WO2015005352A1 - Heat exchanger, and heat pump device - Google Patents

Heat exchanger, and heat pump device 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
French (fr)
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/en
Priority to US14/902,031 priority patent/US20160298886A1/en
Priority to JP2015526356A priority patent/JPWO2015005352A1/en
Priority to CN201480039081.4A priority patent/CN105452794A/en
Publication of WO2015005352A1 publication Critical patent/WO2015005352A1/en

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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)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (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

This heat exchanger is provided with: a plurality of thin-plate members (1) which are disposed with a clearance therebetween, which have a fluid flowing therebetween, and in which passages are formed, said passages having, flowing therethrough, a medium for performing heat exchange with the fluid; and a pair of headers which respectively connect both ends of the plurality of thin-plate members (1). In cases when Fp is the clearance between neighbouring thin-plate members (1), and Ft is the thickness of the thin-plate members (1), the plurality of thin-plate members (1) satisfy the relationship 3 ≤ Fp/Ft ≤ 21.

Description

熱交換器、及びヒートポンプ装置Heat exchanger and heat pump device
　本発明は、熱交換器、及び熱交換器を備えたヒートポンプ装置に関する。 The present invention relates to a heat exchanger and a heat pump device including the heat exchanger.
　従来の熱交換器（いわゆるプレートフィン型熱交換器）では、例えば、間隔を空けて配置された一対のヘッダに、複数の多流路伝熱管の両端部がそれぞれ接続され、複数の多流路伝熱管の間に、熱交換を促進する部材であるフィン、つまり薄板部材が連結される。
　また、他の熱交換器として、間隔を空けて配置された一対のヘッダに、複数のフィン、つまり複数の薄板部材の両端部がそれぞれ接続され、その複数の薄板部材のそれぞれの内部に流路が形成されているものもある（例えば、特許文献１参照）。 In a conventional heat exchanger (so-called plate fin type heat exchanger), for example, 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.
In addition, as another heat exchanger, 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).
特表２００８－５２８９４３号公報（要約）Japanese translation of PCT publication No. 2008-528943 (summary)
　上記特許文献１に記載の技術では、複数の薄板部材の厚さ及び間隔については何ら考慮されていない。
　このため、複数の薄板部材の厚さと間隔が適切でない場合が生じて、熱交換器の熱交換性能が低下する、という問題点があった。
　例えば、薄板部材の厚さを厚くしすぎると流路面積が増加するが、複数の薄板部材の間を通過する空気の通風抵抗が大きくなり、熱交換性能が低下する。また、逆に、薄板部材の厚さを薄くすれば複数の薄板部材の間を通過する空気の通風抵抗が小さくなるが、流路面積が減少し、熱交換性能が低下する。 In the technique described in Patent Document 1, no consideration is given to the thickness and interval of the plurality of thin plate members.
For this reason, the case where the thickness and space | interval of a some thin plate member are not appropriate occurred, and there existed a problem that the heat exchange performance of a heat exchanger fell.
For example, if the thickness of the thin plate member is increased too much, the flow path area increases, but the ventilation resistance of the air passing between the plurality of thin plate members increases, and the heat exchange performance decreases. Conversely, if the thickness of the thin plate member is reduced, the ventilation resistance of the air passing between the plurality of thin plate members is reduced, but the flow path area is reduced and the heat exchange performance is reduced.
　本発明は、上記のような課題を背景としてなされたもので、熱交換性能を向上することができる熱交換器、及びヒートポンプ装置を得るものである。 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.
　本発明に係る熱交換器は、間隔を空けて配置され、その間を流体が流れ、内部に前記流体と熱交換する媒体が流れる流路が形成された複数の薄板部材と、前記複数の薄板部材の両端部をそれぞれ接続する一対のヘッダと、を備え、前記複数の薄板部材は、隣り合う前記薄板部材の間隔をＦｐ、前記薄板部材の厚さをＦｔとした場合、３≦Ｆｐ／Ｆｔ≦２１の関係を満たすものである。 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.
　本発明に係るヒートポンプ装置は、間隔を空けて配置され、その間を流体が流れ、内部に前記流体と熱交換する媒体が流れる流路が形成された複数の薄板部材と、前記複数の薄板部材の両端部をそれぞれ接続する一対のヘッダと、を備えた熱交換器と、圧縮機、凝縮器、膨張手段、及び蒸発器を配管で接続し冷媒を循環させる冷媒回路と、を備え、前記蒸発器に、前記熱交換器を用い、前記熱交換器は、前記一対のヘッダのうち、重力方向の下側に配置された前記ヘッダに前記冷媒が流入し、重力方向の下側に配置された前記ヘッダに流入した前記冷媒が、前記複数の薄板部材に形成された前記流路を重力方向の下側から上側に向かう方向に流れて重力方向の上側に配置された前記ヘッダに流入し、重力方向の上側に配置された前記ヘッダから前記冷媒が流出するように配置及び接続され、前記熱交換器を、重力方向の上側と下側とに並設し、並設された前記熱交換器を、並列に接続したものである。 The heat pump device according to the present invention 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. 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.
　本発明は、間隔を空けて配置され、その間を流体が流れ、内部に前記流体と熱交換する媒体が流れる流路が形成された複数の薄板部材と、前記複数の薄板部材の両端部をそれぞれ接続する一対のヘッダと、を備えた熱交換器において、熱交換性能を向上することができる。 In the present invention, 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. In a heat exchanger provided with a pair of headers to be connected, heat exchange performance can be improved.
　本発明は、間隔を空けて配置され、その間を流体が流れ、内部に前記流体と熱交換する媒体が流れる流路が形成された複数の薄板部材と、前記複数の薄板部材の両端部をそれぞれ接続する一対のヘッダと、を備えた熱交換器と、圧縮機、凝縮器、膨張手段、及び蒸発器を配管で接続し冷媒を循環させる冷媒回路と、を備えたヒートポンプ装置において、熱交換性能を向上することができる。 In the present invention, 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.
本発明の実施の形態１に係る熱交換器を示す斜視図である。It is a perspective view which shows the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る熱交換器を示す側面図である。It is a side view which shows the heat exchanger which concerns on Embodiment 1 of this invention. 図２のＡ－Ａ断面図である。FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. 図３のＢ部を示す拡大図である。It is an enlarged view which shows the B section of FIG. 本発明の実施の形態１に係る熱交換器の性能特性を示す図である。It is a figure which shows the performance characteristic of the heat exchanger which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る空気調和機の冷媒回路図である。It is a refrigerant circuit diagram of the air conditioner according to Embodiment 1 of the present invention. 本発明の実施の形態２に係る熱交換器を示す斜視図である。It is a perspective view which shows the heat exchanger which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係る熱交換器の薄板部材の配列を示す断面図である。It is sectional drawing which shows the arrangement | sequence of the thin plate member of the heat exchanger which concerns on Embodiment 2 of this invention. 本発明の実施の形態３に係る熱交換器を示す斜視図である。It is a perspective view which shows the heat exchanger which concerns on Embodiment 3 of this invention. 本発明の実施の形態３に係る熱交換器の入口側ヘッダを示す断面図である。It is sectional drawing which shows the inlet side header of the heat exchanger which concerns on Embodiment 3 of this invention. 本発明の実施の形態３に係る熱交換器の内管を示す図である。It is a figure which shows the inner tube | pipe of the heat exchanger which concerns on Embodiment 3 of this invention. 本発明の実施の形態４に係る熱交換器を示す側面図である。It is a side view which shows the heat exchanger which concerns on Embodiment 4 of this invention.
実施の形態１．
　図１は、本発明の実施の形態１に係る熱交換器を示す斜視図である。
　図２は、本発明の実施の形態１に係る熱交換器を示す側面図である。
　図３は、図２のＡ－Ａ断面図である。
　図４は、図３のＢ部を示す拡大図である。
　図１～図４に示すように、熱交換器は、複数のフィン、つまり薄板部材１と、一対のヘッダ（入口側ヘッダ２、出口側ヘッダ３）と、を備えている。 Embodiment 1 FIG.
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.
As shown in FIGS. 1 to 4, 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).
　複数の薄板部材１のそれぞれは、例えば、厚さが約２ｍｍ以下のアルミ製である。
　複数の薄板部材１は、間隔を空けて配置され、その間を流体（例えば空気）が流れる。複数の薄板部材１には、内部に媒体（例えば冷媒）が流れる１つ又は複数の流路１１が形成されている。薄板部材１の両端部間とその薄板部材１に隣接して配置された薄板部材１の両端部間とは、内部に流路が形成されない薄板部材によって連結されない。つまり、隣り合う薄板部材１間には、流体と薄板部材１との熱交換を促進する部材が設けられない。 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.
　一対のヘッダ（入口側ヘッダ２、出口側ヘッダ３）は、複数の薄板部材１の両端部をそれぞれ接続する。例えば、入口側ヘッダ２の冷媒流入口４から冷媒が流入する。入口側ヘッダ２に流入した冷媒は、複数の薄板部材１の流路１１を通って出口側ヘッダ３に流入する。そして、出口側ヘッダ３の冷媒出口５から冷媒が流出する。なお、冷媒の流通方向はこれに限定されず逆向きでも良い。
　このような構成によって、熱交換器は、複数の薄板部材１の間を通過する空気と、複数の薄板部材１の内部の流路１１を流れる冷媒とを熱交換する。 A pair of headers (inlet side header 2 and outlet side header 3) connect both ends of the plurality of thin plate members 1, respectively. For example, 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. Then, the refrigerant flows out from the refrigerant outlet 5 of the outlet side header 3. In addition, the distribution direction of a refrigerant | 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.
　また、複数の薄板部材１は、隣り合う薄板部材１の間隔（つまり、フィンピッチ）をＦｐ、薄板部材１の厚さをＦｔとした場合、３≦Ｆｐ／Ｆｔ≦２１、の関係を満たしている。 Further, 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.
　図５は、本発明の実施の形態１に係る熱交換器の性能特性を示す図である。
　図５においては、従来の熱交換器を基準（１００％）として、熱交換器の空気側通風抵抗ΔＰに対する伝熱性能ＡＫ［Ｗ／Ｋ］の割合（ＡＫ／ΔＰ）と、薄板部材１の厚さＦｔに対する薄板部材１の間隔Ｆｐの割合（Ｆｐ／Ｆｔ）との関係を示している。
　ここで、ＡＫ値は熱交換器における熱通過率Ｋと伝熱面積Ａとを乗じた値であり、熱交換器の伝熱特性を表すものである。
　なお、基準となる従来の熱交換器は、複数の薄板部材（内部に流路が形成されない薄板部材）の間を通過する空気と、複数の伝熱管を流通する冷媒との熱交換を行うプレートフィン型の熱交換器である。また、従来の熱交換器の伝熱管は、空気の流れ方向に２列配置され、空気の流れと直交する方向に複数段配置されている。また、伝熱管として、Φ７．９４ｍｍの円管を用い、薄板部材（内部に流路が形成されない薄板部材）の間隔＝１．６ｍｍ、伝熱管の段ピッチＤｐ＝２０．４ｍｍ、伝熱管の列ピッチＬｐ＝１７．７ｍｍの構成である。 FIG. 5 is a diagram showing the performance characteristics of the heat exchanger according to Embodiment 1 of the present invention.
In FIG. 5, the ratio (AK / ΔP) of the heat transfer performance AK [W / K] to the air-side ventilation resistance ΔP of the heat exchanger with the conventional heat exchanger as a reference (100%), and the thin plate member 1 The relationship with the ratio (Fp / Ft) of the space | interval Fp of the thin plate member 1 with respect to thickness Ft is shown.
Here, 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.
In addition, 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. Further, 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. In addition, a circular tube having a diameter of Φ7.94 mm is used as the heat transfer tube, the interval between the thin plate members (thin plate member in which no flow path is formed) = 1.6 mm, the step pitch Dp of the heat transfer tubes = 20.4 mm, the row of the heat transfer tubes The pitch Lp is 17.7 mm.
　図５に示されるように、ＡＫ／ΔＰは、Ｆｐ／Ｆｔが小さくなりすぎると低下する。また、ＡＫ／ΔＰは、Ｆｐ／Ｆｔが大きくなりすぎると低下する。つまり、Ｆｐ／Ｆｔには、ＡＫ／ΔＰを向上できる適正な範囲が存在する。
　例えば、薄板部材１の間隔が同一のＦｐの場合、薄板部材１の厚さＦｔが厚くなると流路１１の流通面積が増加し、冷媒の流速増加によって熱通過率Ｋが増えて伝熱性能ＡＫが大きくなり、ＡＫ／ΔＰが増加する。しかし、薄板部材１の厚さＦｔが厚くなりすぎると、空気側通風抵抗ΔＰが大きくなり、ＡＫ／ΔＰが低下する。
　また、例えば、薄板部材１の厚さＦｔが薄くなると、空気側通風抵抗ΔＰが小さくなり、ＡＫ／ΔＰが増加する。しかし、薄板部材１の厚さＦｔが薄くなりすぎると、流路１１の流路面積が減少し、冷媒の流速減少によって熱通過率Ｋが低下して伝熱性能ＡＫが小さくなり、ＡＫ／ΔＰが低下する。 As shown in FIG. 5, AK / ΔP decreases when Fp / Ft becomes too small. Further, AK / ΔP decreases when Fp / Ft becomes too large. That is, Fp / Ft has an appropriate range in which AK / ΔP 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 / ΔP increases. However, if the thickness Ft of the thin plate member 1 becomes too thick, the air-side ventilation resistance ΔP increases and AK / ΔP decreases.
Further, for example, when the thickness Ft of the thin plate member 1 is reduced, the air-side ventilation resistance ΔP is reduced and AK / ΔP 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 / ΔP Decreases.
　以上のようなことから、本実施の形態１における熱交換器は、従来の熱交換器と比較してＡＫ／ΔＰを向上できる値（１００％）以上となるように、３≦Ｆｐ／Ｆｔ≦２１の関係を満たしている。
　これによって、熱交換器の熱交換性能を向上することができる。 From the above, 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.
　また、従来の熱交換器のように、複数の薄板部材（内部に流路が形成されない薄板部材）の間を通過する空気と、複数の伝熱管を流通する冷媒との熱交換を行うプレートフィン型の熱交換器の場合、伝熱管と薄板部材（内部に流路が形成されない薄板部材）との間に接触熱抵抗が存在する。また、薄板部材（内部に流路が形成されない薄板部材）には熱伝導の抵抗が存在する。
　一方、本実施の形態１における熱交換器は、薄板部材１の内部に冷媒が流通する流路１１が形成されている。このため、熱伝導の抵抗が小さくなる。また、従来の熱交換器のように、薄板部材（内部に流路が形成されない薄板部材）と伝熱管との間の接触熱抵抗は発生しない。よって、従来の熱交換器と比較して、熱交換器の熱交換性能を向上することができる。 Further, like conventional heat exchangers, 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 In the case of a type heat exchanger, contact thermal resistance exists between the heat transfer tube and the thin plate member (thin plate member in which no flow path is formed). Further, the thin plate member (thin plate member in which no flow path is formed) has a heat conduction resistance.
On the other hand, in the heat exchanger according to the first embodiment, 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. Further, unlike the conventional heat exchanger, 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.
　次に、上記熱交換器を空気調和機の冷媒回路に適用した場合を説明する。 Next, the case where the heat exchanger is applied to a refrigerant circuit of an air conditioner will be described.
　図６は、本発明の実施の形態１に係る空気調和機の冷媒回路図である。
　図６に示す冷媒回路は、圧縮機３３、凝縮器３４、膨張手段である絞り装置３５、蒸発器３６によって構成されている。また、空気調和機は、凝縮器３４及び蒸発器３６へ空気を送風する送風機３７と、送風機３７を駆動する送風機用モータ３８とを備えている。
　上記熱交換器を、凝縮器３４又は蒸発器３６、もしくは両方に用いることによって、エネルギー効率の高い空気調和機を実現することができる。
　ここで、エネルギー効率は、次式で構成されるものである。
　　暖房エネルギー効率＝室内熱交換器（凝縮器）能力／全入力
　　冷房エネルギー効率＝室内熱交換器（蒸発器）能力／全入力 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.
By using the heat exchanger for the condenser 34, the evaporator 36, or both, an air conditioner with high energy efficiency can be realized.
Here, energy efficiency is constituted by the following equation.
Heating energy efficiency = indoor heat exchanger (condenser) capacity / total input Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / total input
　蒸発器３６に上記熱交換器を用いる場合、熱交換器は、複数の薄板部材１の長手方向が重力方向となるように配置される。つまり、薄板部材１では、冷媒が重力方向の下側から上側に向かう上昇流となる。
　また、蒸発器３６として用いられる場合、一対のヘッダ（入口側ヘッダ２、出口側ヘッダ３）のうち、重力方向の下側に配置された入口側ヘッダ２に冷媒が流入する。入口側ヘッダ２に流入した冷媒は、複数の薄板部材１のそれぞれの流路１１を通過し、重力方向の上側に配置された出口側ヘッダ３に流入する。
　つまり、入口側ヘッダ２に流入した冷媒は、複数の薄板部材１に形成された複数の流路１１に分配され、複数の薄板部材１の下から上に向かって流動する。その後、出口側ヘッダ３から冷媒が流出する。 When using the said heat exchanger for the evaporator 36, a heat exchanger is arrange | positioned so that the longitudinal direction of the some thin plate member 1 may turn into a gravity direction. That is, in the thin plate member 1, the refrigerant becomes an upward flow from the lower side to the upper side in the gravity direction.
Moreover, when using as the evaporator 36, a refrigerant | coolant flows in into the inlet side header 2 arrange | positioned in the gravity direction lower side among a pair of headers (inlet side header 2, outlet side header 3). The refrigerant that has flowed into the inlet header 2 passes through the flow paths 11 of the plurality of thin plate members 1 and flows into the outlet header 3 disposed on the upper side in the gravity direction.
That is, 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.
　なお、入口側ヘッダ２は、本発明における「重力方向の下側に配置されたヘッダ」に相当する。また、出口側ヘッダ３は、本発明における「重力方向の上側に配置されたヘッダ」に相当する。 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.
　ここで、蒸発器３６を流通する冷媒は気液二相状態となる。この気液二相状態の冷媒は、流動様式がプラグ流又はスラグ流となる場合がある。蒸発器３６に上記熱交換器を用いる場合、冷媒が複数の薄板部材１の流路１１を、下から上に流動するので、プラグ流又はスラグ流の場合には、気泡の浮力によって冷媒が滞りなく上方に流動できる。
　これによって、熱交換器の熱交換性能を向上することができる。 Here, 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. When 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.
　また、蒸発器３６を流通する冷媒の蒸発温度が低くなると、複数の薄板部材１の表面で空気中の水蒸気が結露し、結露水（凝縮水）が発生する場合がある。蒸発器３６に上記熱交換器を用いる場合、熱交換器は、複数の薄板部材１の長手方向が重力方向の下側から上側に延びるように配置される。このため、結露水を複数の薄板部材１の間をスムーズに流下させて、結露水の排水性を向上することができる。また、蒸発器３６に着霜した霜を溶かすデフロスト運転時においても、熱交換器の下部に根氷が積層することを防ぐことができる。 Further, when the evaporation temperature of the refrigerant flowing through the evaporator 36 is lowered, water vapor in the air may condense on the surfaces of the plurality of thin plate members 1 to generate condensed water (condensed water). When using the said heat exchanger for the evaporator 36, a heat exchanger is arrange | positioned so that the longitudinal direction of the some thin plate member 1 may be extended upwards from the downward direction of a gravitational direction. For this reason, condensed water can be smoothly flowed down between the some thin plate members 1, and the drainage property of condensed water can be improved. Further, even during the defrost operation in which the frost that has formed on the evaporator 36 is melted, root ice can be prevented from being stacked on the lower portion of the heat exchanger.
　なお、複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たしていない場合であっても、上記効果が奏される。複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たす場合には、熱交換器の熱交換性能を更に向上することができる。 In addition, even if it is a case where the some thin plate member 1 does not satisfy | fill the relationship of 3 <= Fp / Ft <= 21, the said effect is show | played. When the plurality of thin plate members 1 satisfy the relationship of 3 ≦ Fp / Ft ≦ 21, the heat exchange performance of the heat exchanger can be further improved.
実施の形態２．
　以下、本実施の形態２の熱交換器について、上記実施の形態１との相違点を説明する。なお、上記実施の形態１と同一の構成には同一の符号を付する。 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 | symbol is attached | subjected to the structure same as the said Embodiment 1. FIG.
　図７は、本発明の実施の形態２に係る熱交換器を示す斜視図である。
　図８は、本発明の実施の形態２に係る熱交換器の薄板部材の配列を示す断面図である。
　図７、図８に示すように、本実施の形態２における熱交換器は、流体（空気）の流れ方向に２列設けている。また、流体（空気）の流れ方向において、上流側の複数の薄板部材１と下流側の複数の薄板部材１とが重ならないように配置している。即ち、複数の薄板部材１の配列を千鳥状にしている。 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.
As shown in FIGS. 7 and 8, 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.
　これによって、１列目の複数の薄板部材１の間で発達した空気の流れを、２列目の複数の薄板部材１の前縁における新規の境界層で更に発達させることができ、伝熱を促進することができる。 As a result, 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.
　なお、本実施の形態２では、熱交換器を２列設ける場合を説明したが、本発明はこれに限定されず、３列以上設けても良い。 In addition, in this Embodiment 2, although the case where two rows of heat exchangers were provided was demonstrated, this invention is not limited to this, You may provide three or more rows.
　また、複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たしていない場合であっても、上記効果が奏される。複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たす場合には、熱交換器の熱交換性能を更に向上することができる。 Further, even when the plurality of thin plate members 1 do not satisfy the relationship of 3 ≦ Fp / Ft ≦ 21, the above effect is exhibited. When the plurality of thin plate members 1 satisfy the relationship of 3 ≦ Fp / Ft ≦ 21, the heat exchange performance of the heat exchanger can be further improved.
実施の形態３．
　以下、本実施の形態３の熱交換器について、上記実施の形態１との相違点を説明する。なお、上記実施の形態１と同一の構成には同一の符号を付する。 Embodiment 3 FIG.
Hereinafter, the difference between the heat exchanger of the third embodiment and the first embodiment will be described. In addition, the same code | symbol is attached | subjected to the structure same as the said Embodiment 1. FIG.
　図９は、本発明の実施の形態３に係る熱交換器を示す斜視図である。
　図１０は、本発明の実施の形態３に係る熱交換器の入口側ヘッダを示す断面図である。
　図１１は、本発明の実施の形態３に係る熱交換器の内管を示す図である。
　図９～図１１に示すように、本実施の形態３における熱交換器の入口側ヘッダ２は、外管６と、外管６の内部に設けられた内管７とを備えている。 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.
As shown in FIGS. 9 to 11, 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.
　外管６には、複数の薄板部材１の端部が接続されている。外管６は、例えば断面が矩形形状の管であり、両端が閉塞されている。外管６の側面には、内管７に冷媒を流入する冷媒流入口４を構成する管が貫通している。
　内管７は、例えば円管である。内管７は、冷媒が流入する冷媒流入口４と、流入口から流入した冷媒を外管６内へ流出させる複数の流出口７１とが形成されている。内管７の長さは複数の薄板部材１の配置範囲と略同等である。複数の流出口７１は、内管７の下側（重力方向下部）にのみ形成されている。複数の流出口７１は、内管７の長さ方向に略均等に配置されている。 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.
　このような構成によって、熱交換器が蒸発器３６として用いられる場合、冷媒流入口４から内管７に液相状態の冷媒が流入する。内管７に流入した液相状態の冷媒は、複数の流出口７１のそれぞれから外管６内へ流出する。これによって、入口側ヘッダ２の内部では、液相状態の冷媒が攪拌され、液相状態の冷媒が、均等に複数の薄板部材１へ流入する。よって、複数の薄板部材１のうちの一部に、局所的な冷媒の乾きが生じにくくなり、熱交換器の熱交換性能を向上することができる。 With such a configuration, when the heat exchanger is used as the evaporator 36, 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. As a result, 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.
　なお、複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たしていない場合であっても、上記効果が奏される。複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たす場合には、熱交換器の熱交換性能を更に向上することができる。 In addition, even if it is a case where the some thin plate member 1 does not satisfy | fill the relationship of 3 <= Fp / Ft <= 21, the said effect is show | played. When the plurality of thin plate members 1 satisfy the relationship of 3 ≦ Fp / Ft ≦ 21, the heat exchange performance of the heat exchanger can be further improved.
実施の形態４．
　以下、本実施の形態４の熱交換器について、上記実施の形態１との相違点を説明する。なお、上記実施の形態１と同一の構成には同一の符号を付する。 Embodiment 4 FIG.
Hereinafter, the difference between the heat exchanger of the fourth embodiment and the first embodiment will be described. In addition, the same code | symbol is attached | subjected to the structure same as the said Embodiment 1. FIG.
　図１２は、本発明の実施の形態４に係る熱交換器を示す側面図である。
　図１２に示すように、本実施の形態４では、熱交換器が、重力方向に重ねて２つ設けられる。２つの熱交換器のそれぞれは、複数の薄板部材１の長手方向が重力方向となるように配置される。また、上側に配置された熱交換器の入口側ヘッダ２と下側に配置された熱交換器の入口側ヘッダ２とは、並列に接続され、上側に配置された熱交換器の出口側ヘッダ３と下側に配置された熱交換器の出口側ヘッダ３とは、並列に接続される。つまり、本実施の形態４では、熱交換器が、重力方向の上側と下側とに並設され、蒸発器３６として用いられる際に、それぞれの熱交換器において、重力方向の下側に配置された入口側ヘッダ２に冷媒が流入し、重力方向の上側に配置された出口側ヘッダ３から冷媒が流出する。また、複数の薄板部材１の流路１１は、０．０５～０．２ｍｍの流体相当直径（等価直径）である。 FIG. 12 is a side view showing a heat exchanger according to Embodiment 4 of the present invention.
As shown in FIG. 12, in the fourth embodiment, 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. Moreover, 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, and 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. That is, in the fourth embodiment, 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.
　通常、流路に流入する冷媒流量が小さくなると、その流路での熱伝達率は小さくなる。しかし、熱交換器が蒸発器３６として用いられる場合、つまり、薄板部材１を気液二相状態の冷媒が重量方向の下側から上側に向かって上昇する方向に流れる場合には、冷媒が複数の流路１１に分配されることに起因して、各流路１１に流入する冷媒流量が小さくなっても、各流路１１での熱伝達率は小さくなり難い若しくは大きくなる。これは、冷媒流量が低下すると、流路１１の径が１ｍｍ以下であることに起因して、液相状態の冷媒の滞留が生じ、冷媒の沸騰が起きやすくなるためである。なお、流路１１の断面が、図４に示されるような矩形状の断面である場合には、その現象が著しく顕著となる。 Usually, when the flow rate of the refrigerant flowing into the flow path becomes small, the heat transfer coefficient in the flow path becomes small. However, when 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. This is because when the flow rate of the refrigerant decreases, the diameter of the flow path 11 is 1 mm or less, so that the liquid phase state of the refrigerant stays and the boiling of the refrigerant easily occurs. In addition, when the cross section of the flow path 11 is a rectangular cross section as shown in FIG. 4, the phenomenon becomes remarkably remarkable.
　つまり、本実施の形態４の熱交換器では、薄板部材１が、各流路１１の断面積の合計と等しい断面積の円形状の流路が内側に形成された円管である場合と比較して、各薄板部材１に複数の流路１１が形成される分、一つの流路１１当りの冷媒流量が小さくなるとともに、その冷媒流量の低下に起因して各流路１１での熱伝達率が円管での熱伝達率と等しくなるとの現象が生じることによって、各流路１１における冷媒の相変化が促進されることとなる。
　また、各薄板部材１に形成される流路１１が１つである場合であっても、薄板部材１が薄いことに起因して、薄板部材１の枚数を円管の数と比較して多くする、つまり、流路１１の総数を円管の数と比較して多くすることが可能であるため、一つの流路１１当りの冷媒流量が小さくなるとともに、その冷媒流量の低下に起因して各流路１１での熱伝達率が円管での熱伝達率と等しくなるとの現象が生じることによって、各流路１１における冷媒の相変化が促進されることとなる。 That is, in the heat exchanger according to the fourth embodiment, 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. Thus, 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. When the phenomenon that the rate becomes equal to the heat transfer coefficient in the circular pipe occurs, the phase change of the refrigerant in each flow path 11 is promoted.
Further, even when the number of the flow paths 11 formed in each thin plate member 1 is one, 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.
　そのため、各流路１１の出口における冷媒の乾き度を１程度以下にして、冷凍サイクルの性能を維持するために、複数の薄板部材１の長さを、従来の熱交換器と比較して小さくする必要がある。
　このようなことから本実施の形態４における熱交換器は、重力方向に重ねて２つ設けることで、複数の薄板部材１の長さを短くして冷凍サイクルの性能を維持しつつ十分な熱交換容積を確保することとしている。例えば、空気調和機の室外機に熱交換器を搭載する場合、室外機のユニット高さが従来と同等であっても十分な熱交換容積を確保することができる。 Therefore, in order to maintain the performance of the refrigeration cycle by setting the dryness of the refrigerant at the outlet of each flow path 11 to about 1 or less, the length of the plurality of thin plate members 1 is made smaller than that of the conventional heat exchanger. There is a need to.
For this reason, 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.
　なお、複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たしていない場合であっても、上記効果が奏される。複数の薄板部材１が、３≦Ｆｐ／Ｆｔ≦２１の関係を満たす場合には、熱交換器の熱交換性能を更に向上することができる。 In addition, even if it is a case where the some thin plate member 1 does not satisfy | fill the relationship of 3 <= Fp / Ft <= 21, the said effect is show | played. When the plurality of thin plate members 1 satisfy the relationship of 3 ≦ Fp / Ft ≦ 21, the heat exchange performance of the heat exchanger can be further improved.
　以上、実施の形態１～４の熱交換器、及びそれを用いた空気調和機について説明したが、実施の形態１～４の熱交換器、及びそれを用いた空気調和機の構成を任意に組み合わせても良い。このような構成においても、熱交換器の熱交換効率を向上することができる。 While the heat exchangers of Embodiments 1 to 4 and the air conditioner using the heat exchanger have been described above, the configurations of the heat exchangers of Embodiments 1 to 4 and the air conditioner using the heat exchanger can be arbitrarily set. You may combine. Even in such a configuration, the heat exchange efficiency of the heat exchanger can be improved.
　また、上述の実施の形態１～４で述べた熱交換器、及びそれを用いた空気調和機については、Ｒ４１０Ａ、Ｒ３２、ＨＦＯ１２３４ｙｆ等の何れの冷媒においても、その効果を達成することができる。 Further, with respect to the heat exchanger described in the first to fourth embodiments and the air conditioner using the heat exchanger, the effect can be achieved in any refrigerant such as R410A, R32, HFO1234yf, and the like.
　また、作動流体として、空気と冷媒の例を示したが、他の気体、液体、気液混合流体を用いても、同様の効果を奏する。 Moreover, although the example of air and a refrigerant | coolant was shown as a working fluid, even if it uses other gas, liquid, and gas-liquid mixed fluid, there exists the same effect.
　また、上述の実施の形態１～４で述べた熱交換器を、空気調和機の室内機及び室外機の何れで用いた場合においても同様な効果を奏することができる。 In addition, 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.
　また、上述の実施の形態１～４で述べた熱交換器、及びそれを用いた空気調和機については、鉱油系、アルキルベンゼン油系、エステル油系、エーテル油系、フッ素油系など、冷媒と油が溶ける又は溶けないにかかわらず、どんな冷凍機油についても、その効果を達成することができる。 In addition, 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. The effect can be achieved with any refrigeration oil, whether the oil is soluble or not.
　本発明の活用例としては、上述した空気調和機に限らず、熱交換性能を向上し、省エネルギー性能を向上することが必要なヒートポンプ装置に使用することができる。 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.
　１　薄板部材、２　入口側ヘッダ、３　出口側ヘッダ、４　冷媒流入口、５　冷媒出口、６　外管、７　内管、１１　流路、３３　圧縮機、３４　凝縮器、３５　絞り装置、３６　蒸発器、３７　送風機、３８　送風機用モータ、７１　流出口。 1 thin plate member, 2 inlet header, 3 outlet header, 4 refrigerant inlet, 5 refrigerant outlet, 6 outer pipe, 7 inner pipe, 11 flow path, 33 compressor, 34 condenser, 35 throttling device, 36 evaporator 37 blower, 38 blower motor, 71 outlet.

Claims (11)

  1. 　間隔を空けて配置され、その間を流体が流れ、内部に前記流体と熱交換する媒体が流れる流路が形成された複数の薄板部材と、
    　前記複数の薄板部材の両端部をそれぞれ接続する一対のヘッダと、を備え、
    　前記複数の薄板部材は、
    　隣り合う前記薄板部材の間隔をＦｐ、前記薄板部材の厚さをＦｔとした場合、
    　３≦Ｆｐ／Ｆｔ≦２１
    　の関係を満たす、熱交換器。     A plurality of thin plate members that are arranged at intervals, in which a fluid flows therethrough and in which a flow path through which a medium that exchanges heat with the fluid flows is formed;
    A pair of headers respectively connecting both ends of the plurality of thin plate members,
    The plurality of thin plate members are:
    When the interval between the adjacent thin plate members is Fp, and the thickness of the thin plate member is Ft,
    3 ≦ Fp / Ft ≦ 21
    A heat exchanger that satisfies the relationship of
  2. 　隣り合う前記薄板部材の間には、前記流体と前記薄板部材との熱交換を促進する部材が設けられていない、請求項１に記載の熱交換器。 The heat exchanger according to claim 1, wherein a member that promotes heat exchange between the fluid and the thin plate member is not provided between the adjacent thin plate members.
  3. 　圧縮機、凝縮器、膨張手段、及び蒸発器を配管で接続し冷媒を循環させる冷媒回路を備え、
    　前記凝縮器及び前記蒸発器の少なくとも一方に、請求項１又は２に記載の熱交換器を用いた、ヒートポンプ装置。     A compressor, a condenser, an expansion means, and a refrigerant circuit that connects the evaporator with piping and circulates the refrigerant;
    The heat pump apparatus which used the heat exchanger of Claim 1 or 2 for at least one of the said condenser and the said evaporator.
  4. 　圧縮機、凝縮器、膨張手段、及び蒸発器を配管で接続し冷媒を循環させる冷媒回路を備え、
    　前記蒸発器に、請求項１又は２に記載の熱交換器を用い、
    　前記熱交換器は、
    　前記一対のヘッダのうち、重力方向の下側に配置された前記ヘッダに前記冷媒が流入し、重力方向の下側に配置された前記ヘッダに流入した前記冷媒が、前記複数の薄板部材に形成された前記流路を重力方向の下側から上側に向かう方向に流れて重力方向の上側に配置された前記ヘッダに流入し、重力方向の上側に配置された前記ヘッダから前記冷媒が流出するように配置及び接続された、ヒートポンプ装置。     A compressor, a condenser, an expansion means, and a refrigerant circuit that connects the evaporator with piping and circulates the refrigerant;
    The heat exchanger according to claim 1 or 2 is used for the evaporator,
    The heat exchanger is
    Of the pair of headers, the refrigerant flows into the header disposed below the gravity direction, and the refrigerant flowing into the header disposed below the gravity direction forms the plurality of thin plate members. So that the refrigerant flows in the direction from the lower side to the upper side in the direction of gravity and flows into the header arranged on the upper side in the direction of gravity, and the refrigerant flows out of the header arranged on the upper side in the direction of gravity. A heat pump device arranged and connected to the heat pump device.
  5. 　前記熱交換器を、重力方向の上側と下側とに並設し、
    　並設された前記熱交換器を、並列に接続した、請求項４に記載のヒートポンプ装置。     The heat exchangers are arranged side by side on the upper side and the lower side in the direction of gravity,
    The heat pump device according to claim 4, wherein the heat exchangers arranged in parallel are connected in parallel.
  6. 　間隔を空けて配置され、その間を流体が流れ、内部に前記流体と熱交換する媒体が流れる流路が形成された複数の薄板部材と、
    　前記複数の薄板部材の両端部をそれぞれ接続する一対のヘッダと、を備えた熱交換器と、
    　圧縮機、凝縮器、膨張手段、及び蒸発器を配管で接続し冷媒を循環させる冷媒回路と、を備え、
    　前記蒸発器に、前記熱交換器を用い、
    　前記熱交換器は、
    　前記一対のヘッダのうち、重力方向の下側に配置された前記ヘッダに前記冷媒が流入し、重力方向の下側に配置された前記ヘッダに流入した前記冷媒が、前記複数の薄板部材に形成された前記流路を重力方向の下側から上側に向かう方向に流れて重力方向の上側に配置された前記ヘッダに流入し、重力方向の上側に配置された前記ヘッダから前記冷媒が流出するように配置及び接続され、
    　前記熱交換器を、重力方向の上側と下側とに並設し、
    　並設された前記熱交換器を、並列に接続した、ヒートポンプ装置。     A plurality of thin plate members that are arranged at intervals, in which a fluid flows therethrough and in which a flow path through which a medium that exchanges heat with the fluid flows is formed;
    A heat exchanger comprising a pair of headers respectively connecting both end portions of the plurality of thin plate members;
    A refrigerant circuit that connects the compressor, the condenser, the expansion means, and the evaporator with a pipe to circulate the refrigerant, and
    Using the heat exchanger in the evaporator,
    The heat exchanger is
    Of the pair of headers, the refrigerant flows into the header disposed below the gravity direction, and the refrigerant flowing into the header disposed below the gravity direction forms the plurality of thin plate members. So that the refrigerant flows in the direction from the lower side to the upper side in the direction of gravity and flows into the header arranged on the upper side in the direction of gravity, and the refrigerant flows out of the header arranged on the upper side in the direction of gravity. Arranged and connected to
    The heat exchangers are arranged side by side on the upper and lower sides in the direction of gravity,
    The heat pump apparatus which connected the said heat exchanger arranged in parallel in parallel.
  7. 　隣り合う前記薄板部材の間には、前記流体と前記薄板部材との熱交換を促進する部材が設けられていない、請求項６に記載のヒートポンプ装置。 The heat pump device according to claim 6, wherein a member that promotes heat exchange between the fluid and the thin plate member is not provided between the adjacent thin plate members.
  8. 　前記薄板部材に形成された前記流路は、断面形状が矩形状である、請求項５～７の何れか一項に記載のヒートポンプ装置。 The heat pump device according to any one of claims 5 to 7, wherein the flow path formed in the thin plate member has a rectangular cross-sectional shape.
  9. 　前記一対のヘッダのうち、重力方向の下側に配置された前記ヘッダは、
    　前記複数の薄板部材の端部が接続された外管と、
    　前記外管の内部に設けられた内管と、
    　を備え、
    　前記内管は、
    　前記冷媒が流入する流入口と、
    　前記流入口から流入した前記冷媒を前記外管へ流出させる複数の流出口と、が形成された、請求項３～８の何れか一項に記載のヒートポンプ装置。     Of the pair of headers, the header arranged below the gravitational direction is
    An outer tube to which ends of the plurality of thin plate members are connected;
    An inner pipe provided inside the outer pipe;
    With
    The inner tube is
    An inlet into which the refrigerant flows;
    The heat pump device according to any one of claims 3 to 8, wherein a plurality of outlets for allowing the refrigerant flowing in from the inlet to flow out to the outer pipe are formed.
  10. 　前記複数の流出口は、前記内管の重力方向の下部にのみ形成された、請求項９に記載のヒートポンプ装置。 The heat pump device according to claim 9, wherein the plurality of outlets are formed only at a lower portion of the inner pipe in a gravity direction.
  11. 　前記熱交換器を、前記流体の流れ方向に複数列設け、
    　前記流体の流れ方向において、上流側の前記複数の薄板部材と下流側の前記複数の薄板部材とが重ならないように配置した、請求項３～１０の何れか一項に記載のヒートポンプ装置。     A plurality of the heat exchangers are provided in the fluid flow direction,
    11. The heat pump device according to claim 3, wherein the plurality of thin plate members on the upstream side and the plurality of thin plate members on the downstream side are arranged so as not to overlap each other in the fluid flow direction.
PCT/JP2014/068203 2013-07-08 2014-07-08 Heat exchanger, and heat pump device WO2015005352A1 (en)

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JP2015526356A JPWO2015005352A1 (en) 2013-07-08 2014-07-08 Heat pump equipment
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