / outlet 12 serves as the outlet of the refrigerant flow path. Further, as shown in FIG. 1, since the refrigerant flow direction is reversed during the cooling operation, the liquid side inlet / outlet 13 is the refrigerant flow path outlet and the gas side inlet / outlet 12 is the refrigerant when the outdoor heat exchanger 6 acts as a condenser. It becomes the flow path entrance.
  • FIG. 3 is a cross-sectional view of a heat transfer tube used in the heat exchanger according to the embodiment.
  • the first heat transfer tubes 31 to 36 have a plurality of peaks and valleys on the inner surface of the tubes as shown in FIG. 3A, for example. It is a formed grooved pipe, and penetrates the fin 11 with the gas side inlet / outlet 12 as one end to form a first heat exchange portion.
  • the heat transfer tubes 37 and 38 which are the second heat transfer tubes, are smooth tubes as shown in FIG. 3 (b), and penetrate the fins 11 with the liquid side inlet / outlet 13 as one end to form the second heat exchange portion. do.
  • the inner diameter D2 of the heat transfer tubes 37 and 38 is smaller than the inner diameter D1 of the grooved tubes used for the heat transfer tubes 31 to 36 (D1> D2).
  • the shape of the groove in the heat transfer tubes 31 to 36 does not matter.
  • the inner diameter, the number of fins inside the pipe (hereinafter referred to as the fins inside the pipe), the height of the fins inside the pipe, the helix angle of the fins inside the pipe, the area expansion ratio, and the like are not particularly limited.
  • a mixed refrigerant may be used.
  • FIG. 4 is a characteristic diagram showing an example of the heat transfer performance in the pipe with respect to the dryness of the refrigerant in a general grooved pipe.
  • the vertical axis is the heat transfer coefficient of heat of vaporization of the grooved pipe, and is represented by a value relative to the heat transfer coefficient of heat of vaporization of the smooth pipe.
  • the refrigerant the two characteristics of the single refrigerant and the non-azeotropic mixed refrigerant are plotted with broken lines and solid lines, respectively.
  • the grooved pipe has a heat transfer coefficient of vaporization that is three times or more the smooth pipe ratio regardless of the dryness of the refrigerant, which greatly contributes to the improvement of heat exchange performance. ..
  • the improvement in the heat transfer coefficient of vaporization in the smooth tube ratio is not as great as in the case of a single refrigerant.
  • the heat transfer coefficient of heat of vaporization of the grooved tube is almost the same as the heat transfer coefficient of heat of vaporization of the smooth tube, and does not contribute to the improvement of heat exchange performance.
  • FIG. 5 is a characteristic diagram showing an example of pressure loss with respect to the dryness of the refrigerant in a general grooved pipe.
  • the vertical axis is a relative value representing the pressure loss of the grooved pipe as a smooth pipe ratio.
  • the broken line is the pressure loss in the case of a single refrigerant, and the solid line is the pressure loss in the case of a non-azeotropic mixed refrigerant.
  • the pressure loss of the grooved pipe is large with respect to the pressure loss of the smooth pipe regardless of the dryness of the refrigerant, and is particularly large in the region of the dryness of the refrigerant of 0.3 to 0.5.
  • This phenomenon is the same for both a single refrigerant and a non-azeotropic mixed refrigerant, but the non-azeotropic mixed refrigerant has a larger rate of increase in pressure loss. From FIGS. 4 and 5, it can be said that the heat transfer performance is improved by adopting the grooved pipe for the heat exchanger, but the heat transfer performance is not improved when the dryness of the refrigerant is 0.4 or less, and only the pressure loss is increased. ..
  • FIG. 6 is a Ph diagram showing the refrigeration cycle operation of the air conditioner 100 according to the first embodiment.
  • the vertical axis is pressure
  • the horizontal axis is specific enthalpy
  • X0 is a saturation line connecting points where the refrigerant is in a saturated liquid or saturated gas state.
  • the state A, the state B, the state C, and the state D are the inlet states of each of the compression-condensation-expansion-evaporation processes forming the refrigeration cycle.
  • the refrigeration cycle shown in FIG. 6 is not limited to whether it is a cooling operation or a heating operation, but first, the refrigeration cycle operation will be described below assuming the case of a heating operation.
  • the low-temperature low-pressure gas refrigerant (state A) at the suction position of the compressor 5 is boosted by the compressor 5 to become a high-temperature high-pressure discharge gas (state B).
  • This discharged gas is condensed by the indoor heat exchanger 8 that acts as a condenser, and becomes a high-pressure supercooled liquid (state C).
  • the pressure is reduced by the expansion valve 7 to become a low-pressure gas-liquid two-phase refrigerant (state D).
  • X1 in the figure is an isobaric line with a refrigerant dryness of 0.2.
  • the refrigerant (state D) at the inlet of the evaporator is about 0.2 in the range of the condensation temperature of 40 ° C. ⁇ 10 ° C. and the evaporation temperature of 0 ° C. ⁇ 10 ° C., which are general air conditioning operation conditions. .. That is, in the evaporation process from the state D to the state A in a general air conditioner, the dryness of the refrigerant changes from 0.2 to 1.0 under most operating conditions.
  • the refrigerant in the low-pressure gas-liquid two-phase state D absorbs heat from the outdoor air until it slightly overheats, and then returns to the state A to perform one refrigeration cycle.
  • the indoor heat exchanger 8 acts as an evaporator
  • the outdoor heat exchanger 6 acts as a condenser.
  • the high-temperature high-pressure gas refrigerant in the state B discharged from the compressor 5 flows into the outdoor heat exchanger 6 to exchange heat with the outdoor air, and is condensed to become the supercooling liquid refrigerant in the state C.
  • Most of the amount of refrigerant required for this refrigeration cycle is concentrated in the SC portion, which is the final stage of the condensation process, that is, the SC portion, which is the region after the refrigerant has become saturated.
  • the diameters of the heat transfer tubes 37 and 38 constituting the second heat exchange section on the refrigerant outlet side when used as a condenser are smaller than those of the other heat transfer tubes. Therefore, the amount of refrigerant present in the SC portion becomes small. As a result, the amount of refrigerant sealed in the air conditioner 100 is also reduced, which can contribute to lowering the total amount of GWP and reduce the environmental load.
  • the refrigerant flow velocity in the second heat exchange section increases and convection heat transfer is promoted, so the deterioration in heat transfer performance due to the smooth tube is recovered.
  • the deterioration of heat exchange performance can be suppressed.
  • FIG. 7 is an example of a side view in which one refrigerant flow path portion of the heat exchanger according to the first embodiment is extracted.
  • heat transfer tubes 31 to 38 forming one refrigerant flow path are arranged in two rows in the air flow direction.
  • the eight heat transfer tubes 31 to 38 six of the heat transfer tubes 31 to 36 are grooved tubes, and two of the heat transfer tubes 37 and 38 are smooth tubes thinner than the grooved tubes. That is, 25% of the total refrigerant flow path length on the side close to the liquid side inlet / outlet 13 is a smooth pipe.
  • the first heat exchange section composed of the heat transfer tubes 31 to 36 and the second heat exchange section composed of the heat transfer tubes 37 and 38 are integrally formed, the number of steps required for manufacturing is small and the manufacturing cost is low. Can be reduced.
  • the heat transfer tube connected to the gas side inlet / outlet 12 of one refrigerant flow path is a grooved tube
  • the heat transfer tube connected to the liquid side inlet / outlet 13 is a grooved tube. Since the smoothing tube is made thinner and the length of the smoothing tube is 25% or less of the total length, the required amount of refrigerant can be reduced without deteriorating the heat transfer performance when a non-co-boiling mixed refrigerant is used. .. In addition, the manufacturing cost can be reduced.
  • FIG. 8 is a side view of another example in which one refrigerant flow path portion of the outdoor heat exchanger 6 according to the second embodiment is extracted.
  • the first heat exchange section is formed by arranging the heat transfer tubes 31 to 36 on the upper part of the outdoor heat exchanger 6, and the heat transfer tubes 37 and 38 are arranged on the lower part of the outdoor heat exchanger 6 to form the second heat exchange section. Is forming.
  • the first heat exchange section and the second heat exchange section are separated from each other, the first heat exchange section and the second heat exchange section are separated from each other by the heat transfer tubes and the fins 11. Can be adjusted independently.
  • the first heat exchange part of the grooved tube and the second heat exchange part of the smoothing tube can be manufactured separately, and thus the heat exchange of each can be performed separately.
  • the fin pitch and the distance between the heat transfer tubes can be set appropriately according to the characteristics.
  • FIG. 9 is an external view showing an example of an air conditioner equipped with the heat exchanger according to the first or second embodiment.
  • the air conditioner 100 includes an outdoor unit 1 and an indoor unit 2 connected by a gas pipe 3 and a liquid pipe 4.
  • the outdoor heat exchanger 6 housed in the outdoor unit 1 and the indoor heat exchanger 9 housed in the indoor unit 2 both use the heat exchangers shown in the first or second embodiment.
  • the heat exchange performance is achieved by using the heat exchanger according to the first or second embodiment for the outdoor heat exchanger 6 and the indoor heat exchanger 8. Since the amount of the refrigerant sealed in the air conditioner 100 can be reduced without impairing the above, it is possible to contribute to lowering the total amount of GWP and reduce the environmental load.
  • two near the liquid side inlet / outlet 13 are smooth tubes.
  • four heat transfer tubes form one refrigerant.
  • one near the liquid side inlet / outlet 13 is used as a smoothing tube
  • one near the liquid side inlet / outlet 13 is used as a smoothing tube. If the length of the refrigerant flow path formed of the smooth pipe is at least 25% or less of the total length, the effect of increasing the heat transfer performance by the grooved pipe is not impaired. Further, these effects can be obtained not only when applied to the outdoor heat exchanger 6 but also when applied to the indoor heat exchanger 8.
  • the configuration shown in the above-described embodiment shows an example of the contents of the present disclosure, can be combined with another known technique, and is configured without departing from the gist of the present disclosure. It is also possible to omit or change a part of.
  • Outdoor unit 2 Indoor unit 3: Gas pipe 4: Liquid pipe 5: Compressor, 6: Outdoor heat exchanger, 7: Expansion valve, 8: Indoor heat exchanger, 9: Four-way valve, 11 : Fin, 12: Gas side inlet / outlet, 13: Liquid side inlet / outlet, 14: U-shaped pipe, 31-36: Grooved pipe, 37, 38: Smooth pipe, 100: Air exchanger

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur pour un climatiseur qui utilise un mélange de réfrigérant non azéotropique, l'échangeur de chaleur permettant de réduire la quantité de réfrigérant requise sans provoquer de déclin de la performance de transfert de chaleur lorsqu'il est utilisé comme évaporateur. L'échangeur de chaleur comprend : une pluralité d'ailettes (11) empilées avec un espacement prescrit entre elles ; des premiers tubes de transfert de chaleur (31-36) qui passent à travers la pluralité d'ailettes (11), qui permettent à un milieu de transfert de chaleur de s'écouler au travers, et qui présentent une pluralité de rainures formées sur la surface périphérique interne de chaque premier tube de transfert de chaleur ; et des seconds tubes de transfert de chaleur (37, 38) qui passent à travers la pluralité d'ailettes (11), qui présentent une extrémité raccordée à une extrémité des premiers tubes de transfert de chaleur (31-36) pour former un passage d'écoulement de milieu de transfert de chaleur, qui présentent un diamètre de tuyau plus petit que celui des premiers tubes de transfert de chaleur (31-36), et qui présentent une forme de surface interne configurée de sorte qu'une perte de pression par unité de longueur est inférieure à celle des premiers tubes de transfert de chaleur (31-36).
PCT/JP2020/009421 2020-03-05 2020-03-05 Échangeur de chaleur et climatiseur WO2021176651A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US17/790,299 US20230043875A1 (en) 2020-03-05 2020-03-05 Heat exchanger and air conditioner
JP2022504883A JP7414951B2 (ja) 2020-03-05 2020-03-05 熱交換器及び空気調和機
PCT/JP2020/009421 WO2021176651A1 (fr) 2020-03-05 2020-03-05 Échangeur de chaleur et climatiseur
EP20923061.4A EP4116642A4 (fr) 2020-03-05 2020-03-05 Échangeur de chaleur et climatiseur

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Application Number Priority Date Filing Date Title
PCT/JP2020/009421 WO2021176651A1 (fr) 2020-03-05 2020-03-05 Échangeur de chaleur et climatiseur

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WO2021176651A1 true WO2021176651A1 (fr) 2021-09-10

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024069896A1 (fr) * 2022-09-29 2024-04-04 日立ジョンソンコントロールズ空調株式会社 Climatiseur

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06281293A (ja) * 1993-03-31 1994-10-07 Toshiba Corp 熱交換器
JPH07113555A (ja) * 1993-10-18 1995-05-02 Hitachi Ltd 空気調和機
JPH0875384A (ja) * 1994-07-01 1996-03-19 Hitachi Ltd 非共沸混合冷媒用伝熱管とその伝熱管を用いた熱交換器及び組立方法及びその熱交換器を用いた冷凍・空調機
JPH08145593A (ja) * 1994-11-24 1996-06-07 Sanyo Electric Co Ltd 熱交換器
JP2004332958A (ja) 2003-04-30 2004-11-25 Toshiba Kyaria Kk 空気調和機の熱交換器
JP2009257740A (ja) * 2008-03-25 2009-11-05 Daikin Ind Ltd 冷凍装置
WO2015125525A1 (fr) * 2014-02-24 2015-08-27 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0962725B1 (fr) * 1997-12-16 2017-11-08 Panasonic Corporation Conditionneur d'air dans lequel un réfrigérant inflammable est utilisé
KR20020038002A (ko) * 2000-11-16 2002-05-23 구자홍 증발기의 전열관
EP3380800B1 (fr) * 2015-11-23 2020-04-01 Carrier Corporation Échangeur de chaleur
US10088250B2 (en) * 2016-01-12 2018-10-02 Hamilton Sundstrand Corporation Heat exchangers

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06281293A (ja) * 1993-03-31 1994-10-07 Toshiba Corp 熱交換器
JPH07113555A (ja) * 1993-10-18 1995-05-02 Hitachi Ltd 空気調和機
JPH0875384A (ja) * 1994-07-01 1996-03-19 Hitachi Ltd 非共沸混合冷媒用伝熱管とその伝熱管を用いた熱交換器及び組立方法及びその熱交換器を用いた冷凍・空調機
JPH08145593A (ja) * 1994-11-24 1996-06-07 Sanyo Electric Co Ltd 熱交換器
JP2004332958A (ja) 2003-04-30 2004-11-25 Toshiba Kyaria Kk 空気調和機の熱交換器
JP2009257740A (ja) * 2008-03-25 2009-11-05 Daikin Ind Ltd 冷凍装置
WO2015125525A1 (fr) * 2014-02-24 2015-08-27 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4116642A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024069896A1 (fr) * 2022-09-29 2024-04-04 日立ジョンソンコントロールズ空調株式会社 Climatiseur

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JP7414951B2 (ja) 2024-01-16
EP4116642A1 (fr) 2023-01-11

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