US3053512A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US3053512A
US3053512A US803887A US80388759A US3053512A US 3053512 A US3053512 A US 3053512A US 803887 A US803887 A US 803887A US 80388759 A US80388759 A US 80388759A US 3053512 A US3053512 A US 3053512A
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United States
Prior art keywords
tubes
header
heat exchanger
headers
tube
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
US803887A
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English (en)
Inventor
Soudan Paul
Mercier Henri
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.)
Pechiney SA
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Pechiney SA
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Publication date
Application filed by Pechiney SA filed Critical Pechiney SA
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Publication of US3053512A publication Critical patent/US3053512A/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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1669—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having an annular shape; the conduits being assembled around a central distribution tube
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/005—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having bent portions or being assembled from bent tubes or being tubes having a toroidal configuration
    • 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
    • Y10S165/051—Heat exchange having expansion and contraction relieving or absorbing means
    • Y10S165/052—Heat exchange having expansion and contraction relieving or absorbing means for cylindrical heat exchanger
    • Y10S165/063—Cylindrical heat exchanger fixed to fixed end supports
    • Y10S165/065—Bent cylindrical heat exchanger
    • Y10S165/066—Coiled

Definitions

  • This invention relates to a heat exchanger and more particularly to a heat exchanger which is especially suitable for applications in industries in which liquids must be cooled or heated while being stirred.
  • Heat exchange is a problem which is common to almost all industries, but presents particular difliculties in chemical engineering applications where viscous liquids or suspensions of solids in liquids are used and in which these materials must be heated or cooled while being stirred. Difficulty is especially experienced when the materials which must be treated tend to encrust the apparatus.
  • Another object of this invention is the provision of a heat exchanger for use in heating or cooling viscous liquids or suspensions of solids in liquids while they are being stirred, the heat exchanger being capable of use even when the materials tend to encrust the apparatus.
  • a further object of the present invention is the provision of a heat exchanger which considerably increases the overall coefficient of heat transmission and yet which is easy to construct and maintain.
  • FIG. 1 is a perspective view of the apparatus embodying the principles of the present invention
  • FIG. 2 is a modification of the apparatus
  • FIG. 3 is a further modification of the apparatus.
  • FIG. 4 is a still further modification of the apparatus of the invention.
  • the heat exchanger indicated generally by the reference numeral is shown as consisting of an upper circular main header 17 and a lower main circular header 19 arranged in spaced, parallel relationship.
  • An entrance tube 18 enters the upper main header 17 while an outlet tube leaves the lower main header.
  • a series of sets 14- each of which consists of an upper circular secondary header 15 and a lower circular secondary header 16 joined by parallel tubes 13.
  • a connecting tube 11 joins the lower secondary header 16 to the lower main header 19, while a connecting tube 12 joins the upper secondary header 15 to the upper main header 17, the connecting tube 12 being in the form of a spiral which is capable of considerable expansion and contraction lengthwise of the tubes 13-.
  • the units 14 are arranged so that they are generally tangential to the outer surface of an imaginary cylinder joining the centerlines of the annuli which define the main headers 17 and 19.
  • the heat exchanger unit 10 is intended to be placed in a chemical vessel (not shown) which also contains a stirring apparatus. It is supposed that the stirring apparatus will lie within the circle of the units 14 and the entire vessel will be filled with a chemical which may be a viscous liquid or a thick suspension of solids in a liquid. Depending upon the chemical process, it may be desirable either to heat or cool the liquid in the vessel for which purpose steam or hot water may be introduced into the heat exchanger or cooling liquid. In the case of cooling, the coolant enters the unit through the inlet tube 18 and fills the upper main header 17. It passes down through the individual connecting tubes 12 into the upper secondary headers 15 which distribute it to the individual tubes 13.
  • the principal heat exchange actually takes place through the tubes 13 and the surrounding liquid in the vessel.
  • the cooling liquid passes through the tubes from the upper end to the lower end and is collected in the lower secondary header 16 from which it passes through the connecting tube 11 into the lower main header 19.
  • the coolant fluid then passes through the outlet tube 20' and is returned to its source.
  • the procedure is similar if the fluid is a heating fluid.
  • the stirring apparatus will cause a flow of the liquid in the vessel around the tubes 13 and produce heat exchange between the coolant fluid and the chemical fluid in the vessel.
  • FIGS. 2, 3, and 4 show variations of the shapes of the tubes in the units 14.
  • a connecting tube 2.1 enters a secondary header 22 which is associated with tubes 23.
  • the tubes 23 are formed with spiral corrugations which extend around the tubes. These spiral corrugations increase the heat exchange surface of the tubes and they, therefore, promote the flow of heat from a material exterior of the tubes to the fluid in the interior of the tubes.
  • a connecting tube 24- leads into an upper secondary header 25 which is connected to tubes 26.
  • the tubes are connected to the header 25 in pairs, each pair lying in a plane Which is radial to the header 25; in other words, the centerlines of each pair of tubes lie in a plane which passes through the axis of an imaginary cylinder joining the centerlines of the upper and lower secondary headers.
  • One of each pair is connected to the header 25 at the inner surface and the other of the pairs is connected to the header at the outer surface; the tubes, therefore, form concentric, generally cylindrical sets of tubes.
  • a connecting tube 27 is attached to a secondary header 28 to which are attached tubes 29.
  • Each tube consists of a series of generally radial sections alternated with angular sections to form a zig-zag conformation.
  • the heat exchanger of the present invention contains an improvement whose purpose is mainly in considerably increasing the overall coefficient of heat transfer. At the same time the construction and maintenance is rendered much easier. Another advantage of the new apparatus resides in an important reduction of the incrustation of heat exchange elements. Also, the heat exchanger, according to the invention, leads to a very large increase of exchange surface in comparison with conventional apparatus of a same capacity. It should be noted that the ratio of the diameter of each tube of the sets is much lower than the diameter of tubes used in presently known exchangers. When the ratio of diameter to the length of the tube is made low enough, the interplay of thermal expansion and contraction produces a vibration which is favorable for automatically removing incrustations from the heating surfaces. It can be understood that the units lie well J outwardly against the walls of the vessel where they are subjected to the greatest velocity of flow of the material being stirred in the vessel so that the heat exchange is greatest because of this greater velocity.
  • the invention was used for the alkaline digestion of bauxite under pressure wherein a suspension of powdered bauxite in alkaline liquor was heated within an autoclave provided with a stirrer.
  • an increase of 50% of the heating surface was obtained.
  • the total amount of heat transfer was increased by 100% (doubled).
  • the autoclave had a diameter of 2.60 meters and was 8.5 meters in height. Fifteen sets were used each having twelve uniform tubes placed as shown in FIG. 1. Each tube was 55 millimeters in external diameter and was 6.4 meters long. This provided a heating surface within the autoclave of 200 square meters.
  • a conventional heat exchanger would have only 130 square meters using 28 tubes of 200 millimeters diamter and 7.4 meters in height.
  • the liquid in the autoclave had a density of 1.4 grams per centimeter and viscosity was 2 centipoises at 100 C.
  • an overall heat transfer coeflicient was obtained of 2,000 calories per square meter per hour per degree of centigrade, instead of 800 or 900 calories per square meter per hour per degree of Centigrade obtained with a conventional heat exchanger working in the same conditions.
  • a heat exchanger comprising an upper and a lower main circular header, the headers being arranged in spaced, parallel relationship, a series of sets joining the headers, each set comprising an upper and a lower circular secondary header considerably smaller in diameter than the said main headers, the headers in each set being arranged in spaced parallel relationship, and a series of thin, helically-shaped flexible tubes joining the secondary headers a thin, flexible tube joining each upper secondary header to the upper main header, a thin, flexible tube joining each lower secondary header to the lower main header, the flexible tubes being the sole support for each set.
  • each set is related to the main headers so that most of its tubes lie outside of an imaginary cylinder joining the centerlines of the main headers.
  • a heat exchanger comprising an upper and a lower main annular header, the headers being arranged in spaced, parallel relationship, a series of sets joining the headers, each set comprising an upper and a lower annular secondary header considerably smaller in major diameter than the said main headers, the headers in each set being arranged in spaced parallel relationship, a series of thin, flexible tubes joining the secondary headers, an expansible thin, flexible helicallyshaped inlet tube j0ining each upper secondary header to the upper main header, a thin, flexible outlet tube joining the lower secondary header to the lower main header, each set being related to the main headers that most of its tubes lie outside of an imaginary cylinder joining the centerlines of the main headers, the flexible inlet tube and the flexible outlet tube constituting the sole support for each set.
  • each tube is formed with a spiral corrugation.
  • a heat exchanger as recited in claim 3 wherein the tubes are attached to the secondary headers in pairs, each pair being arranged in a radial plane, one being connected to the inner surface of the headers while the other is connected to the outer surface of the headers.
  • each tube consists of radial portions alternated with angular portions to obtain a zig-zag conformation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Investigating Or Analyzing Materials Using Thermal Means (AREA)
  • Food Preservation Except Freezing, Refrigeration, And Drying (AREA)
US803887A 1958-04-09 1959-04-03 Heat exchanger Expired - Lifetime US3053512A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR762668 1958-04-09

Publications (1)

Publication Number Publication Date
US3053512A true US3053512A (en) 1962-09-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
US803887A Expired - Lifetime US3053512A (en) 1958-04-09 1959-04-03 Heat exchanger

Country Status (4)

Country Link
US (1) US3053512A (enrdf_load_stackoverflow)
ES (1) ES248498A1 (enrdf_load_stackoverflow)
FR (1) FR1194319A (enrdf_load_stackoverflow)
GB (1) GB910788A (enrdf_load_stackoverflow)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3247897A (en) * 1964-02-25 1966-04-26 Babcock & Wilcox Co Differential expansion compensating apparatus
US3380513A (en) * 1966-09-26 1968-04-30 Du Pont Heat exchange arrangement
US3460924A (en) * 1966-03-14 1969-08-12 Lummus Co Manifold system for heaters
US4029143A (en) * 1974-08-29 1977-06-14 Hoechst Aktiengesellschaft Polymerization reactor with gilled-tube radiator and axial agitator
US4289196A (en) * 1971-07-14 1981-09-15 The Babock & Wilcox Company Modular heat exchangers for consolidated nuclear steam generator
DE3126618A1 (de) * 1981-07-06 1983-01-13 Akzo Gmbh, 5600 Wuppertal Vorrichtung, bei welcher waerme durch hohlfaeden uebertragen wird
DE3205571A1 (de) * 1982-02-17 1983-08-25 Akzo Gmbh Vorrichtung, bei welcher waerme durch hohlfaeden uebertragen wird
US4443389A (en) * 1981-04-27 1984-04-17 Leonard Oboler Heat exchange apparatus
US4626387A (en) * 1985-05-29 1986-12-02 Leonard Oboler Evaporative condenser with helical coils and method
US5832994A (en) * 1994-12-14 1998-11-10 Nomura; Shuzo Heat exchanging apparatus
US20050109495A1 (en) * 2003-11-21 2005-05-26 Lin Cheng Complex flow-path heat exchanger having U-shaped tube and cantilever combined coil
WO2006110087A1 (en) * 2005-04-15 2006-10-19 Jerzy Hawranek Axial heat exchanger
FR2902866A1 (fr) * 2006-06-22 2007-12-28 Giat Ind Sa Generateur de gaz chaud et installtion de sechage ou deshydratation mettant en oeuvre un tel generateur
US20090025917A1 (en) * 2007-07-26 2009-01-29 Robert Henri Gauthier Method and apparatus for heat recovery within a syngas cooler
EP2246109A1 (en) * 2009-04-29 2010-11-03 Methanol Casale S.A. Isothermal tube reactor
US20120048527A1 (en) * 2009-05-06 2012-03-01 Shuyan He Steam generator
US20120234312A1 (en) * 2009-12-24 2012-09-20 Mitsubishi Heavy Industries, Ltd. Solar light heat receiver, and solar light collecting and heat receiving system
US20130269919A1 (en) * 2012-04-16 2013-10-17 Technip France Temperature moderated supports for flow tubes

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3160221A (en) * 1961-09-12 1964-12-08 Allis Chalmers Mfg Co Hillside combine with specific axle structure
GB2516440A (en) * 2013-07-22 2015-01-28 Richard Keirnan Waste water heat recovery unit

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1028777A (en) * 1912-01-27 1912-06-04 John Anthony Power Evaporating apparatus.
US1308486A (en) * 1919-07-01 earle
US1884778A (en) * 1928-05-16 1932-10-25 Babcock & Wilcox Co Steam reheater
US1884777A (en) * 1928-04-21 1932-10-25 Babcock & Wilcox Co Longitudinal flow economizer
US2506120A (en) * 1947-06-21 1950-05-02 Annis R Turner Gas wall heater
US2621900A (en) * 1948-02-25 1952-12-16 Turbo Ray Inc Heat exchange unit
US2640686A (en) * 1949-08-30 1953-06-02 Brown Fintube Co Heat exchange type of tank heater

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1308486A (en) * 1919-07-01 earle
US1028777A (en) * 1912-01-27 1912-06-04 John Anthony Power Evaporating apparatus.
US1884777A (en) * 1928-04-21 1932-10-25 Babcock & Wilcox Co Longitudinal flow economizer
US1884778A (en) * 1928-05-16 1932-10-25 Babcock & Wilcox Co Steam reheater
US2506120A (en) * 1947-06-21 1950-05-02 Annis R Turner Gas wall heater
US2621900A (en) * 1948-02-25 1952-12-16 Turbo Ray Inc Heat exchange unit
US2640686A (en) * 1949-08-30 1953-06-02 Brown Fintube Co Heat exchange type of tank heater

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3247897A (en) * 1964-02-25 1966-04-26 Babcock & Wilcox Co Differential expansion compensating apparatus
US3460924A (en) * 1966-03-14 1969-08-12 Lummus Co Manifold system for heaters
US3380513A (en) * 1966-09-26 1968-04-30 Du Pont Heat exchange arrangement
US4289196A (en) * 1971-07-14 1981-09-15 The Babock & Wilcox Company Modular heat exchangers for consolidated nuclear steam generator
US4029143A (en) * 1974-08-29 1977-06-14 Hoechst Aktiengesellschaft Polymerization reactor with gilled-tube radiator and axial agitator
US4443389A (en) * 1981-04-27 1984-04-17 Leonard Oboler Heat exchange apparatus
DE3126618C2 (de) * 1981-07-06 1986-08-07 Akzo Gmbh, 5600 Wuppertal Wärmeaustauscher aus Hohlfäden
DE3126618A1 (de) * 1981-07-06 1983-01-13 Akzo Gmbh, 5600 Wuppertal Vorrichtung, bei welcher waerme durch hohlfaeden uebertragen wird
DE3205571A1 (de) * 1982-02-17 1983-08-25 Akzo Gmbh Vorrichtung, bei welcher waerme durch hohlfaeden uebertragen wird
US4626387A (en) * 1985-05-29 1986-12-02 Leonard Oboler Evaporative condenser with helical coils and method
WO1986007132A1 (en) * 1985-05-29 1986-12-04 Oboler, Leonard Evaporative condenser with helical coils and method
US5832994A (en) * 1994-12-14 1998-11-10 Nomura; Shuzo Heat exchanging apparatus
US20050109495A1 (en) * 2003-11-21 2005-05-26 Lin Cheng Complex flow-path heat exchanger having U-shaped tube and cantilever combined coil
WO2006110087A1 (en) * 2005-04-15 2006-10-19 Jerzy Hawranek Axial heat exchanger
CN100567875C (zh) * 2005-04-15 2009-12-09 杰齐·哈拉内克 轴向热交换器
FR2902866A1 (fr) * 2006-06-22 2007-12-28 Giat Ind Sa Generateur de gaz chaud et installtion de sechage ou deshydratation mettant en oeuvre un tel generateur
US8011113B2 (en) 2006-06-22 2011-09-06 Nexter Munitions Hot gas generator and drying or dehydration facility implementing such a generator
WO2007147961A3 (fr) * 2006-06-22 2008-03-20 Nexter Munitions Generateur de gaz chaud et installation de sechage ou deshydratation mettant en œuvre un tel generateur
US20100162587A1 (en) * 2006-06-22 2010-07-01 Nexter Munitions Hot gas generator and drying or dehydration facility implementing such a generator
US8959769B2 (en) * 2007-07-26 2015-02-24 General Electric Company Method and apparatus for heat recovery within a syngas cooler
US20090025917A1 (en) * 2007-07-26 2009-01-29 Robert Henri Gauthier Method and apparatus for heat recovery within a syngas cooler
US8673232B2 (en) 2009-04-29 2014-03-18 Methanol Casale Sa Isothermal tube reactor
WO2010124916A1 (en) * 2009-04-29 2010-11-04 Methanol Casale Sa Isothermal tube reactor
EP2246109A1 (en) * 2009-04-29 2010-11-03 Methanol Casale S.A. Isothermal tube reactor
US20120048527A1 (en) * 2009-05-06 2012-03-01 Shuyan He Steam generator
US9062918B2 (en) * 2009-05-06 2015-06-23 Tsinghua University Steam generator
US20120234312A1 (en) * 2009-12-24 2012-09-20 Mitsubishi Heavy Industries, Ltd. Solar light heat receiver, and solar light collecting and heat receiving system
US10054335B2 (en) * 2009-12-24 2018-08-21 Mitsubishi Heavy Industries, Ltd. Solar light heat receiver, and solar light collecting and heat receiving system
US20130269919A1 (en) * 2012-04-16 2013-10-17 Technip France Temperature moderated supports for flow tubes

Also Published As

Publication number Publication date
ES248498A1 (es) 1960-01-01
GB910788A (en) 1962-11-21
FR1194319A (enrdf_load_stackoverflow) 1959-11-09

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