US3804159A - Jet impingement fin coil - Google Patents
Jet impingement fin coil Download PDFInfo
- 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
- Authority
- 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
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Images
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.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US00262235A US3804159A (en) | 1972-06-13 | 1972-06-13 | Jet impingement fin coil |
GB2796773A GB1418836A (en) | 1972-06-13 | 1973-06-12 | Finned tube heat exchanger |
FR7321297A FR2188129B1 (de) | 1972-06-13 | 1973-06-12 | |
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 |
JP48065987A JPS4957445A (de) | 1972-06-13 | 1973-06-13 |
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 |
Family
ID=22996727
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 (de) |
JP (1) | JPS4957445A (de) |
DE (1) | DE2330076C3 (de) |
FR (1) | FR2188129B1 (de) |
GB (1) | GB1418836A (de) |
IT (1) | IT990637B (de) |
Cited By (27)
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 (de) * | 2008-07-17 | 2010-01-20 | MAHLE International GmbH | Kunststoffwärmetauscher |
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)
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)
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)
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 |
-
1972
- 1972-06-13 US US00262235A patent/US3804159A/en not_active Expired - Lifetime
-
1973
- 1973-06-12 GB GB2796773A patent/GB1418836A/en not_active Expired
- 1973-06-12 FR FR7321297A patent/FR2188129B1/fr not_active Expired
- 1973-06-13 IT IT25342/73A patent/IT990637B/it active
- 1973-06-13 DE DE2330076A patent/DE2330076C3/de not_active Expired
- 1973-06-13 JP JP48065987A patent/JPS4957445A/ja active Pending
Patent Citations (10)
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)
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 (de) * | 2008-07-17 | 2010-01-20 | MAHLE International GmbH | Kunststoffwärmetauscher |
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 |
---|---|
DE2330076A1 (de) | 1973-12-20 |
DE2330076C3 (de) | 1980-04-30 |
FR2188129B1 (de) | 1976-09-17 |
JPS4957445A (de) | 1974-06-04 |
GB1418836A (en) | 1975-12-24 |
FR2188129A1 (de) | 1974-01-18 |
DE2330076B2 (de) | 1979-08-23 |
IT990637B (it) | 1975-07-10 |
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