WO2022244461A1 - Système d'échange de chaleur - Google Patents

Système d'échange de chaleur Download PDF

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Publication number
WO2022244461A1
WO2022244461A1 PCT/JP2022/013847 JP2022013847W WO2022244461A1 WO 2022244461 A1 WO2022244461 A1 WO 2022244461A1 JP 2022013847 W JP2022013847 W JP 2022013847W WO 2022244461 A1 WO2022244461 A1 WO 2022244461A1
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WIPO (PCT)
Prior art keywords
radiator
section
cooler
condensation
condensed water
Prior art date
Application number
PCT/JP2022/013847
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English (en)
Japanese (ja)
Inventor
裕文 弐又
駿 丹野
剛史 細野
一雄 亀井
栄一 鳥越
功 畔柳
Original Assignee
株式会社デンソー
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Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Publication of WO2022244461A1 publication Critical patent/WO2022244461A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing

Definitions

  • the present disclosure relates to a heat exchange system that exchanges heat between refrigerant and air.
  • a vehicle air conditioner disclosed in Patent Document 1 includes an evaporator and a condenser, and the evaporator and condenser constitute the heat exchange system.
  • the evaporator and condenser are housed in one housing.
  • the condenser is arranged below the evaporator, and is provided with a conduit for guiding the condensed water generated in the evaporator to the condenser.
  • condensed water from the evaporator is applied to the condenser to raise the cooling efficiency of the refrigerant in the condenser, thereby improving the efficiency of the entire refrigeration cycle including the evaporator and the condenser.
  • Patent Document 1 makes no mention of smoothly guiding the condensed water generated in the cooler to the radiator. As a result of detailed studies by the inventors, the above was found.
  • the present disclosure aims to provide a heat exchange system that can smoothly guide condensed water generated in a cooler to a radiator.
  • a heat exchange system includes: A heat exchange system for exchanging heat between a refrigerant and air, a cooler that cools air with a refrigerant; A radiator located below the cooler, arranged so that condensed water generated in the cooler flows down, has a specific configuration, and dissipates heat from the refrigerant to the air,
  • the specific configuration is a radiator, which allows condensed water that has flowed down to the radiator to wet and spread more than when the specific configuration is not provided.
  • the condensed water generated in the cooler is more likely to be pulled toward the radiator due to the specific configuration of the radiator. Therefore, the condensed water is less likely to stay in the cooler, and the condensed water can be smoothly guided to the radiator.
  • FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle circuit having a heat exchanger of a first embodiment
  • FIG. It is a sectional view showing typically a schematic structure of a heat exchanger in a 1st embodiment.
  • FIG. 3 is a diagram showing, in section III-III of FIG. 2, an excerpt of a laminated structure constituting the heat exchanger of the first embodiment;
  • FIG. 3 is a view showing an excerpt from the laminated structure constituting the heat exchanger of the first embodiment in the IV-IV cross section of FIG. 2;
  • FIG. 4 is a cross-sectional view schematically showing a partial cross-section of the condensation tube portion obtained by cutting the plate material constituting the condensation tube portion so as to reveal the thickness of the plate material constituting the condensation tube portion in the first embodiment, and showing the configuration of the condensation portion.
  • FIG. 2 is a diagram in which, in addition to the reference numerals, reference numerals indicating the configuration of the evaporating section are also written.
  • FIG. 4 is a cross-sectional view schematically showing a partial cross-section of a condensation fin obtained by cutting the plate material constituting the condensation fin so that the thickness of the plate material constituting the condensation fin is exposed in the first embodiment; In addition to , reference numerals indicating the configuration of the evaporator are also shown.
  • FIG. 2 is a diagram in which, in addition to the reference numerals, reference numerals indicating the configuration of the evaporating section are also written.
  • FIG. 4 is a cross-sectional view schematically showing a partial cross-section of a condensation
  • FIG. 5 is a cross-sectional view schematically showing the VII-VII cross section of FIG. 1 is a cutaway view of FIG.
  • FIG. 10 is a schematic perspective view of a single condensation fin extracted and partially enlarged in the second embodiment.
  • FIG. 9 is a cross-sectional view schematically showing the IX-IX cross section of FIG. 8 in the second embodiment, and is a portion of the condensation fin obtained by cutting along a plane perpendicular to the direction in which the fine grooves provided in the condensation fin extend.
  • 1 is a diagram showing a typical cross section; FIG. FIG.
  • FIG. 10 is a perspective view schematically showing the condensation fins and the condensation tube portions adjacent to the condensation fins in the second embodiment, in which the flow of condensed water flowing from the condensation tube portions to the condensation fins is indicated by dashed arrows; is.
  • FIG. 5 is a view corresponding to FIG. 4 , showing an excerpt of a laminated structure constituting a heat exchanger in the third embodiment;
  • FIG. 12 is a sectional view showing the XII-XII section of FIG. 11 in the third embodiment;
  • FIG. 12 is a perspective view schematically showing an enlarged portion XIII of FIG. 11 in the third embodiment;
  • FIG. 5 is a view corresponding to FIG. 4 , showing an excerpt of a laminated structure constituting a heat exchanger in the fourth embodiment;
  • FIG. 15 is a schematic enlarged view of the portion corresponding to the XV portion of FIG. 14 in the fifth embodiment, showing a plurality of grooves formed in the intermediate surface.
  • FIG. 10 is a view corresponding to FIG. 4 , showing an excerpt of the laminated structure constituting the heat exchanger in the sixth embodiment.
  • FIG. 17 is a diagram schematically showing an enlarged portion corresponding to the XVII portion of FIG. 16 in the seventh embodiment, showing a plurality of condensation section surface grooves formed on the surface of the condensation section.
  • FIG. 11 is a cross-sectional view schematically showing the schematic configuration of a heat exchanger in an eighth embodiment, corresponding to FIG. 2 ;
  • FIG. 19 is a view corresponding to FIG.
  • FIG. 4 showing the condenser section and the evaporator section of the heat exchanger of the eighth embodiment, taken along the XIX-XIX section of FIG. 18;
  • FIG. 11 is a view corresponding to FIG. 4 , showing a condensing section, an evaporating section, and an intermediate section that constitute a heat exchanger in a ninth embodiment;
  • FIG. 10 is a perspective view showing a unit in which a heat exchanger with a condenser and an evaporator, a pressure reducing device, and an accumulator are integrated in another embodiment.
  • FIG. 5 is a view corresponding to FIG. 4 and showing an extract of a laminated structure constituting a heat exchanger in another embodiment.
  • FIG. 21 is a view corresponding to FIG. 20 and showing an extract of a laminated structure constituting a heat exchanger in another embodiment.
  • a heat exchanger 10 is provided as a heat exchange system for exchanging heat between refrigerant and air.
  • the heat exchanger 10 is used in a vehicle air conditioner and constitutes part of a refrigeration cycle circuit 12 that is included in the vehicle air conditioner and in which a refrigerant circulates.
  • a vehicle air conditioner air-conditions a vehicle interior, which is a space to be air-conditioned.
  • the refrigerant compressed by the compressor 14 included in the refrigerating cycle circuit 12 flows into the condenser section 20 that constitutes a part of the heat exchanger 10 and functions as a radiator. heat is exchanged with
  • the refrigerant that has exchanged heat with the air in the condenser section 20 is decompressed and expanded by the decompression device 15, flows from the decompression device 15 into the evaporator section 22 that constitutes a part of the heat exchanger 10 and functions as a cooler, and then flows into the evaporator section. At 22, it is made to exchange heat with air.
  • the refrigerant that has exchanged heat with the air in the evaporator 22 flows into the accumulator 16, which is a gas-liquid separator, where it is separated into gas and liquid.
  • the gas-phase refrigerant flows out of the accumulator 16 and is sucked into the compressor 14 .
  • the liquid-phase refrigerant is stored in the accumulator 16 .
  • the decompression device 15 is, for example, a capillary tube, an orifice, or an expansion valve.
  • the evaporator 22 of the heat exchanger 10 is arranged in the first air passage through which air flows toward the air-conditioned space, and cools the air flowing through the first air passage with a refrigerant.
  • the condenser section 20 of the heat exchanger 10 is arranged in the second air passage through which the air discharged to the outside of the air-conditioned space flows, and releases heat from the refrigerant to the air flowing through the second air passage.
  • the heat exchanger 10 of the present embodiment is constructed by brazing together a plurality of constituent members made of metal such as aluminum alloy or copper alloy.
  • the heat exchanger 10 includes an intermediate section 24, one side plate section 30, the other side plate section 32, a condenser inlet pipe 34, a condenser outlet pipe 35, and an evaporator.
  • a section inlet pipe 36 and an evaporator section outlet pipe 37 are provided.
  • the one-side side plate portion 30 and the other-side side plate portion 32 are formed in a plate shape with a predetermined stacking direction Ds as the thickness direction. As shown in FIGS. 2 to 4, the evaporating section 22 and the condensing section 20 are arranged in the order of the evaporating section 22 and the condensing section 20 from one side in the heat exchanger vertical direction Dv that matches the alignment direction. An intermediate section 24 is arranged between the evaporating section 22 and the condensing section 20 .
  • the heat exchanger 10 is arranged in a posture inclined with respect to the vertical direction Dg (in other words, the vertical direction Dg) when mounted on a vehicle.
  • the vertical direction Dv is oblique to the vertical direction Dg.
  • One side in the longitudinal direction Dv of the heat exchanger is positioned above the other side. Therefore, the evaporating section 22, the intermediate section 24, and the condensing section 20 are arranged side by side in the order of the evaporating section 22, the intermediate section 24, and the condensing section 20 from the upper side in the vertical direction Dg.
  • the condensation section 20 is arranged to overlap the evaporation section 22 downward in the vertical direction Dg, and the intermediate section 24 is provided between the condensation section 20 and the evaporation section 22 . Therefore, when condensed water Wc is generated in the evaporating section 22 as the air is cooled, the condensed water Wc flows down from the evaporating section 22 to the condensing section 20 through the intermediate section 24 .
  • the stacking direction Ds is a direction intersecting the vertical direction Dg and the heat exchanger vertical direction Dv, or strictly speaking, a direction perpendicular to each.
  • the direction perpendicular to both the stacking direction Ds and the heat exchanger vertical direction Dv is referred to as the heat exchanger width direction Dw.
  • "upper side” means the upper side when mounted on the vehicle (i.e., the upper side of the vehicle)
  • “lower side” means the lower side when mounted on the vehicle (i.e., the upper side of the vehicle). , vehicle underside).
  • the one side plate portion 30 is arranged at one end of the heat exchanger 10 in the stacking direction Ds, and the other side plate portion 32 is arranged at the other end of the heat exchanger 10 in the stacking direction Ds. It is The condensation section 20, the evaporation section 22, and the intermediate section 24 are arranged between the one side plate section 30 and the other side plate section 32 in the stacking direction Ds. It is sandwiched between 32 and Condensing section 20 and evaporating section 22 are fixed to one side plate section 30 and other side plate section 32, respectively, and intermediate section 24 is fixed to condensing section 20 and evaporating section 22, respectively.
  • One side plate portion 30 is provided with a condenser inlet pipe 34 and an evaporator outlet pipe 37
  • the other side plate portion 32 is provided with a condenser outlet pipe 35 and an evaporator inlet pipe 36.
  • the condenser inlet pipe 34 is connected to the refrigerant flow upstream side of the condenser 20 and causes the refrigerant discharged from the compressor 14 to flow into the condenser 20
  • the condenser outlet pipe 35 is connected to the refrigerant flow downstream side of the condenser 20 and causes the refrigerant in the condenser 20 to flow out from the condenser 20 to the decompression device 15 .
  • the evaporator inlet pipe 36 is connected to the refrigerant flow upstream side of the evaporator 22 and allows the refrigerant from the decompression device 15 to flow into the evaporator 22 .
  • the evaporator outlet pipe 37 is connected to the refrigerant flow downstream side of the evaporator 22 and causes the refrigerant in the evaporator 22 to flow out from the evaporator 22 to the accumulator 16 .
  • the condensation section 20 has a first condensation tank section 201, a second condensation tank section 203, a plurality of condensation tube sections 205, and a plurality of condensation fins 206.
  • the condensation section 20 exchanges heat between the refrigerant flowing in the condensation tube section 205 and the air passing through the condensation section 20, and the heat exchange causes the refrigerant to release heat to the air, thereby condensing the refrigerant.
  • the first condensation tank portion 201 is provided on one side of the plurality of condensation tube portions 205 in the heat exchanger vertical direction Dv, and the second condensation tank portion 203 is provided on one side of the plurality of condensation tube portions 205 in the heat exchanger vertical direction Dv. provided on the other side.
  • the first condensation tank portion 201 has a plurality of first condensation tank constituent portions 202 arranged in series in the stacking direction Ds, and is configured by joining the plurality of first condensation tank constituent portions 202 to each other. . Therefore, the first condensation tank portion 201 is formed to extend in the stacking direction Ds.
  • the internal spaces 202a of the first condensing tank forming portions 202 communicate with each other through through holes.
  • the communication between the internal spaces 202a of the first condensing tank forming portions 202 adjacent to each other is blocked.
  • the second condensation tank portion 203 has a plurality of second condensation tank constituent portions 204 arranged in series in the stacking direction Ds, and is configured by joining the plurality of second condensation tank constituent portions 204 to each other. . Therefore, the second condensation tank portion 203 is formed to extend in the stacking direction Ds.
  • the internal spaces 204a of the second condensation tank constituent parts 204 communicate with each other through through holes. However, communication between the inner spaces 204a of the second condensing tank forming portions 204 adjacent to each other is cut off at the C2 and C3 portions (see FIG. 2).
  • the condensation tube portion 205 corresponds to the radiator tube of the present disclosure.
  • the condensation tube portion 205 has a flat shape whose thickness direction is the stacking direction Ds.
  • a condensation tube flow path 205a through which a refrigerant flows is formed inside the condensation tube portion 205.
  • the condensation tube flow path 205a extends in a meandering manner while reciprocating in the longitudinal direction Dv of the heat exchanger.
  • One end of the condensation tube channel 205 a is connected to the internal space 202 a of the first condensation tank component 202
  • the other end of the condensation tube channel 205 a is connected to the internal space 204 a of the second condensation tank component 204 .
  • the plurality of condensing tube portions 205 are stacked so as to be spaced apart from each other in the stacking direction Ds. Ventilation spaces 20a through which air passes are formed between the condensing tube portions 205 adjacent to each other. That is, a plurality of ventilation spaces 20a are formed side by side in the stacking direction Ds.
  • An arrow FLa represents the flow of air flowing into the ventilation space 20a of the condensation section 20. As shown in FIG. That is, the air passing through the ventilation space 20a of the condenser section 20 flows with one side in the heat exchanger width direction Dw as the air flow upstream side and the other side in the heat exchanger width direction Dw as the air flow downstream side.
  • the condenser fins 206 correspond to radiator fins of the present disclosure.
  • a plurality of condensation fins 206 are respectively arranged in the ventilation space 20 a of the condensation section 20 and brazed to the outside of the condensation tube section 205 adjacent to the condensation fins 206 .
  • the condensation fins 206 are corrugated fins, and the condensation fins 206 are formed with a plurality of louvers 206a (see FIG. 8). With such a configuration, the condensation fins 206 promote heat exchange between the air passing through the ventilation space 20 a of the condensation section 20 and the refrigerant in the condensation section 20 .
  • Condensation fins 206 are made of a metal with good thermal conductivity, such as an aluminum alloy or a copper alloy.
  • refrigerant from the compressor 14 is provided at one end of the second condensation tank section 203 in the stacking direction Ds. It flows into the internal space 204 a of the section 204 via the condensation section inlet pipe 34 .
  • the refrigerant flows from one side to the other side in the stacking direction Ds.
  • the refrigerant flows from the first condensation tank forming portion 202 side to the second condensation tank forming portion 204 side, or from the second condensation tank forming portion 204 side to the first condensation tank forming portion. It flows to the part 202 side.
  • arrow A2 indicates the refrigerant flow in the second condensing tank portion 203
  • arrow A3 indicates the refrigerant flow in the condensing tube portion 205. showing.
  • the refrigerant that has flowed through the condensation section 20 in this way flows from the internal space 204 a of the second condensation tank forming section 204 provided at the end of the second condensation tank section 203 on the other side in the stacking direction Ds to the condensation section outlet pipe 35 . to the decompression device 15 (see FIG. 1).
  • the evaporating section 22 has a first evaporating tank section 221, a second evaporating tank section 223, a plurality of evaporating tube sections 225, and a plurality of evaporating fins 226.
  • the evaporating portion 22 exchanges heat between the refrigerant flowing through the evaporating tube portion 225 and the air passing through the evaporating portion 22, and the heat exchange evaporates the refrigerant and cools the air.
  • the first evaporation tank portion 221 is provided on one side of the plurality of evaporation tube portions 225 in the heat exchanger vertical direction Dv, and the second evaporation tank portion 223 is provided on one side of the plurality of evaporation tube portions 225 in the heat exchanger vertical direction Dv. provided on the other side.
  • the first evaporation tank portion 221 has a plurality of first evaporation tank constituent portions 222 arranged in series in the stacking direction Ds, and is configured by joining the plurality of first evaporation tank constituent portions 222 to each other. . Therefore, the first evaporation tank portion 221 is formed to extend in the stacking direction Ds.
  • the internal spaces 222a of the first evaporation tank constituent parts 222 communicate with each other through through holes. However, in the E1 and E2 portions (see FIG. 2), communication between the internal spaces 222a of the first evaporation tank forming portions 222 adjacent to each other is blocked.
  • the second evaporation tank portion 223 has a plurality of second evaporation tank constituent portions 224 arranged in series in the stacking direction Ds, and is configured by joining the plurality of second evaporation tank constituent portions 224 to each other. . Therefore, the second evaporation tank portion 223 is formed to extend in the stacking direction Ds.
  • the internal spaces 224a of the second evaporation tank constituent parts 224 basically communicate with each other through through holes. However, in the E3 portion (see FIG. 2), the communication between the internal spaces 224a of the second evaporation tank forming portions 224 adjacent to each other is blocked.
  • the evaporator tube section 225 corresponds to the cooler tube of the present disclosure.
  • the evaporating tube portion 225 has a flat shape whose thickness direction is the stacking direction Ds. Inside the evaporating tube portion 225, an evaporating tube flow path 225a through which a refrigerant flows is formed.
  • the evaporation tube flow path 225a extends in a meandering manner while reciprocating in the longitudinal direction Dv of the heat exchanger.
  • One end of the evaporation tube flow path 225 a is connected to the internal space 222 a of the first evaporation tank forming part 222 , and the other end of the evaporation tube flow path 225 a is connected to the internal space 224 a of the second evaporation tank forming part 224 .
  • the plurality of evaporating tube portions 225 are arranged in layers so as to be spaced apart from each other in the stacking direction Ds. Ventilation spaces 22a through which air passes are formed between the evaporating tube portions 225 adjacent to each other. That is, a plurality of ventilation spaces 22a are formed side by side in the stacking direction Ds.
  • An arrow FLb (see FIGS. 3 and 4) represents the flow of air flowing into the ventilation space 22a of the evaporator 22. That is, the air passing through the ventilation space 22a of the evaporating section 22 flows with one side in the heat exchanger width direction Dw as the air flow upstream side and the other side in the heat exchanger width direction Dw as the air flow downstream side.
  • the plurality of evaporating fins 226 are arranged in the ventilation space 22a of the evaporating part 22 and are brazed to the outside of the evaporating tube part 225 adjacent to the evaporating fins 226 .
  • the evaporation fins 226 are corrugated fins, and the evaporation fins 226 are formed with a plurality of louvers like the condensation fins 206 .
  • the evaporating fins 226 facilitate heat exchange between the air passing through the ventilation space 22 a of the evaporating section 22 and the refrigerant in the evaporating section 22 .
  • Evaporation fins 226 are made of metal with good thermal conductivity, such as aluminum alloy or copper alloy.
  • the refrigerant from the decompression device 15 (see FIG. 1) is provided at the end of the first evaporating tank section 221 on the other side in the stacking direction Ds. It flows into the internal space 222 a of the unit 222 through the evaporator inlet pipe 36 . In the first evaporation tank portion 221 and the second evaporation tank portion 223, the refrigerant flows from the other side to the one side in the stacking direction Ds.
  • the refrigerant flows from the first evaporation tank forming portion 222 side to the second evaporation tank forming portion 224 side, or from the second evaporation tank forming portion 224 side to the first evaporation tank forming portion. It flows to the part 222 side.
  • Arrow B1 in FIG. 2 indicates the refrigerant flow in the first evaporation tank portion 221
  • arrow B2 indicates the refrigerant flow in the second evaporation tank portion 223
  • arrow B3 indicates the refrigerant flow in the evaporation tube portion 225. showing.
  • the refrigerant that has flowed through the evaporator 22 in this manner flows from the internal space 222 a of the first evaporator tank forming portion 222 provided at one end in the stacking direction Ds of the first evaporator tank 221 to the evaporator outlet pipe 37 . to the accumulator 16 (see FIG. 1).
  • the condensation section 20 and the evaporation section 22 of the heat exchanger 10 are constructed by laminating a plurality of laminated structures 38 in the lamination direction Ds and brazing them together.
  • the laminated structure 38 which is a tube sub-assembly, has a substantially flat shape whose thickness direction is the lamination direction Ds. The hand direction coincides with the heat exchanger width direction Dw.
  • Each of the plurality of laminated structures 38 is composed of a first plate member 381 and a second plate member 382 that are joined together by brazing to form a pair. Both the first plate member 381 and the second plate member 382 are made of a metal having good thermal conductivity, such as an aluminum alloy or a copper alloy.
  • FIG. 2 the cross sections of the first plate member 381, the second plate member 382, the condensation fins 206, and the evaporation fins 226 are indicated by thick lines instead of hatching. Also, in order to make the illustration easier to see, FIG. are displayed with a space between them). These are the same for later-described figures corresponding to FIG. 2 .
  • the first plate member 381 is arranged on one side in the stacking direction Ds with respect to the second plate member 382 in the laminate structure 38 including the first plate member 381.
  • FIG. The first plate member 381 has a plate shape having a thickness in the stacking direction Ds, and is recessed toward one side in the stacking direction Ds so as to form a recessed space through which the coolant flows.
  • the second plate member 382 has a plate shape having a thickness in the stacking direction Ds, and is recessed toward the other side in the stacking direction Ds so as to form a recessed space through which the coolant flows.
  • first plate member 381 and the second plate member 382 are joined together in a posture in which the recessed space of the first plate member 381 and the recessed space of the second plate member 382 face each other. It is composed by
  • the path 225a is formed by combining the concave space of the first plate member 381 and the concave space of the second plate member 382 together.
  • one laminated structure 38 includes one first condensation tank constituent portion 202, one second condensation tank constituent portion 204, one condensation tube constituent portion 205, one first evaporation tank constituent portion 222, and one second condensation tank constituent portion 222. It has two evaporation tank constituent parts 224 and one evaporation tube part 225 .
  • the first condensation tank component 202, the second condensation tank component 204, the condensation tube component 205, the first evaporation tank component 222, the second evaporation tank component 224, and the evaporation tube component 225 are integrated. It's becoming
  • the condensation tube flow path 205a located on the most one side in the stacking direction Ds among the plurality of condensation tube flow paths 205a is formed by the second plate member 382 and the one side plate portion 30.
  • the condensation tube flow path 205 a located on the othermost side in the stacking direction Ds is formed by the first plate member 381 and the other side plate portion 32 .
  • the internal spaces 202a, 204a of the first and second condensing tank components 202, 204, the internal spaces 222a, 224a of the first and second evaporative tank components 222, 224, and the evaporative tube channel 225a It is the same.
  • through-holes 38a are formed in the plurality of laminated structures 38, and the through-holes 38a separate the condensation section 20 and the evaporation section 22 in each of the laminated structures 38. It is arranged between the condensing section 20 and the evaporating section 22 as shown in FIG. This is to insulate between the condenser section 20 and the evaporator section 22 by the through holes 38a.
  • the intermediate portion 24 of the heat exchanger 10 is provided between the condensation portion 20 and the evaporation portion 22 as described above. is arranged in the middle of the path flowing from the evaporating section 22 to the condensing section 20 .
  • the intermediate portion 24 corresponds to the portion of the laminate structure 38 on one side and the portion on the other side of the through hole 38 a in the heat exchanger width direction Dw.
  • the intermediate portion 24 is formed with an intermediate surface 241 disposed in the middle of the flow of the condensed water Wc from the evaporating portion 22 to the condensing portion 20, and the outer surface of the intermediate portion 24 corresponds to the intermediate surface 241. .
  • the condensing section 20 has a specific configuration 207 for promoting the flow of the condensed water Wc from the evaporating section 22 to the condensing section 20.
  • FIG. The specific configuration 207 of the condensation section 20 allows the condensed water Wc that has flowed down to the condensation section 20 to wet and spread in the condensation section 20 compared to the case where the specific configuration 207 is not provided.
  • the specific configuration 207 of the condensation section 20 in this embodiment is the surface coating 207 a applied to the condensation section 20 .
  • the condensation section 20 has a surface coating 207 a applied to the condensation section 20 as the specific configuration 207 .
  • the surface coating 207 a is provided on the respective surfaces of the first condensing tank portion 201 , the second condensing tank portion 203 , the condensing tube portion 205 and the condensing fins 206 .
  • 5 shows the surface coating 207a applied to the surface of the condensation tube portion 205
  • FIG. 6 shows the surface coating 207a applied to the surface of the condensation fins 206.
  • the surface coating 207a of the condensation section 20 is a hydrophilic coating that improves the hydrophilicity of the surface of the condensation section 20 compared to when the surface coating 207a is not provided.
  • the surface of the condensation section 20 is, for example, the surfaces of the first condensation tank section 201 , the second condensation tank section 203 , the condensation tube section 205 and the condensation fins 206 .
  • this surface coating 207a can be formed by surface treatment such as painting or plating.
  • the surface coating 207a is formed by immersing the heat exchanger 10 after brazing in a dip bath containing a liquid coating agent.
  • the same surface coating as the surface coating 207a of the condenser section 20 is applied to the entire heat exchanger 10 . That is, the evaporating section 22 is also coated with a surface coating 227 a , and the surface coating 227 a of the evaporating section 22 is the same hydrophilic coating as the surface coating 207 a of the condensing section 20 . Therefore, the surface coating 207 a of the condenser section 20 gives the surface of the condenser section 20 the same hydrophilicity compared to the evaporator section 22 .
  • the surface coating 227a of the evaporating section 22 is also a hydrophilic coating, the surface coating 227a of the evaporating section 22 improves the hydrophilicity of the surface of the evaporating section 22 compared to the case where the surface coating 227a is not provided.
  • the surface of the evaporating section 22 is, for example, the surfaces of the first evaporating tank section 221 , the second evaporating tank section 223 , the evaporating tube section 225 and the evaporating fins 226 . 5 and 6 each show a cross section of the condensation section 20. In FIGS. 5 and 6, reference numerals indicate the configuration of the evaporation section 22 corresponding to the configuration of the condensation section 20 shown in FIGS. are also listed.
  • the intermediate section 24 has the surface coating 24a applied to the intermediate surface 241 as shown in FIG. have.
  • the surface coating 24a of the intermediate portion 24 is the same hydrophilic coating as the surface coatings 207a and 227a of the condensation portion 20 and the evaporation portion 22.
  • the surface coating 24 a of the intermediate portion 24 gives the intermediate surface 241 the same hydrophilicity compared to the evaporator portion 22 . Also, since the surface coating 24a of the intermediate portion 24 is also a hydrophilic coating, the surface coating 24a of the intermediate portion 24 makes the intermediate surface 241 more hydrophilic than if the surface coating 24a were not provided.
  • the intermediate portion 24 has the surface coating 24a as a promoting structure that promotes the wetting and spreading of the condensed water Wc adhering to the intermediate portion 24 to the same extent or more than that of the evaporating portion 22.
  • the surface coating 24a promotes wetting and spreading of the condensed water Wc more than when the surface coating 24a is not provided.
  • the condensation section 20 is positioned below the evaporation section 22 and arranged so that the condensed water Wc generated in the evaporation section 22 flows down.
  • Condensing section 20 has specific configuration 207 , and specific configuration 207 wets and spreads condensed water Wc that has flowed down to condensation section 20 in comparison with the case where specific configuration 207 is not provided. It's something that makes you laugh. Therefore, the condensed water Wc generated in the evaporating section 22 is easily pulled toward the condensing section 20 by the specific configuration 207 of the condensing section 20 . Therefore, the condensed water Wc is less likely to stay in the evaporating section 22 , and the condensed water Wc can be smoothly guided to the condensing section 20 .
  • the heat exchanger 10 is arranged in a posture inclined with respect to the vertical direction Dg as described above. Specifically, the upper side of the heat exchanger 10 is located upstream of the air flow passing through the condenser section 20 (in other words, upstream of the second air passage in which the condenser section 20 is arranged) with respect to the lower side. , the heat exchanger 10 is inclined with respect to the vertical direction Dg. In other words, the condensing section 20 and the evaporating section 22 of the heat exchanger 10 are each inclined with respect to the vertical direction Dg so that the air inflow surface 20b of the condensing section 20 into which the air flows faces obliquely downward.
  • the condensation section 20 has the surface coating 207a, which is a hydrophilic coating applied to the condensation section 20, as the specific configuration 207.
  • the surface coating 207a of the condensing section 20 imparts the same hydrophilicity to the surface of the condensing section 20 as compared to the evaporating section 22, such that the surface of the condensing section 20 is more hydrophilic than if the surface coating 207a were not provided. Improves hydrophilicity. Therefore, the condensed water Wc flowing into the condensing section 20 is not stagnant due to the surface properties of the condensing section 20, and the condensed water Wc can flow in the condensing section 20 while being thinned.
  • the condensed water Wc that has flowed down to the condenser 20 flows as a thin film, the heat exchange between the condensed water Wc and the refrigerant is efficiently performed in the condenser 20.
  • all of the condensed water that has flowed down to the condenser 20 It is easy to evaporate the water Wc.
  • the performance of the condenser 20 is improved, and the remaining condensed water Wc that has not been evaporated in the condenser 20 is prevented from splashing. can be prevented from remaining as liquid in the condensation section 20 .
  • the intermediate portion 24 is arranged in the middle of the path along which the condensed water Wc flows from the evaporating portion 22 to the condensing portion 20 .
  • the intermediate portion 24 has a surface coating 24a as a promoting structure that promotes the wetting and spreading of the condensed water Wc adhering to the intermediate portion 24 to the same extent or more than that of the evaporating portion 22 .
  • the surface coating 24a promotes wetting and spreading of the condensed water Wc more than when the surface coating 24a is not provided.
  • the surface coating 24 a of the intermediate section 24 gives the intermediate surface 241 the same hydrophilicity as compared to the evaporator section 22 . Also, the surface coating 24a of the intermediate portion 24 makes the intermediate surface 241 more hydrophilic than if the surface coating 24a were not provided.
  • the condensed water Wc can be thinned and flowed. This prevents the condensed water Wc from stagnation while flowing from the evaporating section 22 to the condensing section 20 , and allows the condensed water Wc to smoothly flow down from the evaporating section 22 to the condensing section 20 .
  • the plurality of evaporating tube portions 225 are configured integrally with the plurality of condensing tube portions 205, respectively. Therefore, it is possible to easily realize a structure in which the condensed water Wc generated in the evaporating section 22 easily flows down to the condensing tube section 205 and the condensing fins 206 of the condensing section 20 .
  • the surface coatings 24a, 207a, and 227a applied to the heat exchanger 10 are all the same hydrophilic coating, and it is easy to make the hydrophilicity uniform in the condensation section 20, the evaporation section 22, and the intermediate section 24. .
  • the surface coating 227a of the evaporating section 22 is a hydrophilic coating. Therefore, the surface coating 227a of the evaporating section 22 wets and spreads the condensed water Wc adhering to the surface of the evaporating section 22 in comparison with the case where the surface coating 227a is not provided. Corresponds to certain cooler configurations of the present disclosure that the evaporator section 22 has.
  • the condensation fins 206 have a plurality of fine grooves 206b formed on the surface of the condensation fins 206 as a specific configuration 207.
  • the plurality of fine grooves 206b are fine grooves formed so as to increase the hydrophilicity of the surface of the condensation fins 206. As shown in FIG.
  • each of the plurality of fine grooves 206b extends in a direction that intersects the heat exchanger width direction Dw, and is arranged side by side at predetermined intervals in the heat exchanger width direction Dw. Also, the plurality of fine grooves 206b are evenly provided on the entire surface of the condensation fins 206. As shown in FIG.
  • the condensation fins 206 have a plurality of fine grooves 206b formed to increase the hydrophilicity of the surface of the condensation fins 206 as the specific configuration 207. . Therefore, as indicated by the dashed arrow in FIG. 10, the condensed water Wc adhering to the surface of the condensation tube portion 205 smoothly flows from the condensation tube portion 205 to the condensation fins 206, and the condensed water Wc flowing to the condensation fins 206 is It is led to the louver 206a while being thinned.
  • the condensed water Wc exchanges heat with the refrigerant around the louver 206a, the heat exchange between the condensed water Wc and the refrigerant is efficiently performed in the condenser 20. For example, all the condensed water flowing down to the condenser 20 It is easy to evaporate Wc.
  • this embodiment is the same as the first embodiment.
  • the surface coatings 24a, 207a, and 227a are applied to the heat exchanger 10 in the first embodiment, the surface coatings 24a, 207a, and 227a may be applied to the heat exchanger 10 in the present embodiment. It may or may not be applied. Unless otherwise specified, this also applies to embodiments described later based on the first embodiment.
  • the intermediate section 24 of the heat exchanger 10 has a plurality of recessed sections 242 extending from the evaporating section 22 side to the condensing section 20 side.
  • the recessed portion 242 is formed such that a cross section perpendicular to the direction in which the recessed portion 242 extends (specifically, the longitudinal direction Dv of the heat exchanger) has a recessed shape.
  • the concave portion 242 extends continuously from the intermediate portion 24 to each of the condensation portion 20 and the evaporation portion 22 .
  • the condensation section 20 has a condensation recessed portion 208 formed continuously in series from the recessed portion 242 of the intermediate portion 24 and having a concave cross section.
  • the evaporating portion 22 has an evaporating concave portion 228 which is formed so as to continue in series from the concave portion 242 of the intermediate portion 24 and has a concave cross section.
  • the concave portion 242 of the intermediate portion 24 is also referred to as the intermediate concave portion 242 .
  • the heat exchanger 10 includes a plurality of overall concave portions 39 each composed of a condensation concave portion 208 , an intermediate concave portion 242 and an evaporating concave portion 228 .
  • each of the plurality of overall concave portions 39 is provided at one edge portion of the laminated structure 38 in the heat exchanger width direction Dw. It extends in the heat exchanger longitudinal direction Dv to the lower part of the part 20 . Therefore, in the condenser section 20, the plurality of overall concave portions 39 are provided upstream of the air flow passing through the condenser section 20, and in the evaporator section 22, they are provided upstream of the air flow passing through the evaporator section 22. is provided.
  • the condensation recessed portion 208 wets and spreads the condensed water Wc that has flowed down to the condensation portion 20 in comparison with the case where the condensation recessed portion 208 is not provided. 20 specific configurations 207 are provided.
  • the evaporation recessed portion 228 wets and spreads the condensed water Wc along the evaporation recessed portion 228 in the evaporator 22 compared to the case where the evaporation recessed portion 228 is not provided. It corresponds to a certain cooler configuration.
  • a pair of overall recessed portions 39 are provided for each laminated structure 38 .
  • One of the pair of overall concave portions 39 is formed by bending the edge of the first plate member 381 on one side in the heat exchanger width direction Dw toward one side in the stacking direction Ds.
  • the other of the pair of overall concave portions 39 is formed by bending the edge of the second plate member 382 on one side in the heat exchanger width direction Dw toward the other side in the stacking direction Ds.
  • the cross-sectional concave shape of the intermediate concave portion 242 in the intermediate portion 24 is V-shaped, for example.
  • the cross-sectional shape of the condensation recessed portion 208 is changed by the coupling of the two.
  • a certain concave shape is, for example, a U shape. This is the same for the evaporator 22 as well.
  • the intermediate portion 24 of the heat exchanger 10 has a plurality of concave portions 242 extending from the evaporating portion 22 side to the condensing portion 20 side.
  • the recessed portion 242 of the intermediate portion 24 is formed so that the cross section perpendicular to the direction in which the recessed portion 242 extends has a recessed shape. Therefore, as shown in FIG. 12, it is possible to guide the condensed water Wc inside the recessed portion 242 of the intermediate portion 24 and lead it to the condensation portion 20 .
  • the recessed portion 242 of the intermediate portion 24 acts to wet and spread the condensed water Wc adhering to the intermediate portion 24 , so that the wetting and spreading of the condensed water Wc is the same as that of the evaporating portion 22 . It can be said that it is provided as a promotion configuration for promoting the above.
  • the concave portion 242 of the intermediate portion 24 extends continuously from the intermediate portion 24 to the condensation portion 20 and the evaporation portion 22 respectively.
  • the condensation concave portion 208 formed by extending from the concave portion 242 of the intermediate portion 24 is provided upstream of the air flow passing through the condensation portion 20 in the condensation portion 20 .
  • the condensed water Wc generated in the evaporating section 22 can be guided to the air flow upstream side of the condensing section 20 .
  • This makes it easier for the condensed water Wc to spread in the condensing part 20 along with the air passing through the condensing part 20, making it possible to reduce the thickness of the condensed water Wc and promote the evaporation of the condensed water Wc.
  • the upper side of the heat exchanger 10 of the present embodiment is located on the upstream side of the air flow in the condenser section 20 (in other words, the upstream side of the second air passage) with respect to the lower side. This is particularly effective because the container 10 is inclined with respect to the vertical direction Dg.
  • this embodiment is the same as the first embodiment.
  • this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with the above-described second embodiment.
  • a plurality of grooves 241a are formed in the intermediate surface 241 in this embodiment.
  • the plurality of grooves 241a are longitudinal grooves extending in the vertical direction Dg.
  • the plurality of grooves 241a of the present embodiment are longitudinal grooves extending along the vertical direction Dg. 14 shows the intermediate surface 241 facing the other side in the stacking direction Ds, the plurality of grooves 241a are formed not only in the intermediate surface 241 facing the other side in the stacking direction Ds but also in the stacking direction.
  • An intermediate surface 241 facing one side of Ds is also formed in the same manner as shown in FIG.
  • the plurality of grooves 241a of the intermediate surface 241 may be distributed over the entire intermediate portion 24. It is provided so as to be unevenly distributed. Specifically, the plurality of grooves 241a of the intermediate surface 241 are provided on one side of the through hole 38a of the laminated structure 38 in the heat exchanger width direction Dw.
  • the intermediate surface 241 is formed with a plurality of grooves 241a.
  • the condensed water Wc adhering to the intermediate surface 241 spreads while permeating into the plurality of grooves 241a.
  • the wet spreading of the condensed water Wc is the same or larger than that of the evaporating section 22. It can be said that it is provided as a promotion configuration for further promotion.
  • the plurality of grooves 241a formed in the intermediate surface 241 are vertical grooves extending in the vertical direction Dg. Therefore, the plurality of grooves 241a act to wet and spread the condensed water Wc adhering to the intermediate surface 241 in the vertical direction Dg. Therefore, the synergistic effect of the action of the plurality of grooves 241 a and the action of gravity can promote the flow of the condensed water Wc to the condensation section 20 .
  • the longitudinal grooves extending in the vertical direction Dg do not need to extend parallel to the vertical direction Dg, and may extend at an angle to the vertical direction Dg as long as they extend vertically.
  • this embodiment is the same as the first embodiment.
  • this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with the above-described second or third embodiment.
  • the plurality of grooves 241a formed in the intermediate surface 241 do not extend along the vertical direction Dg.
  • the plurality of grooves 241a extend obliquely with respect to the vertical direction Dg.
  • the plurality of grooves 241a of the intermediate surface 241 are inclined with respect to the vertical direction Dg, they still extend in the vertical direction Dg.
  • the plurality of grooves 241a are provided in a grid pattern. Therefore, the surface area of the intermediate surface 241 can be made larger than when the plurality of grooves 241a are simply arranged in parallel. can do.
  • this embodiment is the same as the fourth embodiment.
  • the same effects as in the fourth embodiment can be obtained from the configuration common to that of the fourth embodiment.
  • a plurality of vertical grooves 241a are formed in an intermediate surface 241, as in the fourth embodiment.
  • the condenser section 20 has a plurality of condensation section surface grooves 209 formed on the surface of the condenser tube section 205 as a specific feature 207 . In this respect, this embodiment differs from the fourth embodiment.
  • the plurality of condensation section surface grooves 209 are formed not only on the surface of the condensation tube section 205 but also on the surface of the condensation section 20 around the first condensation tank forming section 202 . Also, the condensation portion surface grooves 209 are formed on both the surface of the condensation portion 20 on one side and the surface on the other side in the stacking direction Ds.
  • some of the plurality of condensation portion surface grooves 209 are continuously connected to some of the plurality of grooves 241 a formed in the intermediate surface 241 .
  • the groove shape of the condensation portion surface groove 209 is the same as the groove shape of the groove 241 a of the intermediate surface 241 . That is, the plurality of condensation portion surface grooves 209 are longitudinal grooves extending in the vertical direction Dg. Specifically, the plurality of condensation portion surface grooves 209 of this embodiment are longitudinal grooves extending along the vertical direction Dg.
  • the plurality of condensation section surface grooves 209 may be distributed over the entire surface of the condensation section 20 . It is only provided around and on top of the condensation tube section 205 . This is because the condensed water Wc that has flowed down to the condensation section 20 first adheres to the surroundings of the first condensation tank forming section 202 and the upper portion of the condensation tube section 205 in the condensation section 20 .
  • the condensation section 20 has a plurality of condensation section surface grooves 209 formed on the surface of the condensation tube section 205 as the specific configuration 207 .
  • the condensed water Wc adhering to the surface of the condensation tube portion 205 in which the condensation portion surface grooves 209 are formed spreads while permeating into the condensation portion surface grooves 209. It can flow smoothly.
  • the plurality of condensation portion surface grooves 209 are longitudinal grooves extending in the vertical direction Dg. Therefore, the plurality of condensation portion surface grooves 209 act to wet and spread the condensed water Wc adhering to the surface on which the condensation portion surface grooves 209 are formed in the vertical direction Dg. Therefore, the synergistic effect of the action of the plurality of condensing section surface grooves 209 and the action of gravity can promote the flow and spread of the condensed water Wc on the surface of the condensing section 20 .
  • the longitudinal grooves extending in the vertical direction Dg do not need to extend parallel to the vertical direction Dg, and may extend at an angle to the vertical direction Dg as long as they extend vertically.
  • this embodiment is the same as the fourth embodiment.
  • the same effects as in the fourth embodiment can be obtained from the configuration common to that of the fourth embodiment.
  • a plurality of condensation section surface grooves 209 formed on the surface of the condensation section 20 are provided in a lattice similar to the grooves 241a of the intermediate surface 241 shown in FIG. ing. Therefore, since the surface area of the condensation section 20 can be made larger than when the plurality of condensation section surface grooves 209 are simply arranged in parallel, the surface of the condensation section 20 can be made hydrophilic, and the surface of the condensation section 20 can be of water can be promoted.
  • this embodiment is the same as the sixth embodiment.
  • the same effects as in the sixth embodiment can be obtained from the same configuration as in the sixth embodiment.
  • the condensation section 20 and the evaporation section 22 are fixed to the one side plate section 30 and the other side plate section 32, respectively, but are not directly connected. do not have.
  • the evaporating section 22 is spaced apart from the condensing section 20 in the longitudinal direction Dv of the heat exchanger.
  • the heat exchanger 10 does not have a configuration corresponding to the intermediate section 24 of the first embodiment.
  • surface coatings 207a and 227a are applied to the heat exchanger 10 in the same manner as in the first embodiment.
  • this embodiment is the same as the first embodiment.
  • this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with any of the second, third, sixth, and seventh embodiments described above.
  • an intermediate portion 24 configured as a component separate from the condensation portion 20 and the evaporation portion 22 is inserted into the gap between the condensation portion 20 and the evaporation portion 22.
  • the condenser section 20 and the evaporator section 22 are connected to each other in the longitudinal direction Dv of the heat exchanger via the intermediate section 24 .
  • the intermediate portion 24 of the present embodiment has a function of promoting the flow of the condensed water Wc similarly to the intermediate portion 24 of the first embodiment.
  • a surface coating 24a (see FIG. 7), which is a hydrophilic coating, is applied.
  • the surface of the intermediate portion 24 of the present embodiment is formed so as to be smoothly connected to the surface of the evaporating portion 22 and the surface of the condensing portion 20 without any step. This is to prevent the condensed water Wc from flowing from the evaporating portion 22 to the condensing portion 20 via the intermediate portion 24 .
  • the intermediate part 24 may be configured as part of an air conditioning case that accommodates the heat exchanger 10 and forms a ventilation passage.
  • the intermediate portion 24 may be configured as a component separate from the air conditioning case and housed in the air conditioning case together with the heat exchanger 10 .
  • a plurality of intermediate portions 24 are provided side by side in the stacking direction Ds (see FIG. 18). inserted in each.
  • this embodiment is the same as the eighth embodiment.
  • the same effects as in the eighth embodiment can be obtained from the configuration common to that of the eighth embodiment.
  • the intermediate portion 24 of the present embodiment corresponds to the intermediate portion 24 of the first embodiment
  • the effect of the intermediate portion 24, which is provided by the configuration common to that of the first embodiment, is the same as that of the first embodiment.
  • the form can be obtained as well.
  • this embodiment is a modification based on the eighth embodiment, it is also possible to combine this embodiment with any of the above-described second to seventh embodiments.
  • the same surface coating as the surface coating 207a of the condenser section 20 shown in FIGS. be.
  • the evaporation section 22 is not provided with the surface coating 227a.
  • the surface coating 207a of the condensing section 20 will also render the surface of the condensing section 20 more hydrophilic than the evaporator section 22.
  • the evaporating section 22 is not provided with the surface coating 227a and the intermediate section 24 is provided with the surface coating 24a (see FIG. 7).
  • the surface coating 24 a of the intermediate section 24 also renders the intermediate surface 241 more hydrophilic than the evaporator section 22 . That is, it can be said that the intermediate portion 24 is configured to promote the wetting and spreading of the condensed water Wc adhering to the intermediate portion 24 by the surface coating 24a more than the evaporating portion 22.
  • each of the plurality of fine grooves 206b provided in the condensation fin 206 extends in a direction intersecting the heat exchanger width direction Dw. Although they are arranged side by side at predetermined intervals in the exchanger width direction Dw, this is an example.
  • the plurality of fine grooves 206b may be provided in a grid pattern, or may be formed on the surface of the condensation fins 206 so as to extend curvedly.
  • contoured portion 39 is an example.
  • intermediate recess 242 is provided, but one or both of condensing recess 208 and evaporating recess 228 are not provided.
  • the heat exchanger 10, the pressure reducing device 15, and the accumulator 16 are configured as separate devices, but this is an example.
  • the heat exchanger 10, decompression device 15, and accumulator 16 may be integrated.
  • the decompression device 15 shown in FIG. 21 is a capillary tube, the type of the decompression device 15 is not limited.
  • Patent Document 1 discloses a tubular member in which a water conduit is formed to guide condensed water from an evaporator corresponding to the evaporating section 22 to a condenser corresponding to the condensing section 20.
  • Intermediate section 24 may be such a tubular member.
  • the inner wall surface of the tubular member facing the water conduit corresponds to the intermediate surface 241, and for example, the inner wall surface of the tubular member is coated with a hydrophilic coating.
  • the surface coating 227a applied to the surface of the evaporator section 22 corresponds to a certain cooler configuration of the present disclosure
  • the evaporative concave section 228 corresponds to the certain cooler configuration of the present disclosure.
  • the position of the condenser section 20 and the position of the evaporator section 22 in the heat exchanger width direction Dw are aligned with each other.
  • the condensation section 20 and the evaporation section 22 are arranged side by side, this is an example.
  • the condensation section 20 and the evaporation section 22 are arranged side by side so that the positions of the condensation section 20 and the evaporation section 22 in the width direction Dw of the heat exchanger are shifted from each other. It doesn't matter if it is. 22 and 23, the condensation section 20 and the evaporation section 22 are not inclined with respect to the vertical direction Dg, but are oriented along the vertical direction Dg.

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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)

Abstract

Ce système d'échange de chaleur pour réaliser un échange de chaleur entre un fluide frigorigène et l'air comprend : un refroidisseur (22) pour refroidir l'air au moyen d'un fluide frigorigène ; et un radiateur (20) qui provoque la dissipation de la chaleur du fluide frigorigène vers l'air. Le radiateur est positionné au-dessous du refroidisseur et agencé de sorte que l'eau condensée (Wc) générée par le refroidisseur s'écoule vers le bas en direction du radiateur. Le radiateur a une configuration spécifique (207). La configuration spécifique amène l'humidité de l'eau condensée s'écoulant vers le bas vers le radiateur à s'étaler davantage au niveau du radiateur par rapport aux cas dans lesquels le radiateur n'est pas équipé de la configuration spécifique.
PCT/JP2022/013847 2021-05-18 2022-03-24 Système d'échange de chaleur WO2022244461A1 (fr)

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JP2021084033A JP2022177628A (ja) 2021-05-18 2021-05-18 熱交換システム
JP2021-084033 2021-05-18

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0861699A (ja) * 1994-06-15 1996-03-08 Nippondenso Co Ltd 一体型冷房機
US20170167737A1 (en) * 2014-06-05 2017-06-15 Samsung Electronics Co., Ltd Integrated air conditioner
WO2021015272A1 (fr) * 2019-07-23 2021-01-28 株式会社デンソー Échangeur de chaleur et dispositif de climatisation

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0861699A (ja) * 1994-06-15 1996-03-08 Nippondenso Co Ltd 一体型冷房機
US20170167737A1 (en) * 2014-06-05 2017-06-15 Samsung Electronics Co., Ltd Integrated air conditioner
WO2021015272A1 (fr) * 2019-07-23 2021-01-28 株式会社デンソー Échangeur de chaleur et dispositif de climatisation

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