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US3810509A - Cross flow heat exchanger - Google Patents

Cross flow heat exchanger Download PDF

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Publication number
US3810509A
US3810509A US00344429A US34442973A US3810509A US 3810509 A US3810509 A US 3810509A US 00344429 A US00344429 A US 00344429A US 34442973 A US34442973 A US 34442973A US 3810509 A US3810509 A US 3810509A
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US
United States
Prior art keywords
heat exchanger
cross flow
flow heat
exchanger according
fin
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
US00344429A
Inventor
L Kun
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.)
Katalistiks International Inc
Honeywell UOP LLC
Original Assignee
Union Carbide 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 Union Carbide Corp filed Critical Union Carbide Corp
Priority to US00344429A priority Critical patent/US3810509A/en
Priority to DE19732318132 priority patent/DE2318132A1/en
Priority to CA169,241A priority patent/CA983916A/en
Priority to ES413670A priority patent/ES413670A1/en
Priority to SE7305300A priority patent/SE399301B/en
Priority to FR7313571A priority patent/FR2192282B1/fr
Priority to GB1778273A priority patent/GB1424689A/en
Application granted granted Critical
Publication of US3810509A publication Critical patent/US3810509A/en
Assigned to MORGAN GUARANTY TRUST COMPANY OF NEW YORK, AND MORGAN BANK ( DELAWARE ) AS COLLATERAL ( AGENTS ) SEE RECORD FOR THE REMAINING ASSIGNEES. reassignment MORGAN GUARANTY TRUST COMPANY OF NEW YORK, AND MORGAN BANK ( DELAWARE ) AS COLLATERAL ( AGENTS ) SEE RECORD FOR THE REMAINING ASSIGNEES. MORTGAGE (SEE DOCUMENT FOR DETAILS). Assignors: STP CORPORATION, A CORP. OF DE.,, UNION CARBIDE AGRICULTURAL PRODUCTS CO., INC., A CORP. OF PA.,, UNION CARBIDE CORPORATION, A CORP.,, UNION CARBIDE EUROPE S.A., A SWISS CORP.
Assigned to UNION CARBIDE CORPORATION, reassignment UNION CARBIDE CORPORATION, RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: MORGAN BANK (DELAWARE) AS COLLATERAL AGENT
Assigned to UOP, DES PLAINES, IL., A NY GENERAL PARTNERSHIP reassignment UOP, DES PLAINES, IL., A NY GENERAL PARTNERSHIP ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KATALISTIKS INTERNATIONAL, INC.
Assigned to KATALISTIKS INTERNATIONAL, INC. reassignment KATALISTIKS INTERNATIONAL, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: UNION CARBIDE CORPORATION
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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/02—Stamping using rigid devices or tools
    • B21D22/04—Stamping using rigid devices or tools for dimpling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/04—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of sheet metal
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • 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
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356—Plural plates forming a stack providing flow passages therein
    • Y10S165/373—Adjacent heat exchange plates having joined bent edge flanges for forming flow channels therebetween
    • Y10S165/374—Liquid to air heat exchanger having liquid passage formed by joined sheets
    • Y10S165/376—Air passages defined by spacing projections of sheets
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49366—Sheet joined to sheet

Definitions

  • FIG. I4D FIG. I4E FIG.I4F
  • PATENTEBm 14 m4 saw us or 22 Fla/514 SHEET 10 0F 22 PATENTEDm 14 1974 miminmmmu Y 1810.509 suEE1 12-uF 22 Projections in l I l STRESS; PSI
  • PATENTED m 14 m4 sum 15 or 22 Channels/ft I50 I20 I00 80 6O 40 A Iv-Puxz 2 ⁇ DPm q EE E E5 5a 2 1 3 E I Projection Height H,inches Heat Transfer Rate per Unit Frontal Area BTU/MIN -FT (Hc1) PAIENTEnm 14 m4 3810.509
  • PATENTEB m ⁇ 4 m4 sum 13 0f 22 PATENTEDIAY 14 um CAPACITY, BTU/MlN/FT FRONTAL AREA sum 19 0f 22 80% Sreom ('5 7 (V582 83 Steam in Condensate AIR VOLUME FLOW RATE /FT2 FRONTAL AREA FT3/MIN/ FT

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

A cross flow heat exchanger comprising an outer structural frame, a multiplicity of channels longitudinally aligned in parallel spaced relation to form first fluid passageways within the channels, and a multiplicity of wall projection portions formed from the channel side walls and extending outwardly with load-bearing end segments of adjacent side walls abutting and transferring the channel load to the outer structural frame, the channels and wall projection portions arranged for flowing a second fluid normal to and in the space between adjacent channels, and fins extending from the channel edge walls having surface distortions.

Description

[111 3,810,509 [45] May 14,1974
United States Patent 11 1 Kun 3,397,742 8/1968 Jenssen et 165/167 3,590,917 7/1971 CROSS FLOW HEAT EXCHANGER inventor: Leslie C. Kun, Williamsville, NY.
Primary Examiner-Charles .1 Myhre Assignee:
Union Carbide Corporation, New York, N.Y.
Assistant ExaminerTheophil W. Streule, r. Attorney, Agent or Firm.lohn C. LeFever [22] Filed: Mar. 23, 1973 Appl. No.: 344,429
Related U.S. Application Data [63] Continuation-impart of Ser. No. 189,659,0ct. 15, 1971 Pat. No. 3,757,856, and a continuation-in-part of Ser. No. 270,259, July 10. 1972.
fluid passageways within the channels, and a multiplicity of wall projection portions formed from the channel side walls and extending outwardly with loadbearing end segments of adjacent side walls abutting and transferring the channel load to the outer strucd 58 Wm 2 8 m l. 5 6" O SL Um P n 55 [58] Field of Search......................,..... 165/151-l53,
tural frame, the channels and wall projectionportions [56] References Cited arranged for flowing a second fluid normal to and in UNIT-ED STATES PATENTS the space between adjacent channels, and fins extending from the channel edge walls having surface distortions.
165/167 165/167 23 Claims, 51 Drawing Figures 785,580 3/1905 Shiels et 2 281 754 5/1942 Da1zell......... 2,596,008 5/1952 PATENTEDm 14 1914 saw 02 or 22 PATENTEDMAY m 1924 3,810,509
SHEEI v 03 0F 22 PATENTEUIM 14 m4 SHEEI 0 (1F 22 PATENTEDIAY 14 um sum OSUF 22 PATENTEmn 141914 3.810.509
sum '06 HF 22 DeH {d F I G. IIA
TILR-YSK FATENTEDIAY 14 m4 sum 07 or 22 0 3 m m w w o 5 -l.. S 2 e o 4- M 1 w m 8 //l k w MW w O O O O O o O 7 6 5 4 3 2 DEFLECTION 1 m Z Pmmmmmm 3.810.509
sum nanrzz FIG. MA FIG. I48 FIG. 140
FIG. I4D FIG. I4E FIG.I4F
FIG; I46 FIG. I4H
PATENTEBm 14 m4 saw us or 22 Fla/514 SHEET 10 0F 22 PATENTEDm 14 1974 miminmmmu Y 1810.509 suEE1 12-uF 22 Projections in l I l STRESS; PSI
.iHe'af Transfer Rate per Unit Frontal Arecl BTU/MIN FT (Ha) 0- Spacing inches PATENTED m 14 m4 sum 13 0F 22 low D- Spacing inches FIG. |8B
PATENIEDIAYMIHM 3810.509
sum 1n 0F 22 Projecfions/ in 24l5l| 6432 I5 I I l I I] l 2 a CL "A A (D (D B 5 A Bl Hem Transfer Rate per Unit Frontal Area BTU/M|NXFT (H 1) 5,.
.2 .3 he .f'ri
D Spacing inches FIG. I8C
PATENTED m 14 m4 sum 15 or 22 Channels/ft I50 I20 I00 80 6O 40 A Iv-Puxz 2\DPm q EE E E5 5a 2 1 3 E I Projection Height H,inches Heat Transfer Rate per Unit Frontal Area BTU/MIN -FT (Hc1) PAIENTEnm 14 m4 3810.509
saw 16 0F 22 Channels ff. IOX|O '99 P. P 8
7) 0. 3 l X :0 L3 .8 D:
B c D Q] l 1 a .02 .04 .06 .08 .l5 v Projection Height H,inches F l 6. I98
?ATENTED m 14 1914 7 sum 17 0F 22 Channels/ft.
Projection Height H, inches FIG.
PATENTEB m \4 m4 sum 13 0f 22 PATENTEDIAY 14 um CAPACITY, BTU/MlN/FT FRONTAL AREA sum 19 0f 22 80% Sreom ('5 7 (V582 83 Steam in Condensate AIR VOLUME FLOW RATE /FT2 FRONTAL AREA FT3/MIN/ FT

Claims (23)

1. A cross flow heat exchanger comprising: a. an outer structural frame; b. a multiplicity of channels formed of aluminum each having an elongated cross section bound by side walls and edge walls each of between 0.003 and 0.015 inch thickness and an aspect ratio of length to width of an equivalent rectangle equal to at least 4, being longitudinally aligned in parallel spaced relation each with a first fluid entrance opening at one end and a first fluid exit opening at the opposite end, and common inlet manifold means and common exit manifold means respectively for said first fluid entrance openings and said first fluid exit openings, and a multiplicity of wall projection portions formed from each side wall being distributed across the side wall surface and extending outwardly therefrom with load-bearing end segments shaped for mating with and abutting against loadbearing end segments of said projection portions of an adjacent channel side wall thereby spacing adjacent channels with the outermost end segments bearing against and transferring the channel load to said outer structural frame, said wall projection portions having a dimensional size and a dimensional relationship therebetween defined by a D dimension of between about 0.2 and 1 inch, an H dimension of between about 0.02 and 0.14 inch, and a D/d ratio of between about 3 and 18 wherein H equals the maximum height measured perpendicularly from a plane containing the extremity of the projection end segment to a plane containing the most distant point of said side wall surface, D equals the effective spacing between the centers of adjacent wall projection portions of a side wall as determined by the formula: D 3 square root D13 + D23/2 wherein D1 shortest distance between two adjacent wall projection portions in any triangular unit of the projection pattern on tHe side wall, D2 perpendicular distance from a straight line extending through said two adjacent wall projection centers to the center of the third wall projection of the same triangular unit, triangular unit a triangle having a wall projection center only at each of its apexes with each side of the triangle extending between wall projection centers without transversing a shorter line segment interconnecting other projection centers, and d equals the dimension of the ratio 4a/p wherein a equals the area of the load-bearing end segment of the wall-supporting projection and p equals the perimeter of said load-bearing end segment and said wall projection portions also having an elevational contour such that the ratio theta /R is between about 4* and 2,500* per inch wherein theta is the maximum angle of metal in the projection portion with respect to the base plane of said side wall and measured in a cross section passing through the projection portion center perpendicular to the base plane, and R is the minimum radius of curvative of said metal measured outside the projection portion; c. said channels and wall projection portions thereby, and outer structural frame being arranged and constructed for flowing a second fluid through said outer structural frame normal to and in the space between said channels in heat exchange with said first fluid; and d. at least one thin aluminum fin of between 0.003 and 0.015 inch thickness extending at least outwardly from an edge wall of each channel along the entire length thereof, said fins being provided in number and surface area relative to the channel surface area such that the ratio (0C + 0F)/IT of channel outer surface area (0C) plus fin surface area outside said channels (0F) to total surface area inside said channels (IT) is between 1.2 and 4.0, and with each fin having a multiplicity of surface distortions from the fin plane into the gap between adjacent fins of adjacent channels being closely spaced at intervals (S) between 0.01 and 0.2 inch measured to the channel longitudinal axis, so as to comprise a total distortion area which is at least 40 percent of said fin surface area thereby disrupting the second fluid film across the fin width.
2. A cross flow heat exchanger according to claim 1 wherein the fin surface distortions comprise parallel slats and slotted apertures arranged in a louvered configuration across the fin width.
3. A cross flow heat exchanger according to claim 1 wherein the fin surface distortions comprise a multiplicity of pleated strips across the fin width and separated by parallel slits, each pleated strip having crests and valleys with apertures formed by the strip edges between said crests and valleys, and with crests, and valleys of adjacent pleated strips being nonaligned in the direction normal to said slits.
4. A cross flow heat exchanger according to claim 1 wherein the fin surface distortions comprise a series of corrugations having crests and valleys aligned parallel to the channel longitudinal axis and laterally spaced from each other.
5. A cross flow heat exchanger according to claim 1 wherein the fin surface distortions comprise dimples distributed over the fin surface and separated by undistorted metal, said dimples being aligned in longitudinal rows parallel to the channel longitudinal axis.
6. A cross flow heat exchanger according to claim 1 wherein at least one fin extends outwardly from each edge wall of each channel.
7. A cross flow heat exchanger according to claim 1 wherein two fins extend outwardly from each edge wall of each channel.
8. A cross flow heat exchanger according to claim 1 wherein the ratio (0C + 0F)/IT is between 1.3 and 3.0.
9. A cross flow heat exchanger according to claim 1 wherein the fin surface distortions are spaced at intervals (S) between 0.02 and 0.10 inch.
10. A cross flow heat exchanger according to claim 2 wherein the channels are between 0.75 and 2.0 inch wide and the fins are between 0.2 and 0.5 inch wide.
11. A cross flow heat exchanger according to claim 1 wherein the aspect ratio of said channels is at least 8.
12. A cross flow heat exchanger according to claim 1 wherein the wall projection portions have an isostress elevational contour.
13. A cross flow heat exchanger according to claim 1 wherein the wall projection portions have a truncated cone elevational contour.
14. A cross flow heat exchanger according to claim 1 wherein the wall projection portions have an isostress contour and the fin surface distortions comprise parallel slats and slotted apertures arranged in a louvered configuration across the fin width.
15. A cross flow heat exchanger according to claim 1 wherein the wall projection portions have a D dimension of between about 0.3 and 0.85 inch, an H dimension of between about 0.025 and 0.1 inch, and a D/d ratio of between about 6 and 14.
16. A cross flow heat exchanger according to claim 1 wherein the wall projection portions have an isostress elevational contour such that the ratio theta /R is between about 4* and 100* per inch.
17. A cross flow heat exchanger according to claim 15 wherein the wall projection portions have an isostress elevational contour such that the ratio theta /R is between about 4* and 100* per inch.
18. A cross flow heat exchanger according to claim 2 wherein the slotted fins are fabricated with an angle of approach theta '' of between 0* and 70*, said angle of approach theta '' being defined as the angle between a first line which is parallel to a plane containing the maximum dimensional width line and the longitudinal dimensional width line and the longitudinal dimensional length line of the channels and perpendicular to the channels'' longitudinal length line, and a second line formed by the intersection of a plane onto the surface of a slat on the slotted fin, said plane being normal to the surface of the slat and containing the first line as defined above.
19. A cross flow heat exchanger according to claim 18 wherein said angle of approach theta '' is defined as the following: sin theta '' (cos Beta sin gamma -cos gamma sin Beta cos Alpha ) wherein Beta is the angle formed between the plane of the fin and the plane of the slat member between adjacent slotted apertures; gamma is the angle formed between the plane of the fin and a plane containing the maximum width line and longitudinal length line of said channels; and Alpha is the angle formed between the longitudinal length line of the channels and the longitudinal length line of the slot formed between adjacent slats.
20. A cross flow heat exchanger according to claim 19 wherein said angle of approach theta '' is between 0* and 45*.
21. A cross flow heat exchanger according to claim 19, wherein said angle of approach theta '' is between 0* and 45*, the maximum dimensional width line of said channels is between 0.75 inch and 2.0 inches, and the fin width is less than 0.6 inch.
22. A cross flow heat exchanger according to claim 21 wherein the width of the slats of the louvered configuration are at least 0.02 inch.
23. A cross flow heat exchanger according to claim 21 wherein angle Beta is between 30* and 60*, angle is between 45* and 135*, and angle Alpha is between 0* and 60* .
US00344429A 1971-10-15 1973-03-23 Cross flow heat exchanger Expired - Lifetime US3810509A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US00344429A US3810509A (en) 1971-10-15 1973-03-23 Cross flow heat exchanger
CA169,241A CA983916A (en) 1972-07-10 1973-04-11 Cross flow heat exchanger
DE19732318132 DE2318132A1 (en) 1972-07-10 1973-04-11 CROSS-FLOW HEAT EXCHANGER
SE7305300A SE399301B (en) 1972-07-10 1973-04-13 HEAT EXCHANGER OF CROSS CURRENT TYPE
FR7313571A FR2192282B1 (en) 1972-07-10 1973-04-13
GB1778273A GB1424689A (en) 1972-07-10 1973-04-13 Heat exchangers
ES413670A ES413670A1 (en) 1972-07-10 1973-04-13 Heat exchangers

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US18965971A 1971-10-15 1971-10-15
US00344429A US3810509A (en) 1971-10-15 1973-03-23 Cross flow heat exchanger

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Cited By (47)

* Cited by examiner, † Cited by third party
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US4023618A (en) * 1975-08-18 1977-05-17 Union Carbide Corporation Heat exchanger headering arrangement
EP0014481A2 (en) * 1979-02-12 1980-08-20 Union Carbide Corporation Heat exchange wall member, heat exchange channel element and heat exchanger employing same
DE3020424A1 (en) * 1980-04-30 1981-11-05 Nippondenso Co., Ltd., Kariya, Aichi HEAT EXCHANGER WITH RIBBED RIBS
US4469168A (en) * 1980-02-27 1984-09-04 Hitachi, Ltd. Fin assembly for heat exchangers
DE3050963C2 (en) * 1980-04-30 1988-12-01 Nippondenso Co., Ltd., Kariya, Aichi, Jp
US5062475A (en) * 1989-10-02 1991-11-05 Sundstrand Heat Transfer, Inc. Chevron lanced fin design with unequal leg lengths for a heat exchanger
US5340664A (en) * 1993-09-29 1994-08-23 Ceramatec, Inc. Thermally integrated heat exchange system for solid oxide electrolyte systems
US5375328A (en) * 1992-02-18 1994-12-27 Miralfin S.R.L. Method of making an oil radiator structure having flanges with external flat surfaces
US5511610A (en) * 1994-03-15 1996-04-30 Behr Heat Transfer Systems Off-set louvered heat exchanger fin and method for making same
US5529120A (en) * 1994-02-01 1996-06-25 Hubbell Incorporated Heat exchanger for electrical cabinet or the like
US5697433A (en) * 1993-12-21 1997-12-16 Zexel Corporation Heat-exchanger conduit for tube-stacking type heat exchanger and method of manufacturing it
US5730213A (en) * 1995-11-13 1998-03-24 Alliedsignal, Inc. Cooling tube for heat exchanger
US5845705A (en) * 1995-11-13 1998-12-08 Alliedsignal Inc. Tank to header joint for heat exchangers
US20030164233A1 (en) * 2002-02-19 2003-09-04 Wu Alan K. Low profile finned heat exchanger
US20040069441A1 (en) * 2002-06-04 2004-04-15 Burgers Johny G. Lateral plate finned heat exchanger
US20040083012A1 (en) * 2002-10-28 2004-04-29 Miller John P. Method of modeling and sizing a heat exchanger
US20040091735A1 (en) * 2001-01-08 2004-05-13 Frieder Flamm Method for producing evaporator boards
US20040094398A1 (en) * 2000-09-22 2004-05-20 Hilberg Karoliussen Heat exchanger
US20040188078A1 (en) * 2003-03-24 2004-09-30 Wu Alan Ka-Ming Lateral plate surface cooled heat exchanger
US20050109496A1 (en) * 2003-11-25 2005-05-26 Baolute Ren Heat exchanger tubing with connecting member and fins and methods of heat exchange
US20070039719A1 (en) * 2003-11-07 2007-02-22 Eriksen Andre S Cooling system for a computer system
US20070240865A1 (en) * 2006-04-13 2007-10-18 Zhang Chao A High performance louvered fin for heat exchanger
US20070289728A1 (en) * 2006-05-23 2007-12-20 Denso Corporation Heat exchanger and mounting structure of the same
US20070295492A1 (en) * 2005-04-25 2007-12-27 Anthony Sharp Heat exchange system with inclined heat exchanger device
US20080156472A1 (en) * 2006-11-30 2008-07-03 Behr Gmbh & Co. Kg Heat exchanger, arrangement and process for the production of a heat exchanger
US20090008076A1 (en) * 2004-11-29 2009-01-08 Sanmina-Sci Corporation Systems and Methods For Base Station Enclosures
US20090036167A1 (en) * 2004-11-29 2009-02-05 Sanmina-Sci Corporation System and method for base station heat dissipation using chimneys
US20090188655A1 (en) * 2008-01-24 2009-07-30 Keith Agee Heat exchanger flat tube with oblique elongate dimples
CN101655035A (en) * 2008-08-19 2010-02-24 通用电气公司 Dimpled serrated fin tube structure
WO2010119100A1 (en) * 2009-04-17 2010-10-21 Valeo Systemes Thermiques Coolant circulation tube, heat exchange bundle, and heat exchanger comprising such tubes
DE102010003514A1 (en) * 2010-03-31 2011-10-06 Behr Gmbh & Co. Kg heat exchangers
US20120048510A1 (en) * 2010-08-25 2012-03-01 Gea Wtt Gmbh Plate heat exchanger in a sealed design
WO2012079701A1 (en) * 2010-12-14 2012-06-21 Daimler Ag Exhaust heat exchanger of an internal combustion engine
US8245764B2 (en) 2005-05-06 2012-08-21 Asetek A/S Cooling system for a computer system
US20140008046A1 (en) * 2012-07-05 2014-01-09 Airec Ab Plate for heat exchanger, heat exchanger and air cooler comprising a heat exchanger
CN103537529A (en) * 2012-07-12 2014-01-29 珠海格力电器股份有限公司 Punching method of air-cooled heat exchanger and air-cooled heat exchanger
DE102012216146A1 (en) * 2012-09-12 2014-03-13 Udo Hellwig Heat transfer device for use as pipe in heat carrier for transferring heat from water to surrounding air, has convex-shaped element whose point extends through plane that is limited by edge, where edge passes as tangent into surface
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US20140008046A1 (en) * 2012-07-05 2014-01-09 Airec Ab Plate for heat exchanger, heat exchanger and air cooler comprising a heat exchanger
CN103537529A (en) * 2012-07-12 2014-01-29 珠海格力电器股份有限公司 Punching method of air-cooled heat exchanger and air-cooled heat exchanger
CN103537529B (en) * 2012-07-12 2015-08-26 珠海格力电器股份有限公司 Punching method of air-cooled heat exchanger and air-cooled heat exchanger
DE102012216146A1 (en) * 2012-09-12 2014-03-13 Udo Hellwig Heat transfer device for use as pipe in heat carrier for transferring heat from water to surrounding air, has convex-shaped element whose point extends through plane that is limited by edge, where edge passes as tangent into surface
US10557670B2 (en) * 2014-05-30 2020-02-11 Pleat As Device for heat exchange
US20170234621A1 (en) * 2014-05-30 2017-08-17 Pleat As Device for heat exchange
US20180216897A1 (en) * 2017-01-27 2018-08-02 Airxchange, Inc. Rotary heat regenerator using parallel plate media
US11662148B2 (en) * 2017-08-03 2023-05-30 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US11421949B2 (en) * 2017-12-21 2022-08-23 Mahle International Gmbh Flat tube for an exhaust gas cooler
US10739832B2 (en) * 2018-10-12 2020-08-11 International Business Machines Corporation Airflow projection for heat transfer device
WO2020214902A1 (en) * 2019-04-18 2020-10-22 The Babcock & Wilcox Company Perturbing air cooled condenser fin
RU2790404C1 (en) * 2019-04-18 2023-02-17 Дзе Бэбкок энд Уилкокс Компани Gas cooler rib with disturbed air cooling
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