WO2016103437A1 - Appareil à cycle de réfrigération - Google Patents

Appareil à cycle de réfrigération Download PDF

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Publication number
WO2016103437A1
WO2016103437A1 PCT/JP2014/084466 JP2014084466W WO2016103437A1 WO 2016103437 A1 WO2016103437 A1 WO 2016103437A1 JP 2014084466 W JP2014084466 W JP 2014084466W WO 2016103437 A1 WO2016103437 A1 WO 2016103437A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigeration cycle
cycle apparatus
flat tube
flow path
Prior art date
Application number
PCT/JP2014/084466
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English (en)
Japanese (ja)
Inventor
中村　伸
英明 前山
石橋　晃
真哉 東井上
伊東　大輔
繁佳 松井
拓未 西山
裕樹 宇賀神
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 JP2016565792A priority Critical patent/JP6415600B2/ja
Priority to PCT/JP2014/084466 priority patent/WO2016103437A1/fr
Priority to EP14909044.1A priority patent/EP3239640A4/fr
Publication of WO2016103437A1 publication Critical patent/WO2016103437A1/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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus equipped with a heat exchanger.
  • a conventional refrigeration cycle apparatus has been proposed that uses HFO-1123 as a working fluid (see, for example, Patent Document 1).
  • a refrigerant containing an HFO refrigerant such as HFO-1123 described in Patent Document 1 generally has a short atmospheric life because it has a low global warming potential (hereinafter referred to as “GWP”). That is, since the stability is poor, the refrigerant is easily decomposed even when it exists in the refrigerant circuit including the heat exchanger. Therefore, it becomes a factor of the performance fall and reliability fall of a refrigerating cycle device.
  • GWP global warming potential
  • the present invention has been made in the background of the above-described problems, and in the case of using HFO-1123 or a mixed refrigerant containing HFO-1123 as the refrigerant circulating in the refrigerant circuit, the heat transfer performance of the heat exchanger It aims at providing the refrigerating cycle device which can improve.
  • the refrigeration cycle apparatus includes a refrigerant circuit in which a compressor, a first heat exchanger, an expansion unit, and a second heat exchanger are sequentially connected by piping to circulate the refrigerant, and the refrigerant is HFO-1123.
  • at least one of the first heat exchanger and the second heat exchanger has a plurality of fins and a plurality of flow paths through which the refrigerant flows formed therein.
  • the plurality of flat tubes satisfy the relationship of 0.9 mm ⁇ DA ⁇ 3.0 mm when the width is DA.
  • the present invention satisfies the relationship of 0.9 mm ⁇ DA ⁇ 3.0 mm when the width of the flat tube is DA. For this reason, in the case where HFO-1123 or a mixed refrigerant containing HFO-1123 is used as the refrigerant circulating in the refrigerant circuit, the heat transfer performance of the heat exchanger can be improved.
  • COP coefficient of performance
  • FIG. 1 is a circuit diagram illustrating an example of a refrigerant circuit of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • a refrigeration cycle apparatus 10 includes a compressor 11, a first heat exchanger 12, an expansion means 13, and a second heat exchanger 14 that are sequentially connected by a pipe, and circulate the refrigerant. It has a circuit.
  • the first heat exchanger 12 is provided with a fan 15a that blows air
  • the second heat exchanger 14 is provided with a fan 15b that blows air.
  • the heat exchanger 1 when the first heat exchanger 12 and the second heat exchanger 14 are not distinguished, they are referred to as the heat exchanger 1.
  • 1,1,2-trifluoroethylene (HFO-1123) having one double bond in the molecular structure or a mixed refrigerant containing HFO-1123 is used.
  • HFC hydrofluorocarbon
  • HFC-410A hydrofluorocarbon refrigerant
  • HCFC hydrochlorofluorocarbon
  • HCFC22 hydrochlorofluorocarbon
  • ODP ozone depletion coefficient
  • the HFC refrigerant has a possibility of causing global warming, and its index, GWP, shows a high value.
  • HFC-32 having a GWP lower than that of HFC-410A exists among HFC refrigerants having no carbon double bond in the composition.
  • this refrigerant is used as the working fluid of the refrigeration cycle apparatus 10, the discharge temperature at the outlet of the compressor 11 is higher than that of a conventional refrigerant, and therefore it is necessary to use a material that can withstand high temperatures.
  • HFO hydrofluoroolefin
  • examples of such HFO refrigerants include HFO-1234yf and HFO-1234ze.
  • these refrigerants are refrigerants having a high standard boiling point, the pressure is lower than that at the same saturation temperature as that of conventional refrigerants. That is, the refrigerant density becomes smaller than that of the conventional HFC refrigerant, and the frequency of the compressor 11 needs to be increased in order to keep the refrigerant circulation amount in the refrigeration cycle apparatus 10 equal to that of the conventional refrigerant. Therefore, the power consumption increases, which causes a reduction in energy saving performance.
  • the refrigerant circulating in the refrigerant circuit in the first embodiment is HFO-1123.
  • HFO-1123 or a mixed refrigerant containing HFO-1123 is used.
  • HFO-1123 is a refrigerant having a low standard boiling point, and therefore has a higher pressure than at the same saturation temperature as that of a conventional HFC refrigerant. That is, the refrigerant density is larger than that of the conventional refrigerant, and even if the frequency of the compressor 11 is lowered, the refrigerant circulation amount in the refrigeration cycle apparatus 10 can be kept equal to that of the conventional refrigerant.
  • HFO-1123 is superior in energy saving performance among other HFO refrigerants.
  • HFO-1123 has a larger latent heat than HFC-410A that has been used in the past, so that it is possible to reduce the refrigerant circulation amount in the refrigeration cycle apparatus 10. That is, the refrigeration cycle apparatus 10 using HFO-1123 as a working fluid reduces heat loss in the flat tube 2 (heat transfer tube) in the heat exchanger 1 and radiates heat equivalent to the case where a conventional refrigerant is used ( It is possible to demonstrate (cooling) capability.
  • the compressor 11 compresses the refrigerant discharged from the second heat exchanger 14 and supplies the high-temperature and high-pressure refrigerant to the first heat exchanger 12.
  • the first heat exchanger 12 functions as a condenser, performs heat exchange between the air supplied from the fan 15a and the refrigerant, and condenses and liquefies the refrigerant.
  • the expansion means 13 includes an expansion valve, a capillary tube, a decompression device, a throttling device, and the like. The expansion means 13 expands the refrigerant discharged from the first heat exchanger 12 and supplies it to the second heat exchanger 14 as a low-temperature and low-pressure refrigerant.
  • the second heat exchanger 14 functions as an evaporator, performs heat exchange between the air supplied from the fan 15b and the refrigerant, and evaporates the refrigerant.
  • the first heat exchanger 12 functions as an evaporator and the second heat exchanger 14 functions as a condenser. You may do it.
  • FIG. 2 is a perspective view showing an example of a heat exchanger of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the heat exchanger 1 includes a plurality of flat tubes 2, a plurality of fins 3, and a pair of headers 4a and 4b.
  • the plurality of fins 3 are arranged at intervals, and are configured such that a fluid such as air flows through the intervals.
  • the plurality of flat tubes 2 are inserted into the plurality of fins 3.
  • the direction of the longitudinal dimension in the flat cross section faces the flow direction of the air flowing between the plurality of fins 3, and the direction of the width dimension in the flat cross section ( Hereinafter, they are arranged at intervals in the short axis direction).
  • the headers 4a and 4b extend vertically and are opposed to each other, and connect both ends of the plurality of flat tubes 2 respectively.
  • the refrigerant that has flowed into the header 4 a is branched into multiple portions within the header 4 a and flows into each of the plurality of flat tubes 2.
  • the refrigerant flowing through the refrigerant flow paths in the plurality of flat tubes 2 exchanges heat with the air flowing between the plurality of fins 3 and between the plurality of flat tubes 2 and flows into the header 4b.
  • the refrigerant flowing into the header 4b joins inside the header 4b and then flows out from the header 4b.
  • the headers 4a and 4b are written vertically in the drawing, and the refrigerant flows in the horizontal direction toward the flat tube 2.
  • the orientation of the headers 4a and 4b is not limited to this direction.
  • the headers 4a and 4b may be installed sideways, and the refrigerant may flow in the vertical direction.
  • a branch pipe that branches the refrigerant may be provided instead of at least one of the headers 4a and 4b.
  • the fin 3 is made of aluminum, for example.
  • the fin 3 is produced
  • the material of the fin 3 is not limited to aluminum, and any material such as copper can be used.
  • the shape of the fin 3 can use arbitrary shapes, such as a plate-shaped plate fin or the corrugated fin formed in the wave shape, for example. Moreover, you may provide the fin 3 in the shape which improves heat exchange performance, such as cutting and raising processing or forming an uneven
  • FIG. 3 is a cross-sectional view showing an example of a flat tube of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the flat tube 2 has a flat cross section.
  • the flat tube 2 is configured by a flat multi-hole tube, and a plurality of flow paths 21 partitioned by the partition wall 20 are formed along the longitudinal direction of the flat tube 2.
  • the flat tube 2 is made of, for example, aluminum.
  • brazing can be used for joining the fins 3 and the flat tubes 2.
  • the joining of the fin 3 and the flat tube 2 by brazing is a heat exchanger 1 that has higher heat transfer performance and superior heat exchange performance than the pipe expansion method in which the pipe inserted into the fin 3 is expanded and joined. Can be provided.
  • FIG. 4 is a cross-sectional view showing an example of the heat exchanger of the refrigeration cycle apparatus in Embodiment 1 of the present invention.
  • the flat tubes 2 are arranged in, for example, two rows in the row direction that is the air flow direction. Further, the flat tubes 2 are arranged in a plurality of stages in the step direction orthogonal to the row direction. Further, the flat tubes 2 are arranged so that adjacent rows of flat tubes 2 do not overlap in the step direction (for example, a staggered arrangement). And air flows in from the side where the fin 3 is attached upstream of the flat tube 2.
  • the flat tube 2 has, for example, a width dimension (hereinafter referred to as a short axis diameter DA) in a flat cross section of 2.0 mm and a long dimension (hereinafter referred to as a long axis diameter DB) in a flat cross section of 19.0 mm.
  • a width dimension hereinafter referred to as a short axis diameter DA
  • a long dimension hereinafter referred to as a long axis diameter DB
  • the number of holes in the flow path 21 is 20, and the thickness ti of the partition wall 20 in the flow path 21 is 0.20 mm.
  • the wall thickness to between the outer wall of the flat tube 2 and the inner wall of the flow path 21 is 0.30 mm.
  • a step pitch DP which is a distance in the step direction connecting the centers of the adjacent flat tubes 2, is arranged at 13.6 mm.
  • the fin 3 has an air flow direction width L of 22 mm.
  • the heat exchanger 1 has a height H_HEX of 600 mm and a fin product width H_W of 850 mm (see FIG. 2).
  • FIG. 5 is a characteristic diagram showing the relationship between the short axis diameter DA of the flat tube and the coefficient of performance (COP) in the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the case where the heat exchanger 1 is used as an evaporator is taken as an example, and the coefficient of performance (COP) at each short axis diameter DA is extracted by simulation using the short axis diameter DA of the flat tube 2 as a parameter.
  • FIG. 5 shows a comparison between the case of using HFC-410A and the case of using HFO-1123 as the refrigerant circulating in the refrigerant circuit.
  • a certain aspect ratio B / A is constant at a preset value.
  • the aspect ratio B / A is equivalent to the dimension example described above. That is, in the dimension example described above, the in-pipe length B of the flow path 21 is 0.73 mm and the in-pipe length A is 1.4 mm, so the aspect ratio B / A is 0.52.
  • the ratio between the step pitch DP of the flat tube 2 and the short axis diameter DA is constant at a preset value.
  • the dimension example described above it is equivalent to the dimension example described above. That is, DP / DA is 6.8, for example. Further, the ratio between the wall thickness to of the flat tube 2 and the short axis diameter DA is constant at a preset value. For example, it is equivalent to the dimension example described above. That is, to / DA is 0.15, for example. Further, the long axis diameter DB of the flat tube 2, the height H_HEX of the heat exchanger 1, and the fin product width H_W are equivalent to the above-described dimension example.
  • the amount of heat released from the fins 3 and the flat tubes 2 to the air (the amount of heat received) is constant.
  • the parameters of the heat transfer tubes and the heat exchanger 1 other than the above, such as the pitch of the fins 3, the number of holes, the path configuration of the heat exchanger 1, and the operating conditions of the refrigeration cycle are values at which the coefficient of performance is almost optimal. is there.
  • the ventilation resistance between the adjacent flat tubes 2 is reduced.
  • the step pitch DP / the short axis diameter DA is constant at a preset value
  • the flat tube 2 can be mounted with high density.
  • the aspect ratio B / A and the wall thickness to / short axis diameter DA are constant at preset values, when the short axis diameter DA of the flat tube 2 becomes small, the flow path 21 inside the flat tube 2 is reduced. The number of holes will increase.
  • tube of the flat tube 2 contacts with a heat-transfer surface increases, and it can heat-exchange efficiently. Therefore, the performance of the heat exchanger 1 is improved and the coefficient of performance is also improved.
  • the short axis diameter DA of the flat tube 2 becomes too small, the cross-sectional area of the flow path 21 of the flat tube 2 is also narrowed, so that the pressure loss in the tube increases. In order to suppress an increase in the pressure loss in the pipe, it is necessary to increase the number of passes of the heat exchanger 1.
  • the headers 4a and 4b can be used evenly in order to exhibit sufficient performance. It is necessary to distribute the refrigerant.
  • the short axis diameter DA of the flat tube 2 becomes too small, it becomes difficult to distribute the refrigerant evenly.
  • the upper limit of the number of passes is determined depending on the size of the heat exchanger 1, if the short axis diameter DA is reduced, it becomes impossible to cope with an increase in the pressure loss in the pipe due to an increase in the number of passes. For this reason, when the short axis diameter DA of the flat tube 2 becomes too small, the performance of the heat exchanger 1 is lowered and the coefficient of performance is also lowered.
  • the short axis diameter DA of the flat tube 2 is less than 0.8 mm, it becomes difficult in manufacturing the flat tube 2 such as extrusion.
  • the short axis diameter DA of the flat tube 2 is 0.9 mm, for example, when the aspect ratio B / A is 0.52 and the wall thickness to / short axis diameter DA is 0.15 as in the above-described dimension example,
  • the in-tube length B of the flow path 21 in the long axis direction of the flat tube 2 is 0.33 mm.
  • the size of the sludge produced by the chemical reaction of the decomposition product of HFO-1123 is about 0.15 mm. Therefore, if the in-pipe length B of the flow channel 21 is 0.33 mm, sludge is accumulated in the flow channel 21 even when HFO-1123 flowing through the flat tube 2 is decomposed and sludge is generated. It becomes possible to flow without. For this reason, it becomes possible to ensure sufficient reliability.
  • the minor axis diameter DA of the flat tube 2 should satisfy the relationship of 0.9 mm ⁇ DA ⁇ 3.0 mm.
  • the aspect ratio B / A If a smaller value is selected for the aspect ratio B / A, the in-pipe length B of the flow path 21 in the long axis direction of the flat tube 2 is not sufficient, but the pressure loss in the pipe increases. In general, the aspect ratio is increased to such an extent that the pressure resistance is maintained.
  • the heat transfer performance of the heat exchanger 1 is improved when HFO-1123 or a mixed refrigerant containing HFO-1123 is used as the refrigerant circulating in the refrigerant circuit. Can do. Moreover, even if it is a case where the sludge resulting from decomposition
  • FIG. FIG. 6 is a cross-sectional view showing an example of a flat tube of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • FIG. 7 is an enlarged cross-sectional view showing an example of a flat tube of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • one or a plurality of protrusions 22 are formed on the inner wall surface of the flow channel 21 along the flow channel direction. 7 shows a case where a gas-liquid two-phase refrigerant flows, 25 indicates a two-phase liquid film, and 26 indicates a gas-liquid interface.
  • the contact area between the inner wall surface of the flow path 21 and the refrigerant can be increased.
  • the liquid refrigerant concentrates on the bottom 24 of the protrusion 22 due to the surface tension of the refrigerant, so that the drainage in the tube axis direction is improved and the two phases around the bottom 24 of the protrusion 22 are improved.
  • the thickness of the flowing liquid film 25 can be reduced. Therefore, heat exchange can be performed more efficiently than in the case where the protrusions 22 are not provided.
  • the protrusion 22 has a triangular cross-sectional shape, but the present invention is not limited to this.
  • any projection shape such as a semicircular shape, an elliptical shape, or a rectangular shape, an effect equivalent to the above-described object can be achieved.
  • the sludge 31 generated when the HFO-1123 is decomposed is It is easy to deposit.
  • sludge 31 is particularly easily deposited on the inner wall surface 23 facing downward in the gravitational direction.
  • the distance D between the adjacent protrusions 22 satisfies 0.15 mm ⁇ D.
  • the refrigerant can flow without the sludge 31 being deposited.
  • tube falls by increasing the space
  • the distance D between adjacent protrusions 22 has a relationship of 0.15 mm ⁇ D ⁇ 0.50 mm. Try to meet. Thereby, even when the plurality of protrusions 22 are formed on the inner wall surface of the flow path 21, the sludge 31 can flow without being deposited.
  • FIG. 9 is a cross-sectional view showing an example of a flat tube of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • FIG. 10 is an enlarged cross-sectional view showing an example of a flat tube of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • 9 and 10 show a case in which one protrusion 22 is provided on the inner wall surface 23 facing downward in the gravity direction and one protrusion 22 is provided on the inner wall surface facing upward in the gravity direction among the inner wall surfaces of the flow path 21. .
  • the number of protrusions 22 is not limited to this, and a plurality of protrusions 22 may be provided on one inner wall surface.
  • interval D is formed so that the relationship mentioned above may be satisfy
  • sludge 31 generated when the HFO-1123 is decomposed easily accumulates between the protrusion 22 and the side wall of the flow path 21.
  • sludge 31 is particularly easily deposited on the inner wall surface 23 facing downward in the gravitational direction. For this reason, when the distance C from the bottom 24 of the protrusion 22 to the side wall of the flow path 21 satisfies 0.15 mm ⁇ C, the refrigerant can flow without depositing sludge 31 in the flow path 21.
  • the distance C is preferably 0.50 mm or less.
  • the distance C from the bottom 24 of the protrusion 22 to the side wall of the flow path 21 is 0.
  • the relationship of 15 mm ⁇ D ⁇ 0.50 mm is satisfied.
  • FIG. FIG. 11 is a characteristic diagram showing the relationship between the pressure ratio performance and the ratio between the thickness to of the flat tube and the minor axis diameter DA of the refrigeration cycle apparatus according to Embodiment 3 of the present invention.
  • HFO-1123 or a mixed refrigerant containing HFO-1123 is used as the refrigerant circulating in the refrigerant circuit
  • HFO-1123 is a refrigerant having a lower standard boiling point than the conventionally used HFC-410A.
  • the pressure becomes larger than that at the saturation temperature equivalent to that of HFC-410A. For this reason, it is necessary to sufficiently ensure the pressure resistance performance of the flat tube 2.
  • the wall thickness to of the flat tube 2 and the short axis diameter DA are used as parameters in the calculation conditions during the performance coefficient simulation shown in FIG. 5 of the first embodiment described above.
  • the horizontal axis indicates the ratio to / DA between the wall thickness to of the flat tube 2 and the short axis diameter DA
  • the vertical axis indicates the pressure resistance Pr of the flat tube 2 and the flat tube 2 required. The ratio Pr / Pn to the breakdown voltage Pn is shown.
  • the pressure resistance performance Pr needs to exceed the required pressure resistance Pn. That is, when Pr / Pn is 1 or less, the pressure resistance performance cannot be sufficiently ensured, so it is necessary to satisfy Pr / Pn> 1. In the example shown in FIG. 11, when to / DA is less than 0.10, Pr / Pn is 1 or less. Therefore, it is necessary to satisfy the relationship of 0.10 ⁇ to / DA. On the other hand, when to / DA increases too much, the pressure resistance is sufficiently ensured, but the cross-sectional area of the flow path 21 and the heat transfer area of the flow path 21 are reduced, and the heat exchange performance is also reduced.
  • the pressure resistance performance is improved in the case of using HFO-1123 or a mixed refrigerant containing HFO-1123. Sufficiently can be secured and the heat exchange performance can be improved.
  • the heat exchanger 1 has been described as an example when used as an evaporator in an outdoor unit of an air conditioner.
  • the heat exchanger 1 is used as a condenser in an indoor unit of an air conditioner.
  • the same effect can be achieved when used as another heat exchanger 1.
  • the same effect can be achieved also when it is applied to at least one of the first heat exchanger 12 and the second heat exchanger 14 in the refrigeration cycle apparatus 10 using the heat exchanger 1 described above.

Abstract

L'invention concerne un appareil à cycle de réfrigération configuré de telle sorte qu'un réfrigérant mélangé contenant du HFO-1123 ou du HFO-1123 est utilisé en tant que réfrigérant, et au moins l'un parmi un premier échangeur de chaleur et un deuxième échangeur de chaleur possède une pluralité d'ailettes et une pluralité de tubes plats dans lesquels sont formés une pluralité de canaux à travers lesquels s'écoule le réfrigérant. La pluralité de tubes plats satisfait à la relation dans laquelle 0,9 mm ≤ DA ≤ 3,0 mm, DA désignant la largeur du tube plat.
PCT/JP2014/084466 2014-12-26 2014-12-26 Appareil à cycle de réfrigération WO2016103437A1 (fr)

Priority Applications (3)

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JP2016565792A JP6415600B2 (ja) 2014-12-26 2014-12-26 冷凍サイクル装置
PCT/JP2014/084466 WO2016103437A1 (fr) 2014-12-26 2014-12-26 Appareil à cycle de réfrigération
EP14909044.1A EP3239640A4 (fr) 2014-12-26 2014-12-26 Appareil à cycle de réfrigération

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Application Number Priority Date Filing Date Title
PCT/JP2014/084466 WO2016103437A1 (fr) 2014-12-26 2014-12-26 Appareil à cycle de réfrigération

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Cited By (3)

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Publication number Priority date Publication date Assignee Title
JP2018059638A (ja) * 2016-09-30 2018-04-12 株式会社富士通ゼネラル 熱交換器および冷凍サイクル装置
WO2021095567A1 (fr) * 2019-11-14 2021-05-20 ダイキン工業株式会社 Tuyau de transfert de chaleur et échangeur de chaleur
WO2022085067A1 (fr) * 2020-10-20 2022-04-28 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

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