EP3021064B1 - Dispositif de pompe à chaleur - Google Patents

Dispositif de pompe à chaleur Download PDF

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Publication number
EP3021064B1
EP3021064B1 EP14823375.2A EP14823375A EP3021064B1 EP 3021064 B1 EP3021064 B1 EP 3021064B1 EP 14823375 A EP14823375 A EP 14823375A EP 3021064 B1 EP3021064 B1 EP 3021064B1
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EP
European Patent Office
Prior art keywords
thin
plate members
heat
heat exchanger
refrigerant
Prior art date
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EP14823375.2A
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German (de)
English (en)
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EP3021064A4 (fr
EP3021064A1 (fr
Inventor
Akira Ishibashi
Takuya Matsuda
Takashi Okazaki
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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 pump apparatus including a heat exchanger.
  • a heat pump according to the preamble of claim 1 is known from EP 0 838 641 A2 .
  • a plate-fin heat exchanger a conventional heat exchanger has, for example, a pair of headers, a plurality of multi-channel heat-exchanger tubes, and fins.
  • the headers are spaced apart from each other.
  • One of the headers connects ends of one side of the multi-channel heat-exchanger tubes, and the other of the headers connects ends of the other side of the multi-channel heat-exchanger tubes.
  • the fins are thin-plate members for promoting heat exchange coupled between the plurality of multi-channel heat-exchanger tubes.
  • Another conventional heat exchanger has a pair of headers and a plurality of fins.
  • the headers are spaced apart from each other.
  • One of the headers connects ends of one side of the fins, which are thin-plate members, and the other of the headers connects ends of the other side of the thin-plate members.
  • Flow channels are formed in each of the plurality of thin-plate members (see Patent Literature 1, for example).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication (Translation of PCT Application) No. 2008-528943 (Abstract)
  • the draft resistance applied to air passing through each space between adjacent ones of the plurality of thin-plate members increases, thus lowering the heat exchangeability.
  • the draft resistance applied to air passing through each space between adjacent ones of the thin-plate members is reduced. Instead, the channel area is reduced, thus lowering the heat exchangeability.
  • the present invention provides a heat pump apparatus that exhibits improved heat exchangeability.
  • a heat pump apparatus includes the features of claim 1.
  • heat exchangeability in the heat exchanger that includes the plurality of thin-plate members spaced apart from one another, the fluid flowing through the space, the flow channel formed in each of the plurality of thin-plate members, the medium flowing through the flow channel, the medium exchanging heat with the fluid, and the pair of headers each connecting the ends of a corresponding one of the two sides of the plurality of thin-plate members, heat exchangeability can be improved.
  • the heat pump apparatus that includes the heat exchanger including the plurality of thin-plate members spaced apart from one another, fluid flowing through the space, the flow channel formed in each of the plurality of thin-plate members, the medium flowing through the flow channel, the medium exchanging heat with the fluid, and the pair of headers each connecting the ends of a corresponding one of the two sides of the plurality of thin-plate members, and the refrigerant circuit connecting the compressor, the condenser, the expansion unit, and the evaporator by the pipes and circulating refrigerant, heat exchangeability can be improved.
  • Fig. 1 is a perspective view of a heat exchanger according to Embodiment 1 of the present invention.
  • Fig. 2 is a side view of the heat exchanger according to Embodiment 1 of the present invention.
  • Fig. 3 is a sectional diagram taken along line A-A illustrated in Fig. 2 .
  • Fig. 4 is an enlarged view of part B illustrated in Fig. 3 .
  • the heat exchanger includes a plurality of fins, that is, thin-plate members 1, and a pair of headers (an inlet-side header 2 and an outlet-side header 3).
  • the plurality of thin-plate members 1 each have, for example, a thickness of about 2 mm or less and are made of aluminum.
  • the plurality of thin-plate members 1 are spaced apart from one another. Fluid (for example, air) flows through the spaces between the thin-plate members 1.
  • the plurality of thin-plate members 1 each internally have one or a plurality of flow channels 11 in which a medium (for example, refrigerant) flows. A portion between two ends of one thin-plate member 1 and a portion between two ends of another thin-plate member 1 adjacent thereto are not connected to each other with any thin-plate member internally having no flow channels. That is, a member that promotes heat exchange between the fluid and the thin-plate members 1 is not provided between adjacent ones of the thin-plate members 1.
  • the pair of headers each connects ends of a corresponding one of the two sides of the plurality of thin-plate members 1.
  • the refrigerant flows into the inlet-side header 2 from a refrigerant inlet 4 of the inlet-side header 2.
  • the refrigerant having flowed into the inlet-side header 2 passes through the flow channels 11 of the plurality of thin-plate members 1 and flows into the outlet-side header 3.
  • the refrigerant is discharged from a refrigerant outlet 5 of the outlet-side header 3.
  • the direction of the flow of the refrigerant is not limited to the above and may be opposite to the above direction.
  • the heat exchanger causes the air passing through the spaces between the plurality of thin-plate members 1 and the refrigerant flowing in the flow channels 11 provided in the plurality of thin-plate members 1 to exchange heat with each other.
  • the plurality of thin-plate members 1 satisfy a relationship of 3 ⁇ Fp/Ft ⁇ 21, where Fp denotes the intervals of the thin-plate members 1 that are adjacent to one another (i.e., the fin pitch), and Ft denotes the thickness of each of the thin-plate members 1.
  • Fig. 5 is a graph illustrating a performance characteristic of the heat exchanger according to Embodiment 1 of the present invention.
  • Fig. 5 illustrates a relationship between a ratio (AK/ ⁇ P) of heat-transfer performance AK [W/K] to air-side draft resistance ⁇ P of the heat exchanger and a ratio (Fp/Ft) of the pitch Fp of the thin-plate members 1 to the thickness Ft of each thin-plate member 1.
  • the AK value is the result of multiplying an overall heat-transfer coefficient K and a heat-transfer area A of the heat exchanger and represents the heat-transfer characteristic of the heat exchanger.
  • the conventional heat exchanger used as the reference is a plate-fin heat exchanger that causes air passing through spaces between a plurality of thin-plate members (thin-plate members each internally having no flow channels) and refrigerant flowing in a plurality of heat-exchanger tubes to exchange heat with each other.
  • the heat-exchanger tubes of the conventional heat exchanger are provided in two rows that are arranged side by side in the direction of the airflow and in a plurality of steps that are stacked in a direction orthogonal to the airflow.
  • the heat-exchanger tubes are each a circular tube of ⁇ 7.94 mm
  • the pitch of the thin-plate members is 1.6 mm
  • the step pitch Dp of the heat-exchanger tubes is 20.4 mm
  • the row pitch Lp of the heat-exchanger tubes is 17.7 mm.
  • the thickness Ft of the thin-plate member 1 increases, the channel area of the flow channels 11 increases. Accordingly, the flow speed of the refrigerant increases, the overall heat-transfer coefficient K increases, the heat-transfer performance AK becomes high, and AK/ ⁇ P increases.
  • the thickness Ft of the thin-plate member 1 becomes too large, the air-side draft resistance ⁇ P becomes high. Accordingly, AK/ ⁇ P is reduced.
  • the thickness Ft of the thin-plate member 1 becomes small, the air-side draft resistance ⁇ P becomes low. Accordingly, AK/ ⁇ P increases. However, if the thickness Ft of the thin-plate member 1 becomes too small, the channel area of the flow channels 11 is reduced. Furthermore, with a reduction in the flow speed of the refrigerant, the overall heat-transfer coefficient K is reduced, and the heat-transfer performance AK becomes low. Consequently, AK/ ⁇ P is lowered.
  • the heat exchanger according to Embodiment 1 satisfies the relationship of 3 ⁇ Fp/Ft ⁇ 21 so that AK/ ⁇ P becomes higher than or equal to that (100%) of the conventional heat exchanger.
  • the heat exchanger can exhibit improved heat exchangeability.
  • a thermal contact resistance is generated between each of the heat-exchanger tubes and a corresponding one of the thin-plate members (thin-plate members internally having no flow channels). Furthermore, a thermal conductivity resistance is generated in each of the thin-plate members (thin-plate members each internally having no flow channels).
  • the heat exchanger according to Embodiment 1 has the flow channels 11 in which the refrigerant flows provided inside each of the thin-plate members 1. Therefore, the thermal conductivity resistance is low. Moreover, the thermal contact resistance generated between each of the thin-plate members (thin-plate members each internally having no flow channels) and a corresponding one of the heat-exchanger tubes in the conventional heat exchanger is not generated. Hence, the heat exchangeability of the heat exchanger can be made higher than that of the conventional heat exchanger.
  • Fig. 6 is a refrigerant circuit diagram of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the refrigerant circuit illustrated in Fig. 6 includes a compressor 33, a condenser 34, an expansion device 35 as an expansion unit, and an evaporator 36. Furthermore, the air-conditioning apparatus includes fans 37 that each send air to a corresponding one of the condenser 34 and the evaporator 36, and fan motors 38 that each drive a corresponding one of fans 37.
  • Heating-energy efficiency capacity of indoor heat exchanger condenser / total input
  • Cooling-energy efficiency capacity of indoor heat exchanger evaporator / total input
  • the heat exchanger is oriented so that the longitudinal direction of the plurality of thin-plate members 1 corresponds to the direction of gravity. That is, in each of the thin-plate members 1, the refrigerant makes an ascending flow that goes from the lower side toward the upper side in the direction of gravity.
  • the refrigerant flows into the inlet-side header 2, which is one of the pair of headers (the inlet-side header 2 and the outlet-side header 3), provided on the lower side in the direction of gravity.
  • the refrigerant having flowed into the inlet-side header 2 passes through all of the flow channels 11 provided in the plurality of thin-plate members 1, and flows into the outlet-side header 3 provided on the upper side in the direction of gravity.
  • the refrigerant having flowed into the inlet-side header 2 is distributed to the plurality of flow channels 11 provided in each of the plurality of thin-plate members 1, and flows from the bottom toward the top of each of the plurality of thin-plate members 1. Subsequently, the refrigerant is discharged from the outlet-side header 3.
  • inlet-side header 2 corresponds to “the header provided on the lower side in the direction of gravity” according to the present invention
  • outlet-side header 3 corresponds to "the header provided on the upper side in the direction of gravity” according to the present invention.
  • the refrigerant flowing in the evaporator 36 is in a two-phase gas-liquid state.
  • the two-phase gas-liquid refrigerant occasionally flows in a plug-flow or slug-flow pattern. If the above heat exchanger is used as the evaporator 36, the refrigerant flows through the flow channels 11 of the plurality of thin-plate members 1 from the bottom to the top. Thus, if the refrigerant flows in a plug-flow or slug-flow pattern, the refrigerant can smoothly flow upward with the buoyancy of bubbles.
  • the heat exchanger can exhibit improved heat exchangeability.
  • the vapor in the air may be condensed into dew drops (condensed water) on the surfaces of the plurality of thin-plate members 1.
  • the heat exchanger is oriented so that the longitudinal direction of the plurality of thin-plate members 1 corresponds to the direction of gravity from the lower side toward the upper side.
  • dew drops smoothly run down between adjacent ones of the plurality of thin-plate members 1.
  • improved dew drainability can be provided.
  • the generation of solid ice that may build up in a lower part of the heat exchanger can be prevented.
  • the above advantageous effects are produced even if the plurality of thin-plate members 1 do not satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21. If the plurality of thin-plate members 1 satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21, the heat exchanger can exhibit further improved heat exchangeability.
  • Embodiment 2 Heat exchangers according to Embodiment 2 will be described below, focusing on differences from Embodiment 1. Components that are the same as those of Embodiment 1 are denoted by corresponding ones of the reference signs.
  • Fig. 7 is a perspective view of the heat exchangers according to Embodiment 2 of the present invention.
  • Fig. 8 is a sectional diagram illustrating an arrangement of thin-plate members included in the heat exchangers according to Embodiment 2 of the present invention.
  • Embodiment 2 two heat exchangers are provided side by side in the direction of the flow of the fluid (air). Furthermore, in the direction of the flow of the fluid (air), the plurality of thin-plate members 1 on the upstream side do not overlap the plurality of thin-plate members 1 on the downstream side. That is, the plurality of thin-plate members 1 are arranged in a staggered manner.
  • the flow of the air developed between adjacent ones of the plurality of thin-plate members 1 included in the first heat exchanger can further be developed at a new boundary layer formed at the front edges of the plurality of thin-plate members 1 included in the second heat exchanger. Consequently, heat transfer can be promoted.
  • Embodiment 2 concerns a case where two heat exchangers are provided, the present invention is not limited to such a case. Three or more heat exchangers may be provided.
  • the above advantageous effects are produced even if the plurality of thin-plate members 1 do not satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21. If the plurality of thin-plate members 1 satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21, the heat exchanger can exhibit further improved heat exchangeability.
  • Embodiment 3 A heat exchanger according to Embodiment 3 will be described below, focusing on differences from Embodiment 1. Components that are the same as those of Embodiment 1 are denoted by corresponding ones of the reference signs.
  • Fig. 9 is a perspective view of the heat exchanger according to Embodiment 3 of the present invention.
  • Fig. 10 is a sectional diagram of an inlet-side header included in the heat exchanger according to Embodiment 3 of the present invention.
  • Fig. 11 is a diagram of an inner pipe included in the heat exchanger according to Embodiment 3 of the present invention.
  • the inlet-side header 2 of the heat exchanger according to Embodiment 3 includes an outer pipe 6 and an inner pipe 7 provided inside the outer pipe 6.
  • each of the plurality of thin-plate members 1 is connected to the outer pipe 6.
  • the outer pipe 6 is, for example, a pipe having a rectangular cross-sectional shape, with the two ends thereof closed.
  • a tube that forms the refrigerant inlet 4 extends through a sidewall of the outer pipe 6. The refrigerant is taken into the inner pipe 7 from the refrigerant inlet 4.
  • the heat exchanger having such a configuration is used as the evaporator 36, refrigerant in a liquid phase flows into the inner pipe 7 from the refrigerant inlet 4.
  • the liquid-phase refrigerant having flowed into the inner pipe 7 is discharged into the outer pipe 6 from each of the plurality of outlets 71.
  • the liquid-phase refrigerant is stirred and is evenly distributed to the plurality of thin-plate members 1.
  • the heat exchanger can exhibit improved heat exchangeability.
  • the above advantageous effects are produced even if the plurality of thin-plate members 1 do not satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21. If the plurality of thin-plate members 1 satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21, the heat exchanger can exhibit further improved heat exchangeability.
  • Heat exchangers according to Embodiment 4 will be described below, focusing on differences from Embodiment 1. Components that are the same as those of Embodiment 1 are denoted by corresponding ones of the reference signs.
  • Fig. 12 is a side view of the heat exchangers according to Embodiment 4 of the present invention.
  • Embodiment 4 two heat exchangers are mounted one on top of the other in the direction of gravity.
  • Each of the two heat exchangers is oriented so that the longitudinal direction of the plurality of thin-plate members 1 corresponds to the direction of gravity.
  • the inlet-side header 2 of the heat exchanger on the upper side and the inlet-side header 2 of the heat exchanger on the lower side are connected in parallel
  • the outlet-side header 3 of the heat exchanger on the upper side and the outlet-side header 3 of the heat exchanger on the lower side are connected in parallel. That is, in Embodiment 4, the heat exchangers are arranged in parallel on the upper side and the lower side in the direction of gravity.
  • the refrigerant flows, in each of the heat exchangers, into the inlet-side header 2 provided on the lower side in the direction of gravity and is discharged from the outlet-side header 3 provided on the upper side in the direction of gravity.
  • the flow channels 11 provided in each of the plurality of thin-plate members 1 each have a size corresponding to the diameter of the fluid (an equivalent diameter) of 0.05 to 0.2 mm.
  • the heat-transfer coefficient of that flow channel is reduced.
  • the heat exchanger is used as the evaporator 36, that is, if a two-phase gas-liquid refrigerant flows through the thin-plate member 1 upward from the lower side toward the upper side in the direction of gravity, the heat-transfer coefficient of each of the flow channels 11 is less likely to be reduced or is increased even if the flow rate of the refrigerant flowing into the flow channels 11 is reduced, because the refrigerant is distributed among the plurality of flow channels 11. The reason is as follows.
  • each thin-plate member 1 is a circular pipe internally having a circular flow channel whose cross-sectional area is equal to the sum of the cross-sectional areas of the flow channels 11, the flow rate of the refrigerant per flow channel 11 is small because the thin-plate members 1 each have a plurality of flow channels 11.
  • the reduction in the flow rate of the refrigerant causes a phenomenon that the heat-transfer coefficient of each of the flow channels 11 becomes equal to the heat-transfer coefficient of the circular pipe. Consequently, the change in the phase of the refrigerant in each of the flow channels 11 is promoted.
  • the number of thin-plate members 1 can be made larger than the number of circular pipes, that is, the total number of flow channels 11 can be made larger than the number of circular pipes, because each of the thin-plate members 1 is thin.
  • the flow rate of the refrigerant per flow channel 11 is reduced, and the reduction in the flow rate of the refrigerant causes the phenomenon that the heat-transfer coefficient of each of the flow channels 11 becomes equal to the heat-transfer coefficient of the circular pipe. Consequently, the change in the phase of the refrigerant in each of the flow channels 11 is promoted.
  • the length of each of the plurality of thin-plate members 1 needs to be made shorter than that of the conventional heat exchanger.
  • Embodiment 4 two heat exchangers are mounted one on top of the other in the direction of gravity, and the length of each of the plurality of thin-plate members 1 is reduced.
  • a satisfactory heat-exchange capacity is provided while the performance of the refrigeration cycle is maintained.
  • the heat exchanger is incorporated into an outdoor unit of an air-conditioning apparatus, a satisfactory heat-exchange capacity can be provided even if the outdoor unit has substantially the same unit height as the conventional outdoor unit.
  • the above advantageous effects are produced even if the plurality of thin-plate members 1 do not satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21. If the plurality of thin-plate members 1 satisfy the relationship of 3 ⁇ Fp/Ft ⁇ 21, the heat exchanger can exhibit further improved heat exchangeability.
  • the heat exchangers according to Embodiments 1 to 4 and air-conditioning apparatuses including the same have been described, the configurations of the heat exchangers according to Embodiments 1 to 4 and the air-conditioning apparatuses including the same may be combined arbitrarily. In such a case, the heat exchanger can also exhibit improved effectiveness.
  • thermoelectric heat exchanger according to any of Embodiments 1 to 4 and the air-conditioning apparatus including the same can produce the above advantageous effects with any refrigerant such as R410A, R32, and HFO1234yf.
  • the above description concerns an exemplary case where the working fluids are air and refrigerant, the above advantageous effects can be produced with any of other fluids such as gas, liquid, and gas-liquid mixed fluid.
  • the heat exchanger according to any of Embodiments 1 to 4 and the air-conditioning apparatus including the same can produce the above advantageous effects with any refrigerating machine oil based any oil such as mineral oil, alkylbenzene oil, ester oil, ethereal oil, and fluorine oil, regardless of whether or not the refrigerant and the oil are soluble in each other.
  • any refrigerating machine oil based any oil such as mineral oil, alkylbenzene oil, ester oil, ethereal oil, and fluorine oil, regardless of whether or not the refrigerant and the oil are soluble in each other.
  • the present invention is applicable not only to the above air-conditioning apparatus but also to a heat pump apparatus in which energy-saving performance needs to be improved with improved heat exchangeability.

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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)

Claims (5)

  1. Appareil de pompe à chaleur comprenant :
    un échangeur de chaleur comprenant
    une pluralité d'éléments de plaque mince (1) espacés les uns des autres, un fluide s'écoulant à travers l'espace, un canal d'écoulement formé dans chacun de la pluralité d'éléments de plaque mince (1), un milieu s'écoulant à travers le canal d'écoulement, le milieu échangeant de la chaleur avec le fluide, et
    une paire de collecteurs (2, 3) reliant chacun les extrémités d'un côté correspondant parmi les deux côtés de la pluralité d'éléments de plaque mince (1) ; et
    un circuit de fluide frigorigène reliant un compresseur, un condenseur, une unité de détente, et un évaporateur par des tuyaux et faisant circuler un fluide frigorigène,
    où l'évaporateur est l'échangeur de chaleur,
    où l'échangeur de chaleur est agencé et relié de sorte que
    le fluide frigorigène s'écoule dans l'un (2) de la paire de collecteurs (2, 3) prévu d'un côté inférieur dans une direction de la pesanteur, s'écoule à travers le canal d'écoulement formé dans chacun de la pluralité d'éléments de plaque mince (1) dans une direction allant du côté inférieur vers un côté supérieur dans la direction de la pesanteur, s'écoule dans un autre (3) de la paire de collecteurs (2, 3) prévu du côté supérieur dans la direction de la pesanteur, et est évacué par l'autre (3) de la paire de collecteurs (2, 3) du côté supérieur dans la direction de la pesanteur,
    où l'échangeur de chaleur est l'un des échangeurs de chaleur agencés en parallèle du côté supérieur et du côté inférieur dans la direction de la pesanteur,
    où les échangeurs de chaleur agencés en parallèle sont reliés en parallèle, caractérisé en ce que
    l'un de la paire de collecteurs (2, 3) prévu du côté inférieur dans la direction de la pesanteur comprend
    un tuyau extérieur (6) reliant les extrémités d'un côté de la pluralité d'éléments de plaque mince (1) ; et
    un tuyau intérieur (7) prévu à l'intérieur du tuyau extérieur (6),
    où le tuyau intérieur (7) comporte une entrée (4) et une pluralité de sorties (71), le fluide frigorigène s'écoulant dans l'entrée (4) et étant évacué par la pluralité de sorties (71) vers le tuyau extérieur (6),
    où le tuyau extérieur (6) a deux extrémités fermées, et un tube qui forme une entrée de fluide frigorigène (4) s'étend à travers une paroi latérale du tuyau extérieur (6), et
    où la pluralité de sorties (71) est prévue uniquement dans une partie inférieure du tuyau intérieur (7) dans la direction de la pesanteur.
  2. Appareil de pompe à chaleur selon la revendication 1, dans lequel un diamètre du canal d'écoulement dans chacun de la pluralité d'éléments de plaque mince (1) est compris entre 0,05 mm et 0,2 mm.
  3. Appareil de pompe à chaleur selon la revendication 2, dans lequel
    la pluralité d'éléments de plaque mince (1) satisfait à une relation 3 ≤ Fp / Ft ≤ 21 ,
    Figure imgb0005
     où Fp désigne un pas de la pluralité d'éléments de plaque mince (1) adjacents les uns aux autres, et Ft désigne une épaisseur de chacun de la pluralité d'éléments de plaque mince (1).
  4. Appareil de pompe à chaleur selon la revendication 1 ou la revendication 3 dépendant de la revendication 1, dans lequel le canal d'écoulement formé dans chacun de la pluralité d'éléments de plaque mince (1) a une forme en coupe rectangulaire.
  5. Appareil de pompe à chaleur selon l'une quelconque des revendications 1 à 4,
    dans lequel l'échangeur de chaleur est l'un d'une pluralité d'échangeurs de chaleur agencés côte à côte dans une direction d'écoulement du fluide, et
    dans lequel, dans la direction d'écoulement du fluide, chacun de la pluralité d'éléments de plaque mince (1) prévus d'un côté amont est décalé alternativement par rapport à l'un correspondant de la pluralité d'éléments de plaque mince (1) prévus d'un côté aval.
EP14823375.2A 2013-07-08 2014-07-08 Dispositif de pompe à chaleur Active EP3021064B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/JP2013/068677 WO2015004720A1 (fr) 2013-07-08 2013-07-08 Échangeur de chaleur, et appareil de conditionnement de l'air
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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WO2015004720A1 (fr) 2015-01-15
EP3021064A4 (fr) 2017-03-22
CN105452794A (zh) 2016-03-30
US20160298886A1 (en) 2016-10-13
EP3021064A1 (fr) 2016-05-18
JPWO2015005352A1 (ja) 2017-03-02
WO2015005352A1 (fr) 2015-01-15

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