EP1203195B1 - Enhanced crossflow heat transfer - Google Patents

Enhanced crossflow heat transfer Download PDF

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Publication number
EP1203195B1
EP1203195B1 EP00958015A EP00958015A EP1203195B1 EP 1203195 B1 EP1203195 B1 EP 1203195B1 EP 00958015 A EP00958015 A EP 00958015A EP 00958015 A EP00958015 A EP 00958015A EP 1203195 B1 EP1203195 B1 EP 1203195B1
Authority
EP
European Patent Office
Prior art keywords
conduits
heat exchange
fluid flow
conduit
heat transfer
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
EP00958015A
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German (de)
English (en)
French (fr)
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EP1203195A1 (en
EP1203195A4 (en
Inventor
Thomas L. Larsen
Umesh K. Jayaswal
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.)
Stone and Webster Inc
Original Assignee
Stone and Webster Inc
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Filing date
Publication date
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Publication of EP1203195A1 publication Critical patent/EP1203195A1/en
Publication of EP1203195A4 publication Critical patent/EP1203195A4/en
Application granted granted Critical
Publication of EP1203195B1 publication Critical patent/EP1203195B1/en
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media

Definitions

  • the present invention relates generally to methods and related apparatus for enhancing heat transfer to or from a fluid flowing cross-wise in contact with the outer thermally-conductive shells of a plurality of axially-oriented heat exchange conduits capable of acting as heat sources or heat sinks.
  • a fluid flowing cross-wise in contact with the outer thermally-conductive shells of a plurality of axially-oriented heat exchange conduits capable of acting as heat sources or heat sinks By channeling cross-wise fluid flow, flowing generally orthogonal to the axes of the heat exchange conduits, and contouring it around the heat exchange conduits utilizing surrounding sleeve-like elements, a surprisingly more effective and efficient heat transfer between the flowing fluid and the thermally conductive surface is realized.
  • thermal-transfer surface that acts as a heat source or heat sink is the exterior of a thermally-conductive shell of a thermal-transfer tube or pipe, for example, which is heated or cooled by means of a liquid flowing axially through the interior of the tube or pipe.
  • heat may be supplied directly inside a heat exchange conduit by means of flameless combustion of fuel gas (such as hydrogen or a hydrocarbon) as taught, for example, by U.S. Patent Nos. 5,255,742 and 5,404,952 .
  • fuel gas such as hydrogen or a hydrocarbon
  • reactor designs embodying at least in part a radial, crossflow of process fluid relative to a plurality of axially-disposed heat-transfer tubes are shown in U. S. Patent Nos. 4,230,669 ; 4,321,234 ; 4,594,227 ; 4,714,592 ; 4,909,808 ; 5,250,270 ; an 5,585,074 .
  • cross-flow contact of a process fluid with a heat-transfer surface can be an attractive option for many applications, the utility of cross-flow contact for industrial applications has been limited by certain heat transfer inefficiencies which have been experienced in practice.
  • a given portion of the process fluid is in contact with the heat-transfer surface for a shorter time than with a comparable axial flow design.
  • the contact between the cross-flowing process fluid and the heat-transfer surface is uneven due to process fluid separation and recirculation. Short surface contact time, uneven contact, and limited fluid mixing can lead to inefficient, insufficient, and/or non-uniform thermal energy transfer.
  • the present invention provides fluid flow contouring apparatus having the features set out in claim 1 of the accompanying claims.
  • a fluid flow contouring apparatus having the features defined in the preamble of claim 1 is disclosed for instance in US 3616 849 .
  • the invention also provides a method for enhancing heat transfer to or from a fluid flowing cross-wise in contact with the outer surfaces of a plurality of heat exchange conduits, said method having the features set out in claim 13 of the accompanying claims.
  • the fluid flow constriction structure is a larger, generally concentric sleeve-like structure at least partially surrounding each conduit in an array of tubular heat exchange conduits, each such sleeve structure having apertures upstream and downstream of the centrally-located heat exchange tube.
  • Apertured sleeves of this type at least partially surrounding individual heat exchange conduits in an array of such conduits have been found to enhance heat transfer by a factor of about five times or more.
  • Embodiments of the invention may provide heat-transfer conduit arrays of varying sizes and configurations wherein each conduit of the array is associated with its own fluid flow-constriction means upstream, downstream and/or around or alongside of the conduit so as to preferentially contour the portion of the fluid stream flowing crosswise past the outside of the conduit to realize improved heat transfer.
  • the apparatus is designed so as to substantially restrict the bypassing of fluid flow such that a predominant portion of the process fluid is forced to flow past the heat-transfer surface.
  • the heat transfer surface will typically be one or a configured array of heat exchange conduits, oriented to have parallel axes disposed in an axial direction which is generally orthogonal to the direction of fluid flow, and having a thermally-conductive shell.
  • each such conduit is maintained at a temperature different from that of the upstream process fluid so that thermal energy is transferred to or from the process fluid by means of conduction, convection, radiation or some combination thereof, as the fluid flows past and contacts the exterior surfaces of the heat exchange conduits.
  • the heat exchange conduits or ducts of this invention may broadly comprise tubes, pipes, or any other enclosures with heat sources or heat sinks.
  • the exterior surfaces of the heat exchange conduits may be bare or, as discussed below, may be finned or any combination of the two.
  • the cross-section of the conduits or ducts may be circular, elliptical, or any other closed shapes. Where a plurality of such heat exchange conduits are used, they will typically be arrayed in some predetermined configuration such as in a triangular array, a square array, a circular array, an annular array, or other such patterns depending on design choice and/or the requirements of a particular application. Relative to the direction of fluid flow, adjacent conduits may be aligned, staggered or otherwise positioned, again depending on design choice and/or application requirements.
  • the size of the heat exchange conduits will be dictated, at least in part, by process requirements for the rate of heat transfer.
  • conduits having larger cross sections will provide larger surface areas and therefore more heat transfer capacity.
  • Fin elements, baffles or other heat-transfer enhancing structures may be provided on the outside surface of some or all of the heat exchange conduits to further increase surface area and improve heat transfer characteristics.
  • a preferred embodiment utilizes closely spaced circumferential fins applied in a spiral along the exterior length of the conduit. This arrangement increases the heat-transfer surface area exposed to the crossflow without impeding the flow. It will be understood that the nature and flow rate of the process fluid, and the desired temperature change in the fluid between upstream of the heat exchange conduits and downstream of the conduits, will also affect these design choices.
  • the apertures in the fluid flow constriction structure preferably comprise any combination of perforated holes or axial slots (i.e. elongated apertures having a longer axis generally parallel to the axial orientation of the heat exchange conduits).
  • the holes or slots in different portions of the apparatus may be the same or differ in curvature, size and shape.
  • the edges around the inlets and outlets may be straight, rounded, jagged, or some combination thereof.
  • the fluid flow constriction structure is preferably positioned relative to an associated heat exchange conduit such that the distance between the centerline of an upstream or downstream aperture and the associated heat exchange conduit centroid ranges from about 0 to about 2.0, preferably from about 0.50 to about 1.00, times the outer diameter (or largest cross-sectional dimension of a non-circular conduit) of the conduit. In any case, the spacing between aperture and conduit must be sufficiently close to realize substantially enhanced heat transfer.
  • the width (shortest side) of an elongated flow constriction aperture or the diameter of a generally circular hole constriction aperture may preferably range from about 0.02 to about 1.5, preferably from about 0.05 to about 0.25, times the outside diameter (or largest cross-sectional dimension of a noncircular conduit) of the conduit.
  • the fluid flow constriction structure is preferably positioned relative to an associated heat exchange conduit such that the offset between the center of the aperture and the centroid of the heat exchange conduit ranges from 0 to 0.5, preferably 0, times the outside diameter (or largest cross-sectional dimension of a noncircular conduit) of the conduit.
  • the enhanced crossflow heat exchange apparatus of this invention enhances heat transfer between the cross-flowing fluid and the plurality of heat exchange conduits by one or more of the following mechanisms:
  • Fig.1 shows a crossflow heat exchange apparatus 10 according to this invention having a generally circular array of axially-disposed heat exchange conduits 12 distributed around the interior of an annular region 28 defined by an inner cylindrical wall 20 and an outer cylindrical wall 22, each having a common centerpoint 14.
  • conduits 12 are of substantially the same diameter, which is less than the radial width of the annular region, and spaced substantially equidistant from one another.
  • each heat exchange conduit 12 Associated with each heat exchange conduit 12 is an upstream aperture 24 in inner wall 20 and a downstream aperture 26 in outer wall 22. As shown in Fig.1 , respective pairs of upstream apertures 24 and downstream apertures 26 are substantially in radial alignment with the associated conduit 12 and with each other.
  • a process fluid 30 is flowed axially into the inner cylindrical region 16 of the heat exchange apparatus 10 and then directed radially outward through upstream apertures 24, flowing cross-wise into contact with the heat exchange conduits 12, as denoted by the fluid flow arrows in Fig.1 , thereby heating or cooling the process stream to form a thermally conditioned fluid stream 32 which exits annular region 28 through downstream apertures 26.
  • FIG.1 illustrates a radially-outward fluid flow path
  • the same apparatus could be utilized for thermally treating a process stream flowing radially inward to center region 16 and thereafter being axially withdrawn from region 16.
  • apertures 26 in the outer wall 22 would be the upstream apertures and apertures 24 in inner wall 20 would be the downstream apertures.
  • Figs. 2A and 2B show a particularly preferred crossflow heat exchange apparatus 110 according to this invention having a generally circular array of axially-disposed heat exchange conduits 112, each surrounded by an apertured sleeve 120 having either (i) an upstream aperture 124 and a downstream aperture 126 or (ii) offset aperture pairs 174,176 and 184.186 as described below.
  • the individual sleeves 120 are joined together into a larger ring-like or cylindrical structure by connecting walls 122.
  • Apertures 124 and 126 may comprise columns of axially-oriented perforation holes or elongated slots which are radially aligned with the conduits 112. Alternatively, in a preferred embodiment also illustrated in one portion of Fig.
  • aperture pairs 174, 176 and184, 186 are slightly offset from radial alignment in a staggered slot arrangement.
  • the staggered slot arrangement for aperture pairs 174, 176 and 184, 186 is illustrated in Fig. 2A , with additional detail in Fig. 2B , where offset slot pairs 174, 176 and 184, 186 (replacing apertures pairs 124, 126) are staggered in elevation and offset slightly from the radial line from centerpoint 114 by equal angles 9.
  • Fig. 2B shows a side view taken along the line 2B-2B in Fig. 2A of a heat exchange conduit 112 having a cylindrical sleeve 120 with the preferred staggered slot arrangement.
  • FIG. 2A The plan view of this staggered slot conduit/sleeve combination as shown in Fig. 2A is taken along the line 2A-2A in Fig. 2B .
  • the ends of the slots from alternating offset slot pairs can be slightly overlapped or at equal elevation so there is no interruption of flow along the axial direction of the heat exchange apparatus.
  • This design with separation and overlap of the offset slots also leaves connection regions between the axially overlapped portions of adjacent offset slots, indicated generally by the reference numeral 190 in Fig. 2B , to provide the sleeves 120 with better circumferential mechanical integrity without blocking any fluid flow.
  • Fig. 2A shows one apertured sleeve 120 having the two-pair offset aperture configuration while the other sleeves have the one-pair aligned aperture configuration. In practice, however, all of the apertured sleeves for a particular apparatus 110 will typically have the same aperture configuration.
  • a process fluid 130 is flowed axially into the inner cylindrical region 116 having centerpoint 114 of the heat exchange apparatus 110 and then directed radially outward through upstream apertures 124, flowing cross-wise into contact with the heat exchange conduits 112, as denoted by the fluid flow arrows in Fig. 2A , thereby heating or cooling the process stream to form a thermally-conditioned fluid stream 132 which exits the interior regions defined by the sleeves 120 through downstream apertures 126.
  • fluid flowing radially outward would either flow through upstream aperture 174, into contact with conduit 112, and exit through downstream aperture 176, or, depending on the axial elevation, instead flow through aperture pair 184,186.
  • FIG. 2A illustrates a radially outward fluid flow path
  • the same apparatus could be utilized for thermally treating a process stream flowing radially inward to center region 116 and thereafter being axially withdrawn from region 116.
  • apertures 126 or 176 and 186
  • apertures 124 or 174 and 184
  • FIG. 3 shows a crossflow heat exchange apparatus 160 which is a variation of the crossflow heat exchange apparatus 110 shown in Fig. 2 .
  • Apparatus 160 differs from apparatus 110 in the use of a double, concentric circular array of heat exchange conduits instead of the single circular array of Fig. 2 .
  • there is a second circular array of heat exchange conduits 142 each in radial alignment with a corresponding conduit 112 of the first circular array.
  • Each conduit 142 is surrounded by an apertured sleeve 150 having an upstream aperture 164 and a downstream aperture 166.
  • Apertures 164 and 166 for a given sleeve 150 associated with a particular conduit 142 are shown substantially in radial alignment with the apertures 124 and 126 in the sleeve 120 of the corresponding radially adjacent conduit 112.
  • the individual sleeves 150 are joined together into a larger ring-like or cylindrical structure by walls 152.
  • Fig. 3 shows only a single conduit 142 of the second circular array of heat exchange conduits, it will be understood that each conduit 112 of the first circular array is associated with a corresponding conduit 142 of the second circular array.
  • a partially thermally-conditioned fluid stream 132 exiting first downstream apertures 126 in sleeves 120 is directed radially outward through second upstream apertures 164, flowing cross-wise into contact with the second array of heat exchange conduits 142, thereby further heating or cooling the process stream to form a fully thermally-conditioned fluid stream 162 which exits the interior region defined by the sleeves 150 through second downstream apertures 166.
  • Fig. 3 illustrates a radially-outward fluid flow path
  • the same apparatus could be utilized for thermally treating a process stream flowing radially inward to center region 116 and thereafter being axially withdrawn from region 116.
  • apertures 166 and 126 would be respectively the first and second upstream apertures
  • apertures 164 and 124 would be respectively the first and second downstream apertures.
  • Fig. 4 shows a portion of another crossflow heat exchange apparatus 210 according to this invention.
  • a double row of axially-disposed heat exchange conduits comprising a first upstream row of conduits 212 and second downstream row of conduits 216, are disposed in a generally rectangular array in conjunction with: a first, upstream apertured plate 220 having apertures 226; a second, intermediate apertured plate 222 having apertures 228, plate 222 separating the first and second rows of conduits; and, a third, downstream apertured plate 224 having apertures 230.
  • Each set of apertures 226, 228 and 230 associated with an upstream-downstream adjacent pair of conduits 212 and 216 is shown substantially in linear alignment with each other and with the associated pair of upstream and downstream conduits 212 and 216 respectively.
  • a process fluid 232 is directed, as denoted by the fluid flow arrows in Fig. 4 , through apertures 226 and flowed cross-wise into contact with first, upstream heat exchange conduits 212, thereby partially heating or cooling the process stream to form a partially thermally-conditioned fluid stream 234.
  • Stream 234 is then directed through apertures 228 and flowed cross-wise into contact with second, downstream heat exchange conduits 216 thereby further heating or cooling the process stream to form a fully thermally-conditioned fluid stream 236 which is flowed out of the apparatus 210 through exit apertures 230.
  • Fig. 5 illustrates two alternative possible fluid flow paths through a multi-row set of heat exchange conduits 312 arranged in an offset or triangular array in accordance with another embodiment of a crossflow heat exchange apparatus 310 according to this invention.
  • alternate rows of heat exchange conduits are offset from adjacent rows instead of having conduits in adjacent rows substantially in linear alignment as shown in Figs. 4 and 6 .
  • the centerpoints of three adjacent conduits in two adjacent rows form an equilateral triangle 340.
  • the apparatus of Fig. 5 includes upstream and downstream apertured plates respectively located before the after the last row of conduits, as well as intermediate apertured plates separating adjacent rows of conduits.
  • each conduit 312 may be surrounded with an apertured sleeve-like structure as previously described for other figures.
  • Fluid flow arrows 332 in Fig. 5 illustrate a first possible fluid flow orientation which can be utilized with the triangular conduit array of apparatus 310.
  • Fluid flow arrows 334 in Fig. 5 illustrate a second possible fluid flow orientation which can be utilized with the triangular conduit array of apparatus 310.
  • Fig. 5 shows four rows of heat exchange conduits in the triangular array, a smaller or larger number of conduit rows in this configuration may be utilized as appropriate.
  • FIG. 6 illustrates two alternative possible fluid flow paths through a multi-row set of heat exchange conduits 412 arranged in a square array in accordance with still another embodiment of a crossflow heat exchange apparatus 410 according to this invention.
  • conduits 412 in adjacent rows are substantially in linear alignment.
  • the centerpoint of four adjacent conduits in two adjacent rows form a square 440.
  • the apparatus of Fig. 6 includes upstream and downstream apertured plates respectively located before the first row of conduits and after the last row of conduits, as well as intermediate apertured plates separating adjacent rows of conduits.
  • each conduit 412 may be surrounded with an apertured sleeve as previously described.
  • Fluid flow arrows 432 in Fig. 6 illustrate a first possible fluid flow orientation which can be utilized with the square conduit array of apparatus 410.
  • Fluid flow arrows 434 in Fig. 6 illustrate a second possible fluid flow orientation which can be utilized with the square conduit array of apparatus 410.
  • Fig. 6 shows five rows of heat exchange conduits in the square array, a smaller or larger number of conduit rows in this configuration may be utilized as appropriate.
  • FIG. 7 illustrates still another variation of an enhanced crossflow heat transfer apparatus 510 according to this invention.
  • each heat exchange conduit512 is associated with one or more lateral flow-constriction plates 520, 522, 524, 526, and 528 positioned alongside conduit 512 and oriented generally orthogonal to the direction of fluid flow, as indicated by arrows 530 and 532.
  • the edges of the lateral plates 520, 522, 524, 526 and 528 closest to conduit 512 are spaced apart from the exterior walls of conduit 512 so as to create two fluid openings or channels between the plate edges and the conduit wall, one along each side of each conduit 512.
  • the spacing between the plate edges and the conduit wall may be adjusted by routine experimentation to optimize the contouring of the fluid flow path to maximize heat transfer. Where two or more lateral flow-constriction plates are utilized for each conduit 512, the spacing between the plate edges and the conduit wall may be the same or different in order to optimally contour the fluid flow path.
  • the lateral flow-constriction plates may be positioned alongside conduit 512 such that the plane of the plate passes through the centroid 518 of conduit 512 (such as plate 524), or else be positioned such that the planes of the plates intersect conduit 512 upstream (such as plates 520 and 526) of centroid 518, or downstream (such as plates 522 and 528) of centroid 518, or any combination thereof.
  • the distance 542 between the aperture and the conduit centroid 518 may be less than one-half of the diameter 544 as shown, with a distance approaching zero as a limit, for example plate 524.
  • lateral plate positioned alongside a heat exchange conduit is meant to refer to plates such as 520, 522, 524, 526 and 528 in Fig. 7 , oriented generally orthogonal to the direction of fluid flow, wherein the plane of the plate intersects any part of the heat exchange conduit.
  • FIG. 8 illustrates another variation of an enhanced crossflow heat transfer apparatus610 according to this invention showing a variation of the apertured sleeve configuration shown in Fig. 2 .
  • each heat exchange conduit 612 is partially surrounded by a pair of oppositely curved plates 620 generally conforming to the curvature of the outer wall of conduit 612 in a clam-shell configuration.
  • Each curved plate 620 is joined to a wall or lateral plate 622 positioned generally orthogonal to the direction of fluid flow, as indicated by arrows 630 and 632.
  • the pair of curved plates 620 around either side of a given conduit 612 do not touch each other and do not extend either upstream or downstream of the outer wall of conduit 612.
  • a line or plane connecting the upstream or downstream edges of a pair of curved plates 620 would intersect conduit 612.
  • the upstream and downstream openings between the pairs of curved plates 620 are the apertures through which the process fluid stream is directed to realize preferential contouring of the fluid stream.
  • the distance 642 between the aperture and the conduit centroid 618 may be less than one-half of the diameter 644 as shown, with a distance approaching zero as a limit, for example, as the lengths of curved plates 620 approach zero leaving only lateral plate 622, a configuration corresponding to Fig. 7 with a single plate 524. This differs from the baffle structures shown in Figs.1 and 4 where the distance between the apertures and the conduit centroid is greater than one-half the diameter of the conduit.
  • the clam-shell configuration of Fig. 8 with each pair of curved plates 620 around the sides of each conduit 612 differs from the slotted sleeve configuration of Fig. 2 in that in Fig. 8 a line or plane connecting the edges of the upstream and downstream fluid openings intersects the conduit 612, which is not the case for the slotted sleeves shown in Fig. 2A .
  • the embodiment of Fig. 8 may be viewed as an extreme version of the embodiment of Fig. 7 wherein the individual lateral plates positioned alongside the heat exchange conduit are not spaced apart, as seen in Fig. 7 , but instead are positioned face to-face with one another such that their conduit-side edges form the curved plates 620 of Fig. 8 .

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  • Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Polymers With Sulfur, Phosphorus Or Metals In The Main Chain (AREA)
  • Extraction Or Liquid Replacement (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Central Heating Systems (AREA)
  • Laying Of Electric Cables Or Lines Outside (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP00958015A 1999-07-21 2000-07-18 Enhanced crossflow heat transfer Expired - Lifetime EP1203195B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US14494899P 1999-07-21 1999-07-21
US144948P 1999-07-21
PCT/US2000/040401 WO2001007857A1 (en) 1999-07-21 2000-07-18 Enhanced crossflow heat transfer

Publications (3)

Publication Number Publication Date
EP1203195A1 EP1203195A1 (en) 2002-05-08
EP1203195A4 EP1203195A4 (en) 2005-09-28
EP1203195B1 true EP1203195B1 (en) 2009-10-28

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ID=22510885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00958015A Expired - Lifetime EP1203195B1 (en) 1999-07-21 2000-07-18 Enhanced crossflow heat transfer

Country Status (15)

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EP (1) EP1203195B1 (pt)
JP (1) JP2003509650A (pt)
KR (1) KR100768763B1 (pt)
CN (1) CN1292221C (pt)
AT (1) ATE447154T1 (pt)
AU (1) AU6955000A (pt)
BR (1) BR0012680B1 (pt)
CA (1) CA2379283C (pt)
CZ (1) CZ2002250A3 (pt)
DE (1) DE60043227D1 (pt)
ES (1) ES2331405T3 (pt)
MX (1) MXPA02000709A (pt)
PT (1) PT1203195E (pt)
TW (1) TW512219B (pt)
WO (1) WO2001007857A1 (pt)

Families Citing this family (8)

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Publication number Priority date Publication date Assignee Title
JP5612749B1 (ja) * 2013-10-25 2014-10-22 増山 征男 気体冷却装置
FR3048769B1 (fr) 2016-03-14 2019-05-17 Commissariat A L'energie Atomique Et Aux Energies Alternatives Procede de fabrication d'au moins un echangeur de chaleur a plaques par superposition de plaques avec motifs d'alignement
CN106247824A (zh) * 2016-07-29 2016-12-21 太仓英达锅炉设备有限公司 一种换热装置及其组合换热片
JP6950921B2 (ja) * 2017-03-09 2021-10-13 株式会社サムソン 給水予熱装置を持ったボイラ
CN107008206A (zh) * 2017-06-12 2017-08-04 上海理工大学 一种热管式气体水合物快速生成装置
CN107726905A (zh) * 2017-09-27 2018-02-23 北京工业大学 卧式高温蓄热供热设备及使用方法
JP2020051671A (ja) * 2018-09-26 2020-04-02 株式会社ノーリツ 温水装置
CN112122616A (zh) * 2020-08-24 2020-12-25 武汉汉维新材料科技有限责任公司 一种定向微通道和无序孔复合热沉及其制备方法

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Publication number Priority date Publication date Assignee Title
FR436949A (pt)
GB550145A (en) * 1941-07-29 1942-12-24 Briggs & Co Ltd S Improved construction of apparatus for heating liquids
US3616849A (en) * 1970-02-24 1971-11-02 Johannes C Dijt Heat exchange means
US3908628A (en) * 1973-10-16 1975-09-30 Thermo Electron Corp Jet impingement recuperator
FR2340524A1 (fr) * 1976-02-09 1977-09-02 Commissariat Energie Atomique Echangeur de chaleur a rechauffeur
US4284133A (en) * 1979-09-19 1981-08-18 Dunham-Bush, Inc. Concentric tube heat exchange assembly with improved internal fin structure
JPS5915796A (ja) 1982-07-20 1984-01-26 Ishikawajima Harima Heavy Ind Co Ltd 多管式熱交換器
JPS5959242A (ja) 1982-09-28 1984-04-05 Toyo Eng Corp 反応方法およびそのための反応器

Also Published As

Publication number Publication date
PT1203195E (pt) 2009-12-03
BR0012680B1 (pt) 2008-11-18
TW512219B (en) 2002-12-01
EP1203195A1 (en) 2002-05-08
JP2003509650A (ja) 2003-03-11
CN1361856A (zh) 2002-07-31
ES2331405T3 (es) 2010-01-04
CZ2002250A3 (cs) 2002-09-11
AU6955000A (en) 2001-02-13
MXPA02000709A (es) 2003-01-28
DE60043227D1 (de) 2009-12-10
CA2379283A1 (en) 2001-02-01
ATE447154T1 (de) 2009-11-15
WO2001007857A1 (en) 2001-02-01
BR0012680A (pt) 2002-10-22
CA2379283C (en) 2009-02-03
CN1292221C (zh) 2006-12-27
KR20020073327A (ko) 2002-09-23
EP1203195A4 (en) 2005-09-28
WO2001007857A8 (en) 2001-09-13
KR100768763B1 (ko) 2007-10-19

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