US3916989A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US3916989A
US3916989A US500683A US50068374A US3916989A US 3916989 A US3916989 A US 3916989A US 500683 A US500683 A US 500683A US 50068374 A US50068374 A US 50068374A US 3916989 A US3916989 A US 3916989A
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United States
Prior art keywords
louvers
tubes
rows
fins
heat conductive
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Expired - Lifetime
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US500683A
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English (en)
Inventor
Fumio Harada
Takehiko Yanagida
Kunio Fujie
Hajime Futawatari
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Hitachi Ltd
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Hitachi Ltd
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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
    • 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
    • F28F1/32—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 having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
    • Y10S165/50—Side-by-side conduits with fins
    • Y10S165/501—Plate fins penetrated by plural conduits
    • Y10S165/502—Lanced

Definitions

  • ABSTRACT A crossed fin-and-tube type heat exchanger comprising a plurality of fins arranged in juxtaposition to each other, each said fin having a suitable surface area, and a plurality of heat conductive tubes passed through and securely fixed to said fins such that the heat exchanging medium in said heat conductive tubes and another heat exchanging medium (air) passing between said fins will perform heat exchange through said heat conductive tubes and said fins.
  • Each of said fins is provided with a plurality of rectangular slits formed by raising up the cut edges such that they are all transverse to the air stream flowing between the fins sinously along the outer peripheries of said heat conductive tubes, the raised-up portion of each said slit forming a ridge having a wall continuous to the upright at both ends of the slit and parallel to the fins.
  • FIG. 1 A first figure.
  • FIG. 1 A first figure.
  • FIG. 1 A first figure.
  • HEAT EXCHANGER This invention relates to a crossed fin-and-tube type heat exchanger comprising a plurality of slitted fins arranged in juxtaposition to each other and a plurality of heat conductive tubes passed through said juxtaposed fins in securely fixed relation to each other.
  • a plurality of fins made of aluminium material and having a suitable surface area are arranged in juxtaposition at a pitch of several mm, and a plurality of heat conductive tubes such as for example copper tubes are passed through said fins, with the joined portions being securely fixed by expanding the tubes or by using other means:
  • said heat conductive tubes are connected by U-shaped bent pipes on the outside of the fins so as to form a suitable number of heat conductive tube passages which extend meanderingly.
  • each of said heat conductive tubes is disposed a nichrome wire or passed a heat exchanging medium such a cold water, hot water or coolant, while another heat exchanging medium, represented by air, is passed between and parallel to the fins on the outside of the tubes so as to effect heat exchange between the heat exchanging medium in said tubes and the another heat exchanging medium such as air flowing outside of said tubes through the media of tube walls and fins.
  • the heat exchanging medium in the tubes may be either higher or lower in temperature than the one passing between the fins, depending on circumstances.
  • the heat exchanging operation is briefly described by taking an instance where the heat exchanging medium in the tubes is higher in temperature than that passing between the fins. Heat of the heat exchanging medium in the tubes is transferred to the heat conductive tubes and then further transmitted therefrom in a radially diffused form to the plurality of fins which are closely attached to said tubes, so as perform heat exchange between said medium in the tubed and air passing along the fins.
  • Heat transmittability of such heat exchanger is greatly affected by heat transfer between the fin surfaces and the air passing therealong.
  • the air stream flowing between the flat fins forms a boundary layer of the air stream, and such boundary layer grows thicker as the distance from the fin end increases (that is, said boundary layer is thicker in the downstream side of the fin), while the similar boundary layer which develops on the opposed fin surface joins with the first-said layer at a position slightly downstream of the fin end. Heat transfer in this boundary layer is excessively lower than that in the turbulent area.
  • the air stream flowing between the fins is disturbed after passing the heat conductive tubes to break the boundary layer, and a stagnation is produced behind each heat conductive tube. In this portion, little heat transfer is effected due to small temperature difference between the fin surfaces and air.
  • the most effective measure for improving the rate of heat transfer between the fins and the air stream flowing between the fins is to prevent formation of said boundary layers.
  • the present invention is designed to provide an improved crossed fin-tube type heat exchanger wherein generation of such boundary layers is minimized to improve the heat transfer rate.
  • An object of the present invention is to realize improvement of the heat transfer rate in the heat exchangers of the type discussed by providing in each fin a plurality of rectangular slits arranged transversely to the flow lines of air passing between the fins, said slits being formed of raised-up portions of the fins, providing louvers designed to intercept said air flow lines over a wide range to prevent formation of the boundary layers.
  • Another object of the invention is to lower resistance of air flow passing between the fins by arranging the upright walls of the louvers parallel to the air flow lines.
  • Another object of the invention is to provide an arrangement in which said slitsare formed along the flow lines of heat which is transferred from the heat conductive tubes to the fins so that said slits will not prevent transfer of heat from said tubes to said fins.
  • Still another object of the invention is to form the slits by stamping louvers in the fins to facilitate manufacture of the heat exchanger.
  • FIG. 1 is a front view of a known type of crossed fintube heat exchanger
  • FIG. 2 is a front view of a flat fin in the heat exchanger of FIG. 1;
  • FIG. 3 is a sectional view taken along the line Ill-III and in the direction of arrows of FIG. 2;
  • FIG. 4 is a front view of the conventional corrugate fins
  • FIG. 5 is a sectional view taken along the line VV and in the direction of arrows of FIG. 4;
  • FIG. 6 is a partial front view of a conventional slitted fin
  • FIG. 7 is a sectional view taken along the line VII- --VII and in the direction of arrows of FIG. 6;
  • FIG. 8 is a front view of a fin used in a slit-formed crossed fin-tube type heat exchanger according to the embodiment of the present invention.
  • FIG. 9 is a partial sectional view taken along the line IXIX and in the direction of arrows of FIG. 8;
  • FIG. 19 is a partial sectional view taken along the air flow line X-X of FIG. 8;
  • FIG. 1 l is a drawing showing the isothermal lines and heat flow lines on the fin surface
  • FIG. 12 to 15 are front views showing other embodiments of the present invention.
  • FIG. 16 is a perspective view with parts shown in section, of a crossed fin-tube type heat exchanger provided with the fins shown in FIG. 8.
  • reference numeral 1 indicates a plurality of fins made from aluminium plates or the like, each said fin having a suitable surface area and formed with a plurality of holes 2 for inserting the heat conductive tubes.
  • These fins l are arranged in juxtaposition to each other at a pitch of several mm (usually 2 to 5 mm), and a plurality of heat conductive tubes 3 are passed through said holes in the respective fins. Said tubes 3 and fins l are secured to each other by expanding the tubes or by using other means.
  • each of said heat conductive tubes 3 is disposed nichrome wire or passed a heat exchanging medium such a cold water, hot water or coolant (freon coolant), while another heat exchanging medium represented by air is passed between and parallel to the 3 fins l on the outside of the heat conductive tubes so that the heat exchanging medium in said tubes 3 and another heat exchanging medium such as air will perform heat exchange through the tube walls and fins.
  • a heat exchanging medium such as cold water, hot water or coolant (freon coolant)
  • another heat exchanging medium represented by air is passed between and parallel to the 3 fins l on the outside of the heat conductive tubes so that the heat exchanging medium in said tubes 3 and another heat exchanging medium such as air will perform heat exchange through the tube walls and fins.
  • Each said boundary layer 4 grows thicker as the distance from the fin ends 1 toward the downstream side increases as shown in the figure, and another boundary layer which developed on the opposed fin surface is joined with the ajoining boundary layer at a position slightly downstream of the fin ends 1, so that heat transmissability in the area downstream of said position is excessively lowered.
  • FIGS. 4 and 5 a part of a crossed fin-tube heat exchanger using such corrugated (or angular) fins 6.
  • FIGS. 4 and 5 a part of a crossed fin-tube heat exchanger using such corrugated (or angular) fins 6.
  • the air flow which has passed the crest 6' of undulation tends to separate from the fin surfaces giving rise to swirls as noted from FIG. 5, and these swirls prevent formation of the boundary layers improving the heat transfer rate.
  • the air passages between the fins bend in undulation, the passing air flow suffers greater loss of collision, resulting in excessively enlarged air flow resistance. It is therefore required to use an air blower of large opacity, and also noise is increased.
  • the present invention is intended to provide a high-performance crossed fin-andtube type heat exchanger with slitted fins, which has been realized by making improvements over various defects of the conventional devices such as above-mentioned.
  • a plurality of slits are formed in each fin such that said slits will be always transverse to the direction of air flow, thereby to cut off or intercept the air flow lines over a wide range of check generation and development of the boundary layers.
  • the raised-up walls of the portions forming the slits are formed parallel to the air flow line so as to minimize air flow resistance and not to hinder heat transmission by intercepting the flow lines of heat transmitted from the heat conductive tubes to the respective fins.
  • FIG. 8 is a front view of a fin used in a crossed fintube heat exchanger according to one embodiment of the present invention
  • FIG. 9 is an enlarged sectional view as taken along the line [XIX and in the direction of arrows of FIG. 8. It will be seen that there are provided in each fin 11 a plurality of holes 12 for inserting the heat conductive tubes 13, each said hole 12 having formed at its edge a wall raised up in one direction for increased securement with the tubes 13 and for regulating the fin pitch. Formed substantially radially around each said hole 12 are the rectangular slits 15.
  • each said slit 15 At both sides in the longitudinal direction of each said slit 15 are raised up portions of the fin to form upright walls 15 as well as a ridge having a wall 15" continuous to said upright walls 15" and parallel to the fin 11 as shown in FIG. 9, thereby forming louvers in the fin l l.
  • Said fins 11 are provided in plurality in juxtaposed relation to each other, and heat conductive tubes 13 are inserted in the holes 12 in each said fin.
  • Said tubes 13 and fins l l are secured to each other by enlarging the tubes 13 after the latter have been fitted in the respective holes 1 2.
  • the width of each said slit 15 is several mm (for instance 2.5 mm) and the length thereof is for instance IO plus mm.
  • each said upright walls 15" is as close to the hole edge as possible.
  • These slits extend toward the outer periphery of each hole 12, but those which are opposed at the ends to the outer edge of the fin should be of a length that provides a suitable space 17 between said ends and the outer edge of the fin, while those which are directed toward the adjoining hole have formed at their ends the upright walls 15" similar to the above-siad, the height of such upright walls being preferably about one-half of the distance between the adjoining fins.
  • FIGS. 8 and 10 shows a section of a fin assembly as it was out along the air flow line XX and developed. As shown in FIGS. 8 and 10, the same air stream passes plural times through the slits provided in plural number around each heat conductive tube 13, and any laminar flow boundary layer produced by the air flow passing between the fins is cut or intercepted as many times as the number of slits through which the air flow passes, so that no boundary layer of air flow is permitted to develop.
  • the fin ends (including the front ends 15a of the ridged and front edges 11a of the slits formed by cutting the ridges) are formed twice as many in number as the slits to provide many (twice as many) high-heat-transfer-rate areas which almost no boundary layer is present, thereby greatly improving the heat transfer rate as a whole.
  • the boundary layers 18, 19 20 produced downstream of the ridge front ends 15a and the slit front edges 11a are left in an underdeveloped state, and also coincidence of the boundary layers on the opposed upper and lower fin surfaces as observed in the conventional devices such as shown in FIG. 3 is obstructed to markedly improve the heat transfer rate in these sections.
  • any of the louvered slits l5 slits with raised-up portions
  • the upright walls of the louvers stand parallel to the air flow X-X, so that air flow is minimally hindered to minimize air resistance.
  • air resistance is even more lessened if said upright walls 15" are positioned within the laminar flow boundary layers created on the surfaces of the upright walls 14 at the hole edges.
  • Such arrangement of the slits 15 also proves extremely advantageous in respect of heat transfer from the heat conductive tubes 13 to the fins.
  • FIG. 11 shows an example of temperature distribution on the fin surface.
  • numeral 12 indicates the holes into which the heat conductive tubes are to be inserted, and the solid-line curves and the lines surrounding the holes 12 are the isothermal lines.
  • heat of the heat conductive tubes 13 is first transmitted to the rise-up walls 14 at the hole edges secured to said tubes and then is further transferred along the broken lines (heat flow lines) 21 which cross the isothermal lines at right angles.
  • the slits are provided so as not to obstruct the heat transfer, they will not intercept the heat flow lines, that is, they are formed substantially radially around each heat conductive tube.
  • FIGS. 12 to 15 show other embodiments of the present invention where particular consideration is paid to the effective arrangement of the slits to reduce the number of slits for facilitating manufacture.
  • FIG. 12 shows an example where two rows of heat conductive tubes are provided in each fin.
  • FIG. 13 shows another example where the heat conductive tubes are provided in three rows 25, 26 and 27. It is of course possible and most preferable for efficient heat transfer to provide the louvered slits radially around the heat conductive tubes over the entire span of each fin 30 as in the embodiment of FIG. 8, but in this example, the number of slits is reduced for the same reason as said above. That is, no slit is provided behind each tube as turbulence can occur at such part as in the case of the example of FIG. 12, and for the rows of tubes 25 and 27 on both sides, the slits 28 are formed radially within the range of about 180 only on the side facing the fin edge, while for the central row of tubes 26, the radial slits 29 are provided only in the direction of the tube line. It is possible with this arrangement to obtain the desired effect in spite of the reduced number of slits.
  • FIG. 14 shows a modification of the preceding example where the heat conductive tubes are provided in three rows, 31, 32 and 33.
  • the louvered slits 34 are provided radially within the range of about 60 toward the fin periphery, and similar-slits 35 and 36 are also provided in the areas between the tube rows 31 and 32 and between rows 32 and 33.
  • FIG. 15 shows still another modification of the embodiment where the heat conductive tubes are provided in three rows 37, 38 and 39.
  • the louvered slits 40 which are curved along the heat flow lines shown in the embodiment of FIG. 11 are provided within the range of about 60 toward the fin periphery, and for the tubes in the central row, the radial slits 41 are provided only in the direction of the tube row.
  • the curved slits 40 are of course positioned transverse to the air flow lines EE' and the upright walls 40' at both ends of each slit are formed parallel to said air flow lines. The desired effect can be also obtained with this arrangement of slits.
  • substantially radial refers not only to the arrangement of slits which run radially from the center of each heat conductive tube but also to the arrangement of slits which radiate eccentrically from the outer periphery of each tube and also a curved or otherwise deformed arrangement along the heat flow line as shown in FIG. 15.
  • slits which radiate from the entire peripheral range of each tube, this is, in all directions from the tube, as well as the arrangement of slits which are provided radially within the range of l80 as in the embodiment of FIG. 13 or within the range of 60 as in the embodiments of FIGS. 14 and 15, and also the arrangement of slits radiated only in a limited direction as for example only in the diametrical direction as in the embodiment of FIG. 13. All of these modified arrangements of slits are embraced within the scope of the present invention.
  • the slits are fonned by raising up the cut portions in each fin to form louvers
  • the fin end portions where almost no boundary layer is present such as front edges 11a of slit openings and slit front ends 15a as shown in FIG. 10, such portions being formed twice as many as the slits in the foregoing embodiments
  • the heat transfer area is reduced accordingly, so that the heat transfer rate is slightly lowered as compared with the embodiments formed with the slits with the raised-up portions, but air flow resistance is reduced and also the manufacture of the fins is greatly simplified.
  • a crossed fin-and-tube type heat exchanger in which a plurality of slits having the raised-up portions are provided in each fin such that all of such slits will be positioned transverse to the flow of air passing sinously along the outer periphery of each heat conductive tube, raised-up portions of said slits forming the ridges having walls continuous to the upright side walls of the slit louvers and parallel to the fins, so that said slits intercept the air flow lines as well as the laminar flow boundary layers over a wise range corresponding to the slit length.
  • each fin is provided with a great many slit end portions where no boundary layer is present and hence the heat transfer rate is high, thus greatly improving heat transfer efficiency of the heat exchanger.
  • the erect walls at both ends in the longitudinal direction of each slit stay parallel to the sinous air flow so that air flow resistance is markedly reduced as compared with the conventional slitted fins.
  • the slits are arranged radially relative to each heat conductive tube, they are positioned substantially parallel to the heat flow lines in the fins to even more improve heat transfer efficiency of the heat exchanger without hindering heat transfer of the fins.
  • the slits are formed by stamping or punching, there can be obtained a heat exchanger in which air flow resistance is extremely low as the slits produce no air resistance as in the case of flat fins and in which, although the heat transfer rate is slightly lowered as compared with the fins formed with louvered slits, generation and development of the laminar flow boundary layers are greatly suppressed and also the manufacture is simplified. 1
  • a crossed fin-and-tube type heat exchanger including a plurality of juxtaposed fins each having a suitable surface area and a plurality of heat conductive tubes passed through and securely fixed to said juxtaposed fins such that a first heat exhanging medium in said tubes and a second heat exchanging medium passing between the fins will perform heat exchange through said heat conductive tubes and said fins
  • the improvement comprising a plurality of louvers defining slits formed in said fins to extend substantially raadially around said heat conductive tubes and transversely to said second heat exchange medium passing between the fins, each of said plurality of louvers being formed from slotted and raised-up portions of said fins, each of said raised-up portions having upright walls longitudinally opposed to each other and a ridge wall continuous to said upright walls therebetween, said ridge wall being formed substantially parallel to said juxtaposed fins and positioned in a space between said juxtaposed fins.
  • a crossed fin-and-tube type heat exchanger as set forth in claim 2, wherein said plurality of heat conductive tubes include at least one row of aligned heat conductive tubes, and wherein said plurality of louvers include first louvers extending between each adjoining heat conductive tubes in the direction of the tube row and second louvers extending obliquely on each side of the tube row so that said second louvers are equiangular with said first louvers.
  • a crossed fin-and-tube type heat exchanger as set forth in claim 2, wherein said plurality of heat conductive tubes include at least two rows of aligned heat conductive tubes, and wherein said plurality of louvers include first louvers extending between each adjoining heat conductive tubes in respective rows of said at least two rows in the direction of the tube rows and second louvers extending obliquely only on each outer side of said two tube rows so that said second louvers are equiangular with said first louvers and the section of the fin between said tube rows is free of louvers.
  • a crossed fin-and-tube type heat exchanger as set forth in claim 2, wherein said plurality of heat conductive tubes include at least three rows of aligned heat conductive tubes, and wherein said plurality of louvers include first louvers extending between each adjoining heat conductive tubes in opposed outer rows of said three rows of tubes in the direction of the tube row, second louvers extending obliquely on each outer side of the opposed outer tube rows so that said second louvers are equiangular with said first louvers extending between adjoining tubes in said outer rows, and third louvers extending between each adjoining heat conductive tubes in a middle tube row of said three rows of tubes in the direction of the tube row.
  • a crossed fin-and-tube type heat exchanger as set forth in claim 2, wherein said plurality of heat conductive tubes include at least three rows of aligned heat conductive tubes, and wherein said plurality of louvers include first louvers extending between each adjoining 9 hat conductive tubes in the middle row of said three rows of tubes in the direction of the tube row and second louvers extending obliquely only on each outer side of opposed outer tube rows of said three rows of 10 I obliquely on each outer side of opposed outer tube rows of said three rows of tubes.

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  • Engineering & Computer Science (AREA)
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  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US500683A 1973-09-03 1974-08-26 Heat exchanger Expired - Lifetime US3916989A (en)

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JP9827773A JPS5716319B2 (en, 2012) 1973-09-03 1973-09-03

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GB (1) GB1471079A (en, 2012)

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US11225807B2 (en) 2018-07-25 2022-01-18 Hayward Industries, Inc. Compact universal gas pool heater and associated methods
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US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger
US12110707B2 (en) 2020-10-29 2024-10-08 Hayward Industries, Inc. Swimming pool/spa gas heater inlet mixer system and associated methods

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US4465128A (en) * 1980-04-22 1984-08-14 Orszagos Koolaj Es Gazipari Troszt Plate floor heat exchanger
AT385347B (de) * 1981-02-06 1988-03-25 Energiagazdalkodasi Intezet Waermetauscher und verfahren zu dessen herstellung
US4648443A (en) * 1981-02-06 1987-03-10 Energiagazdalkodasi Intezet Heat exchanger with ribbed fin
USD274750S (en) 1982-01-25 1984-07-17 Taylor Shelton E Evaporator for an automotive air conditioner
USD276933S (en) 1982-04-14 1984-12-25 The Trane Company Heat exchanger
US4449581A (en) * 1982-08-30 1984-05-22 Chromalloy American Corporation Heat exchanger fin element with dog-bone type pattern of corrugations
US4550776A (en) * 1983-05-24 1985-11-05 Lu James W B Inclined radially louvered fin heat exchanger
US4615384A (en) * 1983-06-30 1986-10-07 Nihon Radiator Co., Ltd. Heat exchanger fin with louvers
US5042576A (en) * 1983-11-04 1991-08-27 Heatcraft Inc. Louvered fin heat exchanger
US5109919A (en) * 1988-06-29 1992-05-05 Mitsubishi Denki Kabushiki Kaisha Heat exchanger
US5062475A (en) * 1989-10-02 1991-11-05 Sundstrand Heat Transfer, Inc. Chevron lanced fin design with unequal leg lengths for a heat exchanger
US5425414A (en) * 1993-09-17 1995-06-20 Evapco International, Inc. Heat exchanger coil assembly
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US6321833B1 (en) 1999-10-15 2001-11-27 H-Tech, Inc. Sinusoidal fin heat exchanger
US7337831B2 (en) * 2001-08-10 2008-03-04 Yokohama Tlo Company Ltd. Heat transfer device
US20040194936A1 (en) * 2001-08-10 2004-10-07 Kahoru Torii Heat transfer device
US20040085853A1 (en) * 2002-07-24 2004-05-06 Bayer Aktiengesellschaft Mixer/heat exchanger
US7220048B2 (en) * 2002-07-24 2007-05-22 Bayer Aktiengesellschaft Mixer/heat exchanger
US20070163764A1 (en) * 2003-05-23 2007-07-19 Kunihiko Kaga Heat exchanger of plate fin and tube type
US7578339B2 (en) 2003-05-23 2009-08-25 Mitsubishi Denki Kabushiki Kaisha Heat exchanger of plate fin and tube type
US20090301698A1 (en) * 2003-05-23 2009-12-10 Mitsubishi Denki Kabushiki Kaisha Heat exchanger of plate fin and tube type
US8162041B2 (en) 2003-05-23 2012-04-24 Mitsubishi Denki Kabushiki Kaisha Heat exchanger of plate fin and tube type
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US20060081362A1 (en) * 2004-10-19 2006-04-20 Homayoun Sanatgar Finned tubular heat exchanger
US9638476B2 (en) * 2010-08-05 2017-05-02 Mahle International Gmbh Plate-shaped heat exchanger for a cooling device comprising at least one heart exchanger package
US20130264038A1 (en) * 2010-08-05 2013-10-10 Mahle Behr Industry Gmbh & Co. Kg Plate-shaped heat exchanger for a cooling device comprising at least one heat exchanger package
US20130340986A1 (en) * 2011-03-01 2013-12-26 Mitsubishi Electric Corporation Heat exchanger, refrigerator provided with same and air-conditioning apparatus provided with the heat exchanger
US9279624B2 (en) * 2011-03-01 2016-03-08 Mitsubishi Electric Corporation Heat exchanger tube with collared fins for enhanced heat transfer
US20140202442A1 (en) * 2013-01-21 2014-07-24 Carrier Corporation Condensing heat exchanger fins with enhanced airflow
US10006662B2 (en) * 2013-01-21 2018-06-26 Carrier Corporation Condensing heat exchanger fins with enhanced airflow
US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger
US11262139B2 (en) * 2018-07-19 2022-03-01 Kelvion Machine Cooling Systems Gmbh Heat exchanger
US11225807B2 (en) 2018-07-25 2022-01-18 Hayward Industries, Inc. Compact universal gas pool heater and associated methods
US11649650B2 (en) 2018-07-25 2023-05-16 Hayward Industries, Inc. Compact universal gas pool heater and associated methods
US12188255B2 (en) 2018-07-25 2025-01-07 Hayward Industries, Inc. Compact universal gas pool heater and associated methods
WO2020062728A1 (zh) * 2018-09-30 2020-04-02 珠海格力电器股份有限公司 一种翅片及具有其的热交换器
US12110707B2 (en) 2020-10-29 2024-10-08 Hayward Industries, Inc. Swimming pool/spa gas heater inlet mixer system and associated methods

Also Published As

Publication number Publication date
DE2441652B2 (de) 1979-04-26
DE2441652A1 (de) 1975-04-30
JPS5049759A (en, 2012) 1975-05-02
GB1471079A (en) 1977-04-21
DE2441652C3 (de) 1984-06-28
JPS5716319B2 (en, 2012) 1982-04-03

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