US3804159A - Jet impingement fin coil - Google Patents

Jet impingement fin coil Download PDF

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Publication number
US3804159A
US3804159A US00262235A US26223572A US3804159A US 3804159 A US3804159 A US 3804159A US 00262235 A US00262235 A US 00262235A US 26223572 A US26223572 A US 26223572A US 3804159 A US3804159 A US 3804159A
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US
United States
Prior art keywords
fluid
fins
heat exchanger
fin
perforations
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.)
Expired - Lifetime
Application number
US00262235A
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English (en)
Inventor
E Searight
P Brosens
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.)
Thermo Fisher Scientific Inc
Original Assignee
Thermo Electron Corp
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 Thermo Electron Corp filed Critical Thermo Electron Corp
Priority to US00262235A priority Critical patent/US3804159A/en
Priority to FR7321297A priority patent/FR2188129B1/fr
Priority to GB2796773A priority patent/GB1418836A/en
Priority to JP48065987A priority patent/JPS4957445A/ja
Priority to DE2330076A priority patent/DE2330076C3/de
Priority to IT25342/73A priority patent/IT990637B/it
Application granted granted Critical
Publication of US3804159A publication Critical patent/US3804159A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • 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
    • Y10S165/908—Fluid jets

Definitions

  • ABSTRACT A heat exchanger in the form of a finned tube configuration for transferring heat between the contents of the tube and the atmosphere surrounding the finned tube.
  • the tube may actually be made up in numerous multi-path configurations.
  • the fins preferably extend outwardly from the tube and are attached to the tube in good heat-conducting relationship.
  • the fins are perforated in a predetermined pattern to provide openings through which the outside atmosphere is directed as jets upon portions of the fins in such a fashion as to disrupt boundary layers normally existing adjacent the surfaces upon which the jets impinge.
  • boundary layer of fluid is a generally stationary thin layer of fluid which adheres to the heat-exchanging surfaces and acts as an insulating cushion.
  • the existence of such boundary layers has not gone unnoticed and some efforts have been made to remove or disrupt it in order that heat transfer might be improved.
  • Generally, such efforts as have been made have been directed toward the creation of turbulence in the medium surrounding the heat-exchanging surfaces.
  • One specific structure for achieving turbulence utilizes fins in which louvers are formed. The turbulence as fluid is forced through the louvers diminishes the boundary layer primarily along the fin in' which the louvers are formed, but not sufficiently to achieve maximum heat transfer. In such a structure the effectiveness increases as a function of increase in louver openings.
  • the present invention operates in a particular advantageous manner when the present fluid is a condensing vapor or an evaporating liquid.
  • the second fluid is frequently air.
  • 'It is still another object of the present invention to reduce the size and weight of finned tube heat exchangers.
  • a tube 12 preferably of copper or aluminum, which may form a part of a coil or battery of tubes passes through the convolutions of a formed or joined fin arrangement 14 which forms a series of heat transfer surfaces.
  • the formed fin arrangement 14 may be formed or otherwise provided with flanges 16 along its solid fins length, the fin being in any case in good heat-' conducting relationship with the flanges 16.
  • the flanges 16, in turn, are welded, brazed, mechanically expanded or otherwise attached to the tube 12 also in good heat-conducting relationship.
  • ambient air is caused to flow over the finned tube accordion structure in a direction which is preferably substantially perpendicular to the plane defined by the lines along which the fins 14 are folded and must flow along a path which causes all, or at least a major portion, of the fluid to which the fins 14 are exposed to pass through openings 18 formed in the fins 14.
  • the structure may be appropriately enclosed along its sides and ends, as shown in FIG. 4, to cause such major portion of the fluid to pass through the openings 18.
  • the openings 18 are formed according to a convenient selected pattern.
  • an advantageous hole pattern is one wherein holes 18 are substantially evenly distributed across the surface of each fin, with allowances for the passage therethrough of the tube 12, and the openings in each fin are staggered with respect to holes in adjacent fins so fluid passing through the holes will be directed onto solid target surfaces of the adjacent fins.
  • less than 20 percent of the fin area is open.
  • Optimum results lie in the 2 percent to percent range for most applications.
  • the preferred range of opening sizes lies between 0.030 inch and 0.125 inch. However, with some loss in performance, open area and opening sizes outside these ranges may be used and still provide results superior to finned tube constructions without jet forming openings.
  • incoming air is diverted by certain of the folded edges 17 of the fin structure 14 into spaces formed by adjacent fins and thence along crooked paths through the openings 18.
  • the openings 18 form jets which impinge upon solid portions of adjacent fins. This action is indicated by arrows in FIG. I.
  • exhaust air leaves the finned tube heat transfer structure as indicated by the vertical arrows above that structure.
  • FIG. 2 the illustrated structure is very similar to that of FIG. 1. Again, there is a vapor tube 12, folded fins 14, attached to the tube by means of flanges l6, and includingjet-forming openings 18. However, in the embodiment of FIG. 2, the openings 18 are limited to one set of fin members in such a fashion that fluid, such as air, is directed against the unperforated surfaces of a second set of fin members. Thus, there is provided additional surface against which the jets are directed, the unperforated surfaces preventing interaction between jets.
  • fluid such as air
  • FIG. 3 there is shown an embodiment of the invention which includes a tube 12 similar to that discussed above, to which straight fins 22 are attached.
  • flanges may also be used to insure good heatconducting contact between the fins and the tube, although they are not shown.
  • Alternate pairs of the fins 22v are joined or capped at the input and the output sides, as, for example, at 24 and 26, respectively.
  • These closures may be made with the square fins, as illustrated,
  • the closures may be formed, for example, by press fitting, cementing, bending or welding ends of adjacent fins together or by applying individual caps which engage adjacent fin ends along their length.
  • FIG. 3 may be of particular interest when relatively wide fin spacing is desired.
  • FIG. 4 illustrates a small portion of a system in which the finned tube of the invention may be incorporated.
  • a duct member 32 which may be of any desired length I is penetrated by tubes such as the tube 12 which may be independent or a part of a coil or other configuration.
  • the tubes are spaced along the length of the set of fins 34.
  • the set of fins extends from side to side across the width of the duct.
  • Input air, or other fluid may be forced through the duct as indicated by the arrows at the bottom of FIG. 4.
  • the air is diverted from its original path and formed into generally transverse jets by the openings 38 formed in the fins. It will be noted that each opening confronts an unperforated area of an adjacent fin in order that the jets impinge upon a fin surface to break up stagnant boundary layers formed on such surfaces, thereby to enhance heat transfer.
  • Another fluid flows through the tubes 12 and it, of course, is at a different temperature than that of the fluid forced through the duct 32.
  • the other fluid may also be forced through the tubes 12 or it may be a part of a system in which no applied force is necessary.
  • heat transfer (0,) between a refrigerant in the tube 12 and air passing over the structure is:
  • h denotes the heat transfer coefficient between the inner wall of the copper tubes and the refrigerant, h, that between the air and the fins, A, the outside area of the copper tubes, 1;, the fin effectiveness, A, the fin area, and t t and t,, the copper tube, the refrigerant and the air temperatures, respectively, and r, and r, the inner and outer radii of the tube.
  • a heat transfer coil has a length of 54 in. a fin depth of 1.25 in. a fin height of 37.5 in. thirty three eighths inch diameter tubes on 1.25 in. vertical spacing, and heat to be dissipated of 103,000 Btu/hr. Therefore:
  • the values used in determining the jet impingement transfer coefficient, h are based on such initial temperature differences.
  • the jet impingement transfer coefficient, h is a function of the ratio A P/D, where A Pis the pressure drop across the orifice and D is the diameter of the jet at the vena contracta.
  • a Pi the pressure drop across the orifice
  • D the diameter of the jet at the vena contracta.
  • the actual correlation requires, of course, that a number of other factors such as orifice-to-target distance, cross-flow velocity, etc., be held within certain limits to be valid.
  • the correlation does, however, illustrate the desirability of using as small a jet as can be tolerated for the specific application. It will be assumed that, for the case being examined, a relatively large diameter of 0.1 in. is used, and A P is 0.2 in H O. Under the assumed conditions, the average of the h, values available for the inlet and target side of the jet plates will be taken as 18 Btu/hr ft F.
  • fin effectiveness For the purpose of calculating fin effectiveness, 1 assume fins measuring 1.25 by 1.25 in. with a threeeighths .in. OD tube running through their geometric center, the configuration is equivalent to one with circular fins having a ratio of diameters of 4.0.
  • the fin effectiveness, 1; is given by an accepted correlation as a function of the parameter (a):
  • A, Qo/ t... ramh 103,000/23 x 0.63 1s w 395 ft
  • the effective surface area per fin is 0.61 ft' /fin.
  • This design indicates a material saving of approximately 25 percent as compared to conventional finned tubes.
  • a finned tube heat exchanger comprising a tube for containing a first fluid at a first temperature, a plurality of fins attached in heat conducting relationship to said tube, means integral with each of said fins forming the target areas of adjacent fins and staggered with respect to the perforations in adjacent fins.
  • a finned tube heat exchanger for producing heat transfer between first and second fluids comprising a conduit for confining said second fluid at a second temperature under forced draft conditions, a tube extending across said conduit for containing a first fluid at a first temperature, a plurality of fins attached in heatconducting relationship to said tube, means forming perforations in each of said fins, means integral with each of said fins forming target areas in opposition to said perforations, the perforations in each fin being aligned with the target areas of adjacent fins and staggered with respect to the perforations in adjacent fins, means for causing substantially all of said second fluid to pass through said perforations to form fluid jets and for directing said jets of said second fluid onto said-target areas of adjacent fins whereby boundary layers of said second fluid normally adhering to said fins are disrupted and heat exchange between said first fluid and said second fluid is enhanced.
  • a finned tube heat'exchanger according to claim 5 wherein the sum of the areas of said perforations in each fin is less than 20 percent of the fin area.
  • a finned tube heat exchanger according to claim 5 wherein said first fluid comprises an evaporating liquid.
  • I 11 A finned jet heat exchanger as defined in claim 5 wherein said fins comprise a continuous accordion structure, intersections of adjacent fins, with said fins and said conduit, forming said means for forming and directing jets of said second fluid.
  • a finned jet heat exchanger according to claim 11 wherein said accordion structure is of unitary, folded configuration.
US00262235A 1972-06-13 1972-06-13 Jet impingement fin coil Expired - Lifetime US3804159A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US00262235A US3804159A (en) 1972-06-13 1972-06-13 Jet impingement fin coil
FR7321297A FR2188129B1 (it) 1972-06-13 1973-06-12
GB2796773A GB1418836A (en) 1972-06-13 1973-06-12 Finned tube heat exchanger
JP48065987A JPS4957445A (it) 1972-06-13 1973-06-13
DE2330076A DE2330076C3 (de) 1972-06-13 1973-06-13 Rippenrohr-Wärmetauscher
IT25342/73A IT990637B (it) 1972-06-13 1973-06-13 Scambiatore di calore a tubi alettati

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00262235A US3804159A (en) 1972-06-13 1972-06-13 Jet impingement fin coil

Publications (1)

Publication Number Publication Date
US3804159A true US3804159A (en) 1974-04-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00262235A Expired - Lifetime US3804159A (en) 1972-06-13 1972-06-13 Jet impingement fin coil

Country Status (6)

Country Link
US (1) US3804159A (it)
JP (1) JPS4957445A (it)
DE (1) DE2330076C3 (it)
FR (1) FR2188129B1 (it)
GB (1) GB1418836A (it)
IT (1) IT990637B (it)

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2917759A1 (de) * 1978-05-01 1979-11-15 Thermo Electron Corp Heizkessel
US4201195A (en) * 1978-10-25 1980-05-06 Thermo Electron Corporation Jet impingement solar collector
US4220012A (en) * 1976-09-13 1980-09-02 Brister Beryle D Apparatus for freezing a slug of liquid in a section of a large diameter fluid transmission line
US4263878A (en) * 1978-05-01 1981-04-28 Thermo Electron Corporation Boiler
US4575326A (en) * 1983-11-03 1986-03-11 Tamaqua Cable Products Corporation Apparatus for calibrating extruded material
US4643250A (en) * 1985-07-01 1987-02-17 Sundstrand Corporation Fluid jet impingement heat exchanger for operation in zero gravity conditions
US4648443A (en) * 1981-02-06 1987-03-10 Energiagazdalkodasi Intezet Heat exchanger with ribbed fin
US4690210A (en) * 1985-07-01 1987-09-01 Sundstrand Corporation Fluid jet impingement heat exchanger for operation in zero gravity conditions
US4880055A (en) * 1988-12-07 1989-11-14 Sundstrand Corporation Impingement plate type heat exchanger
US5056586A (en) * 1990-06-18 1991-10-15 Modine Heat Transfer, Inc. Vortex jet impingement heat exchanger
US5129449A (en) * 1990-12-26 1992-07-14 Sundstrand Corporation High performance heat exchanger
US5211219A (en) * 1990-07-31 1993-05-18 Daikin Industries, Ltd. Air conditioner
US5228513A (en) * 1991-05-03 1993-07-20 Indugas, Inc. Convective heat transfer by cascading jet impingement
US5603376A (en) * 1994-08-31 1997-02-18 Fujitsu Network Communications, Inc. Heat exchanger for electronics cabinet
US6378605B1 (en) 1999-12-02 2002-04-30 Midwest Research Institute Heat exchanger with transpired, highly porous fins
US6538885B1 (en) * 2000-09-15 2003-03-25 Lucent Technologies Inc. Electronic circuit cooling with impingement plate
US20040123613A1 (en) * 2001-05-04 2004-07-01 Chiang Robert Hong Leung Medium temperature refrigerated merchandiser
US20050133198A1 (en) * 2001-02-14 2005-06-23 Armstrong Ross D. Folded fin heat sink assembly
US7063131B2 (en) 2001-07-12 2006-06-20 Nuvera Fuel Cells, Inc. Perforated fin heat exchangers and catalytic support
US20080047696A1 (en) * 2006-08-28 2008-02-28 Bryan Sperandei Heat transfer surfaces with flanged apertures
US20080173436A1 (en) * 2007-01-23 2008-07-24 Bobbye Kaye Baylis Plastic intercooler
US20090260789A1 (en) * 2008-04-21 2009-10-22 Dana Canada Corporation Heat exchanger with expanded metal turbulizer
EP2146173A1 (en) * 2008-07-17 2010-01-20 MAHLE International GmbH Plastic heat exchanger
US20140116655A1 (en) * 2012-10-31 2014-05-01 Inventec Corporation Heat dissipation module
US20140202442A1 (en) * 2013-01-21 2014-07-24 Carrier Corporation Condensing heat exchanger fins with enhanced airflow
US20200370834A1 (en) * 2017-11-27 2020-11-26 Dana Canada Corporation Enhanced heat transfer surface
US11118847B2 (en) * 2017-12-22 2021-09-14 Shanghai Power Equipment Research Institute Co., Ltd. Finned heat exchanger tube

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3998600A (en) * 1975-06-16 1976-12-21 Wallis Bernard J Heat exchanger strip and method and apparatus for forming same
JPS5883056U (ja) * 1981-11-30 1983-06-04 三洋電機株式会社 太陽熱集熱器
JPS5883055U (ja) * 1981-11-30 1983-06-04 三洋電機株式会社 太陽熱集熱器
GB2131152B (en) * 1982-11-23 1986-03-19 Atomic Energy Authority Uk A heat exchanger
JPS602186U (ja) * 1983-06-20 1985-01-09 ダイキン工業株式会社 フイン付熱交換器
JPS62113851A (ja) * 1985-11-14 1987-05-25 Aisin Seiki Co Ltd スタ−リング機関用燃焼器

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB356406A (en) * 1930-07-28 1931-09-10 Ralph Searle Improvements in evaporators for cooling air in refrigerating chambers or cabinets
US1983549A (en) * 1933-05-10 1934-12-11 Refrigeration Appliances Inc Radiator fin
DE674629C (de) * 1937-10-12 1939-04-18 Wilhelm Lorch Einrichtung zum Kuehlen von Flaechen, insbesondere bei Zylindern von Brennkraftmaschinen, mit Kuehlrippentaschen
US3033536A (en) * 1959-08-27 1962-05-08 Guszmann Max Radiator system
GB914072A (en) * 1961-01-23 1962-12-28 Schwermaschb Karl Liebknecht Improvements in and relating to heat exchangers
US3205147A (en) * 1959-03-21 1965-09-07 Snecma Process and devices of heat exchange and nuclear reactor embodying same
US3416011A (en) * 1965-03-29 1968-12-10 Thermo Electron Corp Thermionic converter heat exchangers
US3450199A (en) * 1967-07-10 1969-06-17 Continental Aviat & Eng Corp Heat exchanger
US3509867A (en) * 1967-12-29 1970-05-05 Thermo Electron Corp Radiant and convective heater
US3540530A (en) * 1968-06-12 1970-11-17 Peerless Of America Gradated heat exchange fins

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB827061A (en) * 1955-04-19 1960-02-03 Rolls Royce Improvements relating to heat exchange apparatus
US2994123A (en) * 1956-06-14 1961-08-01 Richard W Kritzer Method of forming heat transfer units
FR1342953A (fr) * 1962-10-04 1963-11-15 échangeur thermique
SE340102C (sv) * 1966-08-03 1973-01-04 K R A Oestbo Anordning vid avlånga värmeväxlare med tvärs mot deras längriktning anbragta värmeöverförande flänsar

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB356406A (en) * 1930-07-28 1931-09-10 Ralph Searle Improvements in evaporators for cooling air in refrigerating chambers or cabinets
US1983549A (en) * 1933-05-10 1934-12-11 Refrigeration Appliances Inc Radiator fin
DE674629C (de) * 1937-10-12 1939-04-18 Wilhelm Lorch Einrichtung zum Kuehlen von Flaechen, insbesondere bei Zylindern von Brennkraftmaschinen, mit Kuehlrippentaschen
US3205147A (en) * 1959-03-21 1965-09-07 Snecma Process and devices of heat exchange and nuclear reactor embodying same
US3033536A (en) * 1959-08-27 1962-05-08 Guszmann Max Radiator system
GB914072A (en) * 1961-01-23 1962-12-28 Schwermaschb Karl Liebknecht Improvements in and relating to heat exchangers
US3416011A (en) * 1965-03-29 1968-12-10 Thermo Electron Corp Thermionic converter heat exchangers
US3450199A (en) * 1967-07-10 1969-06-17 Continental Aviat & Eng Corp Heat exchanger
US3509867A (en) * 1967-12-29 1970-05-05 Thermo Electron Corp Radiant and convective heater
US3540530A (en) * 1968-06-12 1970-11-17 Peerless Of America Gradated heat exchange fins

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4220012A (en) * 1976-09-13 1980-09-02 Brister Beryle D Apparatus for freezing a slug of liquid in a section of a large diameter fluid transmission line
FR2425035A1 (fr) * 1978-05-01 1979-11-30 Thermo Electron Corp Chaudiere comportant des moyens d'amelioration du transfert de chaleur
US4263878A (en) * 1978-05-01 1981-04-28 Thermo Electron Corporation Boiler
DE2917759A1 (de) * 1978-05-01 1979-11-15 Thermo Electron Corp Heizkessel
US4201195A (en) * 1978-10-25 1980-05-06 Thermo Electron Corporation Jet impingement solar collector
US4648443A (en) * 1981-02-06 1987-03-10 Energiagazdalkodasi Intezet Heat exchanger with ribbed fin
US4575326A (en) * 1983-11-03 1986-03-11 Tamaqua Cable Products Corporation Apparatus for calibrating extruded material
US4690210A (en) * 1985-07-01 1987-09-01 Sundstrand Corporation Fluid jet impingement heat exchanger for operation in zero gravity conditions
US4643250A (en) * 1985-07-01 1987-02-17 Sundstrand Corporation Fluid jet impingement heat exchanger for operation in zero gravity conditions
US4880055A (en) * 1988-12-07 1989-11-14 Sundstrand Corporation Impingement plate type heat exchanger
US5056586A (en) * 1990-06-18 1991-10-15 Modine Heat Transfer, Inc. Vortex jet impingement heat exchanger
US5211219A (en) * 1990-07-31 1993-05-18 Daikin Industries, Ltd. Air conditioner
US5129449A (en) * 1990-12-26 1992-07-14 Sundstrand Corporation High performance heat exchanger
US5228513A (en) * 1991-05-03 1993-07-20 Indugas, Inc. Convective heat transfer by cascading jet impingement
US5603376A (en) * 1994-08-31 1997-02-18 Fujitsu Network Communications, Inc. Heat exchanger for electronics cabinet
US6378605B1 (en) 1999-12-02 2002-04-30 Midwest Research Institute Heat exchanger with transpired, highly porous fins
US6538885B1 (en) * 2000-09-15 2003-03-25 Lucent Technologies Inc. Electronic circuit cooling with impingement plate
US20050133198A1 (en) * 2001-02-14 2005-06-23 Armstrong Ross D. Folded fin heat sink assembly
US8151587B2 (en) * 2001-05-04 2012-04-10 Hill Phoenix, Inc. Medium temperature refrigerated merchandiser
US20040123613A1 (en) * 2001-05-04 2004-07-01 Chiang Robert Hong Leung Medium temperature refrigerated merchandiser
US7063131B2 (en) 2001-07-12 2006-06-20 Nuvera Fuel Cells, Inc. Perforated fin heat exchangers and catalytic support
US10048020B2 (en) 2006-08-28 2018-08-14 Dana Canada Corporation Heat transfer surfaces with flanged apertures
US8453719B2 (en) 2006-08-28 2013-06-04 Dana Canada Corporation Heat transfer surfaces with flanged apertures
US20080047696A1 (en) * 2006-08-28 2008-02-28 Bryan Sperandei Heat transfer surfaces with flanged apertures
US20080173436A1 (en) * 2007-01-23 2008-07-24 Bobbye Kaye Baylis Plastic intercooler
US20090260789A1 (en) * 2008-04-21 2009-10-22 Dana Canada Corporation Heat exchanger with expanded metal turbulizer
EP2146173A1 (en) * 2008-07-17 2010-01-20 MAHLE International GmbH Plastic heat exchanger
US20140116655A1 (en) * 2012-10-31 2014-05-01 Inventec Corporation Heat dissipation module
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
US20200370834A1 (en) * 2017-11-27 2020-11-26 Dana Canada Corporation Enhanced heat transfer surface
US11454448B2 (en) * 2017-11-27 2022-09-27 Dana Canada Corporation Enhanced heat transfer surface
US11118847B2 (en) * 2017-12-22 2021-09-14 Shanghai Power Equipment Research Institute Co., Ltd. Finned heat exchanger tube

Also Published As

Publication number Publication date
IT990637B (it) 1975-07-10
DE2330076B2 (de) 1979-08-23
FR2188129A1 (it) 1974-01-18
FR2188129B1 (it) 1976-09-17
DE2330076A1 (de) 1973-12-20
JPS4957445A (it) 1974-06-04
DE2330076C3 (de) 1980-04-30
GB1418836A (en) 1975-12-24

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