EP4367464B1 - Rohrbündelwärmetauscher mit spiralförmigen ablenkblechen - Google Patents

Rohrbündelwärmetauscher mit spiralförmigen ablenkblechen

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Publication number
EP4367464B1
EP4367464B1 EP22838101.8A EP22838101A EP4367464B1 EP 4367464 B1 EP4367464 B1 EP 4367464B1 EP 22838101 A EP22838101 A EP 22838101A EP 4367464 B1 EP4367464 B1 EP 4367464B1
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EP
European Patent Office
Prior art keywords
heat exchanger
shape
flat segments
segments
flat
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.)
Active
Application number
EP22838101.8A
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English (en)
French (fr)
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EP4367464A4 (de
EP4367464C0 (de
EP4367464A1 (de
Inventor
Janusz Przybyla
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.)
Famet Spolka Akcyjna
Original Assignee
Famet Spolka Akcyjna
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Publication of EP4367464A1 publication Critical patent/EP4367464A1/de
Publication of EP4367464A4 publication Critical patent/EP4367464A4/de
Application granted granted Critical
Publication of EP4367464C0 publication Critical patent/EP4367464C0/de
Publication of EP4367464B1 publication Critical patent/EP4367464B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • 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
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • 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
    • 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
    • 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
    • F28F2009/228—Oblique partitions

Definitions

  • the present invention relates to a shell-and-tube heat exchanger with helical baffles, used in a variety of industry sectors, particularly in refinery and petrochemical systems, power industry, metallurgical industry, and others.
  • the main component of the heat exchanger is typically a cylindrical outer shell with inlet and outlet nozzles. Inside the shell, there is placed a bundle of tubes the ends thereof are fixed in tubesheets. One fluid flows inside the tubes whereas second fluid flows in the shell, in the inter-tube space, so that heat transfer takes place between them. A very significant role is played by so called baffles of the tube bundle.
  • the function of the baffles is to support the tubes and to direct the flow of the second fluid in the shell, so as to obtain high heat transfer rates, reduce fouling in the shell space and eliminate tube vibration.
  • heat exchangers with helical flow inside the shell have also begun to be increasingly used in the last several dozen years.
  • the helical flow in the shell is provided with the use of discontinuous helical baffles in the form of many, typically quarter segments arranged at an angle in relation to the heat exchanger axis.
  • discontinuous helical baffles described in those patents cause that the helical flow in the shell occurs only partially because a significant portion of the fluid moves between the quarter segments in the axial direction, meandering along the tubes.
  • the pressure drop inside the shell increases and the heat transfer deteriorates in such a situation.
  • CN104567485A discloses a shell-and-tube heat exchanger according to the preamble of claim 1.
  • the object of the present invention is to provide the structure of a shell-and-tube heat exchanger with an outer continuous helical baffle and with the use of a central pipe, as well as the structure of an outer continuous helical baffle integrated with an inner discontinuous helical baffle placed in the central flow, in order to achieve higher heat transfer efficiency and the reduction of flow resistance, thus the reduction of energy consumption together with the reduction of CO2 emission.
  • Another object of the present invention is also to achieve high stiffness of said structure as well as a simple and cheap method to precisely make tube holes in large heat exchangers including several hundred or even several thousand tubes.
  • the essence of the present invention is the structure of a continuous helical baffle for the outer bundle of tubes of the shell-and-tube heat exchanger including a central pipe or, in place of the central pipe, having additionally an inner bundle of tubes supported by an inner discontinuous helical baffle.
  • the outer continuous helical baffle is formed of many main flat segments in the shape of an isosceles triangle with the base thereof of the shape of a convex arc facing the inner surface of the heat exchanger shell and the apex of said triangle is located on a circle of a diameter equal to the outside diameter of the central pipe or, respectively, to the diameter of the central flow, as well as of many intermediate flat segments of the shape of an isosceles triangle with the base thereof of the shape of a concave arc facing the X-X axis of the heat exchanger, or many intermediate flat segments of the shape of an isosceles trapezium with one base thereof of the shape of a convex arc facing the inner surface of the heat exchanger shell and the other base thereof of the shape of a concave arc facing the X-X axis of the heat exchanger.
  • the main flat segments and the intermediate flat segments alternately adjoin each other along their legs and are arranged in relation to each other at an alternating angle ⁇ lesser than 180°, and, at the same time, respectively, every other main flat segment or every other intermediate flat segment of the shape of an isosceles triangle, or every other flat segment of the shape of an isosceles trapezium are mutually parallel.
  • the intermediate flat segments are located at an angle ⁇ lesser than 90° in relation to the X-X axis of the heat exchanger.
  • the inner discontinuous helical baffle is formed of many flat segments with one side thereof of the shape of a convex arc congruent with the concave arc of the intermediate flat segment of the shape of an isosceles triangle or to a concave arc of the intermediate flat segment of the shape of an isosceles trapezium, and they form with the intermediate flat segments of the outer continuous helical baffle many common flat segments, where the flat segment of the inner discontinuous helical baffle has the area F larger than the area S of a flat geometric figure similar to an isosceles triangle with the base thereof of the shape of a convex arc congruent with a concave arc of the intermediate flat segment of the shape of an isosceles triangle or to a concave arc of the intermediate flat segment of the shape of an isosceles trapezium whereas the apex of said triangle is located on the X-X axis of the heat exchanger.
  • the projection of said geometric figure on a plane perpendicular to the X-X axis of the heat exchanger corresponds to one fourth or one sixth of the cross-sectional area of the central flow contained in a circle of a diameter equal to the diameter of the central flow.
  • the flat segments of the inner discontinuous helical baffle have the area F larger than the area S of a flat geometric figure in order to accommodate all tube holes located within the flat geometric figure and at least all complete boundary tube holes located at the edge of the flat geometric figure and arranged in accordance with the layout of the inner bundle of tubes.
  • the flat segments of the inner discontinuous helical baffle can have the area F larger than the area S of the flat geometric figure in order to accommodate, apart from all tube holes located within the flat geometric figure and the boundary tube holes, additional tube holes arranged in accordance with the layout of the inner bundle of tubes.
  • the main flat segments together with the intermediate flat segments form couples of segments that, consecutively repeated n-fold, form one full pitch P of the outer continuous helical baffle along the X-X axis of the heat exchanger, where n equals 4 or 6.
  • the essence of the present invention is also that the main flat segments together with the associated flat segments form couples of segments which, consecutively repeated n-fold, form one full pitch P of the outer continuous helical baffle integrated with the inner discontinuous helical baffle, where n equals 4 or 6.
  • the angle ⁇ ranges from 30° to 75° whereas the angle ⁇ is within the range from 120° to 170°.
  • each couple of the flat segments is cut out from a single plate sheet and bent at the angle ⁇ along the legs of the main flat segments.
  • the convex arcs of the intermediate flat segments shaped into an isosceles trapezium and located at the angle ⁇ in relation to the X-X axis of the heat exchanger and the convex arcs of the main flat segments are fragments of an ellipse, and all said arcs in the projection on a plane perpendicular to the X-X axis form a circle of a diameter lesser by 2 to 20 mm than the inside diameter of the shell.
  • the concave arcs of the intermediate flat segments of the shape of an isosceles triangle or the concave arcs of the intermediate flat segments of the shape of an isosceles trapezium are fragments of such an ellipse which in the projection on a plane perpendicular to the X-X axis forms a circle of a diameter equal to the outside diameter of the central pipe or the diameter of the central flow.
  • the shell-and-tube heat exchanger according to the invention with the use of the central pipe and the outer continuous helical baffle formed of many main flat segments of the shape similar to an isosceles triangle and connected one to the other with the intermediate flat segments of the shape similar to an isosceles triangle or to an isosceles trapezium enables the implementation of a uniform optimal plug flow of the second fluid in the heat exchanger shell.
  • the shell-and-tube heat exchanger according to the invention with the outer continuous helical baffle and integrated therewith the inner discontinuous helical baffle in the central flow enables to reduce the velocity of the central flow and, concurrently, to increase the velocity of the helical flow in the outer bundle of tubes.
  • This change has a beneficial effect on the equalization of the velocity and on the increase of the heat transfer capacity in the entire heat exchanger because the heat transfer in the outer bundle of tubes increases.
  • Increasing the area of the segments of the inner discontinuous helical baffle provides the opportunity to optimize the flow-and-thermal parameters of a heat exchanger at the stage of design and thermal calculations.
  • the size of the entire heat exchanger for a particular task can be significantly reduced, even by over a dozen percent, retaining all so far known advantages of the helical flow in the shell of a heat exchanger, namely elimination of fouling, reduction of tube vibrations and the increase of the operational time in between overhauls.
  • the heat exchanger according to the invention can be successfully used in place of existing traditional tube bundles with segmental baffles or in place of the so called Helixchanger heat exchanger. In such cases, the reduction of energy consumption or the increase of flexibility - efficiency of the entire installation will be achieved.
  • the heat exchanger has two tubesheets 3 in which the ends of tubes 4 are fixed.
  • First fluid flows inside the tubes 4 of the entire outer bundle of tubes 2, excluding the central pipe 9.
  • Second fluid is supplied to the shell 1 through the inlet nozzle 5.
  • the holes 10 for tubes 4 were made according to the planned layout.
  • the Inventor computer program for 3D design was used.
  • Second embodiment is a heat exchanger ( Fig. 3 and Fig. 4 ) having two tubesheets 3 in which the ends of the tubes 4 of the outer bundle of tubes 2 and the inner bundle of tubes 22 are fixed.
  • First fluid flows inside the tubes 4 of both bundles of tubes 2 and 22.
  • Second fluid is supplied to the shell 1 through the inlet nozzle 5.
  • the holes 10 for tubes 4 were made according to the planned layout.
  • the parts thus prefabricated are assembled into the appropriate whole of the outer continuous helical baffle 8 integrated with the inner discontinuous helical baffle 23 whose example is presented in ( Fig. 12 ).
  • the inner discontinuous helical baffle 23 is made of twelve flat segments 25 ( Fig. 10 ), which have the area F adequately large to accommodate all tube holes 10 and additionally eleven complete boundary tube holes 10A.
  • the two embodiments presented above do not limit the possibilities of constructing other heat exchangers in accordance with the invention. Particularly, for large, not mentioned before, sizes of heat exchangers, a larger number of flat segments presented as an example in the drawing ( Fig. 13 ) can be used.
  • heat exchangers with a double-scroll structure of the helical baffles can also be constructed.
  • the embodiment described does not limit the construction of a heat exchanger with the use of only four or six couples of segments for one scroll of the helical baffle as well.
  • three or even two couples of flat segments can be used.

Landscapes

  • 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)

Claims (8)

  1. Rohrbündelwärmetauscher mit spiralförmigen Umlenkblechen, der Folgendes umfasst: einen Mantel mit einer Einlass- und Auslassdüse, ein Zentralrohr oder, anstelle des Zentralrohrs, ein zusätzliches inneres Rohrbündel, das im zentralen Strömungsbereich angeordnet ist, ein äußeres Rohrbündel (2), das parallel zur Mantelachse und um das Zentralrohr (9) oder um das zusätzliche innere Rohrbündel (22) herum angeordnet ist, zwei Rohrböden zur Befestigung der Rohrenden darin, ein äußeres durchgehend spiralförmiges Umlenkblech (8), das aus flachen Segmenten gebildet ist und an den Innendurchmesser des Mantels angepasst ist, und, falls anstelle des zentralen Rohrs das zusätzliche innere Rohrbündel vorhanden ist, zusätzlich ein inneres, unterbrochenes spiralförmiges Umlenkblech (23), das im zentralen Strömungsbereich angeordnet ist, wobei jedes Umlenkblech zahlreiche koaxiale Löcher für jedes Rohr eines oder beider Rohrbündel aufweist,
    dadurch gekennzeichnet, dass:
    das äußere durchgehend spiralförmige Umlenkblech (8) besteht aus vielen flachen Hauptsegmenten (11) in Form eines gleichschenkligen Dreiecks, dessen Basis die Form eines konvexen Bogens (12) hat, der zur Innenfläche (13) des Wärmetauschermantels (1) zeigt und der Scheitelpunkt dieses Dreiecks liegt auf einem Kreis (21) mit einem Durchmesser, der dem Außendurchmesser des zentralen Rohrs (9) bzw. dem Durchmesser des zentralen Strömungskanals (24) entspricht, sowie aus vielen flachen Zwischensegmenten (14) in Form eines gleichschenkligen Dreiecks, dessen Basis die Form eines konkaven Bogens (15) hat, der zur X-X-Achse des Wärmetauschers hin ausgerichtet ist, oder aus vielen flachen Zwischensegmenten (16) in Form eines gleichschenkligen Trapezes, dessen eine Basis die Form eines konvexen Bogens (17) hat, der zur Innenfläche (13) des Wärmetauschermantels (1) hin ausgerichtet ist, und dessen andere Basis die Form eines konkaven Bogens hat (18) , der zur X-X-Achse des Wärmetauschers hin ausgerichtet ist, und die flachen Hauptsegmente (11) zusammen mit den flachen Zwischensegmenten (14) in Form eines gleichschenkligen Dreiecks oder mit den flachen Zwischensegmenten (16) in Form eines gleichschenkligen Trapezes abwechselnd entlang der Länge ihrer Schenkel (19) aneinandergrenzen und in einem wechselnden Winkel α von weniger als 180° zueinander angeordnet sind, wobei gleichzeitig jedes zweite flache Hauptsegment (11) oder jedes zweite flache Zwischensegment (14) in Form eines gleichschenkligen Dreiecks oder jedes zweite flache Zwischensegment (16) in Form eines gleichschenkligen Trapezes zueinander parallel sind, während die flachen Zwischensegmente (14) oder (16)
    in einem Winkel β von weniger als 90° in Bezug auf die X-X-Achse des Wärmetauschers positioniert sind, während das innere diskontinuierliche spiralförmige Umlenkblech (23) aus vielen flachen Segmenten (25) gebildet ist, deren eine Seite die Form eines konvexen Bogens (26) hat, der mit dem konkaven Bogen (15) des mittleren flachen Segments (14) in Form eines gleichschenkligen Dreiecks oder mit dem konkaven Bogen (18) des flachen Zwischensegments (16) in Form eines gleichschenkligen Trapezes kongruent ist und die zusammen mit den flachen Zwischensegmenten (14) oder (16) des äußeren durchgehenden spiralförmigen Umlenkblechs (8) viele gemeinsame flache Segmente (27) oder (27A) bilden, wobei das flache Segment (25) des inneren unterbrochenen spiralförmigen Umlenkblechs (23) die Fläche F hat, die größer ist als die Fläche S einer flachen geometrischen Figur (28), die einem gleichschenkligen Dreieck ähnelt, dessen Basis die Form eines konvexen Bogens (26) hat, der mit dem konkaven Bogen (15) des flachen Zwischensegments (14) in Form eines gleichschenkligen Dreiecks oder mit dem konkaven Bogen (18) des flachen Zwischensegments (16) in Form eines gleichschenkligen Trapezes kongruent ist, während sich der Scheitelpunkt dieses Dreiecks auf der X-X-Achse des Wärmetauschers befindet, und wobei die Projektion der genannten geometrischen Figur (28) auf eine Ebene senkrecht zur X-X-Achse 1/4 oder 1/6 der Querschnittsfläche des zentralen Strömungsbereichs (24) entspricht, der in dem Kreis (21) mit einem Durchmesser enthalten ist, der dem Durchmesser des zentralen Strömungsbereichs (24) entspricht.
  2. Wärmetauscher gemäß Anspruch 1, dadurch gekennzeichnet, dass:
    Die flachen Segmente (25) des inneren unterbrochenen spiralförmigen Umlenkblechs (23) eine Fläche F aufweisen, die größer ist als die Fläche S der flachen geometrischen Figur (28), um alle innerhalb der flachen geometrischen Figur (28) angeordneten Rohrlöcher (10) und mindestens alle vollständigen Randrohrlöcher (10A) aufzunehmen, die sich am Rand der flachen geometrischen Figur (28) befinden und entsprechend der Anordnung des inneren Rohrbündels (22) angeordnet sind.
  3. Wärmetauscher gemäß Anspruch 1 oder 2, dadurch gekennzeichnet, dass:
    Die flachen Segmente (25) des inneren unterbrochenen spiralförmigen Umlenkblechs (23) eine Fläche F aufweisen, die größer ist als die Fläche S der flachen geometrischen Figur (28), um neben allen innerhalb der flachen geometrischen Figur (28) angeordneten Rohrlöchern (10) und den Randrohrlöchern (10A) zusätzliche Rohrlöcher (10B) aufzunehmen, die entsprechend der Anordnung des inneren Rohrbündels (22) angeordnet sind.
  4. Wärmetauscher gemäß Anspruch 1, dadurch gekennzeichnet, dass:
    Die flachen Hauptsegmente (11) zusammen mit den flachen Zwischensegmenten (14) in Form eines gleichschenkligen Dreiecks oder mit den flachen Zwischensegmenten (16) in Form eines gleichschenkligen Trapezes Paare von Segmenten (29) bzw. Paare von Segmenten (29A) bilden, die sich n-mal hintereinander wiederholen und einen vollständigen Steigungsabstand P des äußeren kontinuierlichen spiralförmigen Umlenkblechs (8) entlang der X-X-Achse des Wärmetauschers bilden, wobei n = 4 oder 6 ist.
  5. Wärmetauscher gemäß Anspruch 1, dadurch gekennzeichnet, dass:
    Die flachen Hauptsegmente (11) zusammen mit den gemeinsamen flachen Segmenten (27) oder mit den gemeinsamen falchen Segmenten (27A) jeweils Segmentpaare (30) oder Segmentpaare (30A) bilden, die sich n-mal hintereinander wiederholen und einen vollständigen Steigungsabstand P des äußeren kontinuierlichen spiralförmigen Umlenkblechs (8) bilden, der in dem inneren diskontinuierlichen spiralförmigen Umlenkblech (23) integriert ist, wobei n = 4 oder 6 ist.
  6. Wärmetauscher gemäß Anspruch 1, dadurch gekennzeichnet, dass:
    Der Winkel β von 30° bis 75° reicht, während der Winkel α im Bereich von 120° bis 170° liegt.
  7. Wärmetauscher gemäß Anspruch 1, dadurch gekennzeichnet, dass:
    Jedes Paar der flachen Segmente (29), (29A), (30) oder (30A) aus einem einzigen Blech ausgeschnitten und entlang der Schenkel (19) der flachen Hauptsegmente (11) um den Winkel α gebogen wird.
  8. Wärmetauscher gemäß Anspruch 1, dadurch gekennzeichnet, dass:
    Die konvexen Bögen (17) der flachen Zwischensegmente (18) in Form eines gleichschenkligen Trapezes, wobei diese Segmente im Winkel β zur X-X-Achse des Wärmetauschers angeordnet sind, sowie die konvexen Bögen (12) der flachen Hauptsegmente (11) Fragmente einer Ellipse sind und alle diese Bögen in der Projektion auf eine zur X-X-Achse senkrechte Ebene einen Kreis (20) mit einem Durchmesser bilden, der um 2 bis 20 mm kleiner ist als der Innendurchmesser (7) des Mantels (1), und gleichzeitig die konkaven Bögen (15) der flachen Zwischensegmente (14) in Form eines gleichschenkligen Dreiecks oder die konkaven Bögen (18) der
    flachen Zwischensegmente (16) in Form eines gleichschenkligen Trapezes Fragmente einer solchen Ellipse sind, die in der Projektion auf eine Ebene senkrecht zur X-X-Achse einen Kreis (21) mit einem Durchmesser bilden, der dem Außendurchmesser des zentralen Rohrs oder dem Durchmesser des zentralen Strömungskanals (24) gleicht.
EP22838101.8A 2021-07-07 2022-06-24 Rohrbündelwärmetauscher mit spiralförmigen ablenkblechen Active EP4367464B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PL438374A PL244117B1 (pl) 2021-07-07 2021-07-07 Płaszczowo-rurowy wymiennik ciepła z helikoidalnymi przegrodami
PCT/PL2022/050041 WO2023282775A1 (en) 2021-07-07 2022-06-24 A shell-and-tube heat exchanger with helical baffles

Publications (4)

Publication Number Publication Date
EP4367464A1 EP4367464A1 (de) 2024-05-15
EP4367464A4 EP4367464A4 (de) 2025-04-30
EP4367464C0 EP4367464C0 (de) 2025-11-26
EP4367464B1 true EP4367464B1 (de) 2025-11-26

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EP22838101.8A Active EP4367464B1 (de) 2021-07-07 2022-06-24 Rohrbündelwärmetauscher mit spiralförmigen ablenkblechen

Country Status (4)

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US (1) US20240369305A1 (de)
EP (1) EP4367464B1 (de)
PL (1) PL244117B1 (de)
WO (1) WO2023282775A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118705909B (zh) * 2024-07-12 2025-06-27 中国三峡新能源(集团)股份有限公司 一种减少泄露流体的非连续螺旋折流板换热器及方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3400758A (en) * 1966-05-16 1968-09-10 United Aircraft Prod Helical baffle means in a tubular heat exchanger
CN100453951C (zh) * 2007-02-09 2009-01-21 西安交通大学 组合螺旋折流板管壳式换热器
US7740057B2 (en) * 2007-02-09 2010-06-22 Xi'an Jiaotong University Single shell-pass or multiple shell-pass shell-and-tube heat exchanger with helical baffles
CN104567485B (zh) * 2014-12-26 2017-10-31 新奥科技发展有限公司 一种列管式换热器
US11287196B2 (en) * 2019-05-31 2022-03-29 Lummus Technology Llc Helically baffled heat exchanger

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WO2023282775A1 (en) 2023-01-12
PL244117B1 (pl) 2023-12-04
EP4367464A4 (de) 2025-04-30
PL438374A1 (pl) 2023-01-09
EP4367464C0 (de) 2025-11-26
EP4367464A1 (de) 2024-05-15
US20240369305A1 (en) 2024-11-07

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