WO2008062802A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2008062802A1
WO2008062802A1 PCT/JP2007/072481 JP2007072481W WO2008062802A1 WO 2008062802 A1 WO2008062802 A1 WO 2008062802A1 JP 2007072481 W JP2007072481 W JP 2007072481W WO 2008062802 A1 WO2008062802 A1 WO 2008062802A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow path
heat exchanger
channel
fluid
primary
Prior art date
Application number
PCT/JP2007/072481
Other languages
English (en)
Japanese (ja)
Inventor
Takanari Inatomi
Hiroshi Nakamura
Kazuyoshi Aoki
Shigeki Maruyama
Original Assignee
Kabushiki Kaisha Toshiba
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 Kabushiki Kaisha Toshiba filed Critical Kabushiki Kaisha Toshiba
Priority to EP07832211.2A priority Critical patent/EP2110635A4/fr
Priority to US12/515,740 priority patent/US20100051248A1/en
Publication of WO2008062802A1 publication Critical patent/WO2008062802A1/fr

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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
    • 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 plate-stacked heat exchanger, and more particularly to a heat exchanger that has a compact configuration and is excellent in reducing pressure loss, with a fluid to be treated at high temperature and high pressure and a large amount of exchange heat.
  • a flow path member is configured by laminating and joining grooved metal plates, and a primary portion for heat exchange is formed between the metal plates of the flow path member.
  • Plate-stacked heat exchangers with system flow paths and secondary flow paths are used in various fields.
  • the force to be processed is designed to be compact, and the fluid to be processed is not necessarily assumed to be a fluid that is high temperature and pressure and requires a large amount of exchange heat.
  • the fluid to be processed is not necessarily assumed to be a fluid that is high temperature and pressure and requires a large amount of exchange heat.
  • the present invention has been made in order to solve the above-mentioned problems, and in a plate laminated heat exchanger having a compactness with an exchange heat quantity per unit volume of 10 MWt / m 3 or more, a primary fluid and a secondary fluid.
  • a plate laminated heat exchanger having a compactness with an exchange heat quantity per unit volume of 10 MWt / m 3 or more, a primary fluid and a secondary fluid.
  • Non-Patent Document 1 (1) Study of strength evaluation formula, (2) Study of allowable stress, (3) Channel size setting and limit value, (4) Equivalent straight line Examination of diameter, (5) grounds for setting in claims, (6) parameter survey, etc.
  • FIG. 6 and FIG. 15 in the following embodiment for the channel dimensions.
  • FIG. 6 shows a semicircular channel
  • FIG. 15 shows a rectangular channel.
  • the strength evaluation formula when sizing a heat exchanger having such a flow path is expressed as follows by the above-mentioned reference (Non-patent Document 1), and from these, the flow path dimensions d, t, P, t Is determined
  • Pf is the horizontal pitch of the flow path
  • d is the horizontal width of the flow path
  • tp is the pitch between the flow paths
  • tf is the horizontal interval between the flow paths.
  • the plate thickness t which is the pitch of the channel in the height direction, is expressed by the following relational expression.
  • the 10 5 h creep rupture strength is dominant at 500 ° C or higher, so this 10 5 h creep rupture strength is used for S calculation.
  • S is the JSME design / construction standard or Referring to ASME Code, obtain the average value of 10 5 h creep rupture strength by multiplying by 0.67. Therefore, the allowable stress is calculated as follows and set to 25 MPa on the safe side.
  • the plate thickness is determined from the material dimensions.
  • the equivalent diameter d of the flow path is expressed as follows, where the cross-sectional area A of the flow path and the wetting edge length of the flow path are S.
  • the equivalent diameter d of the semicircular channel is calculated as follows from the dimensions in (3).
  • the equivalent diameter d of the square channel is calculated as follows from the dimension of item (3). Woman 10]
  • a flow path member is configured by laminating and joining metal plates that have been grooved, and the flow path member is disposed in front of the portion between the plates.
  • a heat exchanger having a primary flow path and a secondary flow path for heat exchange composed of grooves, wherein the exchange heat quantity per unit volume between both fluids is set to 10 MWt / m3 or more, and the metal plate
  • the heat exchanger is characterized in that the plate thickness of the metal plate is 0.3 times or more of the equivalent diameter of the flow passage and the pitch between the flow passages along the width direction of the metal plate is 0.5 or more times of the equivalent diameter of the flow passage. Offer Provide.
  • a flow path member is configured by stacking and joining metal plates that have been subjected to groove processing, and a primary system flow for heat exchange including the grooves is formed between the plates of the flow path member.
  • a heat exchanger having a channel and a secondary system channel, wherein the metal plate is made of an iron-based oxide dispersion strengthened alloy containing chromium and an anorium. To do.
  • the fluid inlet and the fluid outlet of the primary system flow path and the secondary system flow path are fluid flow directions in a main heat exchange portion of the flow path member. May be provided on each of the surfaces.
  • a plenum portion for branching and joining the primary system flow channel and the secondary system flow channel, respectively, is formed in the flow channel member, and the primary system flow channel and the secondary fluid communicating with these planar portions are formed.
  • the fluid inlet and the fluid outlet of the system channel may be provided on the surface along the fluid flow direction or the surface along the direction orthogonal to the fluid flow direction in the main heat exchange portion of the channel member.
  • the primary system flow path and the secondary system flow path are preferably wave-shaped flow paths.
  • the channel cross-sectional shapes of the primary system channel and the secondary system channel may be semicircular, quadrangular, hexagonal or other polygonal shapes.
  • the flow path cross-sectional areas of the primary system flow path and the secondary system flow path are set to be equal to each other, or the latter is set larger than the former! /.
  • At least one of the primary system flow path and the secondary system flow path is formed as a reciprocating flow path that turns back in a U-shape, and both ends of the reciprocating flow path are formed on the flow path member. It is preferable to communicate with a fluid inlet and a fluid outlet or plenum provided on the same plane.
  • the grooves serving as the primary system flow path and the secondary system flow path are formed on the same metal plate in an arrangement adjacent to each other! /.
  • FIG. 1 is a perspective view showing a heat exchanger according to a first embodiment of the present invention.
  • FIG. 2 is an explanatory diagram showing the flow path configuration of the heat exchanger according to the first embodiment of the present invention (cross-sectional view taken along line II-II in FIG. 1).
  • FIG. 3 is an explanatory diagram (cross-sectional view of component parts) showing a plate structure constituting the heat exchanger according to the first embodiment of the present invention.
  • FIG. 4 is an explanatory view showing a flow path of the heat exchanger according to the first embodiment of the present invention (cross-sectional view taken along the line IV-IV in FIG. 3).
  • FIG. 5 is an explanatory view (longitudinal sectional view) showing the flow path configuration of the heat exchanger according to the first embodiment of the present invention.
  • FIG. 6 is an explanatory diagram regarding the setting of the heat exchanger according to the first embodiment of the present invention.
  • FIG. 7 is a perspective view showing a heat exchanger according to a second embodiment of the present invention.
  • FIG. 8 is an explanatory diagram showing a primary flow path of the heat exchanger according to the second embodiment of the present invention (sectional view taken along line VII I VIII in FIG. 7).
  • FIG. 9 is an explanatory view showing the secondary system flow path of the heat exchanger according to the second embodiment of the present invention (corresponding to the sectional view taken along the line VII I VIII in FIG. 7).
  • FIG. 10 is an explanatory view (transverse view) showing a primary flow path of a heat exchanger according to a second embodiment of the present invention.
  • FIG. 11 is an explanatory view (longitudinal sectional view) showing a secondary system flow path of a heat exchanger according to a third embodiment of the present invention.
  • FIG. 12 is an explanatory diagram (longitudinal sectional view) showing a flow path configuration of a heat exchanger according to a fourth embodiment of the present invention.
  • FIG. 13 is an explanatory diagram (longitudinal sectional view) showing a flow path configuration of a heat exchanger according to a fifth embodiment of the present invention.
  • FIG. 14 is an explanatory diagram (longitudinal sectional view) showing a flow path configuration of a heat exchanger according to a sixth embodiment of the present invention.
  • FIG. 15 is an explanatory diagram regarding the setting of a heat exchanger according to a sixth embodiment of the present invention.
  • FIG. 16 is an explanatory view (vertical sectional view) showing another flow path configuration of the heat exchanger according to the sixth embodiment of the present invention.
  • FIG. 17 is a perspective view showing a heat exchanger according to a seventh embodiment of the present invention.
  • FIG. 18 is an explanatory view showing a primary flow path of the heat exchanger according to the seventh embodiment of the present invention (cross-sectional view taken along line XVIII-XVIII in FIG. 17).
  • FIG. 19 is an explanatory view showing a secondary system flow path of a heat exchanger according to a seventh embodiment of the present invention (corresponding to a cross-sectional view taken along line XVIII-XVIII in FIG. 17).
  • FIG. 20 is a perspective view showing a heat exchanger according to an eighth embodiment of the present invention.
  • FIG. 21 is an explanatory view showing a primary flow path of the heat exchanger according to the eighth embodiment of the present invention (cross-sectional view taken along line XXI—XXI in FIG. 20).
  • FIG. 22 is an explanatory diagram showing the secondary system flow path of the heat exchanger according to the eighth embodiment of the present invention (corresponding to the XXI-XXI line sectional view of FIG. 20).
  • FIG. 23 is a perspective view showing a heat exchanger according to a ninth embodiment of the present invention.
  • FIG. 24 is an explanatory view showing a heat exchanger according to the ninth embodiment of the present invention (a sectional view taken along line XXIV-XXIV in FIG. 23).
  • FIG. 25 is a perspective view showing a heat exchanger according to a tenth embodiment of the present invention.
  • FIG. 26 is an explanatory view showing a heat exchanger according to the tenth embodiment of the present invention (cross-sectional view taken along line XXVI—XXVI in FIG. 25).
  • FIG. 27 is an enlarged sectional view (transverse sectional view) illustrating a heat exchanger according to an eleventh embodiment of the present invention.
  • FIG. 28 is a perspective view illustrating a heat exchanger according to a twelfth embodiment of the present invention.
  • FIG. 29 is an explanatory view showing a primary flow path of the heat exchanger according to the twelfth embodiment of the present invention (cross-sectional view taken along line XXIX XXIX in FIG. 28).
  • FIG. 30 is an explanatory diagram showing the secondary system flow path of the heat exchanger according to the twelfth embodiment of the present invention (corresponding to the cross-sectional view taken along the line XXIX—XXIX in FIG. 28).
  • FIG. 1 is a perspective view showing a heat exchanger according to the first embodiment of the present invention.
  • the heat exchanger 3 of this embodiment is a pair of opposed thin plates.
  • the metal plates 1 and 2 are formed as a set, and these metal plates (hereinafter referred to as “plates”) 1 and 2 are laminated.
  • One metal plate 1 is a primary fluid circulation plate provided on one side surface with a number of semicircular grooves 8a that serve as flow paths 8 through which the primary fluid a flows.
  • This is a secondary fluid circulation plate provided on one side surface with a number of semicircular grooves 8b that become the flow paths 9 for circulating the secondary fluid b.
  • the primary fluid circulation plate 1 has, for example, a rectangular shape, and the plurality of grooves 8 are opened, for example, at one side edge on one end side in the longitudinal direction as shown in FIG. And extending in parallel in the width direction, which is the short side, and then opening to the other side edge on one end side in the longitudinal direction to form a primary fluid outlet 18. That is, the primary fluid forms a main heat exchange section that allows the primary fluid a to flow upward from the lower side of FIG.
  • the secondary fluid circulation plate 2 has the same rectangular shape as the primary fluid circulation plate 1, and the plurality of grooves 9 are open at, for example, one edge of the longitudinal direction.
  • the primary fluid inlet 14 is formed, and the secondary fluid outlet 19 is formed by linearly extending to the other edge of the other end in the longitudinal direction.
  • the secondary fluid circulation plate 2 forms a main heat exchanging portion that allows the secondary fluid b to flow downward from the upper side of FIG.
  • the primary fluid circulation plate 1 and the secondary fluid circulation plate 2 do not have grooves 8a and 9a that form the flow paths 8 and 9, respectively.
  • the surfaces are joined to each other, for example, the formed surface and the groove are not formed! /, And the surfaces are laminated together and integrated by, for example, diffusion bonding.
  • FIG. 4 and FIG. 5 show that the flow path 5 (the secondary system flow path 8 and the secondary system flow path 9) are partitioned by the wall portions la and lb by such joining of the plates 1 and 2.
  • a structure is shown in which the primary system flow path 8 and the secondary system flow path 9 are semicircular in cross-section.
  • the primary system flow path 8 and the secondary system flow path 9 are wave-shaped flow paths, and the cross-sectional areas of the primary system flow path 3 and the secondary system flow path 9 are set to be the same. ing.
  • the temperature range of the primary fluid a supplied to the primary system flow path 8 is 800 ° C or higher and 900 ° C or lower, and the primary fluid a and the secondary fluid b It is designed to maintain the strength that can be withstood when the differential pressure is 4 MPa or more and 7 MPa or less, and the exchange heat per unit volume between both fluids is set to lOMWt / m 3 or more.
  • the plate thickness of the plates 1 and 2 is not less than 0.3 times the channel equivalent diameter, and the pitch tp between the channels along the plate width direction of the plates 1 and 2 is 0.5 times the channel equivalent diameter. That's it.
  • Each of the plates 1 and 2 is made of an iron-based oxide dispersion strengthened alloy containing chromium and aluminum, for example, INCOLOY alloi 956 (Fe: 75%, Cr: 20%, A1: 4.5%, Ti : 0.5%, C: 0.05%, ⁇ 2 ⁇ 3: 0 ⁇ 5%).
  • INCOLOY alloi 956 Fe: 75%, Cr: 20%, A1: 4.5%, Ti : 0.5%, C: 0.05%, ⁇ 2 ⁇ 3: 0 ⁇ 5%).
  • a plate provided with a large number of primary fluid flow paths.
  • the plate 2 provided with a number of secondary fluid flow paths as in the case of 1 is laminated and integrated by, for example, diffusion bonding to form the heat exchanger 3.
  • FIG. 2 shows a case where the flow 15 of the primary fluid entering from the primary fluid inlet 14 and the flow 17 of the secondary fluid entering from the secondary fluid inlet 16 flow in opposite directions.
  • the heat exchange is the best. However, it may be run in parallel depending on the application.
  • the structural material 10 is an iron-based oxide dispersion strengthened (ODS) alloy having a high temperature strength with an allowable stress of about 25 MPa at 900 ° C., for example, INCOLO.
  • ODS iron-based oxide dispersion strengthened
  • the vertical spacing P 11 is the diameter of the semicircular channel dl2 f
  • the structural material 10 may be a high Nikkenole-based alloy such as Alloy 617.
  • a compact heat exchanger having a heat exchange amount per unit volume of lOMWt / m 3 or more is realized, and a high-performance heat exchanger with excellent structural integrity is provided.
  • FIGS. [0063] A second embodiment of the present invention will be described with reference to FIGS. [0063]
  • a description will be given of a configuration in which the fluid inlet and the fluid outlet of the primary channel and the secondary channel are respectively provided on the surface along the fluid flow direction in the main heat exchange portion of the channel member. To do.
  • the plate 1 provided with the flow path for the primary system fluid and the plate 2 provided with the flow path for the secondary system are used.
  • Constructed force Primary fluid inlet 14 and secondary fluid outlet 19 are on the same plane, and primary fluid outlet 18 and secondary fluid inlet 16 are also on the same plane,
  • the inlets 14, 16 and outlets 18, 19 of the primary and secondary flow paths are arranged in the fluid flow direction.
  • both the primary flow path 8 and the secondary system flow path 9 are formed along the longitudinal direction of the plate 1.
  • Other configurations are the same as those in the first embodiment.
  • the primary fluid inlet / outlet 14 is provided at a position perpendicular to the secondary fluid inlet / outlet 16, that is, on the side of the heat exchanger, whereas in the present embodiment, the primary fluid inlet / outlet is provided. Since 14 and the secondary fluid inlet / outlet 16 are provided on the same surface, the external dimensions of the heat exchanger 3 are reduced because it is not necessary to provide a header or piping on the side surface.
  • the pressure loss that the flow direction does not bend at a right angle can be suppressed to a small level.
  • the force composed of the plate 1 provided with the flow path of the primary fluid and the plate 2 provided with the flow path of the secondary system is provided with a system flow path, and the plate 2 is provided with a secondary system flow path.
  • the primary system flow path 8 branches and merges, and is connected to the plenum 20 as the inlet and outlet of the flow path on the side surface of the heat exchanger, and faces the side surface as shown in the first embodiment. Folded Compared with the case where the flow path 21 is used to provide an inlet and an outlet on the side surface, it is possible to reduce the area 22 where the fluid does not counter flow.
  • the amount of exchange heat per unit volume is lOMWt.
  • guide vanes or reinforcing materials for guiding each fluid along the curved portion are provided in the curved portion of each flow path! To do.
  • the plate wall la and the guide rod 24 force that the heat exchanger 3 forms the flow path are also configured.
  • FIG. 12 which is an enlarged view of the flow path
  • the flow 25 of the fluid flowing through the flow path 5 is caused by vortices and separation at the bent portion by the guide blades 24 provided at the bent portion of the flow path 5. Is suppressed
  • the heat exchanger will be described in which the latter has a larger cross-sectional area of the primary system flow path and the secondary system flow path than the former.
  • a secondary system channel 9 having a larger channel cross-sectional area than the primary system channel 8 is formed.
  • it is substantially the same as that of the said embodiment.
  • the secondary system channel 26 having a large channel cross-sectional area suppresses an increase in the flow rate of the secondary system fluid. It is possible to reduce the pressure loss of the secondary fluid.
  • the exchange heat per unit volume is lOMWt.
  • FIG. 14 a substantially rectangular cross-sectional flow path 27 is formed in the flow path member 4.
  • FIG. 15 shows dimensions and the like of each flow path 8, 9, that is, the horizontal pitch Pf of the flow path, the horizontal width d of the flow path, the pitch tp between the flow paths, and the horizontal interval between the flow paths. tf is shown.
  • the cross-sectional shapes of the flow paths 8 and 9 are substantially rectangular as compared to the case of the semicircular flow path having the same cross-sectional area shown in the previous embodiment.
  • These channels 8 and 9 have a large heat transfer area with the structural material of the flow channel member 4, so that the heat transfer performance can be improved.
  • the stress value is equivalent to that in the case of a semicircular force in which stress due to differential pressure or temperature difference is concentrated at the corner of the rectangular channel.
  • FIG. 16 it may be a polygon such as a hexagon formed by only a quadrangle. Even with such a configuration, since the heat transfer area between the flow paths 8 and 9 and the structural material of the flow path member 4 is increased, the heat transfer performance can be improved.
  • a heat exchanger having a compactness with an exchange heat amount per unit volume of 10 MWt / m 3 or more, high performance and excellent structural soundness.
  • a plenum portion for branching and joining the primary system flow channel and the secondary system flow channel is formed in the flow channel member, and the primary system flow channel and the secondary system communicating with these planar portions are formed.
  • a heat exchanger in which the fluid inlet and the fluid outlet of the flow path are provided on the surface along the fluid flow direction or the surface along the direction perpendicular to the fluid flow direction in the main heat exchange portion of the flow path member will be described.
  • the plate 1 is provided with a primary system flow path
  • the plate 2 is provided with a secondary system flow path.
  • the primary system flow path 8 branches and merges, and is connected to the primary system plenum 28 which becomes the primary system flow path inlet 14 and the primary system flow path outlet 19 on the front and rear surfaces of the heat exchanger.
  • the secondary system flow path 9 is also provided by the secondary system plenum 29 because the secondary system flow path inlet 16 and the secondary system flow path outlet 18 are provided on the front and rear surfaces of the heat exchanger. And the inlet / outlet of the secondary system channel is arranged in the fluid flow direction.
  • the exchange heat per unit volume is lOMWt.
  • a heat exchanger formed as a reciprocating flow path in which at least one of the primary flow path and the secondary flow path is folded back in a U shape will be described.
  • the plate 1 is provided with a primary system flow path, and the plate 2 force is provided with a secondary system flow path.
  • the secondary system flow path inlet 16 and the secondary system flow path outlet 18 are connected to the front surface of the heat exchanger. Each is provided on the rear surface.
  • the grooves serving as the primary system flow path and the secondary system flow path are formed in the same metal plate in an arrangement adjacent to each other, and the tips of the primary system flow path and the secondary system flow path But, A heat exchanger communicating with a fluid outlet and a plenum provided on the same surface of the flow path member will be described.
  • the primary system flow path 8 and the secondary system flow path 9 are configured by the plate 30 provided in an arrangement adjacent to each other.
  • the leading ends of the primary system flow path 8 and the secondary system flow path 9 are connected to the fluid outlets 18 and 19 provided on the same surface as the upper surface of the flow path member and the height direction plenums 31 and 32 extending upward.
  • the plenum 31 makes it possible to arrange the primary fluid 18 and the secondary outlet 19 on a plane parallel to the plate 30 provided with the primary and secondary flow paths.
  • heat exchange is performed only by the counter flow, so that the direct flow can be eliminated and the external dimensions of the heat exchanger can be reduced.
  • At least one of the primary system flow path and the secondary system flow path is formed as a reciprocating flow path that folds back in a U-shape, and both ends of the reciprocating flow path are formed at the fluid inlet and the fluid flow path.
  • the plate 30 is provided with a primary system and a secondary system flow path.
  • a variation of this Embodiment 9 is shown, and the U-shaped primary system flow path 8 and the secondary system flow path 9 are arranged on the same plate.
  • the heat exchanging section has only a counter flow.
  • the external dimensions of the heat exchanger can be reduced, and the heat exchange density is increased due to the presence of the U-shaped folded portion.
  • a heat exchanger having a compactness in which the amount of exchange heat per unit volume is 10 MW t / m 3 or more and excellent in heat exchange performance. I can do it. [Eleventh embodiment (FIG. 27)]
  • the plate 1 is provided with a primary system flow path
  • the plate 2 is provided with a secondary system flow path
  • the flow path reinforcing member 32 increases the rigidity of the plates on the upper and lower surfaces of the flow path, that is, the moment of inertia of the cross section, so that the pressure resistance performance can be greatly improved. . Furthermore, the flow path reinforcing material 32 plays a role of heat transfer fins or turbulence generating factors, and thus greatly contributes to improvement of heat transfer performance.
  • a heat exchanger having a compact structure with a heat exchange capacity per unit volume of 10 MW t / m 3 or more, high performance and excellent structural soundness. Deliver with the power S to provide.
  • the flow path component member 4 has a substantially hexagonal shape in plan view, and both ends are formed in a substantially triangular shape.
  • the plate 1 is provided with the primary system flow path
  • the plate 2 is provided with the secondary system flow path.
  • the part is formed in a substantially triangular shape.
  • the primary fluid a and the secondary fluid b flow in from the adjacent primary fluid inlet 14 and the secondary fluid inlet 16 located on the opposite side, and are substantially parallel to the primary fluid outlet 18 and the secondary fluid outlet 19. Discharged from.
  • a heat exchanger having a compactness with an exchange heat amount per unit volume of 10 MW t / m 3 or more, being inexpensive and excellent in reducing pressure loss. Deliver with the power S to provide.

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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)

Abstract

L'invention concerne un échangeur de chaleur (3) à lamination de plaque compact ayant un élément de canal constitué par empilement et liaison de plaque métallique (1, 2) doté d'une rainure (9), un canal de système primaire et un canal de système secondaire pour un échange de chaleur formé de la rainure (9) entre les plaques métalliques (1, 2) de l'élément de canal, et une capacité de chaleur d'échange par zone unitaire non inférieure à 10 MWt/m3 est utilisée dans des conditions de haute température haute pression où la pression différentielle entre le fluide de système primaire et le fluide de système secondaire est de 4-7 MPa, et la température maximale est de 500-900°C. L'épaisseur des plaques métalliques (1, 2) est 0,3 fois ou plus le diamètre équivalent du canal, et le pas de canal le long de la direction de l'épaisseur des plaques métalliques (1, 2) est 0,5 fois ou plus le diamètre équivalent du canal.
PCT/JP2007/072481 2006-11-21 2007-11-20 Échangeur de chaleur WO2008062802A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP07832211.2A EP2110635A4 (fr) 2006-11-21 2007-11-20 Échangeur de chaleur
US12/515,740 US20100051248A1 (en) 2006-11-21 2007-11-20 Heat exchanger

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Application Number Priority Date Filing Date Title
JP2006-314864 2006-11-21
JP2006314864A JP2008128574A (ja) 2006-11-21 2006-11-21 熱交換器

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WO2008062802A1 true WO2008062802A1 (fr) 2008-05-29

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EP (1) EP2110635A4 (fr)
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WO (1) WO2008062802A1 (fr)

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US20170211893A1 (en) * 2016-01-22 2017-07-27 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Heat exchanger and heat exchange method
WO2019167491A1 (fr) * 2018-02-28 2019-09-06 株式会社富士通ゼネラル Échangeur thermique à cloisons
CN111051805A (zh) * 2017-08-29 2020-04-21 株式会社威工 换热器
WO2021019993A1 (fr) * 2019-07-29 2021-02-04 株式会社富士通ゼネラル Échangeur de chaleur de type à paroi de séparation
WO2022030319A1 (fr) * 2020-08-04 2022-02-10 シャープ株式会社 Évaporateur et dispositif de refroidissement
CN115615233A (zh) * 2022-11-08 2023-01-17 中国核动力研究设计院 流体承载组件及热量交换装置

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DE202011005693U1 (de) * 2011-04-28 2011-09-26 Behr Gmbh & Co. Kg Schichtwärmeübertager
JP5727327B2 (ja) * 2011-08-08 2015-06-03 株式会社神戸製鋼所 熱交換器
HUE045594T2 (hu) * 2012-06-05 2020-01-28 Soc Technique Pour Lenergie Atomique Lemezes hõcserélõ a járatok közötti homogén közegáramlások megvalósításához
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