EP4242571A1 - Nichtmetallische ablenkplatte für wärmetauscher - Google Patents

Nichtmetallische ablenkplatte für wärmetauscher Download PDF

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Publication number
EP4242571A1
EP4242571A1 EP23160579.1A EP23160579A EP4242571A1 EP 4242571 A1 EP4242571 A1 EP 4242571A1 EP 23160579 A EP23160579 A EP 23160579A EP 4242571 A1 EP4242571 A1 EP 4242571A1
Authority
EP
European Patent Office
Prior art keywords
tube
lobes
hole
diameter
tube bundle
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.)
Pending
Application number
EP23160579.1A
Other languages
English (en)
French (fr)
Inventor
Luis Avila
Ian Robinson
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.)
Carrier Corp
Original Assignee
Carrier 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 Carrier Corp filed Critical Carrier Corp
Publication of EP4242571A1 publication Critical patent/EP4242571A1/de
Pending legal-status Critical Current

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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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/062—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing tubular conduits
    • F28F21/063—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing tubular conduits for domestic or space-heating systems
    • 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
    • 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
    • F25B39/04—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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0131—Auxiliary supports for elements for tubes or tube-assemblies formed by plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B39/02—Evaporators
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/226—Transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/10—Fastening; Joining by force joining
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements

Definitions

  • Embodiments of the present invention pertain to the art of heat exchangers, and more particularly, to a baffle used to support a plurality of tubes of a heat exchanger.
  • Heat exchangers commonly used in vapor compression system include a tube bundle conventionally formed from copper tubes. These tube bundles are typically supported by a rigid connection formed between the tubes of the tube bundle and two or more spaced steel support plates or baffles, which are commonly metallic. To form this rigid connection, the tubes can be swaged into the baffles.
  • the tube bundle is subject to vibrations along with expansion and contraction due to changes in temperature during the heat exchange process.
  • significant abrasion and wear can occur on the tubes at the locations where they contact the baffles, which can result in a friction failure over time. Accordingly, there remains a need for a solution to improve the interface between the tube bundle and the baffles.
  • a tube bundle assembly includes at least one tube and a baffle having at least one hole for receiving the at least one tube.
  • the at least one hole has a non-uniform diameter such that only a portion of a periphery of the at least one hole is positionable in contact with the at least one tube.
  • the baffle is formed from a non-metallic material.
  • the baffle is formed from a polymeric or elastomeric material.
  • the at least one tube is formed from an aluminum material.
  • the at least one hole has a plurality of lobes protruding inwardly towards a center of at least one hole.
  • the plurality of lobes are equidistantly spaced about the at least one hole.
  • the plurality of lobes includes between three and ten lobes.
  • a configuration of each of the plurality of lobes is substantially identical.
  • each of the plurality of lobes has a land positionable in contact with the at least one tube.
  • the land is positionable in line contact with the at least one tube.
  • the land has a convex curvature.
  • the convex curvature has a radius C and a diameter B extends between an origin of the radius C for oppositely positioned lobes at the at least one hole, wherein the radius C is between .09 and . 15 times the diameter B.
  • a vapor compression system includes a compressor for circulating a refrigerant and a tube bundle assembly for transferring the refrigerant through a shell of the vapor compression system.
  • the tube bundle assembly comprising a plurality of tubes and at least one baffle.
  • the at least one baffle includes a plurality of holes for receiving the plurality of tubes, wherein each respective hole comprises a non-uniform diameter such that only a portion of a periphery of each hole is positionable in contact with each tube.
  • the plurality of holes are arranged in a plurality of rows, and a diameter A is defined by an outermost surface of the plurality of holes surrounding each hole of the plurality of holes.
  • holes in adjacent rows are separated by a first axial distance P and the first axial distance P is between .75 and 1.2 times the diameter A.
  • adjacent holes within the same row are separated by a second axial distance Rw and the second axial distance Rw is between .8 and 1.5 times the diameter A.
  • each respective hole comprises a plurality of lobes protruding inwardly towards a center of the respective hole.
  • each of the plurality of lobes comprises a land positionable in contact with the tube.
  • the land of each of the plurality of lobes defines a maximum allowable diameter of the at least one tube and the diameter A is between .81 and 1.16 times the maximum allowable diameter.
  • a base of each of the plurality of lobes has a fillet radius Z and the fillet radius Z is between .05 and 1.1 times the diameter A.
  • the vapor compression system 20 includes a compressor 22 having a suction port (inlet) 24 and a discharge port (outlet) 26.
  • the vapor compression system 20 further includes a first, heat rejection heat exchanger 28, for example a condenser.
  • the vapor compression system 20 additionally includes a second, heat absorption heat exchanger 30, for example an evaporator, located downstream from the heat rejection heat exchanger 28.
  • an expansion device 32 is located along the fluid flow path downstream of the compressor 22 and upstream of the evaporator heat absorption heat exchanger. As shown, the expansion device 32 may be located at a position along the fluid loop between the heat rejection heat exchanger 28 and the heat absorption heat exchanger 30.
  • the heat rejection heat exchanger 28 is a water-cooled heat exchanger such that the refrigerant within the heat exchanger is cooled by a flow of an external flow of water.
  • the vapor compression system of FIG. 1 may be referred to herein as a water-cooled chiller.
  • the flow of water may be delivered from a source 36, such as a cooling tower for example, located directly adjacent to the heat rejection heat exchanger 28, or alternatively, located remotely from a heat rejection heat exchanger 28, such as at a different location within a building being conditioned by the vapor compression system 20 for example.
  • a pump 38 may be used to circulate a flow of cool water from the cooling tower 36 to the heat rejection heat exchanger 28 and also to return a flow of heated water to the cooling tower 36 from the heat rejection heat exchanger 28.
  • the water may be cooled via a flow of an external gas driven by a fan 40, such as an air-flow for example, before being returned to the heat rejection heat exchanger 28.
  • a fan 40 such as an air-flow for example
  • the heat rejection heat exchanger 28 is described herein as the water-cooled heat exchanger, in other embodiments the heat absorption heat exchanger may alternatively, or additionally be configured as an air-cooled heat exchanger.
  • the vapor compression system 20 illustrated and described herein is a simplified system and that a vapor compression system 20 having additional components is also within the scope of the invention.
  • the heat exchanger 50 has a shell and tube configuration.
  • the shell 52 has a generally cylindrical body with a hollow interior 54 and is capped at opposite ends by manifolds 56, 58.
  • An inlet port 60 for the refrigerant may be formed at a first location of the shell 52, such as near a bottom of the shell 52 for example, and an outlet port 62 may be formed at a second location of the shell 52, such as near a top portion thereof for example.
  • a tube bundle 64 including a plurality of tubes 66 is positioned within the hollow interior 54 of the shell 52.
  • the tube bundle 64 generally spans the width of the shell 52, extending between the manifolds 56, 58.
  • a tube inlet 68 and a tube outlet 70 are arranged in fluid communication with the at least one tube of the tube bundle.
  • a refrigerant circulating through the vapor compression system 20 is provided to the heat exchanger 50 via the inlet 60.
  • a secondary fluid W such as water for example, is provided to the tube bundle 64 via the tube inlet 68.
  • the heat exchanger 50 is a heat rejection heat exchanger
  • a warmed secondary fluid W is provided at the tube outlet 70 and a cooled liquid refrigerant R is provided at the outlet 62.
  • both the tube inlet 68 and the tube outlet 70 are illustrated as being arranged at the same manifold 56, embodiments where the tube inlet 68 and the tube outlet 70 are arranged at opposite manifolds are also within the scope of the present invention.
  • the tube bundle 64 may be operably coupled to one or more tube sheets or baffles 72 to not only maintain the relative position of the tubes 66 within the tube bundle 64, and also to maintain the position of the tube bundle 64 relative to the shell 52.
  • the heat exchanger 50 includes a plurality of baffles 72 (shown in FIG. 3 ) spaced at intervals over an axial length of the tube bundle 64, between the manifolds 56, 58.
  • Each baffle 72 has at least one hole 74 (shown in FIG. 4 ) formed therein for receiving the plurality of tubes 66 of the tube bundle 64.
  • the total number of holes 74 may be equal to the total number of tubes 66 within the tube bundle 64 such that each tube 66 is receivable within a corresponding hole 74 of the baffle 72.
  • the plurality of tubes 66 is laced through the plurality of holes 74 and may be arranged in direct contact with the baffle 72 at the hole 74.
  • baffles 72 such as each baffle for example, is formed from a non-metallic material.
  • the baffle 72 is formed from a polymeric or elastomeric material with or without internal reinforcements.
  • a configuration of the holes 74 formed in the baffle 72 may be selected to engage and restrict movement of a tube 66 received therein without another mechanical connection.
  • one or more of the holes 74 formed in the baffle 72 has a non-uniform diameter.
  • a hole 74 includes a one or more teeth or lobes 76 that protrude inwardly towards the center of the hole 74.
  • a hole 74 formed in the baffle 72 has between three and ten lobes 76, and in some embodiment between 4 and 8 lobes 76.
  • a configuration of each of the plurality of the lobes 76 may be substantially identical, or may vary.
  • the plurality of lobes 76 may be equidistantly spaced about a periphery of the hole 74, or alternatively, may be non-uniformly spaced.
  • the lobes 76 may have a fillet radius Z formed at the curve of a base thereof. Further, each of the lobes 76 has a land 78 arranged at the innermost surface thereof. In an embodiment, the diameter of the land 78 defines the maximum allowable diameter of the tube 66 receivable within the hole 74. The contour or configuration of the land 78 may be selected to maintain contact with a tube 66 over the substantially entire surface of the land 78, or alternatively, may be designed such that only a portion of the land 78 is arranged in contact with the tube 66.
  • the land 78 has a convex curvature defined by a radius C such that the land 78 is arranged in line contact with a tube 66 (and in point contact in the cross-sectional view of FIG. 6 ).
  • the friction between the land 78 and the exterior surface of the tube 66 may form a self-locking interface, thereby restricting movement of the tube 66 relative to the baffle 72.
  • a diameter B is defined between an origin of the radius of curvature C for oppositely positioned lobes 76.
  • the holes 74 may be arranged in a plurality of rows positioned over the height of the baffle 72, and the holes 74 within adjacent rows may be offset or staggered relative to one another.
  • a first axial distance between the center of holes 74 located in adjacent rows of the baffle 72 and extending in a first direction is represented by P.
  • a second axial distance between a center of adjacent holes 74 within the same row and extending in a second direction, oriented orthogonal to the first direction is represented by Rw.
  • the second axial distance Rw is measured within a horizontally oriented plane.
  • the distance P is illustrated as being a vertical distance and the distance Rw is illustrated as a horizontal distance, embodiments where one or both of P and Rw are measured along another axis are also contemplated herein.
  • P and Rw are substantially identical, and in other embodiments, P and Rw may vary.
  • A is a diameter defined by the outermost surface of a plurality of holes 74 within the same row and the adjacent rows.
  • the diameter A is defined by the outermost surface of the holes to the left and right of the centrally located hole, and by the outermost surface of the adjacent holes in the row above and below the central row.
  • the diameter A relative to the maximum allowable tube diameter defined by the lobes may be between about .81 and 1.16.
  • the distance P is between about .75 and about 1.2 times the diameter A
  • the distance Rw is between .8 and about 1.5 times the diameter A.
  • the diameter A may be between about .77 and about 1.33 times the diameter B.
  • the fillet radius Z may be between about .05 and 1.1 times the diameter A and in an embodiment, the radius C of the land 78 may be between about .09 and about .15 times the diameter B.
  • the tubes 66 can be formed from an aluminum material rather than a costly copper material. Further, by forming holes 74 in the baffle 72 having one or more lobes 76 configured to frictionally engage, and therefrom grip a respective tube 66, the need to swage the tubes into the baffles, in applications that currently requires swaging is eliminated.
  • the non-metallic baffles 72 disclosed herein may also be used in applications where swaging is not needed currently, by sizing the lobe geometries accordingly to reduce the amount of gripping force. As a result, the cost of material and labor associated with the heat exchanger 50 is reduced.

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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)
EP23160579.1A 2022-03-09 2023-03-07 Nichtmetallische ablenkplatte für wärmetauscher Pending EP4242571A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US202263318198P 2022-03-09 2022-03-09

Publications (1)

Publication Number Publication Date
EP4242571A1 true EP4242571A1 (de) 2023-09-13

Family

ID=85510848

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23160579.1A Pending EP4242571A1 (de) 2022-03-09 2023-03-07 Nichtmetallische ablenkplatte für wärmetauscher

Country Status (3)

Country Link
US (1) US20230288152A1 (de)
EP (1) EP4242571A1 (de)
CN (1) CN116734652A (de)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4204305A (en) * 1971-08-27 1980-05-27 The Babcock & Wilcox Company Method of assembling a heat exchange apparatus
DE3136865A1 (de) * 1981-09-17 1983-03-31 Schwelmer Eisenwerk Müller & Co GmbH, 5830 Schwelm "roehrenwaermetauscher mit im stroemungsraum angeordneten stroemungsleiteinbauten"
EP0184344A1 (de) * 1984-11-13 1986-06-11 Westinghouse Electric Corporation Stütze für Dampferzeugerröhren
EP0568713A1 (de) * 1992-05-05 1993-11-10 Deggendorfer Werft Und Eisenbau Gmbh Stützrost für Rohrbündel
US5893410A (en) * 1997-06-09 1999-04-13 General Electric Co. Falling film condensing heat exchanger with liquid film heat transfer
US6498827B1 (en) * 1999-11-01 2002-12-24 Babcock & Wilcox Canada, Ltd. Heat exchanger tube support structure
FR3002316A1 (fr) * 2013-02-19 2014-08-22 Dcns Echangeur de chaleur monophasique du type a chicanes ameliore et plaque de cloisonnement pour un tel echangeur
DE112016006146T5 (de) * 2016-02-08 2018-09-20 Mitsubishi Hitachi Power Systems, Ltd. U-rohr wärmetauscher

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4204305A (en) * 1971-08-27 1980-05-27 The Babcock & Wilcox Company Method of assembling a heat exchange apparatus
DE3136865A1 (de) * 1981-09-17 1983-03-31 Schwelmer Eisenwerk Müller & Co GmbH, 5830 Schwelm "roehrenwaermetauscher mit im stroemungsraum angeordneten stroemungsleiteinbauten"
EP0184344A1 (de) * 1984-11-13 1986-06-11 Westinghouse Electric Corporation Stütze für Dampferzeugerröhren
EP0568713A1 (de) * 1992-05-05 1993-11-10 Deggendorfer Werft Und Eisenbau Gmbh Stützrost für Rohrbündel
US5893410A (en) * 1997-06-09 1999-04-13 General Electric Co. Falling film condensing heat exchanger with liquid film heat transfer
US6498827B1 (en) * 1999-11-01 2002-12-24 Babcock & Wilcox Canada, Ltd. Heat exchanger tube support structure
FR3002316A1 (fr) * 2013-02-19 2014-08-22 Dcns Echangeur de chaleur monophasique du type a chicanes ameliore et plaque de cloisonnement pour un tel echangeur
DE112016006146T5 (de) * 2016-02-08 2018-09-20 Mitsubishi Hitachi Power Systems, Ltd. U-rohr wärmetauscher

Also Published As

Publication number Publication date
US20230288152A1 (en) 2023-09-14
CN116734652A (zh) 2023-09-12

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