EP0212878A1 - Echangeur de chaleur à plaques et à courant croisé - Google Patents

Echangeur de chaleur à plaques et à courant croisé Download PDF

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Publication number
EP0212878A1
EP0212878A1 EP86305842A EP86305842A EP0212878A1 EP 0212878 A1 EP0212878 A1 EP 0212878A1 EP 86305842 A EP86305842 A EP 86305842A EP 86305842 A EP86305842 A EP 86305842A EP 0212878 A1 EP0212878 A1 EP 0212878A1
Authority
EP
European Patent Office
Prior art keywords
channels
core
group
plates
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.)
Ceased
Application number
EP86305842A
Other languages
German (de)
English (en)
Inventor
Anthony Matthew Johnson
Graham Robert Mcbride
Colin Roland Watson
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.)
HEATRIC Pty Ltd
Original Assignee
HEATRIC Pty 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
Priority claimed from AU60347/86A external-priority patent/AU587842B2/en
Application filed by HEATRIC Pty Ltd filed Critical HEATRIC Pty Ltd
Publication of EP0212878A1 publication Critical patent/EP0212878A1/fr
Ceased 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
    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0037—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 paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other

Definitions

  • This invention relates to a plate-type heat exchanger and, in particular, to a heat exchanger which is configured to provide for cross-flow thermal contact between fluids which pass through the heat exchanger.
  • the heat exchanger does have broader application, it has been developed particularly for use in refrigeration and air conditioning applications where a need exists for a unit which is very compact, which can be produced economically and which will meet seemingly incompatible working requirements.
  • the heat exchanger has been developed such that it will accommodate various types of working fluids (including gases, liquids, two-phase fluids, refrigerants, oil, water and glycol) such that it may be manufactured in a range of capacities (from a few kilowatts to hundreds of kilowatts) and such that it can accommodate various temperature conditions, including conditions under which thermally contacting fluids are at widely different temperatures.
  • a heat exchanger which provides for cross-flow thermal contact between fluids and which has some relevance in the context of the present invention is disclosed in the publication Chemical Engineering, December 1974, pages 80-83, in an article entitled "Graphite Heat Exchangers".
  • This article describes a rectangular block-type cross-flow heat exchanger which is constructed from graphite plates and which nocrporates two groups of orthogonally disposed parallel holes. The graphite plates are bonded together with a thermosetting resin and the composite block is permanently compressed between cast iron clamping plates. Headers are bolted to four faces of the block for carrying fluids to and from the respective groups of holes in the blocks and, whilst resident in the holes, the fluids exchange heat through the surrounding portions of the graphite blocks.
  • United States Patent No.1,662,870 also discloses a cross-flow heat exchanger which is constructed from a stack of orthogonally grooved plates. The plates are bolted together to form a core and, as in the case of the graphite heat exchanger, fluid is delivered to and taken from the respective grooves by headers which are bolted to four faces of the core.
  • headers or manifolds are attached to a heat exchanger core
  • headers will tend to attain the temperature of the fluid passing therethrough, whereas the core temperature will lie somewhere between the inlet temperatures of the fluids. Therefore, if the core-header attachment is solid (e.g., effected by welding, brazing or soldering), severe stresses will be induced in the vicinity of the core-header attachment region because of differential expansion between the header and the core. This may lead to fatigue failure of the assembly following a number of operating cycles when ductile materials are employed or to immediate failure if brittle materials are employed.
  • the present invention seeks to avoid the above problems by providing a heat exchanger which comprises a core which is constituted by a stack of flat metal plates which are diffusion bonded together in face-to-face contact. At least some of the plates are formed with a first group of channels which extend between a first pair of opposed edges of the plates, and at least some of the plates are formed with a second group of channels which are transversely disposed with respect to the first group, which extend between a second pair of opposed edges of the plates and which do not communicate with the first group of channels.
  • the channels in each plate are formed within the thickness of the plate and have a depth falling within the range 0.2 mm to 1.5 mm.
  • First and second headers are bonded to opposite edges of the core and are in fluid passage communication with the first group of channels, and means are provided for directing a first fluid to and from the first group of channels by way of the first and second headers.
  • the core, together with the first and second headers is located within a vessel, and the interior of the vessel is in fluid passage communication with the second group of channels.
  • Means are provided for admitting a second fluid to the second group of channels in the core and to the interior of the vessel, whereby the second fluid contacts the exterior surface of the first and second headers, and for conveying the second fluid from the vessel after it has contacted the headers.
  • the second fluid preferably is chosen as that having the higher thermal conductivity, in which case the core, headers and vessel will attain a similar temperature.
  • the channels preferably are formed to follow a zig-zag, serpentine or other tortuous path which has the effect of inducing turbulence in a fluid stream flowing through the channels.
  • the channels connect with the edges of the plates and preferably are in the form of grooves which extend for the full length or width of the plates.
  • the longitudinally extending channels do not cover the full width of the surface of the plate in which they are located, and the transversely extending channels do not cover the full length of the plates in which they are located.
  • the two groups of channels may be formed in each of the plates, the first group being formed in one face and the second group being formed in the other face of each plate.
  • the first (longitudinally extending) group of channels preferably are formed in one set of the plates and the second (transversely extending) group of channels preferably are formed in another set of the plates, with plates of the respective sets being alternatingly placed in the stack.
  • spacer plates may be located between adjacent channelled plates.
  • the spacer plates, when used, preferably have a thickness in the range 0.4 mm to 1.0 mm.
  • each plate preferably are formed by a chemical or electrochemical machining process. Also, the plates each preferably have a total thickness which provides a metal thickness in the order of 0.4 mm L o 1.0 mm below or between the channels.
  • the second fluid stream may be induced to flow through the second group of channels in the core, as a consequence or under the influence of inertia, buoyancy or gravity, simply by exposing the core to the fluid stream.
  • a third header is secured to one edge of the core with which the second group of channels communicate and the second fluid stream is directed into or from the core by way of the third header. Either prior to or after passing through the core, the second fluid flows into and from the vessel and, in so doing, contacts the external surface of the first, second and third headers.
  • first and second headers are both contacted on their inner and outer surfaces with the first and second fluids respectively
  • the third header is contacted on both of its (inner and outer) surfaces with the second fluid only. This is acceptable for the following reasons:
  • the headers may be bonded to the core by welding, brazing or soldering them to the respective edges of the core.
  • the heat exchanger core comprises a stack of flat stainless steel plates 20 which are bonded together in face-to-face contact between a pair of end plates 21 and 22.
  • the plates are diffusion bonded together at their contacting surfaces and, to effect such bonding, the plates are pressed together whilst subjected to a temperature approaching the melting point of the metal whereby interfacial crystal growth is promoted.
  • a compression of 0.5% to 5.0% is applied to the stack of plates during the bonding process in order to assure a sound bond and to compensate for any lack of plate flatness.
  • the stack 20 is composed of two different types of plates 23 and 24 which are alternatingly placed in the stack.
  • Each of the plates 23 is formed with longitudinally extending grooves or channels 25 which extend between a first pair of opposite edges 26a and 26b of the plate.
  • the other plates 24 are formed with tranversely extending grooves or channels 27 which extend between a second pair of opposed edges 28a and 28b of the plate.
  • One plate 23 which is formed with the longitudinally extending channels 25 is illustrated in Figure 2, from which it will be seen that the channels extend right to the edges 26a and b of the plate but do not cover the full width of the plate. Thus, unchannelled borders 29 extend along both sides of the plate.
  • one of the plates 24 which is formed with the transversely extending channels 27 is illustrated in Figure 3 and, in this case, the channels can be seen to extend across the full width of the plate between the edges 28a and b.
  • the transverse channels 27 do not cover the full length of the plate and, thus, unchannelled borders 30 extend along the ends of the plate.
  • the channels 25 within the plate 23 follow a zig zag path and they have a depth which is less than the full thickness of the plates.
  • the channels 27 are linear and they too have a depth which is less than the full thickness of the associated plate 24.
  • each channel within each of the plate forms 23 and 24 may be profiled in cross-section as simple grooves, as shown in Figure 4A, or they may have the alternative profiles which are shown by way of example in Figures 4B to 4D.
  • each channel may be formed with a longitudinally extending cusp 31, as shown in Figure 4B. or with a succession of transversely extending webs 32, as shown in Figure 4C.
  • a series of staggered posts 33 may be left within each channel to create a tortuous path for fluid passing along the channels.
  • Metal is removed from the plates to form the channels 25 and 27 by a chemical or electro-chemical machining process.
  • the unremoved metal is protected by a mask which is printed, screen-printed or photographically applied (using a photoresist) to the metal prior to exposing the plate surface to the m d chining medium.
  • This process permits the economical use of various materials in the heat exchanger core, including steel, stainless steel, brass, copper, bronze and aluminium provided that, as in the case of the present invention, the plates are relatively thin and the channels are shallow.
  • the plates 23 and 24 When used in a heat exchanger in which water is the first fluid, which passes through the channels in the plate of Figure 2, and oil is the second fluid, which passes through the channels in the plate of Figure 3, the plates 23 and 24 might typically be 450mm long, 70mm wide and 1.0mm thick.
  • the channels 25 and 27 have a width in the range 1.0mm to 2.0mm and a depth in the order of 0.3mm to 0.6mm.
  • the end plates 21 and 22 have a thickness in the order of 10.0mm.
  • first and second headers 35 and 36 are welded to opposite edges of the core and fluid inlet/outlet conduits 37 connect with the interior of each header.
  • fluid inlet/outlet conduits 37 connect with the interior of each header.
  • FIG. 6 The core construction which is shown in Figure 6 is similar to that of Figure 5, but a further (third) header 38 is welded to a third edge of the core for delivering fluid to the transversely extending channels 27. Fluid is carried into the header 38 by a conduit 39.
  • the core which is shown in Figure 7 of the drawings is constructed in a manner similar to that of Figure 6, but it provides for bi directional fluid flow through the transverse channels 27.
  • a third header 40 (which corresponds to the header 38 in Figure 6) is welded to the third edge of the core and the header is partitioned at 41 and provided with inlet and outlet conduits 42 and 43.
  • fluid is admitted to the transversely extending channels 27 by way of the conduit 42 and, after passing through the channels at one end of the core, the fluid enters a surrounding vessel (not shown).
  • the fluid contacts the headers 35, 36 and 40 whilst resident in the vessel and the fluid then flows back through a further group of the channels 27 to exit from the conduit 43.
  • another heat exchange fluid is passed straight through the core by entering the header 35, passing through the longitudinally extending channels 25 and exiting from the core by way of header 36.
  • the multi--pass arrangement that is illustrated in Figure 7 is appliable to both fluid streams, and arrangements may be made for one or the other or both streams to make more than two passes.
  • the heat exchanger core can most readily be fabricated in the manner shown in Figure 1.
  • the core may be constructed in various other ways. For example, as shown in Figure 8, two cores 45 and 46 of the type shown in Figure 1 may be connected together at their ends by bridging bars 47.
  • a second heat exchange fluid may be admitted to the space between the cores and be split into two separate (oppositely flowing) streams to pass in the transverse directions through the two cores 45 and 46
  • the core construction as shown in Figures 9 and 9a may be employed.
  • the core is fabricated from three separate stacks of plates 49 and 50, and the respective stacks are then joined together (e.g. by welding) with intervening spacer plates 60.
  • the alternate plates 49 and 50 in each stack are formed with orthogonally disposed channels 25 and 27 as indicated in Figure 9a and as shown by the dotted outlines in Figure 9.
  • a first heat exchange fluid is directed through the core in the direction indicated by arrows Al, A2 and A3 and a second heat exchange fluid is directed through the core in the direction indicated by arrows Bl. B2 and B3.
  • a composite core may be constructed by combining the structures which are shown separately in Figures 8 and 9.
  • a core of the type shown in Figure 5 may be embodied in a complete heat exchanger as shown in Figure 10, with the transversely extending channels 27 of the core being orientated in a vertical direction.
  • the heat exchanger of Figure 10 comprises a vessel 51, having inlet and outlet conduits 52 and 53, and the core is located wholly within the vessel.
  • a first heat exchange fluid is directed through the core by way of the conduits 37 and heat is exchanged (in the core) with a second fluid which is passed through the vessel itself and which, as a consequence, washes the outside of the headers 35 and 36.
  • the headers 35 and 36 are contacted by both the first and the second heat exchange fluids.
  • the heat exchanger which is shown in Figure 10 is intended for use principally with a second fluid which is at saturation temperature within the vessel and which will boil as it passes upwardly through the core 20.
  • the second fluid makes one or more passes through the core as a consequence of the buoyancy effect created by the boiling action, and the vapour-liquid density difference separates the upstream and downstream levels of the fluid.
  • no headers are required for directing the heat exchange fluid into or from the (vertical) transversely extending channels within the core.
  • Figure 11 shows a heat exchanger construction which is similar to that of Figure 10, but one which for which external pressure is required to move the second fluid stream through the core.
  • the heat exchanger includes a vessel 54 in which the core 20, together with the headers 35 and 36, forms a baffle.
  • a first heat exchange fluid passes through the core, from right to left as shown in the drawing, entering and exiting through the headers 35 and 36.
  • the second heat exchange fluid passes upwardly through the (vertically orientated) transverse channels 27 in the core under the influence of a pressure differential across the core.
  • the core 20 is contained within a vessel 55 which has a cylindrical wall and dished end caps 56.
  • the core is constructed in the manner shown in Figure 6 and, thus, has oppositely disposed headers 35 and 36 for directing a first heat exchange fluid longitudinally into and from the core 20.
  • Conduits 37 are connected with the headers 35 and 36 and extend through the end cap 36 for conveying the first heat exchange fluid into and from the heat exchanger.
  • the second heat exchange fluid is directed into the core by way of the conduit 39 and the header 38. After passing in a transverse direction through the core. the second heat exchange fluid then enters the interior of the vessel 55 and is conveyed away from the vessel by way of the exit conduit 57. Having passed through the core 20 and having entered the interior of the heat exchanger vessel, the second heat exchange fluid contacts the external surfaces of each of the headers 35, 36 and 38.

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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)
EP86305842A 1985-08-08 1986-07-30 Echangeur de chaleur à plaques et à courant croisé Ceased EP0212878A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AUPH186085 1985-08-08
AU1860/85 1985-08-08
AU60347/86A AU587842B2 (en) 1985-08-08 1986-07-18 Plate-type cross-flow heat exchanger

Publications (1)

Publication Number Publication Date
EP0212878A1 true EP0212878A1 (fr) 1987-03-04

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EP86305842A Ceased EP0212878A1 (fr) 1985-08-08 1986-07-30 Echangeur de chaleur à plaques et à courant croisé

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EP (1) EP0212878A1 (fr)

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0292245A1 (fr) * 1987-05-21 1988-11-23 Heatric Pty. Limited Echangeur de chaleur à plaques plates
WO1989005951A1 (fr) * 1987-12-24 1989-06-29 Sumitomo Precision Products Company Limited Echangeur thermique a plaques et ailettes
WO1997003281A1 (fr) * 1995-07-10 1997-01-30 Westinghouse Electric Corporation Prechauffage de combustible pour turbine a gaz a l'aide d'air de refroidissement comprime
WO1998037457A1 (fr) * 1997-02-20 1998-08-27 Atotech Deutschland Gmbh Microreacteurs chimiques et procede de fabrication correspondant
WO1998053263A1 (fr) * 1996-04-30 1998-11-26 Chart Marston Limited Echangeur thermique
WO2001010773A1 (fr) * 1999-08-07 2001-02-15 Lattice Intellectual Property Ltd. Reacteur compact
US6736983B1 (en) 1999-05-28 2004-05-18 Atotech Deutschland Gmbh Method for producing microcomponents
DE10251658B4 (de) * 2002-11-01 2005-08-25 Atotech Deutschland Gmbh Verfahren zum Verbinden von zur Herstellung von Mikrostrukturbauteilen geeigneten, mikrostrukturierten Bauteillagen sowie Mikrostrukturbauteil
US7087651B2 (en) 2001-12-05 2006-08-08 Gtl Microsystems Ag Process and apparatus for steam-methane reforming
US7186388B2 (en) 2001-10-18 2007-03-06 Compactgtl Plc Catalytic reactor
US7201883B2 (en) 2001-10-12 2007-04-10 Compactgtl Plc Catalytic reactor
US7223373B2 (en) 2001-10-18 2007-05-29 Compactgtl Plc Catalytic reactor
US7235218B2 (en) 2004-04-20 2007-06-26 Compactgtl Plc Catalytic reactors
WO2010103259A2 (fr) 2009-03-09 2010-09-16 Bp Alternative Energy International Limited Séparation de dioxyde de carbone et d'hydrogène
WO2011010111A2 (fr) 2009-07-24 2011-01-27 Bp Alternative Energy International Limited Séparation de gaz
WO2011086345A1 (fr) 2010-01-12 2011-07-21 Bp Alternative Energy International Limited Separation de gaz
WO2011089383A1 (fr) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Séparation de gaz
WO2011089382A2 (fr) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Purification d'un courant riche en co2
WO2011095759A1 (fr) 2010-02-02 2011-08-11 Bp Alternative Energy International Limited Séparation de gaz
US8021633B2 (en) 2001-12-05 2011-09-20 Compactgtl Plc Process an apparatus for steam-methane reforming
US8118889B2 (en) 2001-07-11 2012-02-21 Compactgtl Plc Catalytic reactor
US9157687B2 (en) 2007-12-28 2015-10-13 Qcip Holdings, Llc Heat pipes incorporating microchannel heat exchangers
CN106642039A (zh) * 2016-11-03 2017-05-10 中国核动力研究设计院 一种多用途板式蒸汽发生器
CN107782181A (zh) * 2016-08-31 2018-03-09 航天海鹰(哈尔滨)钛业有限公司 一种新型换热器芯部
CN107782182A (zh) * 2016-08-31 2018-03-09 航天海鹰(哈尔滨)钛业有限公司 一种用于三种流体换热的换热器芯部
US10012107B2 (en) 2011-05-11 2018-07-03 Dresser-Rand Company Compact compression system with integral heat exchangers
US10107554B2 (en) 2013-08-09 2018-10-23 Hamilton Sunstrand Corporation Cold corner flow baffle
US10124452B2 (en) 2013-08-09 2018-11-13 Hamilton Sundstrand Corporation Cold corner flow baffle
US10281219B2 (en) 2014-10-01 2019-05-07 Mitsubishi Heavy Industries Compressor Corporation Plate laminated type heat exchanger
US10365045B2 (en) 2012-11-22 2019-07-30 Alfa Laval Corhex Ltd. 3-D channel gas heat exchanger

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1662870A (en) * 1924-10-09 1928-03-20 Stancliffe Engineering Corp Grooved-plate heat interchanger
GB488571A (en) * 1937-01-09 1938-07-11 Andrew Swan Improvements in plate heat exchangers for fluids
US2467935A (en) * 1946-04-25 1949-04-19 Walter D Harper Heat exchange system
DE875667C (de) * 1943-03-12 1953-05-04 Chem Fab Griesheim Waermeaustauscher
GB732778A (en) * 1951-10-10 1955-06-29 Nat Res Dev Improvements in or relating to heat exchangers
FR2103583A1 (fr) * 1970-08-28 1972-04-14 Ici Ltd
DE2161604A1 (de) * 1971-12-11 1973-06-14 Linde Ag Plattenwaermetauscher, insbesondere zur kuehlung eines verdichteten gases mittels einer fluessigkeit, wie wasser, z.b. als turbokompressor-nachkuehler
GB1484124A (en) * 1974-11-21 1977-08-24 Ass Eng Ltd Heat exchangers
US4083400A (en) * 1976-05-13 1978-04-11 Gte Sylvania, Incorporated Heat recuperative apparatus incorporating a cellular ceramic core
US4219079A (en) * 1976-10-01 1980-08-26 Hisaka Works, Ltd. Plate type condenser
FR2509028A1 (fr) * 1981-07-06 1983-01-07 Chausson Usines Sa Dispositif de condensation et de traitement de fluides frigorigenes
EP0136481A2 (fr) * 1983-10-03 1985-04-10 Rockwell International Corporation Echangeur de chaleur à plaques empilées munies d'ailettes

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1662870A (en) * 1924-10-09 1928-03-20 Stancliffe Engineering Corp Grooved-plate heat interchanger
GB488571A (en) * 1937-01-09 1938-07-11 Andrew Swan Improvements in plate heat exchangers for fluids
DE875667C (de) * 1943-03-12 1953-05-04 Chem Fab Griesheim Waermeaustauscher
US2467935A (en) * 1946-04-25 1949-04-19 Walter D Harper Heat exchange system
GB732778A (en) * 1951-10-10 1955-06-29 Nat Res Dev Improvements in or relating to heat exchangers
FR2103583A1 (fr) * 1970-08-28 1972-04-14 Ici Ltd
DE2161604A1 (de) * 1971-12-11 1973-06-14 Linde Ag Plattenwaermetauscher, insbesondere zur kuehlung eines verdichteten gases mittels einer fluessigkeit, wie wasser, z.b. als turbokompressor-nachkuehler
GB1484124A (en) * 1974-11-21 1977-08-24 Ass Eng Ltd Heat exchangers
US4083400A (en) * 1976-05-13 1978-04-11 Gte Sylvania, Incorporated Heat recuperative apparatus incorporating a cellular ceramic core
US4219079A (en) * 1976-10-01 1980-08-26 Hisaka Works, Ltd. Plate type condenser
FR2509028A1 (fr) * 1981-07-06 1983-01-07 Chausson Usines Sa Dispositif de condensation et de traitement de fluides frigorigenes
EP0136481A2 (fr) * 1983-10-03 1985-04-10 Rockwell International Corporation Echangeur de chaleur à plaques empilées munies d'ailettes

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0292245A1 (fr) * 1987-05-21 1988-11-23 Heatric Pty. Limited Echangeur de chaleur à plaques plates
WO1989005951A1 (fr) * 1987-12-24 1989-06-29 Sumitomo Precision Products Company Limited Echangeur thermique a plaques et ailettes
US5035284A (en) * 1987-12-24 1991-07-30 Sumitomo Presicion Products Co. Ltd. Plate-fin-type heat exchanger
WO1997003281A1 (fr) * 1995-07-10 1997-01-30 Westinghouse Electric Corporation Prechauffage de combustible pour turbine a gaz a l'aide d'air de refroidissement comprime
WO1998053263A1 (fr) * 1996-04-30 1998-11-26 Chart Marston Limited Echangeur thermique
US6409072B1 (en) * 1997-02-20 2002-06-25 Atotech Deutschland Gmbh Chemical microreactors and method for producing same
WO1998037457A1 (fr) * 1997-02-20 1998-08-27 Atotech Deutschland Gmbh Microreacteurs chimiques et procede de fabrication correspondant
US6736983B1 (en) 1999-05-28 2004-05-18 Atotech Deutschland Gmbh Method for producing microcomponents
WO2001010773A1 (fr) * 1999-08-07 2001-02-15 Lattice Intellectual Property Ltd. Reacteur compact
US8118889B2 (en) 2001-07-11 2012-02-21 Compactgtl Plc Catalytic reactor
US7201883B2 (en) 2001-10-12 2007-04-10 Compactgtl Plc Catalytic reactor
US7186388B2 (en) 2001-10-18 2007-03-06 Compactgtl Plc Catalytic reactor
US7223373B2 (en) 2001-10-18 2007-05-29 Compactgtl Plc Catalytic reactor
US8021633B2 (en) 2001-12-05 2011-09-20 Compactgtl Plc Process an apparatus for steam-methane reforming
US7087651B2 (en) 2001-12-05 2006-08-08 Gtl Microsystems Ag Process and apparatus for steam-methane reforming
DE10251658B4 (de) * 2002-11-01 2005-08-25 Atotech Deutschland Gmbh Verfahren zum Verbinden von zur Herstellung von Mikrostrukturbauteilen geeigneten, mikrostrukturierten Bauteillagen sowie Mikrostrukturbauteil
US7380698B2 (en) 2002-11-01 2008-06-03 Atotech Deutschland Gmbh Method of connecting module layers suitable for the production of microstructure modules and a microstructure module
US7235218B2 (en) 2004-04-20 2007-06-26 Compactgtl Plc Catalytic reactors
US9157687B2 (en) 2007-12-28 2015-10-13 Qcip Holdings, Llc Heat pipes incorporating microchannel heat exchangers
WO2010103259A2 (fr) 2009-03-09 2010-09-16 Bp Alternative Energy International Limited Séparation de dioxyde de carbone et d'hydrogène
WO2011010111A2 (fr) 2009-07-24 2011-01-27 Bp Alternative Energy International Limited Séparation de gaz
WO2011086345A1 (fr) 2010-01-12 2011-07-21 Bp Alternative Energy International Limited Separation de gaz
WO2011089383A1 (fr) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Séparation de gaz
WO2011089382A2 (fr) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Purification d'un courant riche en co2
WO2011095759A1 (fr) 2010-02-02 2011-08-11 Bp Alternative Energy International Limited Séparation de gaz
US10012107B2 (en) 2011-05-11 2018-07-03 Dresser-Rand Company Compact compression system with integral heat exchangers
US10365045B2 (en) 2012-11-22 2019-07-30 Alfa Laval Corhex Ltd. 3-D channel gas heat exchanger
US11391518B2 (en) 2012-11-22 2022-07-19 Alfa Laval Corhex Ltd. Method of operating a heat exchanger
US10107554B2 (en) 2013-08-09 2018-10-23 Hamilton Sunstrand Corporation Cold corner flow baffle
US10124452B2 (en) 2013-08-09 2018-11-13 Hamilton Sundstrand Corporation Cold corner flow baffle
US10281219B2 (en) 2014-10-01 2019-05-07 Mitsubishi Heavy Industries Compressor Corporation Plate laminated type heat exchanger
CN107782181A (zh) * 2016-08-31 2018-03-09 航天海鹰(哈尔滨)钛业有限公司 一种新型换热器芯部
CN107782182A (zh) * 2016-08-31 2018-03-09 航天海鹰(哈尔滨)钛业有限公司 一种用于三种流体换热的换热器芯部
CN106642039A (zh) * 2016-11-03 2017-05-10 中国核动力研究设计院 一种多用途板式蒸汽发生器

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