WO2020246003A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

Info

Publication number
WO2020246003A1
WO2020246003A1 PCT/JP2019/022629 JP2019022629W WO2020246003A1 WO 2020246003 A1 WO2020246003 A1 WO 2020246003A1 JP 2019022629 W JP2019022629 W JP 2019022629W WO 2020246003 A1 WO2020246003 A1 WO 2020246003A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow path
fluid
heat exchanger
resistance
inflow port
Prior art date
Application number
PCT/JP2019/022629
Other languages
English (en)
Japanese (ja)
Inventor
潤 宮本
亮介 末光
長谷川　泰士
和島　一喜
Original Assignee
三菱重工サーマルシステムズ株式会社
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 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to CN201980095333.8A priority Critical patent/CN113677946A/zh
Priority to PCT/JP2019/022629 priority patent/WO2020246003A1/fr
Priority to US17/612,483 priority patent/US20220221232A1/en
Publication of WO2020246003A1 publication Critical patent/WO2020246003A1/fr

Links

Images

Classifications

    • 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
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28D9/0043—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 plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present disclosure relates to a heat exchanger constituting a condenser or an evaporator of a refrigerator such as a turbo chiller, for example.
  • shell & tube heat exchangers Conventionally, shell & tube heat exchangers, fin & tube heat exchangers, plate heat exchangers, plate fin heat exchangers, etc. have been used as heat exchangers that accompany fluid phase changes such as evaporators and condensers. ing.
  • the shell and tube heat exchanger is configured to allow a single-phase fluid to flow through the tube, heat / cool the external fluid, and evaporate / condense the external fluid.
  • the fin and tube heat exchanger is configured to allow gas to flow between the fins outside the tube to heat / cool the fluid inside the tube and evaporate / condense the fluid inside the tube.
  • Plate heat exchangers and plate fin heat exchangers have a configuration in which a single-phase fluid flows between one plate and the fluid between the other plates is heated / cooled to evaporate / condense.
  • the plate fin heat exchanger for example, the following Patent Documents 1 to 3 have been reported.
  • the fluid evaporates or condenses, the fluid undergoes a phase change, so the fluid volume changes significantly during the heat exchange process.
  • the fluid volume in the fluid flow path becomes very large, and an excessive pressure loss may occur.
  • the fluid flow path is determined so that excessive pressure loss does not occur in the flow on the gas side, the flow velocity on the liquid side (the part where the fluid inside is in the liquid phase state) is significantly reduced, and the heat transfer performance is improved. There is a problem of decline.
  • the present disclosure has been made in view of such circumstances, and is a compact heat capable of suppressing the occurrence of excessive pressure loss and ensuring an appropriate flow velocity in response to the volume change of the fluid due to the phase change.
  • the purpose is to provide a switch.
  • the present disclosure includes an inflow port into which a fluid flows in and an outflow port from which the inflowing fluid flows out, and a flow path in which a phase change is performed from a liquid phase to a gas phase between the inflow port and the outflow port.
  • the fluid flowing into the flow path changes (evaporates) from the liquid phase to the gas phase by heat exchange in the flow path
  • the fluid volume increases.
  • an excessive pressure loss may occur due to an increase in the fluid volume.
  • the magnitude of the flow path resistance applied to the flow of the fluid inside the flow path is larger on the outlet side than on the inlet side (for example, in five stages). A smaller resistance shape is formed. Therefore, on the outlet side (gas side), the magnitude of the flow path resistance applied to the fluid flow is small, so that the occurrence of excessive pressure loss can be suppressed.
  • the present disclosure includes an inflow port into which a fluid flows in and an outflow port from which the inflowing fluid flows out, and a flow path in which a phase change is performed from a gas phase to a liquid phase between the inflow port and the outflow port.
  • a heat exchanger having a resistance shape formed inside the flow path so that the magnitude of the flow path resistance applied to the flow of the fluid is larger on the outlet side than on the inlet side.
  • the fluid flowing into the flow path changes (condenses) from the gas phase to the liquid phase by heat exchange in the flow path
  • the fluid volume decreases.
  • excessive pressure loss may occur on the inflow port side due to the large fluid volume.
  • the magnitude of the flow path resistance applied to the fluid flow inside the flow path is larger on the outlet side than on the inlet side (for example, in five stages). A resistance shape that increases is formed. Therefore, on the inflow port side (gas side), the magnitude of the flow path resistance applied to the fluid flow is small, so that the occurrence of excessive pressure loss can be suppressed.
  • the resistance shape is preferably formed by a plate forming the flow path or a plurality of fins provided on the plate.
  • the resistance shape formed inside the flow path is thus formed by the plate forming the flow path (for example, in the plate heat exchanger) and the plurality of fins provided on the plate (for example, in the plate fin heat exchanger). Can be formed. Specifically, in the portion where the flow path resistance is increased, the plates and fins are arranged perpendicular to the fluid flow direction. On the other hand, in the portion where the flow path resistance is reduced, the plates and fins are arranged parallel to the fluid flow direction. By doing so, the resistance shape can be formed. Therefore, the heat exchangers of the present disclosure are particularly suitably applicable to plate heat exchangers and plate fin heat exchangers. Since the plate heat exchanger and the plate fin heat exchanger can be made compact, if the heat exchanger of the present disclosure is applied to the plate heat exchanger and the plate fin heat exchanger, the heat transfer performance is improved and compact. It becomes a heat exchanger.
  • a separate flow path for heat exchange with the fluid flowing through the flow path is provided adjacent to the flow path.
  • heat exchanger of the present disclosure by providing a separate flow path as described above, heat exchange can be performed between the fluid flowing through the flow path and the fluid flowing through the separate flow path.
  • the same flow path resistance is imparted to the inside of the separate flow path between the inflow port where the fluid flowing through the separate flow path flows in and the outflow port where the inflowing fluid flows out. It is preferable that a resistance shape is formed.
  • one fluid can be obtained. It can be suitably applied to a heat exchanger having a single-phase structure in which the other fluid undergoes a phase change.
  • the inside of the separate flow path has a resistance shape in which the flow path resistance is larger at the outlet where the inflowing fluid flows out than at the inflow port where the fluid flowing through the separate flow path flows in. It is preferable that a resistance shape having a small flow path resistance is formed.
  • the flow path in the first aspect and the flow path in the second aspect can be combined. That is, the heat exchanger of the present disclosure can be suitably applied to a heat exchanger in which one fluid evaporates in the flow path and the other fluid condenses in the flow path. ..
  • the heat exchanger of the present disclosure is a compact heat exchanger that can suppress the occurrence of excessive pressure loss in response to the volume change of the fluid due to the phase change and can secure an appropriate flow velocity.
  • FIG. 5 is an image view of a flow path and another flow path in the heat exchanger according to the fourth embodiment of the present disclosure as viewed from the longitudinal side surface.
  • FIG. 1 is a perspective exploded view showing the structure of the heat exchanger (plate fin heat exchanger) according to the present embodiment.
  • the heat exchanger 1 shown in FIG. 1 is used for a condenser or an evaporator of a refrigerator such as a turbo chiller, for example.
  • plates (first plate) 2a and plates (second plate) 2b are alternately laminated and joined, bosses 3a and 3b are attached to the first plate 2a at the start end, and the first plate at the end ends.
  • It has a structure in which the cover plate 4 is attached to 2a.
  • Inner fins 5a and 5b are provided on the surfaces of the first plate 2a and the second plate 2b on the cover plate 4 side, respectively.
  • the fluid (first fluid) 6 flows into the heat exchanger 1 from the boss 3a, and the fluid (second fluid) 7 flows into the heat exchanger 1 from the boss 3b.
  • the first fluid 6 circulates in the flow path 8 formed between the second plate 2b and the inner fin 5a.
  • the second fluid 7 is formed between the first plate 2a and the inner fin 5b, and circulates in another flow path 9 adjacent to the flow path 8.
  • the flow path 8 of the first fluid 6 and the separate flow path 9 of the second fluid 7 are alternately arranged, and between the two fluids 6 and 7.
  • the structure is such that heat exchange is performed.
  • FIG. 2 is a plan view showing a flow path 8 in the heat exchanger 1 of the present embodiment.
  • the flow path 8 has an inflow port 10 into which the first fluid 6 flows in and an outflow port 11 from which the inflowing first fluid 6 flows out.
  • the first fluid 6 undergoes a phase change from a liquid phase to a gas phase between the inflow port 10 and the outflow port 11. That is, the heat exchanger 1 is used as an evaporator for evaporating the refrigerant.
  • a resistance shape 12 is formed in which the magnitude of the flow path resistance applied to the flow of the first fluid 6 is smaller on the outflow port 11 side than on the inflow port 10 side.
  • the resistance shape 12 is formed so that the magnitude of the flow path resistance decreases in five steps from the inflow port 10 side to the outflow port 11 side.
  • the resistance shape 12 is formed by a plurality of fins 13 provided on the first plate 2a.
  • the fins 13 are arranged perpendicular to the flow direction of the fluid 6, and the fins 13 are arranged from the inflow port 10 side toward the outflow port 11 side. (The length in the direction perpendicular to the flow direction of the fluid 6) is shortened.
  • the fins 13 are arranged parallel to the flow direction of the fluid 6, and the number of fins 13 increases from the inflow port 10 side toward the outflow port 11. Arrange from dense to coarse.
  • the magnitude of the flow path resistance applied to the flow of the fluid 6 inside the flow path 8 becomes smaller in five steps from the inflow port 10 side to the outflow port 11 side. 12 is formed. Therefore, on the outlet 11 side (gas side), the magnitude of the flow path resistance applied to the flow of the fluid 6 is small, so that the occurrence of excessive pressure loss can be suppressed. On the other hand, on the inflow port 10 side (liquid side), since the magnitude of the flow path resistance applied to the flow of the fluid 6 is large, it is possible to prevent the flow velocity of the fluid 6 from being significantly reduced (that is, an appropriate flow velocity can be secured).
  • heat exchanger 1 As described above, in the heat exchanger 1 according to the present embodiment, it is possible to suppress the occurrence of excessive pressure loss and promote turbulence in response to the volume change of the fluid 6 due to the phase change. Therefore, such a heat exchanger 1 is a heat exchanger 1 having high heat transfer performance (evaporation heat transfer performance). Since it is only necessary to form a specific resistance shape 12 inside the flow path 8, the heat exchanger 1 can be made compact.
  • the resistance shape 12 formed inside the flow path 8 can be formed by a plurality of fins 13 provided on the first plate 2a (in the plate fin heat exchanger) in this way. Therefore, the heat exchanger 1 of the present embodiment is particularly suitably applicable to the plate fin heat exchanger. Since the plate fin heat exchanger can be made compact, if the heat exchanger 1 of the present embodiment is applied to the plate fin heat exchanger, the heat transfer performance is improved and the heat exchanger 1 becomes compact.
  • the resistance shape 12 described above can also be formed by the first plate 2a constituting the flow path 8 (in the plate heat exchanger). Therefore, the heat exchanger 1 of the present embodiment is also suitably applicable to the plate heat exchanger. Since the plate heat exchanger can also be made compact, if the heat exchanger 1 of the present embodiment is applied to the plate heat exchanger, the heat transfer performance is improved and the heat exchanger 1 becomes compact as described above.
  • a resistance shape 12 is formed in which the magnitude of the flow path resistance applied to the flow of the fluid 6 decreases in five steps from the inflow port 10 side to the outflow port 11 side.
  • the magnitude of the flow path resistance can be reduced from the inflow port 10 side to the outflow port 11 side, preferably in 3 to 10 steps.
  • the basic configuration of the present embodiment is basically the same as that of the first embodiment, but the first embodiment is a point in which the first fluid 26 undergoes a phase change from a gas phase to a liquid phase in the flow path 28. , And the structure of the resistance shape 22 is different. Therefore, in the present embodiment, this different part will be described, and the description of other overlapping parts will be omitted.
  • the same components as those in the first embodiment are designated by the same reference numerals, and the duplicated description thereof will be omitted.
  • FIG. 3 is a plan view showing a flow path 28 in the heat exchanger 21 of the present embodiment.
  • the first fluid 26 undergoes a phase change from a gas phase to a liquid phase between the inflow port 10 and the outflow port 11. That is, the heat exchanger 1 is used as a condenser for condensing the refrigerant.
  • a resistance shape 22 is formed inside the flow path 28, in which the magnitude of the flow path resistance applied to the flow of the first fluid 26 is larger on the outflow port 11 side than on the inflow port 10 side.
  • the resistance shape 22 is formed so that the magnitude of the flow path resistance increases in five steps from the inflow port 10 side to the outflow port 11 side.
  • the resistance shape 22 is formed by a plurality of fins 13 provided on the first plate 2a as in the first embodiment.
  • the fins 13 are arranged parallel to the flow direction of the fluid 26, and the fins 13 are arranged from the inflow port 10 side toward the outflow port 11 side. Arrange so that the number of is coarse to dense.
  • the fins 13 are arranged perpendicular to the flow direction of the fluid 26, and the length of the fins 13 increases from the inflow port 10 side to the outflow port 11 side. (Length in the direction perpendicular to the flow direction of the fluid 26) is lengthened.
  • the magnitude of the flow path resistance applied to the flow of the fluid 26 inside the flow path 28 increases in five steps from the inflow port 10 side to the outflow port 11 side. 22 is formed. Therefore, on the inflow port 10 side (gas side), the magnitude of the flow path resistance applied to the flow of the fluid 26 is small, so that the occurrence of excessive pressure loss can be suppressed. On the other hand, on the outlet 11 side (liquid side), since the magnitude of the flow path resistance applied to the flow of the fluid 26 is large, it is possible to prevent the flow velocity of the fluid 26 from being significantly reduced (that is, an appropriate flow velocity can be secured). ), And turbulence can be promoted.
  • heat exchanger 21 As described above, in the heat exchanger 21 according to the present embodiment, it is possible to suppress the occurrence of excessive pressure loss and promote turbulence in response to the volume change of the fluid 26 due to the phase change. Therefore, such a heat exchanger 21 is a heat exchanger 21 having high heat transfer performance (condensation performance). Since it is only necessary to form a specific resistance shape 22 inside the flow path 28, the heat exchanger 21 can be made compact.
  • the basic configuration of the present embodiment is basically the same as that of the second embodiment, but is the same as that of the second embodiment inside the separate flow path 49 between the inflow port 40 and the outflow port 41.
  • the difference is that the resistance shape 42 that imparts the flow path resistance of is formed. Therefore, in the present embodiment, this different part will be described, and the description of other overlapping parts will be omitted.
  • the same components as those in the second embodiment are designated by the same reference numerals, and the duplicated description thereof will be omitted.
  • the shapes of the resistance shapes 22 and 42 are conceptually shown, but this is just an image diagram.
  • FIG. 4 is an image view of the flow path 28 and the separate flow path 49 in the heat exchanger 31 according to the present embodiment as viewed from the side surface in the longitudinal direction.
  • the first fluid 26 undergoes a phase change from a gas phase to a liquid phase between the inflow port 10 and the outflow port 11.
  • a resistance shape 22 is formed inside the flow path 28, in which the magnitude of the flow path resistance applied to the flow of the first fluid 26 is larger on the outflow port 11 side than on the inflow port 10 side.
  • the separate flow path 49 has an inflow port 40 into which the second fluid 47 flows in and an outflow port 41 from which the inflowing second fluid 47 flows out.
  • the second fluid 47 does not undergo a phase change between the inflow port 40 and the outflow port 41, and flows through the separate flow path 49 as a liquid phase (that is, is a single phase).
  • a resistance shape 42 that imparts the same flow path resistance is formed between the inflow port 40 and the outflow port 41.
  • the internal resistance shape 42 is a separate flow path 49 having a resistance shape 42 in which the magnitude of the flow path resistance applied to the flow of the fluid 47 is constant, and the flow path according to the second embodiment described above. Can be combined with 28. That is, the present disclosure can be suitably applied to the heat exchanger 31 in which one fluid 47 is single-phase and the other fluid 26 undergoes a phase change.
  • the basic configuration of the present embodiment is basically the same as that of the third embodiment, but the configuration of the resistance shape 52 formed inside the separate flow path 59 is different from that of the third embodiment. Therefore, in the present embodiment, this different part will be described, and the description of other overlapping parts will be omitted.
  • the same components as those in the third embodiment are designated by the same reference numerals, and the duplicated description thereof will be omitted.
  • the shapes of the resistance shapes 22 and 52 are conceptually shown, but this is just an image diagram.
  • FIG. 5 is an image view of the flow path 28 and the separate flow path 59 in the heat exchanger 51 according to the present embodiment as viewed from the side surface in the longitudinal direction.
  • the second fluid 57 undergoes a phase change from a liquid phase to a gas phase between the inflow port 40 and the outflow port 41.
  • a resistance shape 52 is formed inside the separate flow path 59 in which the flow path resistance of the outflow port 41 is smaller than that of the inflow port 40. That is, the configuration of the separate flow path 59 is substantially the same as the configuration of the flow path 8 in the first embodiment.
  • the following functions and effects are obtained by the configuration described above.
  • the flow path 8 (separate flow path 59) in the first embodiment and the flow path 28 in the second embodiment can be combined. That is, the heat exchanger 51 of the present embodiment is configured such that one fluid 57 evaporates in the flow path 8 (separate flow path 59) and the other fluid 26 condenses in the flow path 28. It can be suitably applied to the exchanger 51.
  • the heat exchanger of the present disclosure is applied to the plate fin heat exchanger as an example, but the present disclosure is not limited to this. Specifically, the heat exchanger of the present disclosure is also applicable to a plate heat exchanger, a fin & tube heat exchanger, and the like.
  • the heat exchangers of the present disclosure are preferably applied to plate heat exchangers and plate fin heat exchangers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'objectif de la présente invention est de fournir un échangeur de chaleur compact grâce auquel la génération d'une perte de pression excessive peut être supprimée et un débit approprié peut être assuré en fonction des changements volumétriques d'un fluide en raison de changements de phase. Cet échangeur de chaleur (1) comprend un trajet d'écoulement (8) qui comporte une entrée (10) dans laquelle s'écoule un fluide (6) et une sortie (11) traversée par le fluide écoulé (6), et dans lequel un changement de phase d'une phase fluide à une phase gazeuse se produit entre l'entrée (10) et la sortie (11), l'intérieur du trajet d'écoulement (8) étant réalisé de manière à créer une résistance (12), de sorte que la résistance appliquée à l'écoulement du fluide (6) est plus faible du côté de la sortie (11) que du côté de l'entrée (10).
PCT/JP2019/022629 2019-06-06 2019-06-06 Échangeur de chaleur WO2020246003A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201980095333.8A CN113677946A (zh) 2019-06-06 2019-06-06 热交换器
PCT/JP2019/022629 WO2020246003A1 (fr) 2019-06-06 2019-06-06 Échangeur de chaleur
US17/612,483 US20220221232A1 (en) 2019-06-06 2019-06-06 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/022629 WO2020246003A1 (fr) 2019-06-06 2019-06-06 Échangeur de chaleur

Publications (1)

Publication Number Publication Date
WO2020246003A1 true WO2020246003A1 (fr) 2020-12-10

Family

ID=73653082

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/022629 WO2020246003A1 (fr) 2019-06-06 2019-06-06 Échangeur de chaleur

Country Status (3)

Country Link
US (1) US20220221232A1 (fr)
CN (1) CN113677946A (fr)
WO (1) WO2020246003A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5538700A (en) * 1994-12-22 1996-07-23 Uop Process and apparatus for controlling temperatures in reactant channels
WO2014087225A1 (fr) * 2012-12-05 2014-06-12 Blue Box Group S.R.L. Echangeur thermique
US20140262186A1 (en) * 2013-03-14 2014-09-18 Rochester Institute Of Technology Heat Transfer System and Method Incorporating Tapered Flow Field

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992168A (en) * 1968-05-20 1976-11-16 Kobe Steel Ltd. Heat exchanger with rectification effect
US5709264A (en) * 1996-03-18 1998-01-20 The Boc Group, Inc. Heat exchanger
US7073573B2 (en) * 2004-06-09 2006-07-11 Honeywell International, Inc. Decreased hot side fin density heat exchanger
CN100516758C (zh) * 2007-06-12 2009-07-22 缪志先 一种无封条板翅式换热器
BR112012022531B1 (pt) * 2010-03-08 2020-05-12 Arvind Accel Limited Elemento trocador de calor, um trocador de calor que compreende os elementos, e um equipamento para a fabricação dos elementos.
KR101534497B1 (ko) * 2013-10-17 2015-07-09 한국원자력연구원 증기발생기용 열교환기 및 이를 구비하는 증기발생기
DE102014004322B4 (de) * 2014-03-25 2020-08-27 Modine Manufacturing Company Wärmerückgewinnungssystem und Plattenwärmetauscher

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5538700A (en) * 1994-12-22 1996-07-23 Uop Process and apparatus for controlling temperatures in reactant channels
WO2014087225A1 (fr) * 2012-12-05 2014-06-12 Blue Box Group S.R.L. Echangeur thermique
US20140262186A1 (en) * 2013-03-14 2014-09-18 Rochester Institute Of Technology Heat Transfer System and Method Incorporating Tapered Flow Field

Also Published As

Publication number Publication date
US20220221232A1 (en) 2022-07-14
CN113677946A (zh) 2021-11-19

Similar Documents

Publication Publication Date Title
US9823025B2 (en) Heat recovery system having a plate heat exchanger
WO2014132602A1 (fr) Échangeur de chaleur empilé
US10371461B2 (en) Multi-layered counterflow expanding microchannel cooling architecture and system thereof
JP6094261B2 (ja) 積層型熱交換器
US20140060789A1 (en) Heat exchanger and method of operating the same
US20120181005A1 (en) Compact high performance condenser
JP6016935B2 (ja) プレート式熱交換器及びこのプレート式熱交換器を備えた冷凍サイクル装置
JP2020079693A (ja) 熱交換器
JP6160385B2 (ja) 積層型熱交換器
WO2015020048A1 (fr) Échangeur de chaleur
WO2020246003A1 (fr) Échangeur de chaleur
JP2005127529A (ja) 熱交換器
JP2019184133A (ja) 熱交換器
JP5526494B2 (ja) 冷凍装置
WO2014154547A1 (fr) Échangeur de chaleur, en particulier condenseur
JP2009186142A (ja) ブレージングプレート式熱交換器
WO2020203555A1 (fr) Échangeur de chaleur
WO2020110638A1 (fr) Échangeur de chaleur
JPS6252238B2 (fr)
JP2018096568A (ja) 熱交換器
JPH02143094A (ja) 伝熱管を備えた熱交換器
JP7081417B2 (ja) 熱交換器
JP6658242B2 (ja) 熱交換器
JP6865354B2 (ja) プレートフィン積層型熱交換器およびそれを用いた冷凍システム
WO2020100687A1 (fr) Échangeur de chaleur

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19932117

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 07/03/2022)

NENP Non-entry into the national phase

Ref country code: JP

122 Ep: pct application non-entry in european phase

Ref document number: 19932117

Country of ref document: EP

Kind code of ref document: A1