EP1520147A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur

Info

Publication number
EP1520147A1
EP1520147A1 EP03737806A EP03737806A EP1520147A1 EP 1520147 A1 EP1520147 A1 EP 1520147A1 EP 03737806 A EP03737806 A EP 03737806A EP 03737806 A EP03737806 A EP 03737806A EP 1520147 A1 EP1520147 A1 EP 1520147A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
heat exchanger
flow path
primary
fluid
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Withdrawn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
EP03737806A
Other languages
German (de)
English (en)
Inventor
Daniel Chartouni
Eric Killer
Christian Ohler
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.)
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
EIDP Inc
Original Assignee
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
EI Du Pont de Nemours and Co
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 ABB Research Ltd Switzerland, ABB Research Ltd Sweden, EI Du Pont de Nemours and Co filed Critical ABB Research Ltd Switzerland
Priority to EP03737806A priority Critical patent/EP1520147A1/fr
Publication of EP1520147A1 publication Critical patent/EP1520147A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04082—Arrangements for control of reactant parameters, e.g. pressure or concentration
    • H01M8/04089—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants
    • H01M8/04119—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants with simultaneous supply or evacuation of electrolyte; Humidifying or dehumidifying
    • H01M8/04156—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants with simultaneous supply or evacuation of electrolyte; Humidifying or dehumidifying with product water removal
    • H01M8/04164—Arrangements for control of reactant parameters, e.g. pressure or concentration of gaseous reactants with simultaneous supply or evacuation of electrolyte; Humidifying or dehumidifying with product water removal by condensers, gas-liquid separators or filters
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/026—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 helically coiled the conduits of only one medium being helically coiled and formed by bent members, e.g. plates, the coils having a cylindrical configuration
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0273—Cores having special shape, e.g. curved, annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/50—Fuel cells
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/50—Manufacturing or production processes characterised by the final manufactured product

Definitions

  • the invention relates to the field of fluid-to-fluid through-lhe-wall heat exchangers for condensation of a vapour in a fluid stream. It also relates to the use of such a heat exchanger in fuel cell systems.
  • a fuel el requires that a fuel such as hydrogen, hydrocarbon, metal or any other reducing agent is fed to the anode electrode on one side of an electrolyte barrier while oxygen or any other oxidising agent is supplied to die cathode electrode.
  • the oxygen can be supplied from a pure oxygen source, but is most often supplied using ambient air as the source. Common practice is to supply the required flow rate of air to the cathode where a fraction of the oxygen in the air is used in the chemical reaction and the remaining gas is expelled as part of an exhaust gas.
  • the cooling air at the secondary side is preferably blown in a direction perpendicular to the plane of the tubings, this cross-flow configuration results again in a relatively high flow resistance and further high parasitic power demand for the blowers and therefore a lower net total power output of the system.
  • fuel cells especially polymer membrane fuel cells are very sensitive to ionic impurities. If water is re-introduced into the fuel cell it should have the quality of de- ionised water with a u ⁇ riimum amount of metallic ions.
  • Commercially available condensers have metallic heat-exchanger walls and deliver the water with a non-negligible amount of (metallic) impurities deteriorating the performance of the fuel cell. Because of their limited heat conductivity, it is disadvantageous to make the complete heat exchanger from non-metallic materials. It is also extremely costly to provide a thin coating on the inner walls of the thin tubes of the abovementioned finned tube heat exchangers.
  • a water-to-water heat exchanger with a cylindrical water reservoir surrounded by an annular space forming a helical flow path for the heating water is disclosed.
  • the helical flow path is made up of a flat metallic strip oriented perpendicularly and being soldered or glued to the wall of the water reservoir and surrounding the latter in the form of a helix.
  • This object is achieved by a heat exchanger according to claim 1 and a use of such a heat exchanger according to claim 10.
  • Preferred embodiments arc evident from the dependent patent claims.
  • a helical primary flow path for a primary fluid consisting of or containing vapour to be condensed is defined by an outer cylinder forming a double wall cylinder together with the inner cylinder, and a helical space holder arranged in between the two cylinders.
  • the space holder forms a wall guiding the primary fluid along a helical flow path devoid of any sharp bends and therefore representing a low flow resistance to the primary fluid.
  • the space holder determines the radial distance between the two cylinders.
  • An inner cylinder wall of the inner cylinder or an outer cylinder wall of the outer cylinder delimits a secondary flow path with reduced flow resistance for the cooling fluid flowing alongside said cylinder wall.
  • the outer cylinder wall of the inner or the inner cylinder wall of the outer cylinder separating the primary and the secondary flow path is coated with a chemically resistant and preferably non-metallic or non-corrosive material i ⁇ > order to avoid contamination of the condensate.
  • the cylinder delimiting the secondary flow path for the cooling fluid is the inner cylinder with an interior space accessible to a cooling fluid entering on one side and exiting on the opposite side of the cylinder.
  • the inner cylinder defines by itself the secondary flow path and renders unnecessary the provision of a further delimiting means.
  • the outer surface of the inner cylinder is easier to be coated with the chemically resistant material than the inner surface of the hollow outer cylinder.
  • the space holder is not fixed to the abovementioned cylinder separating the two fluids.
  • the surface to be coated remains flat and uniform which further facilitates the coating procedure.
  • the space holder is either attached to the other cylinder delimiting the primary flow path or eventually wound around the inner cylinder after coating.
  • a third concentrical cylinder is provided, which further delimits the secondary flow path and forces the cooling fluid to pass close to the inner cylinder wall of the inner cylinder or the outer cylinder wall of the outer cylinder.
  • the heat is transferred to the secondary fluid through cooling fins contacting the inner cylinder surface of the inner cylinder and/or the outer cylinder surface of the outer cylinder.
  • a second helical space holder may be provided to guide the cooling fluid.
  • the cylinders are in a vertical position and the inner cylinder is dimensioned such as to act as a chimney for the secondary cooling fluid, the latter being at least partially moved due to natural convection.
  • a blower or pump power for the secondary fluid is further reduced, and in case the former breaks, the system nevertheless continues to operate without it, i.e, in a passive way.
  • Fig.l schematically shows an oblique front view of a heat exchanger
  • Fig,2 schematically shows a top view of a heat exchanger according to the invention.
  • the reference symbols used in the drawings, and their meanings, are listed in summary form in the list of reference symbols.
  • a double wall cylindrical heat exchanger is composed of an inner cylinder 1 and an outer cylinder 2 arranged concentrically around the former. Between the two cylinders a helically shaped space holder 3 is arranged and defines a helical flow path 5 between an inlet 4 and an outlet 6.
  • the fluid containing the vapour to be condensed enters the heat exchanger at the inlet 4 and follows the helical path 5 between the two cylinder walls, guided by the space holder 3.
  • the vapour (component) condenses by transfer of heat to the secondary side and a two-phase (liquid and gas) flow exits at the outlet 6 of the primary flow path.
  • a multitude of radial fins 7 on the inside of the open inner cylinder 1 assure a sufficient surface area for the heat transfer to a cooling fluid at the secondary side, e.g. a stream of ambient air 8.
  • the open inner cylinder 1 conducts a stream of cooling fluid preferably in a direction opposite to the direction of the primary fluid, i.e. leaving the inner tube near the inlet 6. If the cylinder axis is vertical with the inlet 6 on top, this leads to a chimney effect, and the secondary fluid is at. least partially moved due to natural convection and the blower or pump power at the secondary side is further reduced or a blower can even be omitted completely.
  • One or several fans may however be used to conduct the ambient air through the f s. They can be placed either at the top or the bottom, drawing or blowing air through the secondary side of the heat exchanger.
  • the space holder 3 is preferably made of an EPDM-rubber (Ethylenepropyleneterpolymer) or polypropylene hose or of a flexible PTFE-tube (Polytetrafluorethyle ⁇ e) with an arbitrary, not necessarily hollow cross section, tightly wound around the inner cylinder 1, Alternatively, it may be fixed either to the inner surface 22 of the outer tube 2 or to the outer surface 11 of the inner tube 1 by means of soldering. Following this, the second cylinder is either inserted into the outer tube or placed around the inner tube. If the space holder 3 is made of an elastic rubber material, the relative position of the cylinders 1,2 has to be fixed by other mechanical means.
  • EPDM-rubber Ethylenepropyleneterpolymer
  • polypropylene hose or of a flexible PTFE-tube (Polytetrafluorethyle ⁇ e) with an arbitrary, not necessarily hollow cross section, tightly wound around the inner cylinder 1, Alternatively, it may be fixed either to the inner surface 22
  • any wall separating the two fluids of a heat exchanger there are two basic requirements for any wall separating the two fluids of a heat exchanger.
  • the wall should conduct the heat from the primary to the secondary fluid without any noticeable temperature drop.
  • the wall must be made of a thin yet mechanically stable heat conductor, i.e. preferably a metal.
  • contamination of the condensate or any primary fluid has to be prevented, consequently a wall made of a polymer material would appear most suitable. It is therefore advantageous to have the wall made of a first material with optimized heat conducting and mechanical properties, coated by a corrosion resistant material of a thickness of 50 to 500 ⁇ m that by itself does constitute an acceptable thermal barrier.
  • Thin layers of polymer are most efficiently applied or sprayed to metallic bodies having a flat surface that can be easily exposed to a stream of the thin layer material or its precursor.
  • the entire outer cylinder surface 11 (delimiting the primary flow path 5) of the inner cylinder 1 (separating the two fluids) is prepared correspondingly, with the space holder 3 itself being preferably fixed to the inner cylinder surface 22 of the outer cylinder 2.
  • the outer cylinder 2 can be made out of a polymer, preferably PP (polypropylene), PVDF (polyvinylidene fluoride), FIFE (Polytetrafluorethylene) or the like. However it can also be a metallic cylinder (e.g.
  • PVDF Polyvinylidene fluoride
  • PEEK Polyarylcthcrctherketone
  • E-CTFE Ethylene-chlortrifl ⁇ orethylene-Copolymcr
  • PTFE Polytetrafluorethylene
  • PFA Perfluoralkoxy-Copolymer
  • the inner cylinder 1 is preferably a metallic cylinder (example stainless steel), coated with a thin, chemically resistant material on the outer surface 11, preferably PVDF (Polyvinylidene fluoride), PEEK (Polyaryletheretherketone), E-CTFE (Ethylene-chlortrifluorethylene-Copolymer), PTFE (Polytetrafluorethylene), PFA (Perfluoralkoxy-Copolymer) or the like.
  • PVDF Polyvinylidene fluoride
  • PEEK Polyaryletheretherketone
  • E-CTFE Ethylene-chlortrifluorethylene-Copolymer
  • PTFE Polytetrafluorethylene
  • PFA Perfluoralkoxy-Copolymer
  • the heat transfer depends on the contact area between the fins and the secondary cooling fluid and hence on the length of the fins measured from the inside 12 of the inner cylinder 1 towards the centre of the cylinder.
  • a third cylinder 9 of a smaller diameter and with a closed top and bottom surface can be provided such that secondary flow path is restricted to the space between the inner cylinder 1 and said third cylinder 9.
  • the pressure drop in the primary helical flow path is minimal because sharp bends are avoided, but depends on the cross section and on the length of the path. Therefore, both the pressure drop and the heat transfer rate can be adapted to the requirements of the system by changing the dimensions of the helical flow path or the fin geometry, respectively.
  • the outer cylinder 2 is metallic, fins might be placed at the outer surface 21 of the outer cylinder 2, either in addition to the fins within the inner cylinder 1 or instead of them. In this case, a third cylinder 9 around these fins placed at the outer cylinder is necessary in order to ensure that the cooling fluid passes along these f s. This situation is not depicted in the fig.l.
  • the geometry of the cylinders does not necessarily imply a circular cylindrical cross section.
  • a cross section of an elliptical shape . or involving straight sections connected by suitably rounded corners is found to be working in a satisfactory manner, too.
  • the cross section may vary along the height of the cylinder, thereby forming a cone for the cooling fluid on the secondary side.
  • the heat exchanger as described herein is particularly suited in connection with fuel cells, such as direct methanol or hydrogen fuel cells where the condensed water has to be recirculated in the system and where purity demands are high and parasitic blower power should be minimal. But the heat-exchanger provided is also advantageous in other condensation applications where mii ⁇ misati ⁇ n of pressure drop and high purity of the condensate are required.
  • the present invention provides a double envelope cylindrical fluid-to-fluid tbrough-the- wall heat exchanger for condensation of a vapour in a fluid stream.
  • this condenser is easier to coat with a corrosion resistant coating and shows a smaller flow resistance resulting in a smaller power demand of the air blower.
  • the manufacturing of such a double envelope cylindrical heat exchanger is particularly simple and cost effective.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Electrochemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Fuel Cell (AREA)

Abstract

La présente invention concerne un échangeur de chaleur de type fluide à fluide, à fonctionnement à travers la paroi, destiné à la condensation d'une vapeur dans un premier flux de fluide, la conduite d'écoulement (5) du premier flux de fluide étant définie par un cylindre intérieur (1), un cylindre extérieur (2) aménagé concentrique par rapport au cylindre intérieur et entourant celui-ci, et un support d'espace hélicoïdal (3) aménagé entre les cylindres intérieur et extérieur. En outre, les surfaces des cylindres délimitant la première voie d'écoulement sont faites d'un matériau résistant à la corrosion ou plaquées avec un tel matériau, et ce pour réduire la contamination du fluide primaire. En comparaison aux condenseurs fonctionnant dans des régimes normaux identiques, cet échangeur de chaleur manifeste une plus faible résistance au flux, ce qui réduit la consommation de puissance de la soufflante et des pompes. De ce fait, l'échangeur de chaleur est particulièrement bien adapté aux systèmes à piles à combustible dans lesquels l'eau de condensation doit être réinjectée dans le système, ce qui pousse vers le haut les exigences en termes de pureté et en termes d'économie d'énergie de la soufflante. La fabrication de cet échangeur de chaleur cylindrique à enveloppe double est particulièrement aisée et efficace en termes de coûts.
EP03737806A 2002-06-24 2003-06-18 Echangeur de chaleur Withdrawn EP1520147A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03737806A EP1520147A1 (fr) 2002-06-24 2003-06-18 Echangeur de chaleur

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP02405521A EP1376038A1 (fr) 2002-06-24 2002-06-24 Echangeur de chaleur
EP02405521 2002-06-24
PCT/CH2003/000395 WO2004001313A1 (fr) 2002-06-24 2003-06-18 Echangeur de chaleur
EP03737806A EP1520147A1 (fr) 2002-06-24 2003-06-18 Echangeur de chaleur

Publications (1)

Publication Number Publication Date
EP1520147A1 true EP1520147A1 (fr) 2005-04-06

Family

ID=29716994

Family Applications (2)

Application Number Title Priority Date Filing Date
EP02405521A Withdrawn EP1376038A1 (fr) 2002-06-24 2002-06-24 Echangeur de chaleur
EP03737806A Withdrawn EP1520147A1 (fr) 2002-06-24 2003-06-18 Echangeur de chaleur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP02405521A Withdrawn EP1376038A1 (fr) 2002-06-24 2002-06-24 Echangeur de chaleur

Country Status (5)

Country Link
US (1) US20050150643A1 (fr)
EP (2) EP1376038A1 (fr)
JP (1) JP2005536706A (fr)
AU (1) AU2003246078A1 (fr)
WO (1) WO2004001313A1 (fr)

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RU2471626C2 (ru) 2008-12-17 2013-01-10 Шарп Кабусики Кайся Роликовый импринтер и способ изготовления импринт-листа
US20120118335A1 (en) * 2010-11-17 2012-05-17 Dean Gillingham Pressure wash system
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US20170211478A1 (en) * 2014-04-11 2017-07-27 Unison Industries, Llc Tubular cooler with integrated fan
CN104654823B (zh) * 2014-12-02 2016-11-30 长成新能股份有限公司 一种工业用废蒸汽冷凝装置
US20190041135A1 (en) * 2015-09-18 2019-02-07 Nopparat Thipchuwong Double plated heat exchanger
TWI636724B (zh) * 2017-03-01 2018-09-21 雙鴻科技股份有限公司 具有散熱功能的電子設備及其水冷排總成
CN116222147B (zh) * 2022-12-28 2024-04-19 华中科技大学 一种实验级液氢冷凝制取装置

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WO2004001313A1 (fr) 2003-12-31
AU2003246078A1 (en) 2004-01-06
US20050150643A1 (en) 2005-07-14
JP2005536706A (ja) 2005-12-02
AU2003246078A8 (en) 2004-01-06
EP1376038A1 (fr) 2004-01-02

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