US3225824A - Air-cooled heat exchanger for cooling liquid media - Google Patents

Air-cooled heat exchanger for cooling liquid media Download PDF

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Publication number
US3225824A
US3225824A US311153A US31115363A US3225824A US 3225824 A US3225824 A US 3225824A US 311153 A US311153 A US 311153A US 31115363 A US31115363 A US 31115363A US 3225824 A US3225824 A US 3225824A
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United States
Prior art keywords
elements
members
heat exchanger
rows
common
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Expired - Lifetime
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US311153A
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English (en)
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Wartenburg Kurt
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    • 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
    • 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
    • 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
    • F28D9/0062—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 the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • 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
    • F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
    • 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
    • Y10T24/00—Buckles, buttons, clasps, etc.
    • Y10T24/21—Strap tighteners
    • Y10T24/2187—Rack and pinion and circular tighteners

Definitions

  • the efliciency of the heat exchanger besides other factors, is governed particularly by the velocity of flow and by the state of flow.
  • a special problem encountered in this connection is the nonuniformity of the flow rates of the separate currents. Thus, it is extremely diflicult to maintain a uniform flow throughout the system, and the longer the separate channels, the greater will be the difliculty of making the flow uniform.
  • the flow pattern is subject to continuous changes and can be stabilized only by special apparatus as throttling members at the outlet of the liquid medium.
  • heavyduty tube-type heat exchanging systems are divided into short tube sections arranged in series, with a mixing chamber being inserted between each two sections, thereby providing for an equalization of pressure and temperature between successive tube sections.
  • a mixing chamber being inserted between each two sections, thereby providing for an equalization of pressure and temperature between successive tube sections.
  • such an arrangement has the advantage that heat-exchanger units of any desired capacity can be assembled to meet any operational requirements, using building blocks of like shape and like dimensions as standard tube elements.
  • the tubes are designed with a view toward keeping die manufacturing costs at a minimum, at the same time insuring that an optimum amount of heat will be transferred from the tube surface to the atmosphere.
  • Tube-type heat exchangers of the type described before have proved highly useful, particularly in the case of great differences between the inlet and outlet temperatures in the heat exchanging system.
  • heat exchangers are not suitable for cooling highly viscous media whose inlet and outlet temperatures differ only slightly from one another.
  • To cool highly viscous liquids large unrestricted passage areas of small hydrodynamic diameter are required. This requirement, however, cannot be satisfied by conventional tube-type heat exchanging systems.
  • the main disadvantage of plate-type heat exchangers consists in that plates of certain dimensions are required for each width of cooling zone, that is, the distance beticular outlet temperature. This is due to the fact that the depth of plates is predetermined by the length of passage provided for the cooling air, which length can be varied only within extremely small limits, and that the height of the channels, that is, the distance between the plates, must be selected in accordance with the characteristics of the liquid. Hence, it is the width of the channels that is the only variable which can be altered to obtain a desired rate of flow.
  • each heat exchanger operating on the crosscounter flow principle in which the pressure losses of the cooling air and of the medium to be cooled are given and the flow rates in each of the cooling zones should be alike, is assigned a distinct width of plate. From this follows that plate-type heat exchangers for any operating conditions cannot be constructed of identical components.
  • Another object of the invention is to provide a heat exchanger incorporating the advantages of tube-type and plate-type heat exchangers and in which channels of large unrestricted cross-sectional areas having small hydrodynamic diameters are provided for the liquid medium to be cooled.
  • a further object of the invention is to provide a heat exchanger in which the rates of flow can be easily controlled.
  • Still another object of the invention is to provide a heat exchanger that can be constructed of identical components whereby its adaptability to distinct operating conditions is greatly improved.
  • the heat exchanger of the invention is composed of internally finned tube members of substantially rectangular cross-section through which the coolant is passed.
  • tubes are arranged side by side to form rows of tubes or tube levels, and the rows of tubes are disposed in superjacent relationship and are separated from one another by spacer bars known per se whereby channels are defined by the outer surfaces of the tubes and the spacer bars through which the liquid to be cooled is passed in crosscounter flow. At the flow-reversal points all liquid flow levels are in communication with one another.
  • heat exchangers for any desired operating condition can be constructed of identical elements.
  • the height of the liquid stream can be varied over a wide range by proper selection of the spacing between superjacent tube levels, while the width of the channels is determined by the selected width of the spacer bars.
  • each tube level can be enlarged by simply adding to it the required number of rectangular tubes together with the corresponding number of spacer bars.
  • Another advantage of the invention is that if one of the channels should become clogged because of incrustation only that particular channel will malfunction rather than the entire tube level.
  • the obstruction of the channels by sediments caused by undercooling is considerably reduced by continuous equalization of the temperature at the reversing points.
  • the life of the heat exchanger is considerably extendedv
  • FIGURE 1 is a perspective view, partly broken away, of a standard tube element with internal finning as utilized in the construction of the heat exchanger of the invention
  • FIGURE 2 is a sectional view taken along line IIIIII (FIG. 3) showing the arrangement of the flat iron bars welded to the tube elements and serving as spacer bars between superjacent tube levels, and the outer walls of the heat exchanger;
  • FIGURE 3 is an exploded view of a heat exchanger unit constructed in accordance with the invention.
  • FIGURE 4 is a general side elevation, partly broken away, of a heat exchanger unit with cooling-air blower.
  • FIG. 1 a heat exchanger element or tube of substantially rectangular cross-section.
  • fin structures 3 are provided which extend throughout the length of heat exchanger element It.
  • two fin structures 3' and 3" are provided which are mutually acted upon by tension and are firmly secured to the inner sides of a tube wall 2 as by soldering or hot-galvanizing, to insure a proper thermal connection between the fin structures and the tube wall.
  • elements it are arranged side by side to form rows of tube elements or tube levels which are disposed one above the other thereby making up a stack of heat exchanger elements.
  • Each row of tube elements 1 arranged in one plane is spaced apart from the next row of tube elements in another plane by fiat iron bar members 4' thereby forming between superjacent rows of tubes flat channels 4 of substantially rectangular cross-section through which the liquid to be cooled is passed.
  • the height of channels 4 is determined by the thickness of spacing bar members 4 which are preferably welded to the outer sides of tube walls 2 and are adapted to direct the liquid through channels 4 which are defined by members 4 and the outer surfaces of tube elements 1.
  • Spacer bar members 4 have threaded pins 5 at their ends to permit vertical bar members 6 and side walls 5 and 5" having corresponding holes to be secured thereto by nuts 5", bar members 6 being welded to heat exchanger elements 1 and holding the entire stack of superjacent rows of tubes in place.
  • vertically extending passages or channels 16 are defined between bar members 6, which constitute partitions, by wall members 5 or 5" and the lateral surfaces of the outer elements 1 extending perpendicularly to the direction of flow of the cooling medium. Passages or channels 16 are in communication with channels 4 which are formed by the upper and lower surfaces of tube elements 1 on different levels and whose height is defined by the thickness of the spacer bar members 4' as mentioned before.
  • the liquid to be cooled enters distribution chambers 9 of the heat exchanger through an input manifold constitute a feed pipeline 7 and branch pipes 8 and then flows in cross-counter flow through channels 4 to chambers 10 thereby giving off its heat.
  • the cooled liquid leaves the heat exchanger through an output manifold constituted by branch pipes 11 and collecting pipe 12.
  • cooling is effected by an axial blower 13 and a diffusor 14 which force air through each of the heat exchanger elements 1 in the direction indicated by arrows 15.
  • the formation of solid substances in the liquid to be cooled is directly controlled by the connecting channels, inasmuch as these channels serve to prevent the liquid from being excessively cooled. Thus, the formation of solid substances will be reduced.
  • the connecting channels also minimize the loss in emciency caused by the formation of solid substances in the liquid.
  • air as used herein includes any type of gas suitable for cooling as atmospheric air, carbonic acid, nitrogen or the like.
  • a heat exchanger comprising, in combination:
  • each row being contiguously juxtaposed in a common plane and being spaced from the elements of adjacent rows in a direction transverse of said plane, said rows jointly constituting a stack of tubular elements;
  • each pair of said rows, the interposed group of spacer members, and said wall members define an elongated serpentine shaped flow path having a plurality of areas of flow reversal adjacent said Wall members, the several flow paths being spaced in said transverse direction,

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US311153A 1962-09-29 1963-09-24 Air-cooled heat exchanger for cooling liquid media Expired - Lifetime US3225824A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT771762A AT232017B (de) 1962-09-29 1962-09-29 Luftgekühlter Wärmeaustauscher zur Kühlung von Flüssigkeiten aller Art

Publications (1)

Publication Number Publication Date
US3225824A true US3225824A (en) 1965-12-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
US311153A Expired - Lifetime US3225824A (en) 1962-09-29 1963-09-24 Air-cooled heat exchanger for cooling liquid media

Country Status (5)

Country Link
US (1) US3225824A (de)
AT (1) AT232017B (de)
CH (1) CH416698A (de)
ES (1) ES291962A1 (de)
GB (1) GB1016725A (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3424235A (en) * 1966-10-11 1969-01-28 Lummus Co Air-cooled condenser with provision for prevention of condensate freezing
US3470950A (en) * 1967-01-31 1969-10-07 Milton Menkus Heat exchanger
US3556199A (en) * 1968-05-13 1971-01-19 United Aircraft Prod Free convection cooling method and apparatus
US3570593A (en) * 1968-02-05 1971-03-16 Trane Soc Heat-exchanger
US4029146A (en) * 1974-04-01 1977-06-14 John Zink Company Corrugated sheet heat exchanger
FR2345686A1 (fr) * 1976-03-23 1977-10-21 Maschf Augsburg Nuernberg Ag Echangeur de chaleur
US4154182A (en) * 1977-01-13 1979-05-15 Pfaff Industriemaschinen Gmbh Sewing machine with a cooling system
US4455158A (en) * 1983-03-21 1984-06-19 Air Products And Chemicals, Inc. Nitrogen rejection process incorporating a serpentine heat exchanger
US4496382A (en) * 1983-03-21 1985-01-29 Air Products And Chemicals, Inc. Process using serpentine heat exchange relationship for condensing substantially single component gas streams
EP1541953A4 (de) * 2002-07-09 2006-04-19 Zexel Valeo Climate Contr Corp ROHR FÜR WûRMETAUSCHER
US20090025915A1 (en) * 2006-03-13 2009-01-29 Volvo Lastvagnar Ab Heat exchanger for egr-gas
US20090050302A1 (en) * 2005-12-02 2009-02-26 Pierburg Gmbh Cooling device for an internal combustion engine
US20110038762A1 (en) * 2009-08-12 2011-02-17 Florin Girlea Apparatus, systems and methods for the production of hydrogen
US20140318125A1 (en) * 2011-12-13 2014-10-30 Kroens Co., Ltd. Apparatus for generating superheated vapor using waste heat recovery
US20160123230A1 (en) * 2013-06-14 2016-05-05 United Technologies Corporation Curved plate/fin heater exchanger

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1275212B (de) * 1965-06-02 1968-08-14 Kernforschungsanlage Juelich Kernaufbau fuer einen Atomkernreaktor
SE461610B (sv) * 1984-02-24 1990-03-05 Stubinen Utvecklings Ab Demonterbar plattvaermevaexlare daer kanalernas utformning kan varieras
DE10304692A1 (de) * 2003-02-06 2004-08-19 Modine Manufacturing Co., Racine Gewellter Einsatz für ein Wärmetauscherrohr

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US791876A (en) * 1905-03-14 1905-06-06 Archibald Fraser Burdh Condensing apparatus.
US1874360A (en) * 1930-12-02 1932-08-30 Texas Co Heat exchanger
US1899080A (en) * 1931-10-29 1933-02-28 Res & Dev Corp Heat exchange device
CH189806A (de) * 1935-12-02 1937-03-15 Richard Dr Wenzl Einrichtung zur Trockenluft-Tiefkühlung.
US2650073A (en) * 1949-06-25 1953-08-25 Air Preheater Combined regenerator and precooler for gas turbine cycles
US3017161A (en) * 1959-01-12 1962-01-16 Modine Mfg Co Heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US791876A (en) * 1905-03-14 1905-06-06 Archibald Fraser Burdh Condensing apparatus.
US1874360A (en) * 1930-12-02 1932-08-30 Texas Co Heat exchanger
US1899080A (en) * 1931-10-29 1933-02-28 Res & Dev Corp Heat exchange device
CH189806A (de) * 1935-12-02 1937-03-15 Richard Dr Wenzl Einrichtung zur Trockenluft-Tiefkühlung.
US2650073A (en) * 1949-06-25 1953-08-25 Air Preheater Combined regenerator and precooler for gas turbine cycles
US3017161A (en) * 1959-01-12 1962-01-16 Modine Mfg Co Heat exchanger

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3424235A (en) * 1966-10-11 1969-01-28 Lummus Co Air-cooled condenser with provision for prevention of condensate freezing
US3470950A (en) * 1967-01-31 1969-10-07 Milton Menkus Heat exchanger
US3570593A (en) * 1968-02-05 1971-03-16 Trane Soc Heat-exchanger
US3556199A (en) * 1968-05-13 1971-01-19 United Aircraft Prod Free convection cooling method and apparatus
US4029146A (en) * 1974-04-01 1977-06-14 John Zink Company Corrugated sheet heat exchanger
FR2345686A1 (fr) * 1976-03-23 1977-10-21 Maschf Augsburg Nuernberg Ag Echangeur de chaleur
US4154182A (en) * 1977-01-13 1979-05-15 Pfaff Industriemaschinen Gmbh Sewing machine with a cooling system
US4496382A (en) * 1983-03-21 1985-01-29 Air Products And Chemicals, Inc. Process using serpentine heat exchange relationship for condensing substantially single component gas streams
US4455158A (en) * 1983-03-21 1984-06-19 Air Products And Chemicals, Inc. Nitrogen rejection process incorporating a serpentine heat exchanger
EP1541953A4 (de) * 2002-07-09 2006-04-19 Zexel Valeo Climate Contr Corp ROHR FÜR WûRMETAUSCHER
US20090050302A1 (en) * 2005-12-02 2009-02-26 Pierburg Gmbh Cooling device for an internal combustion engine
US20090025915A1 (en) * 2006-03-13 2009-01-29 Volvo Lastvagnar Ab Heat exchanger for egr-gas
US8136578B2 (en) * 2006-03-13 2012-03-20 Volvo Lastvagnar Ab Heat exchanger for EGR-gas
US20110038762A1 (en) * 2009-08-12 2011-02-17 Florin Girlea Apparatus, systems and methods for the production of hydrogen
US8263027B2 (en) * 2009-08-12 2012-09-11 Alliant Techsystems Inc. Apparatus, systems and methods for the production of hydrogen
US20140318125A1 (en) * 2011-12-13 2014-10-30 Kroens Co., Ltd. Apparatus for generating superheated vapor using waste heat recovery
US20160123230A1 (en) * 2013-06-14 2016-05-05 United Technologies Corporation Curved plate/fin heater exchanger
US10100740B2 (en) * 2013-06-14 2018-10-16 United Technologies Corporation Curved plate/fin heater exchanger

Also Published As

Publication number Publication date
AT232017B (de) 1964-02-25
GB1016725A (en) 1966-01-12
ES291962A1 (es) 1964-01-16
CH416698A (de) 1966-07-15

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