WO2016013100A1 - 熱交換器およびこの熱交換器を備えた空調冷凍装置 - Google Patents

熱交換器およびこの熱交換器を備えた空調冷凍装置 Download PDF

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Publication number
WO2016013100A1
WO2016013100A1 PCT/JP2014/069642 JP2014069642W WO2016013100A1 WO 2016013100 A1 WO2016013100 A1 WO 2016013100A1 JP 2014069642 W JP2014069642 W JP 2014069642W WO 2016013100 A1 WO2016013100 A1 WO 2016013100A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
drainage
flat tube
exchanger according
flat
Prior art date
Application number
PCT/JP2014/069642
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English (en)
French (fr)
Japanese (ja)
Inventor
石橋　晃
真哉 東井上
伊東　大輔
繁佳 松井
中村　伸
裕樹 宇賀神
岡崎　多佳志
厚志 望月
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2014/069642 priority Critical patent/WO2016013100A1/ja
Priority to JP2016535601A priority patent/JPWO2016013100A1/ja
Priority to EP14898303.4A priority patent/EP3173725A4/de
Publication of WO2016013100A1 publication Critical patent/WO2016013100A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • F25B39/02—Evaporators
    • 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
    • F28F1/10—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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/22—Safety or protection arrangements; Arrangements for preventing malfunction for draining

Definitions

  • the present invention relates to a heat exchanger and an air-conditioning refrigeration apparatus provided with the heat exchanger.
  • the corrugated fin is formed in a zigzag shape in which flat portions and curved portions are alternately connected, and in Patent Document 1, a heat exchanger using this type of corrugated fin is used as an evaporator.
  • a technique for ensuring drainage of condensed water is disclosed. Specifically, in Patent Document 1, the flat portion of the corrugated fin is formed into a valley bottom shape with the center in the air flow direction as the bottom, and a through hole is provided at the junction between the valley bottom portion and the flat tube, and the corrugated fin surface The condensed water is led to the bottom of the flat part and drained from the through hole.
  • flat tube groups composed of a plurality of flat tubes arranged in parallel at intervals are arranged in two rows in the heat exchanger depth direction, which is a direction orthogonal to the parallel arrangement direction of the flat tubes.
  • a heat exchanger having a heat exchanging portion in which flat tubes and corrugated fins are alternately stacked in the parallel direction of the flat tubes is disclosed.
  • a pair of header is arrange
  • Patent Document 1 discloses a technique for improving drainage of condensed water, it is a technique for a configuration in which flat tube groups are arranged in a row.
  • Patent Document 2 In recent years, in order to meet the demands for smaller and lighter heat exchangers and higher performance, a configuration in which flat tube groups are arranged in multiple rows as in Patent Document 2 is increasing.
  • corrugated fins are provided in common in flat tube groups provided in two rows, and are longer in the depth direction of the heat exchanger than corrugated fins corresponding to one row.
  • the corrugated fins become longer in the heat exchanger depth direction, improvement in drainage of condensed water is required, but Patent Document 2 does not discuss anything about drainage of condensed water from the corrugated fin itself. Absent.
  • the present invention has been made to solve the above-described problems, and in a multi-row heat exchanger, the heat exchanger capable of improving drainage of condensed water and the heat exchanger are provided. It aims at obtaining an air-conditioning freezer.
  • the heat exchanger according to the present invention includes a flat tube group provided in a plurality of rows with a space between rows in the depth direction of the heat exchanger, and corrugated fins provided in common to the plurality of flat tube groups.
  • the heat exchanger is composed of a plurality of flat tubes in which the flat tube groups are arranged upright in the direction of gravity, and the corrugated fins communicate with the gaps between the rows of the flat tube groups. It has a 1st drainage part to do.
  • an air-conditioning refrigeration apparatus includes the above heat exchanger.
  • the drainage of condensed water can be enhanced in a multi-row heat exchanger.
  • FIG. 5 is a cross-sectional view taken along the line AA in FIG. 4. It is a cross-sectional view of the heat exchanger according to Embodiment 2 of the present invention. It is a cross-sectional view of the heat exchanger which concerns on Embodiment 3 of this invention. It is a cross-sectional view of the heat exchanger which concerns on Embodiment 4 of this invention. It is a refrigerant circuit diagram of the air-conditioning refrigerating apparatus which concerns on Embodiment 5 of this invention.
  • FIG. 1 is a diagram collectively showing a front view and a side view of a heat exchanger according to Embodiment 1 of the present invention.
  • 1A is a front view
  • FIG. 1B is a side view.
  • FIG. 2 is a schematic perspective view of a flat tube of the heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 1, FIG. 2, and the figure mentioned later what attached
  • the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.
  • the heat exchanger 1 is used for an outdoor unit of an air conditioner, for example, and mainly includes a heat exchange unit 10, a header 20, and a header 30.
  • the arrow shown in the header 20 indicates the flow direction of the refrigerant
  • the white arrow indicates the flow direction of air in FIG.
  • the heat exchanging unit 10 has a flat tube group 11 ⁇ / b> A and 11 ⁇ / b> B composed of a plurality of flat tubes 11 arranged side by side at intervals, with a space in the heat exchanger depth direction that is a direction orthogonal to the direction in which the flat tubes 11 are arranged. It has multiple rows (here 2 rows). Then, the flat tubes 11 and the corrugated fins 12 are alternately stacked in the direction in which the flat tubes 11 are arranged side by side.
  • the corrugated fins 12 are two-row common fins provided in common to the windward side flat tube group 11A and the leeward side flat tube group 11B, and the heat exchanging unit 10 is configured in two rows as a whole.
  • each flat tube 11 has a plurality of through-holes 11a (four as an example here) serving as a refrigerant flow path, and is arranged in a gravitational direction. 11 are connected to a pair of headers 20 and 30 at both ends in the direction of gravity. Specifically, the lower end of each flat tube 11 is connected to a header 20 (20a, 20b) as an inlet / outlet header, and the upper end of each flat tube 11 is connected to a header 30 as a folded header.
  • the corrugated fins 12 and the headers 20 and 30 are made of, for example, aluminum or an aluminum alloy.
  • header 20 is composed of two headers 20a and 20b independent of the windward side flat tube group 11A and the leeward side flat tube group 11B is shown, but the inside of one header is separated by a partition plate. It is good also as a structure.
  • the square headers are illustrated as the headers 20 and 30 here, they may be cylindrical headers.
  • the refrigerant flows into the header 20a in the lower part of the gravity direction and on the windward side, and the header 20a makes the same path as the number of the windward flat tube group 11A. It separates and raises the inside of each flat tube 11 of 11A of windward flat tube groups. Thereafter, the refrigerant that has flowed out from the upper ends of the flat tubes 11 in the windward flat tube group 11A merges in the header 30, is folded back in the header 30, and flows into the flat tubes 11 in the leeward flat tube group 11B from the upper ends. .
  • the refrigerant that has flowed in from the upper ends of the respective flat tubes 11 in the leeward flat tube group 11B passes through the flat tubes 11 and flows out from the lower ends, merges in the header 20b, and then flows out of the heat exchanger 1.
  • FIG. 3 is an enlarged schematic front view of the heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 4 is a cross-sectional view of the heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 5 is a cross-sectional view taken along the line AA in FIG.
  • the corrugated fins 12 are formed in a zigzag shape in which the plane portions 13 and the curved portions 14 are alternately arranged, and a plurality of louvers 15 are formed in each plane portion 13.
  • the louver 15 is cut and raised so as to be inclined with respect to the flat surface portion 13 of the corrugated fin 12, and a plurality of (here, (It is eight as an example.)
  • each louver 15 is formed so as to be inclined downward toward the center in the depth direction of the heat exchanger.
  • the corrugated fins 12 have a configuration common to the two rows of the windward flat tube group 11A and the leeward flat tube group 11B, and thus are longer in the heat exchanger depth direction than those corresponding to one row. For this reason, the improvement of the drainage property of the condensed water which generate
  • the first drainage portion 17 is a groove that extends in the parallel direction of the flat tubes 11 (the left-right direction in FIG. 4) at the center of the flat portion 13 in the depth direction of the heat exchanger, and is concave downward in the gravitational direction. 13 is formed.
  • the first drainage portion 17 is aligned in the inter-row gap 16 and the heat exchanger depth direction, and the first drainage portion 17 and the inter-row gap 16 serving as a drainage path in the juxtaposed direction (left-right direction in FIG. 4). Are alternately arranged and communicated with each other.
  • the corrugated fin 12 has a fin windward side end 12a extending to the windward side from the windward side end 11b of the flat tube 11, and a second drainage portion 18 is constituted by this extended portion.
  • the condensed water generated on the windward side of the corrugated fin 12 flows through the second drainage part 18 due to the inclination of the flat part 13 and moves in the direction of gravity. Drained to the bottom.
  • the inter-column gap is located in the portion located between the windward flat tube group 11 ⁇ / b> A and the leeward flat tube group 11 ⁇ / b> B in the heat exchanger depth direction. Since the 1st drainage part 17 which drains to 16 was provided, it has the following effects. That is, even if the corrugated fins 12 are long in the heat exchanger depth direction, the condensed water of the entire fins can be collected in the first drainage part 17 and drainage using the inter-row gaps 16 is possible. Can increase the sex.
  • the corrugated fins 12 are common two-row common fins between the two rows of flat tubes 11, compared to the case where the two-row divided fins are used, the fin insertion at the time of manufacturing is only once, thereby improving the productivity. .
  • the heat exchanger 1 when used as an evaporator under a low outside air temperature condition, condensed water adhering to the surface of the corrugated fins 12 may freeze and form frost. In particular, the portion on the windward side where the air collides first tends to frost.
  • the fin windward side of the corrugated fin 12 Concentration of frost near the end 12a can be avoided.
  • the direction of the inclination of the louver 15 is not restricted to this direction, All may be in the same orientation.
  • Embodiment 2 FIG. In the second embodiment, the inter-row gap 16 is provided with a drainage promoting body. Items not described in the second embodiment are the same as those in the first embodiment. The following description will focus on the differences of the second embodiment from the first embodiment.
  • FIG. 6 is a cross-sectional view of a heat exchanger according to Embodiment 2 of the present invention.
  • the smaller the inter-row gap 16 that is, the smaller the drainage path, the greater the surface tension of the condensed water and the condensate flowing from the first drainage portion 17 into the inter-row gap 16.
  • Water increases and drainage improves. Therefore, in the second embodiment, by arranging two rods 40 as drainage promotion bodies in the inter-row gap 16, the inter-row gap 16 communicates with the first drainage portion 17 and the other portions.
  • a part that communicates with the partition and the first drainage part 17 is a drainage path 41.
  • the rod 40 is a rod having a circular cross section in which a brazing material is clad (attached) to the outer periphery in advance, and is made of, for example, aluminum or an aluminum alloy, and is fixed to at least one of the corrugated fin 12 and the flat tube 11.
  • the same effects as those of the first embodiment can be obtained, and the rod 40 is disposed in the inter-column gap 16 to partition the inter-column gap 16. Since the small drainage channel 41 is configured, the following effects can be obtained. That is, in the first embodiment, the entire inter-row gap 16 is a drainage path, but in the second embodiment, the drainage path is reduced by disposing the rod 40, so that the condensation is performed compared to the case where the rod 40 is not provided.
  • action which guides water to the drainage path 41 improves. Moreover, since the rod 40 extends in the direction of gravity, the effect of guiding condensed water in the direction of gravity is improved. Therefore, drainage can be further improved.
  • the corrugated fin 12 and the flat tube 11 can be easily joined, and the manufacturability is also improved.
  • the rod 40 has a circular cross section.
  • the rod 40 is not limited thereto, and may have a rectangular cross section, an elliptical cross section, or the like.
  • the number of bars 40 is two here, but the number is not limited to this, and may be one or three or more. In short, by disposing the rods 40, it is only necessary to form a drainage path that separates the inter-row gap 16 and communicates with the first drainage portion 17 in the inter-row gap 16, and the number of the rods 40 is arbitrary. is there.
  • Embodiment 3 FIG.
  • the third embodiment is different from the second embodiment in the configuration of the drainage promotion body, and items not described in the third embodiment are the same as those in the first and second embodiments.
  • the following description will focus on the differences of the third embodiment from the first and second embodiments.
  • FIG. 7 is a cross-sectional view of a heat exchanger according to Embodiment 3 of the present invention.
  • a rectangular plate 50 curved in an arc shape in the short direction is inserted into the inter-column gap 16 of the flat tube 11.
  • Two plates 50 are disposed in the inter-row gaps 16 and are fixed to the corrugated fins 12 by brazing material previously attached to both side surfaces of the arc.
  • a drainage path 51 communicating with the first drainage unit 17 is formed separately in the inter-row gap 16.
  • the number of the plates 50 is two here, the number is not limited to this. In short, by disposing the plates 50, it is only necessary to form a drainage path that divides the gaps 16 between the rows and communicates with the first drainage portions 17 separately in the gaps 16 between the rows, and the number of the plates 50 is arbitrary. is there.
  • Embodiment 4 relates to the improvement of drainage at the leeward side end of the corrugated fin 12. Items not described in the fourth embodiment are the same as those in the first embodiment. Hereinafter, the difference between the fourth embodiment and the first embodiment will be mainly described.
  • FIG. 8 is a cross-sectional view of a heat exchanger according to Embodiment 4 of the present invention.
  • the fin leeward side end 12b extends further to the leeward side than the flat tube leeward side end 11c of the leeward side flat tube group 11B.
  • a third drainage part 19 is formed. The extension distance a of the third drainage part 19 is configured to be shorter than the extension distance b of the second drainage part 18.
  • the same effects as those of the first embodiment can be obtained, and when used as an evaporator, the condensed water that has flowed to the leeward side due to the flow of air travels along the third drainage section 19 and between the rows. It can drain in the direction of gravity from the gap 16a.
  • both the fin windward end 12a and the fin windward end 12b of the corrugated fin 12 are extended from the flat tube windward end 11b and the flat tube windward end 11c so that the second drainage portion 18 and the third drainage portion 19 are provided.
  • the distribution of the extension distance was set such that the extension distance a of the third drainage portion 19 was shorter than the extension distance b of the second drainage portion 18.
  • FIG. 9 is a refrigerant circuit diagram of an air-conditioning refrigeration apparatus according to Embodiment 5 of the present invention.
  • the air conditioning refrigeration apparatus includes a compressor 61, a condenser 62, an expansion device 63, and an evaporator 64, and includes a refrigerant circuit in which refrigerant circulates and a blower 65.
  • the condenser 62 and the evaporator 64 heat exchange between the air blown by the blower 65 rotated by the blower motor 66 and the refrigerant is performed.
  • coolant was shown as a working fluid, even if it uses other gas, a liquid, and a gas-liquid mixed fluid, there exists the same effect.
  • refrigerants and oils such as mineral oils, alkylbenzene oils, ester oils, ether oils, fluorine oils, etc.
  • refrigerants and oils such as mineral oils, alkylbenzene oils, ester oils, ether oils, fluorine oils, etc.
  • the effect can be achieved with any refrigeration oil, whether or not it melts.
  • the flat tube group has a two-row configuration of the windward flat tube group 11A and the leeward flat tube group 11B. However, it may have a plurality of rows. Also in this case, drainage performance can be secured by providing the first drainage portion 17 similar to the above in the corrugated fins 12 at the portion corresponding to the inter-row. Moreover, the 2nd drainage part 18 and the 3rd drainage part 19 are similarly applicable in a multi-row structure.
  • the embodiments have been described as different embodiments.
  • a heat exchanger and an air-conditioning refrigeration apparatus including the heat exchanger by appropriately combining the characteristic configurations of the embodiments are described. May be configured.
  • the second embodiment shown in FIG. 6 may be combined with the eighth embodiment shown in FIG. 8, and the third drainage unit 19 may be further provided in FIG.
  • the present invention can be used in a heat pump apparatus that is easy to manufacture, needs to improve heat exchange performance, and improve energy saving performance.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2014/069642 2014-07-25 2014-07-25 熱交換器およびこの熱交換器を備えた空調冷凍装置 WO2016013100A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2014/069642 WO2016013100A1 (ja) 2014-07-25 2014-07-25 熱交換器およびこの熱交換器を備えた空調冷凍装置
JP2016535601A JPWO2016013100A1 (ja) 2014-07-25 2014-07-25 熱交換器およびこの熱交換器を備えた空調冷凍装置
EP14898303.4A EP3173725A4 (de) 2014-07-25 2014-07-25 Wärmetauscher und klimaanlage sowie kühlvorrichtung mit wärmetauscher

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PCT/JP2014/069642 WO2016013100A1 (ja) 2014-07-25 2014-07-25 熱交換器およびこの熱交換器を備えた空調冷凍装置

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JP2017187243A (ja) * 2016-04-07 2017-10-12 ダイキン工業株式会社 室内熱交換器
WO2018078800A1 (ja) * 2016-10-28 2018-05-03 三菱電機株式会社 熱交換器及び冷凍サイクル装置
WO2019167839A1 (ja) * 2018-03-01 2019-09-06 ダイキン工業株式会社 熱交換器
JP2020034184A (ja) * 2018-08-27 2020-03-05 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 熱交換器および空気調和機
CN114641663A (zh) * 2019-11-11 2022-06-17 三菱电机株式会社 热交换器及制冷循环装置
WO2022249281A1 (ja) * 2021-05-25 2022-12-01 三菱電機株式会社 熱交換器及び空気調和装置
JP7305085B1 (ja) * 2022-04-12 2023-07-07 三菱電機株式会社 熱交換器および冷凍サイクル装置

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DE102018214871A1 (de) * 2018-08-31 2020-03-05 Mahle International Gmbh Wärmepumpenheizer
EP4365533A4 (de) * 2021-06-29 2024-08-21 Mitsubishi Electric Corp Wärmetauscher, kältekreislaufvorrichtung und verfahren zur herstellung eines wärmetauschers

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