EP2110635A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP2110635A1
EP2110635A1 EP07832211A EP07832211A EP2110635A1 EP 2110635 A1 EP2110635 A1 EP 2110635A1 EP 07832211 A EP07832211 A EP 07832211A EP 07832211 A EP07832211 A EP 07832211A EP 2110635 A1 EP2110635 A1 EP 2110635A1
Authority
EP
European Patent Office
Prior art keywords
flow path
heat exchanger
primary
exchanger according
secondary flow
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Withdrawn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
EP07832211A
Other languages
German (de)
English (en)
Other versions
EP2110635A4 (fr
Inventor
Takanari Inatomi
Hiroshi Nakamura
Kazuyoshi Aoki
Shigeki Maruyama
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.)
Toshiba Corp
Original Assignee
Toshiba Corp
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 Toshiba Corp filed Critical Toshiba Corp
Publication of EP2110635A1 publication Critical patent/EP2110635A1/fr
Publication of EP2110635A4 publication Critical patent/EP2110635A4/fr
Withdrawn legal-status Critical Current

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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the present invention relates to a heat exchanger of stacked plate type, and more particularly, to a heat exchanger processing a fluid of high temperature and high pressure requiring a large heat exchange rate, having a compact structure, and performing an excellent work in reducing pressure loss.
  • a heat exchanger of stacked plate type including a flow path member which is formed by metal plates being subjected to groove-forming processing, stacked and bonded to each other, the flow path member including the grooves formed between as a primary flow path and a secondary flow path for heat exchange respectively.
  • the stacked plate type heat exchangers proposed in the past include, for example, a heat exchanger having a structure of sandwiching one plate formed with perforations for flowing a secondary fluid therethrough between two plates formed with perforations for flowing a primary fluid therethrough, and causing the two plates to be firmly attached to each other (for example, refer to Japanese Patent No. 2862213 , (Patent Document 1)).
  • Patent Document 2 Japanese Unexamined Patent Application Publication No. 2000-506966
  • the heat exchangers proposed in the past technology aim at compactness of the structure, they do not necessarily assume a fluid at high temperature and high pressure requiring a large heat exchange rate as a target fluid, and thus, they are not applicable to, for example, a power generation facility and a hydrogen production facility using a high temperature gas furnace as a heat source.
  • Non-Patent Document 1 a common technology installing a high temperature and high pressure heat exchanger is disclosed (refer to INL/EXT-05-00453, 2005, Thermal-Hydraulic Analyses of Heat Transfer Fluid Requirements and Characteristics for Coupling a Hydrogen Product Plant to a High-Temperature Nuclear Reactor, Idaho National Laboratory, (for example, Figures 1 and 2 of page 5), (Non-Patent Document 1)).
  • a heat exchanger which is applicable to a plant operating under high temperature and high pressure conditions of 4 to 7 MPa of pressure difference between the primary fluid and the secondary fluid and 800°C to 900°C of maximum operating temperature, such as a power generation facility or a hydrogen production facility using a high temperature gas furnace as the heat source.
  • the present invention has been made to solve the above-described deficiencies, and an object of the present invention is to provide a stacked plate type heat exchanger having compactness providing a heat exchange rate per unit volume of 10 MWt/m 3 or more, wherein it is possible to provide a heat exchanger applicable under high temperature and high pressure conditions of 4 to 7 MPa of pressure difference between the primary fluid and the secondary fluid and 500°C to 900°C of the maximum operating temperature, providing the compactness and providing high performance and structural integrity under the conditions.
  • Non-Patent Document 1 Investigation of strength evaluation formula, (2) investigation of allowable stress, (3) determination of flow path dimensions and limit thereof, (4) equivalent diameter, (5) grounds for set values in claims, (6) parameter survey, and the like, are investigated.
  • Fig. 6 shows a semicircular flow path
  • Fig. 15 shows a tetragonal flow path.
  • the strength evaluation formula for determining a size of a heat exchanger having a such type of flow path is expressed as follows based on the above reference literature (Non-Patent Document 1), from which formula the respective flow path dimensions, tf, Pf, and tp, are determined.
  • Pf is a pitch of flow paths in a horizontal direction
  • d is a width of flow path in a horizontal direction
  • tp is a pitch between flow paths
  • tf is a distance between flow paths in a horizontal direction.
  • a necessary distance tf between the flow paths in the horizontal direction is limited to t f ⁇ P f S 0 ⁇ ⁇ P + 1
  • a thickness of plate tp which is the pitch of flow paths in a vertical direction is limited by a following formula. t p ⁇ d 2 ⁇ S 0 + P i S 0 + 2 ⁇ P o - P i
  • the 10 3 h creep fracture stress intensity of an iron-based oxide dispersion strengthened alloy containing chromium and aluminum is 80 MPa at 900°C.
  • a value multiplied by 0.5 is adopted as a safety factor.
  • the maximum allowable stress intensity So is used as the allowable stress.
  • the 10 5 h creep fracture strength becomes predominant, so that the 10 5 h creep fracture strength is used for calculating So.
  • the value of So is determined, referring to the JSME design and construction standards or the ASME Code, by multiplying the average value of 10 5 h creep fracture strength with a factor 0.67.
  • the allowable stress is calculated as below, and the value is set at 25 MPa on a safety side.
  • the plate thickness is determined based on the dimensions of a base material.
  • the equivalent diameter d e1 of a semicircular flow path is calculated as follows based on the dimensions of paragraph (3).
  • the equivalent diameter d e2 of tetragonal flow path is calculated as follows based on the dimensions of paragraph (3).
  • the calculations are conducted to confirm that the minimum thickness of the thin metal sheet-shaped plate is 0.3 times or more of the equivalent diameter of the flow path, and that the pitch distance of flow paths in the plate width direction is 0.5 times or more of the equivalent diameter of flow path.
  • a heat exchanger comprising a flow path member which is formed by stacking and bonding metal plates which is subjected to a groove-forming processing, the grooves being formed as a primary flow path and a secondary flow path for heat exchange between the metal plates of the flow path member, wherein a heat exchanging rate per unit volume between both fluids flowing through the respective flow paths is set at 10 MWt/m 3 or more, a thickness of the metal plate is set at 0.3 times or more of an equivalent diameter of the flow path, and a pitch between the flow paths along a width direction of the metal plate is set at 0.5 times or more of the equivalent diameter of the flow path.
  • a heat exchanger comprising a flow path member which is formed by stacking and bonding metal plates which is subjected to a groove-forming processing, the grooves being formed as a primary flow path and a secondary flow path for heat exchange between the metal plates of the flow path member, wherein the metal plate is composed of an iron-based oxide dispersion strengthened alloy containing chromium and aluminum.
  • the primary flow path and the secondary flow path may be provided, respectively, with fluid inlet ports and fluid outlet ports at surfaces of a main heat exchange portion of the flow path member along flow directions of the fluids.
  • the flow path member may be provided with plenum portions for branching or combining the primary flow path and the secondary flow path, and the fluid inlet ports and the fluid outlet ports of the primary flow path and the secondary flow path, respectively, communicating with the plenum portions are provided at surfaces of the main heat exchange portion of the flow path member along flow directions of the fluids or at surfaces thereof along directions perpendicular to the flow directions of the fluids.
  • the primary flow path and the secondary flow path may be wave-shaped flow paths.
  • the respective flow paths may be provided with bent portions in which a guide vane or a reinforcement material for guiding each of the fluids along the bent portion.
  • the primary flow path and the secondary flow path may have cross sectional shapes formed in semicircle, tetragon, hexagon, or other polygon shape.
  • the primary flow path and the secondary flow path may have cross sectional areas which are set to be equal with each other, or are set such that a cross sectional area of the secondary flow path is larger than a cross sectional area of the primary flow path.
  • At least one of the primary flow path and the secondary flow path may be formed as a reciprocating flow path in a U-shape, and both front end portions of the reciprocating flow path communicate with the fluid inlet port or the fluid outlet port or with the plenums provided on a same surface of the flow path member.
  • the grooves formed as the primary flow path or the secondary flow path may be formed in a manner arranged adjacent to each other on the same metal plate.
  • Fig. 1 is a perspective view of the heat exchanger of the first embodiment of the present invention.
  • a heat exchanger 3 of the first embodiment is constituted by stacking the thin metal plates 1 and 2, which are one pair of opposing metal plates, as one set (hereinafter referred to as "the plates").
  • the metal plate 1 is a plate for the flow of primary fluid, having a number of semicircular grooves 8a functioning as a flow path 8 of the primary fluid "a" on one side surface thereof.
  • the other metal plate 2 is a plate for the flow of secondary fluid having a number of semicircular grooves 8b functioning as a flow path 9 of the secondary fluid "b" on one side surface thereof.
  • the plate 1 for the flow of primary fluid is, for example, in a rectangular shape.
  • a plurality of grooves 8 opens at one side-edge portion at an end side in the longitudinal direction of the plate 1 so as to form a primary fluid inlet port 14, and extends in parallel to each other in the width direction as a shorter side of the plate, and then opens at the other side-edge portion at an end side in the longitudinal direction of the plate 1 to thereby form a primary fluid outlet port 18. That is, the primary fluid forms a main heat exchange portion to flow the primary fluid "a" upward from the lower side of Fig. 2 .
  • the plate 2 for the flow of secondary fluid has the rectangular shape identical to that of the plate 1 for the flow of the primary fluid.
  • a plurality of grooves 9 opens, for example, at a side-edge part at one end side edge portion in the longitudinal direction of the plate 2 to form the primary fluid inlet port 14, and extends linearly to and opens at the other side edge portion at the other end side in the longitudinal direction, thus forming a secondary fluid outlet port 19.
  • the plate 2 for the flow of the secondary fluid forms the main heat exchange portion to let the secondary fluid "b" flow downward from upper side of Fig. 2 .
  • the plates 1 for the flow of the primary fluid and the plates 2 for the flow of the secondary fluid are integrated by bonding them together with surfaces having no grooves 8a and 9a which form the flow paths 8 and 9, respectively, facing the same direction each other, by stacking the bonded plates, for example, in a state that the surface having grooves of a plate face the surface without grooves of the other plate, and by, for example, diffusion bonding the plates.
  • Figs. 4 and 5 illustrate a structure in which the above-described plates 1 and 2 are bonded together to form flow paths 5 (primary flow path 8 and secondary flow path 9) separately by wall portions 1a and 1b, and are integrated with each other, while forming the primary flow path 8 and the secondary flow path 9 into semicircular cross section.
  • the primary flow path 8 and the secondary flow path 9 are in a wave-shaped flow path, and the cross sectional areas of the primary flow path 8 and the secondary flow path 9 are designed to be the same with each other.
  • Fig. 6 shows the dimensions and the like of the respective flow paths 8 and 9, that is, Pf: as the flow path pitch in the horizontal direction; d: as the flow path width in the horizontal direction; tp: as the pitch of flow paths; and tf: as the distance between flow paths in the horizontal direction.
  • the setting is determined so as to keep the strength to endure the conditions of temperature range of the primary fluid "a” supplied to the primary flow path 8 in a range from 800°C to 900°C, the pressure difference between the primary fluid "a” and the secondary fluid “b” in a range from 4 to 7 MPa, and the heat exchange rate per unit volume between fluids of 10 MWt/m 3 or more.
  • each of the plates 1 and 2 has a thickness of 0.3 times or more of the equivalent diameter of flow path, and the pitch tp of flow paths in the width direction of the plates 1 and 2 is 0.5 times or more of the equivalent diameter of flow path.
  • the plates 1 and 2 are made of an iron-based oxide dispersion strengthened alloy containing chromium and aluminum, such as INCOLOY alloy 956 (Fe: 75%, Cr: 20%, Al: 4.5%, Ti: 0.5%, C: 0.05%, and Y 2 O 3 : 0.5%).
  • INCOLOY alloy 956 Fe: 75%, Cr: 20%, Al: 4.5%, Ti: 0.5%, C: 0.05%, and Y 2 O 3 : 0.5%).
  • the plate 1 having a number of flow paths of the primary fluid with the plate 2 having a number of flow paths of the secondary fluid are stacked and integrated by means of, for example, diffusion joining, thus forming the heat exchanger 3.
  • Fig. 2 illustrates a case of the opposing flows of a flow 15 of the primary fluid entering through the primary fluid inlet port 14 and a flow 17 of the secondary fluid flow entering through a secondary fluid inlet port 16.
  • this case may give the best heat exchanging performance, depending on the use, flows parallel to each other may be adopted.
  • the structural material 10 there may be used an iron-based oxide dispersion strengthened (ODS) alloy having high temperature strength of about 25 MPa of allowable stress at 900°C, for example INCOLOY alloy MA 956, and there may be adopted dimensions that the distance P f 11 between flow paths in the vertical direction is set at 0.7 times or more of the diameter dl 2 of the semicircular flow path and that the distance 13 of flow paths in the horizontal direction is set at 1.3 times or more of the diameter dl 2 of the semicircular flow path.
  • the structural material 10 may be a high nickel-based alloy, such as Alloy 617.
  • a heat exchanger realizing compactness having a heat exchanging rate per unit volume of 10 MWt/m 3 or more, thus providing high performance and excellent structural integrity.
  • the second embodiment provides a structure in which the fluid inlet port and the fluid outlet port of the respective primary flow path and secondary flow path are provided on the surface of a flow path member along the fluid flow direction at the main heat exchange portion of the flow path member.
  • the second embodiment is also composed of the plate 1 having the flow path of the primary fluid and the plate 2 having the flow path of the secondary fluid.
  • the primary fluid inlet port 14 and the secondary fluid outlet port 19 are positioned on the same surface, and the primary fluid outlet port 18 and the secondary fluid inlet port 16 are also arranged on the same surface, so that the inlet ports 14 and 16 and the outlet ports 18 and 19 of the primary fluid and the secondary fluid are arranged, respectively, along the fluid flow direction.
  • both the primary flow path 8 and the secondary flow path 9 are formed along the longitudinal direction of the plate 1. Further the other structure is the same to that of the first embodiment.
  • the primary fluid outlet/inlet port 14 is provided at the position in a direction perpendicular to the secondary fluid outlet/inlet port 16, or at the side surface of the heat exchanger
  • the primary fluid outlet/inlet port 14 and the secondary fluid outlet/inlet port 16 are positioned on the same surface, so that it is not necessary to install a header or piping on the side surface, thereby decreasing the outer configuration of the heat exchanger 3.
  • the flow direction does not turn in right angle as in the case of the first embodiment, and accordingly, in the second embodiment, the pressure loss can be kept at a low level.
  • a heat exchanger having compact structure providing a heat exchange rate per unit volume of 10 MWt/m 3 or more can be provided, thus achieving excellent performance to reduce the pressure loss.
  • this third embodiment also relates to a heat exchanger having the plate 1 provided with the flow path of the primary fluid and the plate 2 provided with the flow path of the secondary fluid.
  • the primary flow path 8 is branched and then combined, and connected to plenums 20 functioning as an inlet port and an outlet port of the flow path, respectively, at side surfaces of the heat exchanger.
  • this third embodiment can decrease a region 22 in which fluid does not flow countercurrently.
  • this third embodiment provides a heat exchanger having compact structure providing a heat exchanging rate per unit volume of 10 MWt/m 3 or more, thus providing excellent performance to reduce the pressure loss.
  • the fourth embodiment describes a heat exchanger equipped with guide vanes or reinforcement materials in the bent portion of each flow path for guiding each fluid along the bent portion.
  • the fourth embodiment constitutes the heat exchanger 3 by the plate walls 1a forming the flow path and guide vanes 24.
  • a flow 25 of fluid flowing through the flow path 5 is suppressed from generating vortex and separation at curved portions owing to the guide vanes 24 provided at the curved portions of the flow path 5 to thereby reduce the pressure loss.
  • Other structure is almost the same to that of previous embodiments.
  • this fourth embodiment can provide a heat exchanger having compact structure providing a heat transfer rate per unit volume of 10 MWt/m 3 or more, thus providing excellent performance to reduce the pressure loss.
  • the fifth embodiment describes a heat exchanger in which the cross sectional area of the secondary flow path is set to be larger than that of the primary flow path.
  • the fifth embodiment forms the secondary flow path 9 having larger flow path cross sectional area than that of the primary flow path 8.
  • Other structure is almost the same to that of the previous embodiments.
  • a secondary flow path 26 which has larger flow path cross sectional area suppresses the increase in the velocity of the secondary fluid, which can reduce the pressure loss of the secondary fluid.
  • this fifth embodiment can provide a heat exchanger having compact structure providing a heat exchanging rate per unit volume of 10 MWt/m 3 or more, thus providing excellent performance to reduce the pressure loss.
  • the sixth embodiment forms flow paths 27 in a cross section of almost rectangular shape in the flow path member 4.
  • Fig. 15 shows the dimensions and the like of the respective flow paths 8 and 9, in which character Pf denotes the flow path pitch in the horizontal direction; letter “d” denotes the flow path width in the horizontal direction, tp denotes the pitch of flow paths; and tf denotes the distance between flow paths in the horizontal direction.
  • this sixth embodiment having the structure mentioned above provides the flow paths 8 and 9 having almost rectangular cross section. These flow paths 8 and 9 increase the heat transfer area with the structural material of the flow path member 4, thus the heat transfer performance being further improved.
  • polygonal cross section such as hexagonal shape, other than tetragonal shape, may be applied. Even with such a structure, the flow paths 8 and 9 increase the heat transfer area with the structural material of the flow path member 4 so that the heat transfer performance can be increased.
  • a heat exchanger having compact structure providing a heat transfer rate per unit volume of 10 MWt/m 3 or more can be provided, thus achieving high performance and excellent structural integrity.
  • the seventh embodiment describes a heat exchanger in which the plenum portions are formed in the flow path member each branching and combining the primary flow path and the secondary flow path, respectively.
  • the fluid inlet ports and the fluid outlet ports of the primary flow path and the secondary flow path, respectively, communicating with the respective plenum portions are provided at surfaces of the main heat exchanging portion of the flow path member along the flow directions of the fluids or at surfaces thereof along directions perpendicular to the flow directions of the fluids.
  • This seventh embodiment provides the heat exchanger with the plate 1 provided with the primary flow path and the plate 2 provided with the secondary flow path.
  • the primary flow path 8 is branched and then combined to be connected with primary plenums 28 serving as the primary flow path inlet port 14 and the primary flow path outlet port 19 at the front surface and the rear surface of the heat exchanger, respectively.
  • the secondary flow path 9 also has the secondary flow path inlet port 16 of and the secondary flow path outlet port 18, formed by a secondary plenums 29, at the front surface and the rear surface of the heat exchanger, respectively, thereby making it possible to arrange the inlet/outlet ports of the primary flow path and the secondary flow path in the fluid flow direction.
  • the flow path outlet/inlet ports are positioned only on both end-surfaces, it is not necessary to position the flow path outlet/inlet portions at side surface, and it becomes possible to provide the structure reducing the region of cross flow appeared in the case of the first embodiment, thus reducing the longitudinal size of the heat exchanger.
  • the seventh embodiment it is possible to provide a heat exchanger having compact structure providing a heat exchanging rate per unit volume of 10 MWt/m 3 or more.
  • the eighth embodiment describes a heat exchanger in which at least one of the primary flow path and the secondary flow path is formed as reciprocating flow path in a U-shape.
  • This eighth embodiment provides the heat exchanger with the plate 1 provided with the primary flow path and the plate 2 provided with the secondary flow path.
  • the secondary flow path inlet port 16 and the primary flow path outlet port 18 are positioned at front surface and rear surface of the heat exchanger, respectively.
  • the eighth embodiment can provide a heat exchanger having excellent compact structure providing a heat exchanging rate per unit volume of 10 MWt/m 3 or more.
  • This ninth embodiment describes a heat exchanger in which the grooves functioning as the primary flow path and the secondary flow path, respectively, are formed in such an arrangement that the grooves are arranged adjacent to each other on the same metal plate, and the front end portions of the primary flow path and the secondary flow path communicate with the respective fluid outlet ports and the plenums provided on the same surface of the flow path member.
  • the heat exchanger is provided with plates 30 in which the primary flow path 8 and the secondary flow path 9 are positioned adjacent to each other. Furthermore, the front end portions of the primary flow path 8 and the secondary flow path 9 communicate with the respective fluid outlet ports 18 and 19 opened on the same surface as upper surface of the flow path member and also communicate with the respective plenums 31 and 32 extending in the vertical direction.
  • the primary flow path 8 and the secondary flow path 9 are positioned on the same plate, the heat transfer between the fluids can be enhanced, and it is possible to arrange primary fluid outlet port 18 and the secondary fluid outlet port 19 in a surface parallel with the plate 30 provided with the primary flow path and the secondary flow path owing to the vertically located plenums 31.
  • the heat exchanging function is conducted only by countercurrent flow mode, eliminating the cross flow, and thus, the outer size of the heat exchanger can be reduced.
  • the ninth embodiment it is possible to provide a heat exchanger having compact structure exhibiting a heat exchanging rate per unit volume of 10 MWt/m 3 or more, thus achieving excellent heat exchange performance.
  • the tenth embodiment describes a heat exchanger in which at least one of the primary flow path and the secondary flow path is formed as reciprocating flow path so as to provide a U-shape, and the front end portions of the reciprocating flow paths communicate with the fluid inlet port and/or the fluid outlet port of the plenum.
  • the heat exchanger is formed with plates 30 in which the primary flow path and the secondary flow path are provided, giving a modification of the ninth embodiment, arranging the primary flow path 8 in U-shape and the secondary flow path 9 in U-shape on the same plate.
  • the structure makes the heat exchange portion solely countercurrent flow.
  • the tenth embodiment can reduce the outer size of the heat exchanger, and further the presence of turning portion in U-shape increases heat exchange density.
  • a heat exchanger having compact structure providing a heat transfer rate per unit volume of 10 MWt/m 3 or more can be provided, thus achieving excellent heat exchange performance.
  • the eleventh embodiment describes a heat exchanger in which reinforcement materials are provided in the curved portion of each flow path so as to guide the fluid along the curved portion.
  • the heat exchanger is configured with the plate 1 provided with the primary flow path, the plate 2 provided with the secondary flow path, and the flow path reinforcement materials 32 shown in the flow path enlarged view of Fig. 27 .
  • the flow path reinforcement materials 32 increase the stiffness of upper and lower surfaces of the flow path of the plate, or increase the geometric moment of inertia, thereby significantly increasing the pressure-resistance performance. Furthermore, since the flow path reinforcement materials 32 also play the role of heat transfer fins or turbulators, thus considerably contributing to the improvement of heat transfer performance.
  • a heat exchanger having compact structure providing a heat transfer rate per unit volume of 10 MWt/m 3 or more can be provided, thus achieving high performance and excellent structural integrity.
  • the twelfth embodiment describes a heat exchanger 3 in which the flow path structuring member 4 has near-hexagonal shape in planar view, with both end portions thereof in near-triangular shape.
  • the heat exchanger of this twelfth embodiment is provided with the plate 1 provided with the primary flow path and the plate 2 provided with the secondary flow path, and both end portions of each plate are formed into approximately triangular shape.
  • the primary fluid "a” and the secondary fluid “b” enter the primary fluid inlet ports 14 adjacent to each other and the secondary fluid inlet ports 16 at opposite side to the primary fluid inlet ports 14, and the respective fluids are discharged from the primary fluid outlet ports 18 and the secondary fluid outlet ports 19, arranged at substantially parallel with each other.
  • the materials of fluid inlet/ outlet portions can be reduced in comparison with the case of the rectangular plate 2, and cost reduction can be achieved. Furthermore, the obtuse angle of the curve of the flow path may reduce the pressure loss.
  • the twelfth embodiment can provide a heat exchanger having compact structure providing a heat exchange rate per unit volume of 10 MWt/m 3 or more, thus reducing cost and pressure loss.

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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)
EP07832211.2A 2006-11-21 2007-11-20 Échangeur de chaleur Withdrawn EP2110635A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006314864A JP2008128574A (ja) 2006-11-21 2006-11-21 熱交換器
PCT/JP2007/072481 WO2008062802A1 (fr) 2006-11-21 2007-11-20 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP2110635A1 true EP2110635A1 (fr) 2009-10-21
EP2110635A4 EP2110635A4 (fr) 2013-12-11

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EP07832211.2A Withdrawn EP2110635A4 (fr) 2006-11-21 2007-11-20 Échangeur de chaleur

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US (1) US20100051248A1 (fr)
EP (1) EP2110635A4 (fr)
JP (1) JP2008128574A (fr)
WO (1) WO2008062802A1 (fr)

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FR2991443A1 (fr) * 2012-06-05 2013-12-06 Technicatome Echangeur de chaleur a plaques visant des debits homogenes de fluide entre canaux
EP2518428A3 (fr) * 2011-04-28 2014-04-16 Behr GmbH & Co. KG Echangeur thermique à empilement
WO2017019142A1 (fr) * 2015-07-24 2017-02-02 Exxonmobil Upstream Research Company Transfert de chaleur amélioré dans des échangeurs de chaleur à circuit imprimé
CN106996708A (zh) * 2016-01-22 2017-08-01 株式会社神户制钢所 热交换器及热交换方法

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JP2015031420A (ja) * 2013-07-31 2015-02-16 株式会社神戸製鋼所 水素ガスの冷却方法及び水素ガスの冷却システム
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JP6432613B2 (ja) * 2017-01-13 2018-12-05 ダイキン工業株式会社 水熱交換器
US10823511B2 (en) 2017-06-26 2020-11-03 Raytheon Technologies Corporation Manufacturing a heat exchanger using a material buildup process
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US20100051248A1 (en) 2010-03-04

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