WO2015005352A1 - Échangeur de chaleur, et dispositif de pompe à chaleur - Google Patents

Échangeur de chaleur, et dispositif de pompe à chaleur Download PDF

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Publication number
WO2015005352A1
WO2015005352A1 PCT/JP2014/068203 JP2014068203W WO2015005352A1 WO 2015005352 A1 WO2015005352 A1 WO 2015005352A1 JP 2014068203 W JP2014068203 W JP 2014068203W WO 2015005352 A1 WO2015005352 A1 WO 2015005352A1
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WO
WIPO (PCT)
Prior art keywords
thin plate
heat exchanger
plate members
refrigerant
heat
Prior art date
Application number
PCT/JP2014/068203
Other languages
English (en)
Japanese (ja)
Inventor
石橋　晃
拓也 松田
岡崎　多佳志
厚志 望月
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 EP14823375.2A priority Critical patent/EP3021064B1/fr
Priority to CN201480039081.4A priority patent/CN105452794A/zh
Priority to JP2015526356A priority patent/JPWO2015005352A1/ja
Priority to US14/902,031 priority patent/US20160298886A1/en
Publication of WO2015005352A1 publication Critical patent/WO2015005352A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • the present invention relates to a heat exchanger and a heat pump device including the heat exchanger.
  • both ends of a plurality of multi-channel heat transfer tubes are respectively connected to a pair of headers arranged at intervals, and a plurality of multi-channel Fins, i.e., thin plate members, which are members that promote heat exchange are connected between the heat transfer tubes.
  • a plurality of fins that is, both ends of a plurality of thin plate members are connected to a pair of headers arranged at intervals, and a flow path is provided inside each of the plurality of thin plate members. Is formed (see, for example, Patent Document 1).
  • the present invention has been made against the background of the above problems, and provides a heat exchanger and a heat pump device that can improve heat exchange performance.
  • the heat exchanger according to the present invention includes a plurality of thin plate members that are arranged at intervals, a fluid flows between them, and a flow path through which a medium that exchanges heat with the fluid flows, and the plurality of thin plate members A plurality of thin plate members, wherein the interval between the adjacent thin plate members is Fp, and the thickness of the thin plate members is Ft, 3 ⁇ Fp / Ft ⁇ 21 is satisfied.
  • the heat pump device includes a plurality of thin plate members that are arranged at intervals, a fluid flows between them, a flow path through which a medium that exchanges heat with the fluid flows, and a plurality of the thin plate members
  • a heat exchanger comprising a pair of headers that connect both ends, respectively, and a refrigerant circuit that connects the compressor, the condenser, the expansion means, and the evaporator by piping and circulates the refrigerant, the evaporator
  • the heat exchanger is used, and the heat exchanger flows into the header disposed on the lower side in the gravity direction of the pair of headers, and the heat exchanger is disposed on the lower side in the gravity direction.
  • the refrigerant that has flowed into the header flows through the flow path formed in the plurality of thin plate members in a direction from the lower side to the upper side in the gravitational direction, and flows into the header disposed on the upper side in the gravitational direction.
  • the refrigerant Placed above the header Et the refrigerant are arranged and connected so as to flow out, the heat exchanger, and arranged in the upper and lower sides of the gravity direction, the heat exchanger arranged in parallel, which are connected in parallel.
  • a plurality of thin plate members formed with a flow path in which a fluid flows between them and a medium through which heat exchange with the fluid flows are formed, and both ends of the plurality of thin plate members are respectively provided.
  • heat exchange performance can be improved.
  • a plurality of thin plate members formed with a flow path in which a fluid flows between them and a medium through which heat exchange with the fluid flows are formed, and both ends of the plurality of thin plate members are respectively provided.
  • Heat exchange performance in a heat pump device comprising: a heat exchanger comprising a pair of headers to be connected; and a refrigerant circuit that connects the compressor, the condenser, the expansion means, and the evaporator by piping and circulates the refrigerant. Can be improved.
  • FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. It is an enlarged view which shows the B section of FIG. It is a figure which shows the performance characteristic of the heat exchanger which concerns on Embodiment 1 of this invention. It is a refrigerant circuit diagram of the air conditioner according to Embodiment 1 of the present invention. It is a perspective view which shows the heat exchanger which concerns on Embodiment 2 of this invention. It is sectional drawing which shows the arrangement
  • FIG. 1 is a perspective view showing a heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 2 is a side view showing the heat exchanger according to Embodiment 1 of the present invention.
  • 3 is a cross-sectional view taken along the line AA in FIG.
  • FIG. 4 is an enlarged view showing a portion B of FIG.
  • the heat exchanger includes a plurality of fins, that is, a thin plate member 1, and a pair of headers (an inlet side header 2 and an outlet side header 3).
  • Each of the plurality of thin plate members 1 is made of aluminum having a thickness of about 2 mm or less, for example.
  • the plurality of thin plate members 1 are arranged at intervals, and a fluid (for example, air) flows therebetween.
  • the plurality of thin plate members 1 are formed with one or a plurality of flow paths 11 through which a medium (for example, a refrigerant) flows.
  • the both ends of the thin plate member 1 and the both ends of the thin plate member 1 disposed adjacent to the thin plate member 1 are not connected by a thin plate member in which no flow path is formed. That is, a member that promotes heat exchange between the fluid and the thin plate member 1 is not provided between the adjacent thin plate members 1.
  • a pair of headers connect both ends of the plurality of thin plate members 1, respectively.
  • the refrigerant flows from the refrigerant inlet 4 of the inlet header 2.
  • the refrigerant flowing into the inlet header 2 flows into the outlet header 3 through the flow paths 11 of the plurality of thin plate members 1.
  • the refrigerant flows out from the refrigerant outlet 5 of the outlet side header 3.
  • coolant is not limited to this, A reverse direction may be sufficient. With such a configuration, the heat exchanger exchanges heat between the air passing between the plurality of thin plate members 1 and the refrigerant flowing through the flow paths 11 inside the plurality of thin plate members 1.
  • the plurality of thin plate members 1 satisfy the relationship of 3 ⁇ Fp / Ft ⁇ 21 when the interval between the thin plate members 1 (that is, the fin pitch) is Fp and the thickness of the thin plate member 1 is Ft. Yes.
  • FIG. 5 is a diagram showing the performance characteristics of the heat exchanger according to Embodiment 1 of the present invention.
  • interval Fp of the thin plate member 1 with respect to thickness Ft is shown.
  • the AK value is a value obtained by multiplying the heat transfer rate K and the heat transfer area A in the heat exchanger, and represents the heat transfer characteristics of the heat exchanger.
  • the conventional heat exchanger used as a reference is a plate that performs heat exchange between air passing between a plurality of thin plate members (thin plate members in which no flow path is formed) and a refrigerant flowing through the plurality of heat transfer tubes. It is a fin-type heat exchanger.
  • the heat transfer tubes of the conventional heat exchanger are arranged in two rows in the air flow direction, and are arranged in a plurality of stages in a direction orthogonal to the air flow.
  • AK / ⁇ P decreases when Fp / Ft becomes too small. Further, AK / ⁇ P decreases when Fp / Ft becomes too large. That is, Fp / Ft has an appropriate range in which AK / ⁇ P can be improved. For example, in the case where the distance between the thin plate members 1 is the same Fp, when the thickness Ft of the thin plate member 1 is increased, the flow area of the flow path 11 is increased, and the heat transfer rate K is increased due to the increase in the flow rate of the refrigerant, thereby increasing the heat transfer performance AK Increases and AK / ⁇ P increases.
  • the thickness Ft of the thin plate member 1 becomes too thick, the air-side ventilation resistance ⁇ P increases and AK / ⁇ P decreases. Further, for example, when the thickness Ft of the thin plate member 1 is reduced, the air-side ventilation resistance ⁇ P is reduced and AK / ⁇ P is increased. However, if the thickness Ft of the thin plate member 1 becomes too thin, the flow passage area of the flow passage 11 decreases, the heat transfer rate K decreases due to the decrease in the flow rate of the refrigerant, the heat transfer performance AK decreases, and AK / ⁇ P Decreases.
  • the heat exchanger according to the first embodiment is 3 ⁇ Fp / Ft ⁇ so that the value (100%) or more can be improved as compared with the conventional heat exchanger. 21 relationships are satisfied. Thereby, the heat exchange performance of the heat exchanger can be improved.
  • plate fins that exchange heat between air passing between a plurality of thin plate members (thin plate members in which no flow path is formed) and a refrigerant flowing through the plurality of heat transfer tubes
  • contact thermal resistance exists between the heat transfer tube and the thin plate member (thin plate member in which no flow path is formed).
  • the thin plate member has a heat conduction resistance.
  • the flow path 11 through which the refrigerant flows is formed inside the thin plate member 1. For this reason, the resistance of heat conduction becomes small.
  • contact thermal resistance between the thin plate member (thin plate member in which no flow path is formed) and the heat transfer tube does not occur. Therefore, compared with the conventional heat exchanger, the heat exchange performance of the heat exchanger can be improved.
  • FIG. 6 is a refrigerant circuit diagram of the air conditioner according to Embodiment 1 of the present invention.
  • the refrigerant circuit shown in FIG. 6 includes a compressor 33, a condenser 34, an expansion device 35 that is an expansion means, and an evaporator 36.
  • the air conditioner includes a blower 37 that blows air to the condenser 34 and the evaporator 36, and a blower motor 38 that drives the blower 37.
  • Cooling energy efficiency indoor heat exchanger (evaporator) capacity / total input
  • a heat exchanger is arrange
  • coolant flows in into the inlet side header 2 arrange
  • the refrigerant flowing into the inlet header 2 is distributed to the plurality of flow paths 11 formed in the plurality of thin plate members 1 and flows from the bottom to the top of the plurality of thin plate members 1. Thereafter, the refrigerant flows out from the outlet header 3.
  • the inlet header 2 corresponds to the “header arranged on the lower side in the gravity direction” in the present invention.
  • the outlet header 3 corresponds to the “header arranged on the upper side in the direction of gravity” in the present invention.
  • the refrigerant flowing through the evaporator 36 is in a gas-liquid two-phase state.
  • the gas-liquid two-phase refrigerant may have a plug flow or a slag flow.
  • the heat exchanger is used for the evaporator 36, the refrigerant flows through the flow paths 11 of the plurality of thin plate members 1 from the bottom to the top. Therefore, in the case of a plug flow or a slag flow, the refrigerant stagnates due to bubble buoyancy. It can flow upwards. Thereby, the heat exchange performance of the heat exchanger can be improved.
  • condensed water condensed water
  • a heat exchanger is arrange
  • Embodiment 2 FIG. Hereinafter, the difference between the heat exchanger of the second embodiment and the first embodiment will be described. In addition, the same code
  • FIG. 1
  • FIG. 7 is a perspective view showing a heat exchanger according to Embodiment 2 of the present invention.
  • FIG. 8 is a cross-sectional view showing the arrangement of the thin plate members of the heat exchanger according to Embodiment 2 of the present invention.
  • the heat exchanger according to the second embodiment is provided in two rows in the fluid (air) flow direction. Further, the plurality of thin plate members 1 on the upstream side and the plurality of thin plate members 1 on the downstream side are arranged so as not to overlap each other in the fluid (air) flow direction. That is, the arrangement of the plurality of thin plate members 1 is staggered.
  • the air flow developed between the plurality of thin plate members 1 in the first row can be further developed in a new boundary layer at the leading edge of the plurality of thin plate members 1 in the second row, and heat transfer is improved. Can be promoted.
  • Embodiment 3 the difference between the heat exchanger of the third embodiment and the first embodiment will be described.
  • symbol is attached
  • FIG. 9 is a perspective view showing a heat exchanger according to Embodiment 3 of the present invention.
  • FIG. 10 is a cross-sectional view showing the inlet header of the heat exchanger according to Embodiment 3 of the present invention.
  • FIG. 11 is a diagram showing an inner tube of a heat exchanger according to Embodiment 3 of the present invention.
  • the inlet-side header 2 of the heat exchanger according to the third embodiment includes an outer tube 6 and an inner tube 7 provided inside the outer tube 6.
  • the outer tube 6 is connected to the ends of the plurality of thin plate members 1.
  • the outer tube 6 is a tube having a rectangular cross section, for example, and is closed at both ends.
  • a pipe constituting the refrigerant inlet 4 through which the refrigerant flows into the inner pipe 7 passes through the side surface of the outer pipe 6.
  • the inner tube 7 is, for example, a circular tube.
  • the inner pipe 7 is formed with a refrigerant inlet 4 through which refrigerant flows and a plurality of outlets 71 through which the refrigerant flowing in from the inlet flows out into the outer pipe 6.
  • the length of the inner tube 7 is substantially the same as the arrangement range of the plurality of thin plate members 1.
  • the plurality of outlets 71 are formed only on the lower side (lower part in the direction of gravity) of the inner tube 7.
  • the plurality of outlets 71 are arranged substantially evenly in the length direction of the inner tube 7.
  • the liquid phase refrigerant flows from the refrigerant inlet 4 into the inner tube 7.
  • the liquid-phase refrigerant that has flowed into the inner pipe 7 flows out of each of the plurality of outlets 71 into the outer pipe 6.
  • the liquid-phase refrigerant is agitated inside the inlet-side header 2, and the liquid-phase refrigerant flows equally into the plurality of thin plate members 1. Therefore, local drying of the refrigerant hardly occurs in some of the plurality of thin plate members 1, and the heat exchange performance of the heat exchanger can be improved.
  • Embodiment 4 FIG.
  • the difference between the heat exchanger of the fourth embodiment and the first embodiment will be described.
  • symbol is attached
  • FIG. 12 is a side view showing a heat exchanger according to Embodiment 4 of the present invention.
  • two heat exchangers are provided so as to overlap in the direction of gravity.
  • Each of the two heat exchangers is arranged such that the longitudinal direction of the plurality of thin plate members 1 is the direction of gravity.
  • the inlet-side header 2 of the heat exchanger arranged on the upper side and the inlet-side header 2 of the heat exchanger arranged on the lower side are connected in parallel
  • the outlet-side header of the heat exchanger arranged on the upper side. 3 and the outlet header 3 of the heat exchanger arranged on the lower side are connected in parallel.
  • each heat exchanger when the heat exchangers are arranged side by side on the upper side and the lower side in the direction of gravity and are used as the evaporator 36, each heat exchanger is arranged on the lower side in the direction of gravity.
  • the refrigerant flows into the inlet-side header 2 and the refrigerant flows out from the outlet-side header 3 arranged on the upper side in the direction of gravity.
  • the flow paths 11 of the plurality of thin plate members 1 have a fluid equivalent diameter (equivalent diameter) of 0.05 to 0.2 mm.
  • the heat transfer coefficient in the flow path becomes small.
  • the heat exchanger is used as the evaporator 36, that is, when the refrigerant in the gas-liquid two-phase state flows through the thin plate member 1 in the direction of rising from the lower side in the weight direction toward the upper side, a plurality of refrigerants are used. Due to the distribution to the flow paths 11, even if the flow rate of the refrigerant flowing into each flow path 11 decreases, the heat transfer coefficient in each flow path 11 is difficult to increase or increases.
  • the thin plate member 1 is compared with a case where the thin plate member 1 is a circular tube having a circular flow path having an inner cross-sectional area equal to the total cross-sectional area of each flow path 11.
  • the flow rate of the refrigerant per flow channel 11 is reduced by the amount of the plurality of flow channels 11 formed in each thin plate member 1, and the heat transfer in each flow channel 11 due to the decrease in the flow rate of the refrigerant.
  • the phase change of the refrigerant in each flow path 11 is promoted.
  • the number of the thin plate members 1 is larger than the number of circular tubes due to the thin plate member 1 being thin. That is, since the total number of the flow paths 11 can be increased as compared with the number of circular tubes, the refrigerant flow rate per flow path 11 is reduced and the flow rate of the refrigerant is reduced. The phenomenon that the heat transfer coefficient in each flow path 11 becomes equal to the heat transfer coefficient in the circular pipe is generated, whereby the phase change of the refrigerant in each flow path 11 is promoted.
  • the length of the plurality of thin plate members 1 is made smaller than that of the conventional heat exchanger.
  • two heat exchangers according to the fourth embodiment are provided so as to overlap each other in the direction of gravity, thereby reducing the length of the plurality of thin plate members 1 and maintaining sufficient refrigeration cycle performance.
  • the exchange volume is to be secured. For example, when a heat exchanger is mounted on an outdoor unit of an air conditioner, a sufficient heat exchange volume can be ensured even if the unit height of the outdoor unit is the same as that of the conventional unit.
  • the effect can be achieved in any refrigerant such as R410A, R32, HFO1234yf, and the like.
  • coolant was shown as a working fluid, even if it uses other gas, liquid, and gas-liquid mixed fluid, there exists the same effect.
  • the same effect can be obtained when the heat exchanger described in the first to fourth embodiments is used in either an indoor unit or an outdoor unit of an air conditioner.
  • the heat exchanger described in Embodiments 1 to 4 above and the air conditioner using the heat exchanger include refrigerants such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil.
  • refrigerants such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil. The effect can be achieved with any refrigeration oil, whether the oil is soluble or not.
  • the utilization example of the present invention is not limited to the above-described air conditioner, but can be used for a heat pump apparatus that needs to improve heat exchange performance and energy saving performance.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

L'échangeur de chaleur de l'invention est équipé : d'une pluralité d'éléments lamelle (1) qui sont disposés à intervalles et entre lesquels s'écoule un fluide, et dans lesquels sont formés des trajets d'écoulement dans la partie interne desquels s'écoule un milieu destiné à un échange de chaleur avec le fluide ; et d'une paire de colonnes connectant chacune des deux parties extrémité de la pluralité d'éléments lamelle (1). La pluralité d'éléments lamelle (1) satisfait la relation 3≦Fp/Ft≦21 lorsque l'intervalle des éléments lamelle (1) adjacents est représenté par Fp, et l'épaisseur des éléments lamelle (1) est représentée par Ft.
PCT/JP2014/068203 2013-07-08 2014-07-08 Échangeur de chaleur, et dispositif de pompe à chaleur WO2015005352A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP14823375.2A EP3021064B1 (fr) 2013-07-08 2014-07-08 Dispositif de pompe à chaleur
CN201480039081.4A CN105452794A (zh) 2013-07-08 2014-07-08 热交换器以及热泵装置
JP2015526356A JPWO2015005352A1 (ja) 2013-07-08 2014-07-08 ヒートポンプ装置
US14/902,031 US20160298886A1 (en) 2013-07-08 2014-07-08 Heat exchanger and heat pump apparatus

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PCT/JP2013/068677 WO2015004720A1 (fr) 2013-07-08 2013-07-08 Échangeur de chaleur, et appareil de conditionnement de l'air
JPPCT/JP2013/068677 2013-07-08

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WO2015005352A1 true WO2015005352A1 (fr) 2015-01-15

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PCT/JP2014/068203 WO2015005352A1 (fr) 2013-07-08 2014-07-08 Échangeur de chaleur, et dispositif de pompe à chaleur

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WO (2) WO2015004720A1 (fr)

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WO2020230267A1 (fr) 2019-05-14 2020-11-19 三菱電機株式会社 Échangeur de chaleur, et dispositif de cycle frigorifique

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WO2015004720A1 (fr) 2015-01-15
EP3021064A4 (fr) 2017-03-22
JPWO2015005352A1 (ja) 2017-03-02
EP3021064B1 (fr) 2019-05-01
CN105452794A (zh) 2016-03-30
EP3021064A1 (fr) 2016-05-18

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