EP0962736A2 - Gewellte Rippe für Verdampfer mit verbesserter Kondensatabführung - Google Patents

Gewellte Rippe für Verdampfer mit verbesserter Kondensatabführung Download PDF

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Publication number
EP0962736A2
EP0962736A2 EP99201397A EP99201397A EP0962736A2 EP 0962736 A2 EP0962736 A2 EP 0962736A2 EP 99201397 A EP99201397 A EP 99201397A EP 99201397 A EP99201397 A EP 99201397A EP 0962736 A2 EP0962736 A2 EP 0962736A2
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EP
European Patent Office
Prior art keywords
fin
louver
channels
walls
pairs
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP99201397A
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English (en)
French (fr)
Other versions
EP0962736A3 (de
Inventor
Steven R. Falta
Mohinder Singh Bhatti
Shrikant Mukund Joshi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP0962736A2 publication Critical patent/EP0962736A2/de
Publication of EP0962736A3 publication Critical patent/EP0962736A3/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
    • 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

Definitions

  • This invention relates to condensation formation in evaporators in general, and specifically to a novel feature in the corrugated heat transfer fins which improves condensate drainage.
  • Air conditioning system evaporators since they blow warm, humid air over cold metal heat transfer surfaces, are uniquely subject to the condensation of water films on those surfaces. While this is a plus in terms of dehumidifying the air, it is a detriment in terms of several possible effects on the evaporator and its efficient operation, especially in the case of automotive air conditioning system evaporators.
  • Surface water can accumulate until it is actually blown out of the rear face of the evaporator core, the so called “spitting" phenomenon. This is generally prevented with screens on the rear face to retard the water, but this adds cost and represents an additional air flow obstruction.
  • Wet cores are also more subject to microbial growth and odor, which can generally only be prevented with the addition of expensive anti microbial coatings.
  • a more efficient evaporator core design incorporates wide, flat flow tubes, formed either as runs of a continuous, serpentine tube, or as individual stamped plates brazed together in pairs. In either case, the flow tubes are oriented with their flat outer surfaces generally vertical, again, so that condensed water can drain easily downwardly.
  • the heat transfer fins used with such designs are generally corrugated fins.
  • the typical corrugated heat transfer fin is a series of folded fin walls, which diverge from a sharply angled "V" shaped crest.
  • the outer, convex surfaces of the crests are brazed to the vertical, flat flow tube surfaces.
  • the inner, concave channels formed by the diverging fin walls are horizontally oriented, aligned with the direction of air flow.
  • corrugated fins are not conducive to condensate drainage.
  • the fin walls are oriented generally horizontally, and run almost the full width of the flat flow tube surfaces to which they are brazed. Without more, the horizontal fin walls would totally block downward condensate drainage along the vertical flow tube surfaces, as well as blocking drainage from between the fin walls themselves.
  • the corrugated fin walls typically have openings therethrough in the form of louvers which, though intended for other purposes, also coincidentally provide a downward drainage path.
  • an automotive air conditioning system evaporator of the general type described above is indicated generally at 10.
  • the evaporator core is built up from a series of vertically oriented, regularly spaced pairs of parallel flow tubes 12, through which relatively cold refrigerant vapor is circulated in a U shaped flow pattern.
  • a large corrugated fin is brazed between the opposed pairs of the flow tubes 12.
  • Each fin 14 consists of a series of integrally folded pairs of divergent, rectangular fin walls 16.
  • Basic dimensions of the fin walls 16 include a length of approximately fifty millimeters, and width of about ten millimeters, and a wall thickness of around 1 millimeter.
  • Each pair of fin walls 16 are joined alternately at a sharply angled V, shown at ⁇ , with an internal angle of 15 degrees at most, and potentially less than that, since the fin walls 16 may be almost parallel to one another in the core, in order to achieve high fin densities.
  • the external, convex crests of the fin 14 are brazed to the surfaces of flow tubes 12, making a much wider external angle that is, potentially, almost 90 degrees.
  • the internal surface juncture of the divergent pairs of fin walls 16 is radiused at approximately a millimeter or less, rather than making a very sharp V point. Therefore, even if the interior angle ⁇ is essentially zero, there is still a tight, concave internal channel formed between the interior surfaces of the fin walls 16, with consequences described below.
  • Each fin wall 16 is also pierced by four (or some even number of) rectangular banks of regularly spaced, conventional louvers 18, spaced apart by approximately 2 millimeters.
  • Each bank 18 consists of a regular pattern of individual louvers (ten to twenty total in each bank 18) bent out of the plane of the fin wall 16. The angle of each individual louver relative to the fin wall 16 out of which it is bent is typically about 45 degrees, and the direction of the louver angle, positive or negative, alternates from one bank of louvers 18 to the next.
  • the basic purpose of the louver banks 18, as is well known to those skilled in the art, is to break up the flow of air over the fin wall, and prevent the formation of efficiency reducing boundary layers that could otherwise occur.
  • each louver regardless of its dimensions, does create a long, thin opening through the fin wall 16, because of the way it is formed.
  • Each bank of louvers 18 has a width of approximately 7 mm, so that the ends of the individual louver openings approach very near the "bottom" of the channels, leaving an uncut fin wall width ⁇ of only approximately one to one and a half millimeter.
  • louver length would be maximized, (and ⁇ consequently minimized), within the constraints of manufacture, so as to optimized air flow. This fact operates to help drain condensate in a fashion described in more detail next.
  • the surface tension force is sufficient to retain the film F against being blown or "spit" off of the trailing fin wall edge, at least at this initial stage.
  • the film thickness initially reaches a greatest width W, as shown in Figure 7, of approximately three millimeters, and is also thick enough to bridge and fill the channel completely out to that width W.
  • the film F is therefore wide enough to overlap with the ends of the louver openings in the louver banks 18.
  • the surface tension force predominates over the gravity force tending to pull it vertically down and through the open louver banks 18, so that drainage is minimal. The film F will continue to thicken.
  • condensed water collects in a much wider "corner,” that is, the external angle formed between the exterior of the fin wall 16 and the external surface of the flow tube 12. Film surface tension is much less effective in the wider corner, and condensed water can drain much more easily through the louver banks 18, without collecting and adhering as it does in the internal fin channels.
  • the surface film F becomes both wider and thicker, with the width W growing eventually to a "critical" width of approximately six millimeters.
  • the film F becomes less stable, and the surface tension forces no longer can prevent drainage down through the open banks of louvers 18.
  • Water retained in the channels begins to drain down successively through successive fin walls 16, shrinking the film width, and eventually draining out from the bottom of the core.
  • the film width and thickness again expand to the critical width, however, clogging the narrow channels formed between the diverging fin walls 16, reducing air flow and increasing air pressure drop.
  • the process of instability, draining, shrinkage, and re expansion begins again, in a repeating cycle.
  • the air flow blocking effect of the water films alone reduces thermal efficiency.
  • the water film F also tends to insulate the metal conduction surfaces form the air flow, reducing conduction and convection efficiency.
  • An improved corrugated heat conduction fin in accordance with the subject invention is characterised by the features specified in Claim 1.
  • the subject invention takes a very different design approach to enhancing condensate drainage. No vertical troughs are formed in the flow tube surface. No change is made to the basic dimensions of the fin or fin walls, or to the banks of louvers. A very slight change is made to the areas of the fin walls located between the louver banks. This area is altered in such a way that the surface tension forces cannot create a film. Consequently, the typical long and continuous film is broken up into a series of shorter films, each located directly over a respective louver bank, but with no film forming in the area between louver banks. These individual, discontinuous films, for reasons not perfectly understood, are less stable, and therefore drain more frequently and efficiently down through the louver banks over which they form. The critical film width is significantly less, as is the air pressure drop across the core. Efficiency is conversely enhanced.
  • the fin wall areas between louver banks are rendered incapable of supporting a water film by the very simple expedient of piercing through the fin walls at their channel forming juncture with an aligned pair of small, semi circular notches.
  • Water film cannot form on a surface that does not exist, so the continuos film is broken at each notch, between each bank of louvers.
  • the aligned notches in consecutive fins would appear to effectively form vertical drainage troughs opening through the fin channels, drainage does not, surprisingly, appear to take place through the aligned notches to any significant extent. Instead, what apparently happens is that drainage still occurs primarily through the louver banks, but with the critical thickness of the various individual films greatly reduced.
  • Two possible embodiments of the notches are disclosed, with the same basic shape and effect, but manufactured differently.
  • FIG. 20 a first embodiment of an improved fin made according to the invention is indicated generally at 20.
  • Fin 20 has essentially every feature that the conventional fin 14 described above has, and with the same dimensions.
  • Fin walls 22 identical to fin walls 16 diverge from relatively sharp, integral internal channels with the same small included angle and radius.
  • Fin wall width and length are the same, and the louver banks 24 have the same number, size, spacing, orientation, and dimensions for the individual louvers. This is significant, as the louver banks 24 have a shape and size intended to optimize air flow, not to optimize condensate drainage, even though they do coincidentally provide condensate drainage out of the channels.
  • louver banks themselves changed so as to enhance condensate drainage, that would likely involve an increase in the louver openings' width, louver angles or the like, which could negatively affect their primary function of air flow enhancement.
  • the subject invention instead alters a different area of the fin in a way that cooperates with conventional louver banks 24 to enhance condensate drainage.
  • a localized void in the form of an aligned pair of generally semi circular notches 26 is cut completely out. In terms of manufacturing, this would most conveniently be done concurrently with the cutting of the louver banks 24, and a feature to do so would be incorporated within the same cutting and forming tool.
  • one notch between each adjacent pair of four louver banks 24 amounts to three notches 26 total.
  • the radius of notch 26 is approximately one millimeter, making it wide enough to take up much of the unused area between adjacent louver banks 24, and deep enough to exceed ⁇ as defined above.
  • the notches 26, when viewed from the perspective of Figure 10, would all be vertically aligned, taking on the aspect of a vertical trough. Surprisingly, however, the aligned notches 26 do not act as, and are not intended to act as, open vertical drainage paths, as is described next.
  • an evaporator incorporating fin 20 would be identical to evaporator 10, with the same flow tubes 12, would be assembled in the same way, and would also be operated at all the same parameters, in terms of refrigerant flow rate, air flow rate and direction, and temperature. Water would condense on the internal channel forming surfaces of the fin walls 22, just as with the fin walls 16, but with a very significant difference.
  • Each of the separate films F1, F2 and F3 is located almost entirely over a respective louver bank 24, and displaced somewhat in the direction of air flow, which is downward on the page, as shown by the arrows.
  • surface tension forces still predominate.
  • the three films have grown wide enough to just begin overlapping with the ends of the openings of the individual louvers, but have not yet become unstable enough to begin to drain through.
  • the film width, indicated at W' is measured in the same direction as the width W described above, and the film thickness, by definition, runs from inner surface to inner surface of the fin walls 22 between which the film is drawn and formed.
  • the critical width W' is closer here to the initial film width, reaching approximately only three to three and a half millimeters, enough to overlap with the louver banks 24, but significantly narrower than that for the single film F on fin 14 noted above.
  • critical width it is meant that the films have become unstable and have begun to drain down through the louver banks 24 and shrink, before re expanding in a continuing cycle.
  • the net drainage rate is thus greater than that achieved with conventional fins, and the significantly smaller critical film width is very beneficial in terms of allowing air to flow more freely through the fins 20, and the air pressure drop has been observed to be almost twenty five percent less in tests.
  • the trailing ends of the films F1, F2 and F3 "crowd up" to the leading edges of the notches 26, but have not been observed to be spilling any significant amounts of water over those edges and down through the notches 26.
  • the notches 26 would not be able to drain a great deal water out of the individual films anyway, since they do not overlap with them, and do not constitute a significant amount of open area, as compared to all the pre existing louver openings. Instead, the notches 26 assist the pre existing ability of the louver banks 24 to act as drains.
  • FIG. 28 An alternate embodiment of the invention, designated generally at 28, is illustrated in Figures 18 and 19. It works exactly the same way, and has the same basic dimensions as fin 20, but has some potential manufacturing and structural advantages.
  • Fin 28 has identical fin walls 30 and louver banks 32, as compared to fin 20. However, instead of cutting out voids in the form of aligned pairs of semi circular notches 26 through each fin wall 30, a flap of wall material is lanced inwardly from and out of the crest, forming a generally vertical strut 38 in the internal channel and a single window 36 behind the strut 38.
  • the single window 36 removes fin wall surface area from both fin walls 30, between the louver banks 32, effectively creating a pair of aligned notches in each pair of diverging fin walls 30 simultaneously.
  • the vertical strut 38 acts to brace and strengthen the juncture of the fin walls 30 at the very point where the window 36 is formed. Being thin and basically aligned with the air flow, the struts 38 would not themselves significantly block air flow through the channels, while the windows 36 would break up the surface film of water in the same fashion as the notches 26.
  • Alternate means might include localized hydrophobic coatings, surface roughenings, or the like, applied to the same area as the notches disclosed above, in order to substantially reduce the ability of the surface to support and create a water film, but without removing the surface completely.
  • a void represents the ultimate in reduction of surface tension potential, since it has no surface at all.
  • Voids with a shape other than the semi circular notch 26 could be used, such as square or triangular, although a semi circular is generally the easiest to punch out. Therefore, it will be understood that it is not intended to limit the invention to just the embodiments disclosed.

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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)
EP99201397A 1998-06-01 1999-05-04 Gewellte Rippe für Verdampfer mit verbesserter Kondensatabführung Withdrawn EP0962736A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US8854498A 1998-06-01 1998-06-01
US88544 1998-06-01

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EP0962736A2 true EP0962736A2 (de) 1999-12-08
EP0962736A3 EP0962736A3 (de) 2000-08-16

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1111318A1 (de) * 1999-12-21 2001-06-27 Delphi Technologies, Inc. Verdampfer mit verbessertem Kondensatablauf
EP1522813A1 (de) * 2003-10-09 2005-04-13 Behr Industrietechnik GmbH & Co. KG Vorrichtung zum Austausch von Wärme und Verfahren zur Herstellung einer derartigen Vorrichtung
WO2007009220A1 (en) * 2005-07-18 2007-01-25 Dana Canada Corporation Heat exchangers with corrugated heat exchange elements of improved strength
EP2478318A1 (de) * 2009-09-16 2012-07-25 Carrier Corporation Gerippte oberflächenarchitektur mit freiem abfluss für einen wärmetauscher
CN102893117A (zh) * 2010-05-24 2013-01-23 三电有限公司 热交换器
WO2012027098A3 (en) * 2010-08-24 2013-01-24 Carrier Corporation A heatexchanger with a microchannel fin
JP2013082353A (ja) * 2011-10-11 2013-05-09 Honda Motor Co Ltd 車両用空気調和装置
US9689618B2 (en) * 2010-07-20 2017-06-27 Sharp Kabushiki Kaisha Heat exchanger and air conditioner equipped therewith with water guiding condensate notches and a linear member
CN108131980A (zh) * 2016-12-01 2018-06-08 摩丁制造公司 用于热交换器的翅片及其制造方法
US10247481B2 (en) 2013-01-28 2019-04-02 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
US10539374B2 (en) 2014-04-16 2020-01-21 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Fin and bending type heat exchanger having the fin
CN115183484A (zh) * 2022-09-13 2022-10-14 杭州医维之星医疗技术有限公司 置于室内的设备用二级冷却冷气机及电气设备
US12078431B2 (en) 2020-10-23 2024-09-03 Carrier Corporation Microchannel heat exchanger for a furnace

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* Cited by examiner, † Cited by third party
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KR100348710B1 (ko) * 2000-04-17 2002-08-13 한국기계연구원 모듈형 다중유로 편평관 증발기
KR100420515B1 (ko) * 2001-06-21 2004-03-02 엘지전자 주식회사 열교환기
KR20040017920A (ko) * 2002-08-22 2004-03-02 엘지전자 주식회사 열교환기의 응축수 배출장치
US8307669B2 (en) 2007-02-27 2012-11-13 Carrier Corporation Multi-channel flat tube evaporator with improved condensate drainage

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US4353224A (en) 1980-10-16 1982-10-12 Nippondenso Co., Ltd. Evaporator
US4621685A (en) 1983-09-12 1986-11-11 Diesel Kiki Co., Ltd. Heat exchanger comprising condensed moisture drainage means
US4926932A (en) 1987-08-09 1990-05-22 Nippondenso Co., Ltd. Plate type heat exchanger
US4966230A (en) 1989-01-13 1990-10-30 Modine Manufacturing Co. Serpentine fin, round tube heat exchanger

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US4353224A (en) 1980-10-16 1982-10-12 Nippondenso Co., Ltd. Evaporator
US4621685A (en) 1983-09-12 1986-11-11 Diesel Kiki Co., Ltd. Heat exchanger comprising condensed moisture drainage means
US4926932A (en) 1987-08-09 1990-05-22 Nippondenso Co., Ltd. Plate type heat exchanger
US4966230A (en) 1989-01-13 1990-10-30 Modine Manufacturing Co. Serpentine fin, round tube heat exchanger

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6439300B1 (en) 1999-12-21 2002-08-27 Delphi Technologies, Inc. Evaporator with enhanced condensate drainage
EP1111318A1 (de) * 1999-12-21 2001-06-27 Delphi Technologies, Inc. Verdampfer mit verbessertem Kondensatablauf
EP1522813A1 (de) * 2003-10-09 2005-04-13 Behr Industrietechnik GmbH & Co. KG Vorrichtung zum Austausch von Wärme und Verfahren zur Herstellung einer derartigen Vorrichtung
WO2007009220A1 (en) * 2005-07-18 2007-01-25 Dana Canada Corporation Heat exchangers with corrugated heat exchange elements of improved strength
EP2478318A4 (de) * 2009-09-16 2014-05-28 Carrier Corp Gerippte oberflächenarchitektur mit freiem abfluss für einen wärmetauscher
EP2478318A1 (de) * 2009-09-16 2012-07-25 Carrier Corporation Gerippte oberflächenarchitektur mit freiem abfluss für einen wärmetauscher
CN102893117A (zh) * 2010-05-24 2013-01-23 三电有限公司 热交换器
CN102893117B (zh) * 2010-05-24 2014-11-26 三电有限公司 热交换器
US9689618B2 (en) * 2010-07-20 2017-06-27 Sharp Kabushiki Kaisha Heat exchanger and air conditioner equipped therewith with water guiding condensate notches and a linear member
WO2012027098A3 (en) * 2010-08-24 2013-01-24 Carrier Corporation A heatexchanger with a microchannel fin
JP2013082353A (ja) * 2011-10-11 2013-05-09 Honda Motor Co Ltd 車両用空気調和装置
US10247481B2 (en) 2013-01-28 2019-04-02 Carrier Corporation Multiple tube bank heat exchange unit with manifold assembly
US10337799B2 (en) 2013-11-25 2019-07-02 Carrier Corporation Dual duty microchannel heat exchanger
US10539374B2 (en) 2014-04-16 2020-01-21 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Fin and bending type heat exchanger having the fin
CN108131980A (zh) * 2016-12-01 2018-06-08 摩丁制造公司 用于热交换器的翅片及其制造方法
US10436156B2 (en) 2016-12-01 2019-10-08 Modine Manufacturing Company Air fin for a heat exchanger, and method of making the same
CN108131980B (zh) * 2016-12-01 2020-09-08 摩丁制造公司 用于热交换器的翅片及其制造方法
US11162742B2 (en) 2016-12-01 2021-11-02 Modine Manufacturing Company Air fin for a heat exchanger
US12078431B2 (en) 2020-10-23 2024-09-03 Carrier Corporation Microchannel heat exchanger for a furnace
CN115183484A (zh) * 2022-09-13 2022-10-14 杭州医维之星医疗技术有限公司 置于室内的设备用二级冷却冷气机及电气设备
CN115183484B (zh) * 2022-09-13 2022-11-18 杭州医维之星医疗技术有限公司 置于室内的设备用二级冷却冷气机及电气设备

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Publication number Publication date
JP2000028228A (ja) 2000-01-28
EP0962736A3 (de) 2000-08-16

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