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EP2322890A1 - Échangeur thermique marin - Google Patents

Échangeur thermique marin Download PDF

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Publication number
EP2322890A1
EP2322890A1 EP09176089A EP09176089A EP2322890A1 EP 2322890 A1 EP2322890 A1 EP 2322890A1 EP 09176089 A EP09176089 A EP 09176089A EP 09176089 A EP09176089 A EP 09176089A EP 2322890 A1 EP2322890 A1 EP 2322890A1
Authority
EP
European Patent Office
Prior art keywords
coolant
heat exchange
heat exchanger
process fluid
tubes
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.)
Withdrawn
Application number
EP09176089A
Other languages
German (de)
English (en)
Inventor
David Evans
Julian Gareth Crossley
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.)
Thermex Ltd
Original Assignee
Thermex Ltd
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 Thermex Ltd filed Critical Thermex Ltd
Priority to EP09176089A priority Critical patent/EP2322890A1/fr
Priority to US12/946,165 priority patent/US20110117800A1/en
Publication of EP2322890A1 publication Critical patent/EP2322890A1/fr
Withdrawn legal-status Critical Current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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/02—Flexible 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
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between 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
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the invention relates to a marine heat exchanger.
  • Heat exchangers for marine vessel engines typically comprise a number of tubes through which the process fluid, typically air, is passed for cooling through the action of a coolant flowing externally across the tubes.
  • These heat exchangers typically also comprise a number of fins, generally in the form of metal plates, having apertures formed therein through which the coolant tubes are located.
  • the coolant tubes are, traditionally, bullet expanded or roller expanded in order to form a close mechanical fit within the respective apertures of the cooling plate fins through which the tubes pass.
  • a marine heat exchanger comprising:
  • a marine heat exchanger which has a smaller amount of metal required for joining the coolant tubes and the heat exchange fins by using cuprobraze joints.
  • the marine heat exchanger is thus able to have the same cooling capacity for a smaller weight or a larger cooling capacity for the same weight, as compared to prior art heat exchangers in which coolant tubes are joined to heat exchange plates by means of bullet expanded joints.
  • the use of cuprobraze joints between the ends of the coolant tubes and the tube plates additionally reduces the weight of the tube plates as compared to prior art heat exchangers where such joints are made using bullet expanded joints.
  • the use of cuprobraze joints enables a more thermally efficient and reliable joint to be formed between the coolant tubes and the tube plates than is achievable using bullet expanded or roller expanded joints.
  • the marine heat exchanger provides improved performance against pressure losses as compared to a heat exchanger constructed using bullet expanded or roller expanded joints for the same cooling capacity.
  • the coolant comprises water, which may be one of sea water, engine water and jacket water.
  • the process fluid may comprise one of air, oil and water.
  • cupronickel within the heat exchanger protects the heat exchanger against erosion and corrosion when sea water is used as the coolant.
  • the coolant tubes comprise cupronickel copper alloy.
  • the cupronickel cooper alloy preferably comprises at least 70% copper, and most preferably comprises at least 90% copper.
  • the coolant tubes have a substantially round or obround cross-sectional shape.
  • the heat exchange fins each have a corrugated form, and most preferably have a square-wave corrugated form. In an alternative embodiment, the heat exchange fins each have a substantially flat sheet form. In an embodiment, the fins are provided with secondary surfaces.
  • corrugated heat exchange fins are enabled by the use of cuprobraze joints.
  • the use of corrugated heat exchange fins enables the marine heat exchanger to provide an improved thermal performance.
  • the use of corrugated heat exchange fins enables the marine heat exchanger to be constructed with a smaller footprint and/or lower weight than a heat exchanger constructed using bullet expanded or roller expanded joints for the same cooling capacity.
  • the coolant passageway comprises a single pass through the process fluid passageway. In an alternative embodiment, the coolant passageway comprises two or more passes through the process fluid passageway.
  • the heat exchange core assembly further comprises first and second tube plates respectively provided towards each end of the coolant tubes.
  • the tube plates comprise a copper alloy and the coolant tubes are joined to the respective tube plates by cuprobraze joints.
  • at least one tube plate comprises a flexible tube plate.
  • the flexible tube plate comprises an expansion section having a substantially S-shaped sectional profile.
  • the flexible tube plates enables the marine heat exchanger to be rigidly and securely constructed whilst accommodating expansion and contraction of the coolant tubes caused by changes in the temperature of the coolant and the process fluid.
  • Providing the flexible tube plate with an expansion section having a substantially S-shaped sectional profile enables the flexible tube plate to undergo controlled, diaphragm like flexing within its central region, whilst retaining secure and rigid coupling to the heat exchange core assembly.
  • the heat exchange core assembly further comprises first and second side plates comprising copper alloy and the side plates are joined to adjacent heat exchange fins by cuprobraze joints.
  • the heat exchanger further comprises an inlet manifold tank, provided in fluid communication between the coolant fluid inlet and an inlet end of the coolant passageway, and an outlet manifold tank, provided in fluid communication between an outlet end of the coolant fluid passageway and the coolant outlet.
  • the heat exchanger further comprises a return manifold tank provided in fluid communication with the coolant tubes and forming a part of the coolant passageway.
  • the heat exchange core assembly is arranged within the housing assembly such that the heat exchange core assembly is free to expand within the housing assembly.
  • a first embodiment of the invention provides a marine heat exchanger 10 comprising a housing assembly 12 and a heat exchange core assembly 14.
  • the housing assembly 12 comprises a process fluid inlet 16, a process fluid outlet 18, a coolant inlet 20 and a coolant outlet 22.
  • the housing assembly 12 defines a process fluid passageway between the process fluid inlet 16 and the process fluid outlet 18.
  • the heat exchange core assembly 14 comprises a plurality of, in this example 40, coolant tubes 24 and a plurality of, in this example 9, heat exchange fins 26.
  • the coolant tubes comprise cupronickel copper alloy tubes having an obround cross-sectional shape, as shown in figure 5 .
  • the cupronickel is 90/10 cupronickel but it may alternatively be 70/30 cupronickel.
  • the heat exchange fins 26 have a square wave corrugated form, as shown best in figure 6 , and are formed from copper metal sheeting.
  • the coolant tubes 24 are arranged in a spaced array of 8 layers of 5 tubes 24.
  • a heat exchange fin 26 is provided between each layer of tubes 24.
  • Heat exchange fins 26 are additionally provided on top of the uppermost layer of tubes and below the lower most layer of tubes, as shown in figure 5 .
  • the coolant tubes 24 are joined to the respective adjacent fins 26 by cuprobraze joints.
  • the heat exchange fins 26 may have any physical configuration which presents a suitable surface for connection to the coolant tubes 24 by means of a cuprobraze joint, include a flat sheet form and other corrugated forms.
  • the coolant tubes may have any cross-sectional shape which provides a suitable surface for connection to the heat exchange fins, including a round section.
  • the heat exchange core assembly 14 is arranged within the housing assembly 12 such that at least part of the coolant tubes 24 and at least part of the heat exchange fins 26 extend through the process fluid passageway between the process fluid inlet 16 and the process fluid outlet 18.
  • the housing assembly 12 defines an internal cavity in which the heat exchange core assembly 14 is located and through which the process fluid flows.
  • the coolant tubes 24 and the heat exchange fins 26 thereby extend through the process fluid passageway and the process fluid flows around and across the heat exchange fins and the coolant tubes 24 as it flows from the process fluid inlet 16 to the process fluid outlet 18.
  • the flow of the process fluid is indicated by the arrows P in the figures.
  • the flow of coolant is indicated by the arrows C in the figures.
  • the coolant tubes 24 define a coolant passageway between the coolant fluid inlet 20 and the coolant fluid outlet 22.
  • the coolant tubes 24 are arranged such that the coolant passageway comprises 2 passes through the process fluid passageway.
  • a first set of the coolant tubes 24, being the lower 4 layers of tubes shown in figure 4 form a first part of the coolant fluid passageway which comprises a first pass through the process fluid passageway.
  • a second set of the coolant tubes 24, being the upper 4 layers of the coolant tubes shown in figure 4 form a second part of the coolant fluid passageway through the process fluid passageway.
  • the heat exchange core assembly 14 further comprises first and second side plates 28.
  • the side plates 28 comprise cupronickel and are joined to the respective adjacent heat exchange fins 26 by cuprobraze joints.
  • the heat exchange core assembly 14 further comprises a first tube plate 30 and a second tube plate 32.
  • the tube plates 30, 32 comprise copper alloy, which in this example takes the form of the same cupronickel alloy as the coolant tubes 24.
  • Each tube plate 30, 32 is provided with a matrix of apertures adapted to receive an end of a respective coolant tube 24.
  • the coolant tubes 24 are joined at each end to the respective tube plate 30, 32 by cuprobraze joints.
  • one of the tube plates 32 is a flexible tube plate and is provided with an expansion section 32a which enables the flexible tube plate 32 to flex, in the manner of a diaphragm, under the action of elongate expansion of the coolant tubes 24.
  • the expansion section has a substantially S-shaped sectional profile and, as best shown in figure 3 , the expansion section extends around the matrix of apertures coupled to the coolant tubes 24.
  • tube plates 30, 32 may alternatively comprise flexible tube plates or both may comprise fixed tube plates.
  • the expansion of the coolant tubes 24 may alternatively be accommodated within the heat exchanger 10 by mounting the heat exchange core assembly 14 for free movement within the housing assembly 12, thus enabling the entire heat exchange core assembly 14 to expand with the coolant tubes 24.
  • the heat exchanger 10 further comprises an inlet manifold tank 34, an outlet manifold tank 36 and a return manifold tank 38.
  • the inlet manifold tank 34 is provided in fluid communication between the coolant fluid inlet 20 and the inlet end of the first set of coolant tubes 24, being the inlet of the coolant fluid passageway.
  • the outlet manifold tank 36 is provided in fluid communication between the outlet end of the second set of coolant tubes 24, being the outlet end of the coolant fluid passageway, and the coolant outlet 22.
  • the return manifold tank is provided in fluid communication between the outlet ends of the first set of coolant tubes 24 and the inlet ends of the second set of coolant tubes 24.
  • coolant fluid (C) which in this example comprises sea water, flows in through the coolant inlet 20 and through the inlet manifold tank 34 to the inlet ends of the coolant tubes 24 in the first set of the coolant tubes.
  • the coolant flows through the first set of coolant tubes 24, undertaking a first pass through the process fluid passageway, to the outlet end of the first set of coolant tubes 24 and into the return manifold tank 38.
  • the coolant flows around the return manifold tank 38 and enters the inlet ends of the second set of coolant tubes 24.
  • the coolant then flows through the second set of coolant tubes 24 and out through the outlet manifold tank 36 and the coolant outlet 22.
  • the coolant water may alternatively comprise engine water or jacket water, which may be pre-cooled before delivery to the marine heat exchanger 10.
  • a second embodiment of the invention provides a marine heat exchanger comprising a heat exchange core assembly 40, a coolant inlet 42, an inlet manifold tank 44, an outlet manifold tank 46 and a coolant outlet 48, as shown in figure 6 .
  • the marine heat exchanger of this embodiment is substantially the same as the marine heat exchanger 10 of the first embodiment, with the following modifications. The same reference numbers are retained for corresponding features.
  • the coolant passageway comprises a single pass through the process fluid passageway, and the coolant (C) therefore flows from the inlet manifold tank 44 through all of the coolant tubes 24 to the outlet manifold tank 46.
  • the coolant inlet 42 and the coolant outlet 48 are provided on opposing sides of the housing assembly in this embodiment.
  • the use of cuprobraze joints between the coolant tubes 24 and the heat exchange fins 26 in the described marine heat exchangers provides the advantage of a parent metal joint between the parts and therefore a more thermally efficient joint.
  • the use of cuprobraze joints between the coolant tubes 24 and the heat exchange fins 26 enables the use of corrugated fins within the marine heat exchangers, which provides enhanced thermal performance. As a result, a marine heat exchanger having a smaller size and footprint can be constructed. Further, a marine heat exchanger can be produced having either the same cooling capacity for a lower weight or a greater cooling capacity for the same weight.
  • cuprobraze joints can also reduce the amount of metal required for each of the fins 26, since the metal flange provided around each aperture in a heat exchange fin when coolant tubes are joined to the fins using the method of bullet expanding or roller expanding is not produced.
  • the use of cuprobraze joints between the ends of the coolant tubes 24 and the tube plates 30, 32 provides a more thermally efficient joint between these parts. It also reduces the weight of the tube plates as compared to those joined using the bullet expansion or roller expansion methods.
  • a flexible tube plate enables the heat exchanger to be rigidly and securely constructed whilst accommodating expansion and contraction of the coolant tubes 24 caused by changes in the temperature of the coolant.
  • the expansion section 32a in the flexible tube plate 32 provides a tube plate 32 which may be securely and rigidly coupled to the side plates 28 and to the housing assembly 12, whilst allowing diaphragm like flexing of the tube plate 32 within its central region coupled to the coolant tubes 24.
  • cupronickel within the heat exchanger protects the heat exchanger against erosion and corrosion when using sea water as the coolant and the general salt water environment on board a marine vessel.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP09176089A 2009-11-16 2009-11-16 Échangeur thermique marin Withdrawn EP2322890A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09176089A EP2322890A1 (fr) 2009-11-16 2009-11-16 Échangeur thermique marin
US12/946,165 US20110117800A1 (en) 2009-11-16 2010-11-15 Marine Heat Exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09176089A EP2322890A1 (fr) 2009-11-16 2009-11-16 Échangeur thermique marin

Publications (1)

Publication Number Publication Date
EP2322890A1 true EP2322890A1 (fr) 2011-05-18

Family

ID=42634904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09176089A Withdrawn EP2322890A1 (fr) 2009-11-16 2009-11-16 Échangeur thermique marin

Country Status (2)

Country Link
US (1) US20110117800A1 (fr)
EP (1) EP2322890A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110297359A1 (en) * 2010-06-04 2011-12-08 Jack Chisenhall System and method for attaching stainless steel side plates to the copper/brass tubes of a heat exchanger core
DE102013100885B4 (de) * 2013-01-29 2020-02-27 Benteler Automobiltechnik Gmbh Wärmetauscher für ein Kraftfahrzeug
KR101655174B1 (ko) * 2014-12-09 2016-09-07 현대자동차 주식회사 수냉식 인터쿨러 장치
CN112857104A (zh) * 2021-02-01 2021-05-28 无锡市普尔换热器制造有限公司 一种多介质集成钛合金板翅式换热器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1501512A (fr) * 1965-12-31 1967-11-10 Sulzer Ag échangeur de chaleur
US4799973A (en) * 1984-04-02 1989-01-24 Olin Corporation Process for treating copper-nickel alloys for use in brazed assemblies and product
US20050121184A1 (en) * 2003-12-05 2005-06-09 Geoff Smith Flat-round tube-to-header joint in a CuproBraze heat exchanger
EP1750078A2 (fr) * 2005-08-01 2007-02-07 Jose Maria Vergara Uranga Echangeur de chaleur en alliages de cuivre et laiton avec recuit à haute température et facteur de dureté élevé, capable de résister aux pressions internes élevées
DE102005037156A1 (de) * 2005-08-06 2007-02-08 Daimlerchrysler Ag Wärmetauscher
US20080034571A1 (en) * 2004-06-09 2008-02-14 Mill Masters, Inc. Tube mill with in-line braze coating process
EP1921412A1 (fr) * 2006-11-09 2008-05-14 VALEO AUTOSYSTEMY Sp. Z. o.o. Echangeur de chaleur avec joues latérales améliorées

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2153977A (en) * 1936-12-24 1939-04-11 Revere Copper & Brass Inc Condenser tube
US2152266A (en) * 1937-05-14 1939-03-28 Andale Co Heat exchange equipment
US2653799A (en) * 1949-11-12 1953-09-29 Young Radiator Co Heat exchanger
GB1488349A (en) * 1974-11-29 1977-10-12 Haldor Topsoe As Heat exchange apparatus
US4453592A (en) * 1981-08-03 1984-06-12 The Air Preheater Company, Inc. Expansion guide
JP4604759B2 (ja) * 2005-02-22 2011-01-05 株式会社デンソー 熱交換器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1501512A (fr) * 1965-12-31 1967-11-10 Sulzer Ag échangeur de chaleur
US4799973A (en) * 1984-04-02 1989-01-24 Olin Corporation Process for treating copper-nickel alloys for use in brazed assemblies and product
US20050121184A1 (en) * 2003-12-05 2005-06-09 Geoff Smith Flat-round tube-to-header joint in a CuproBraze heat exchanger
US20080034571A1 (en) * 2004-06-09 2008-02-14 Mill Masters, Inc. Tube mill with in-line braze coating process
EP1750078A2 (fr) * 2005-08-01 2007-02-07 Jose Maria Vergara Uranga Echangeur de chaleur en alliages de cuivre et laiton avec recuit à haute température et facteur de dureté élevé, capable de résister aux pressions internes élevées
DE102005037156A1 (de) * 2005-08-06 2007-02-08 Daimlerchrysler Ag Wärmetauscher
EP1921412A1 (fr) * 2006-11-09 2008-05-14 VALEO AUTOSYSTEMY Sp. Z. o.o. Echangeur de chaleur avec joues latérales améliorées

Also Published As

Publication number Publication date
US20110117800A1 (en) 2011-05-19

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