EP0854344B1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP0854344B1
EP0854344B1 EP98100889A EP98100889A EP0854344B1 EP 0854344 B1 EP0854344 B1 EP 0854344B1 EP 98100889 A EP98100889 A EP 98100889A EP 98100889 A EP98100889 A EP 98100889A EP 0854344 B1 EP0854344 B1 EP 0854344B1
Authority
EP
European Patent Office
Prior art keywords
tube
fin
bent portions
peripheral portion
finned tube
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.)
Expired - Lifetime
Application number
EP98100889A
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English (en)
French (fr)
Other versions
EP0854344A2 (de
EP0854344A3 (de
Inventor
Kenichi 203 Yoshiba Coporasu Kimura
Minoru Yamada
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toshiba Corp
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Toshiba Corp
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Filing date
Publication date
Application filed by Toshiba Corp filed Critical Toshiba Corp
Publication of EP0854344A2 publication Critical patent/EP0854344A2/de
Publication of EP0854344A3 publication Critical patent/EP0854344A3/de
Application granted granted Critical
Publication of EP0854344B1 publication Critical patent/EP0854344B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals

Definitions

  • the present invention relates to a heat exchanger having finned tubes according to the preamble of claim 1.
  • a heat exchanger is known for instance from FR-A-1604823.
  • a heat exchanger has a plurality of properly arranged finned tubes for heat transfer, and makes an internal fluid, such as cooling water, flowing through the finned tubes and an external fluid, such as a fluid to be cooled, flowing in a direction intersecting the axes of the finned tubes exchange heat.
  • the finned tubes of the heat exchanger is provided with fins to provide a large external heat transfer area and to increase the heat transfer coefficient of each finned tube.
  • a plurality parallel finned tubes 1 are arranged in a staggered arrangement. An external fluid is made to flow through the casing in the direction of the arrow intersecting the axes of the finned tubes 1, and an internal fluid is made to flow through the finned tubes 1.
  • FIGs. 34a and 34b A solid-fin tube as shown in Figs. 34a and 34b, and a serrated-fin tube as shown in Figs. 35a and 35b are used prevalently in heat exchangers.
  • the arrows indicate the flowing direction of an external fluid.
  • the solid-fin tube shown in Figs. 34a and 34b is formed by attaching solid fins 3 to the outer circumference of a tube 2.
  • the serrated-fin tube is formed by attaching serrated fins 3 each having segments 4, i.e., radial teeth, to the outer surface of a tube 2.
  • the segments 4 of the serrated fins 3 prevents the development of a thermal boundary layer and hence the external heat transfer coefficient of the serrated-fin tube is higher than that of the solid-fin tube, and the heat-carrying capacity, i.e., the product of heat transfer area and external heat transfer coefficient, of the serrated-fin tube is not less than that of the solid-fin tube. Accordingly, the solid-fin tube or the serrated-fin tube are used selectively according to purposes.
  • the number of the heat exchanging tubes and the dimensions of a fin tube heat exchanger may be smaller than those of a bare tube heat exchanger for the same heat exchanging capacity, and the heat exchanging capacity of a fin tube heat exchanger is greater than that of a bare tube heat exchanger for the same number of heat exchanging tubes.
  • the flow of an external fluid flowing in the direction of the arrow separates from the outer surface of the solid-fin tube consisting of a tube and solid fins at an angular position on the outer surface of tube at an angular distance from a stagnation point to form a wake behind the tube.
  • the flow velocity of the external fluid in the wake is substantially zero or the external fluid flows in the reverse direction in the wake. Therefore, local external heat transfer coefficient is very low. Accordingly, a portion of the fin in the wake contributes scarcely to heat transfer and the effect of the fin on increasing heat transfer area is not fully exercised.
  • the condition of a wake formed behind the serrated-fin tube is substantially the same as that of the wake formed behind the solid-fin tube, and even the serrated fin has a portion which does not contribute to heat transfer.
  • resistors 5 having the shape of a plate of an appropriate width to fins 3 at positions obliquely behind a tube 2 where the flow of an external fluid separates from the tube 2 as shown in Figs. 37a and 37b or bends portions of fins 3 at positions obliquely behind a tube 2 as shown in Figs. 38a and 38b to form resistors 6.
  • resistors 5 and 6 deflect the flow of the external fluid separating from the tube 2 toward the downstream side of the fin tube to enhance the external heat transfer coefficient of the fin tube.
  • the position where the flow of the external fluid separates from the tube and the shape and condition of the wake are dependent on matters specifying the condition of the external fluid, such as the type, temperature, pressure and flow velocity of the external fluid. Therefore, the position, the range L covered by the bent portion (Figs. 37a and 38a) and the height h (Fig. 38b) of the bent portion must be determined taking into consideration matters specifying the condition of the external fluid.
  • the range L covered by the bent portion 5 of Figs. 37a and 37b can be adjusted by properly determining the width of the bent portion 5, however, the range L covered by the resistor 6 of Figs. 38a and 38b is dependent on the height h of the fin 3.
  • the sectional area of passages between the fins 3 is reduced by the resistors 5, and if the range L is great, the reduction of the sectional area of the passages causes an unignorable pressure loss of the external fluid, and the resistors 5 increase the weight of the heat exchanger.
  • the height h of the resistor 6 is geometrically dependent on the range L .
  • the present invention has been made in view of the foregoing problems in the prior art and it is therefore an object of the present invention to provide a heat exchanger of a high heat transfer performance provided with finned tubes each having fins provided in their peripheral portions with bent portions of a shape having a high degree of freedom of design according to the condition of an external fluid, and capable of effectively controlling the separation of the flow of the external fluid from the tube and of reducing a wake on the downstream side of the corresponding finned tube to enhance the local external heat transfer coefficient by the heat transfer area increasing effect thereof.
  • the heat exchanger comprises the features of claim 1.
  • the bent portions may be formed by in the same direction bending the segments formed by dividing the peripheral region of the fin by the radial slits.
  • the bent portions may be formed by alternately in opposite directions bending the segments formed by dividing the peripheral portion of the fin by the radial slits.
  • the bent portions may be formed by bending the alternate segments formed by dividing the peripheral portion of the fin by the radial slits.
  • the bent portions may be formed by in the same direction bending the alternate segments formed by dividing the peripheral portion of the fin by the radial slits.
  • the bent portions may be formed only in a specific circumferential range in the peripheral portion of each fin corresponding to a region in which streams of the external fluid separate from the tube.
  • Figs. 1a and 1b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger in a first embodiment according to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 having the shape of a circular plate to the outer surface of a tube 11.
  • the arrows shown in Figs. 1a through 32, similarly to that shown in Fig. 33, indicate the flowing direction of an external fluid.
  • a plurality of radial slits 13, twelve radial slits in Fig. 1a, are formed in a peripheral portion of the fin 12 to divide the peripheral portion into a plurality of segments, and portions of each segment are bent in an axial direction of the tube 11 along bending lines 14, which will be described below.
  • the radial slits 13 are formed in the peripheral portion of the fin 12.
  • the bending lines 14 extend between a point a on each radial slit and points b on the circumference of the fin 12 on the opposite sides of the radial slit 13, respectively.
  • Substantially triangular portions of the fin 12 defined by the bending lines 14, the radial slit 13 and sections of the outer circumference of the fin 12 are bent in opposite directions substantially perpendicular to the surface of the fin 12 along the bending lines 14 to form substantially triangular bent portions 15.
  • the bent portions 15 project alternately in opposite directions from one of the surfaces of the fin 12 and the other surface of the same as shown in Fig. 3.
  • the point a need not necessarily be at the inner end of the radial slit 13 as shown in Fig. 2, but may be at any suitable point between the outer and the inner end of the radial slit 13 as indicated at a' in Fig. 2 depending on the length of the radial slit 13 and intervals between the fins 12 on the tube 11.
  • the optimum dimensions and optimum positions of the bent portions 15 can be determined by properly determining the length and positions of the radial slits 13.
  • the bent portions 15 has a high degree of freedom of design.
  • the finned tubes 10 thus fabricated are arranged with their axes extended so as to intersect the flowing direction of the external fluid indicated by the arrow to construct a heat exchanger.
  • Fig. 4 showing streamlines representing the flow of the external fluid around one of the finned tubes 10 of this heat exchanger, the external fluid is deflected by an upstream section of the outer surface of the tube 11 so as to flow along an upper section and a lower section of the outer surface of the tube 11, and then streams of the external fluid flowing along upper and lower sections of the outer surface of the tube 11 are deflected by the bent portions 15 toward a region directly behind the tube 11 so that the external fluid flows substantially along a downstream section of the outer surface of the tube 11 and a wake is scarcely formed behind the tube 11.
  • the size of the wake is reduced greatly by the bent portions 15 formed by bending the segments formed by dividing the peripheral portion of the disk 12 by the radial slits 13 as mentioned above, and the size of the wake is far smaller than that of a wake which would be formed if the disks 12 are not provided with the bent portions 15.
  • the flow velocity of the external fluid increases in the region behind the finned tube 10, whereby local external heat transfer coefficient is increased; that is, the entire surfaces of the fins 12 contribute to heat transfer, so that the effective heat transfer area of the fins 12 can be increased. Since the disadvantage of the conventional finned tube that the local external heat transfer coefficient of the downstream side of the finned tube is very low as compared with that of the upstream side of the same can be overcome by the present invention, and the average external heat transfer coefficient of the finned tube 10 is very high as compared with that of the conventional finned tube.
  • Fig. 5 is a graph comparatively showing the respective heat transfer characteristics of the heat exchanger of the present invention and a conventional heat exchanger, in which approach flow velocity is measured to the right on the horizontal axis and average external heat transfer coefficient is measured upward on the vertical axis. It is known from Fig. 5 that the bent portions 15 increases the average external heat transfer coefficient of the finned tube greatly.
  • each fin of the finned tubes employed in the heat exchanger in this embodiment is provided with the bent portions 15 distributed over the entire outer circumference thereof, the finned tubes are suitable for use in a heat exchanger which is required to operate under conditions where the flow velocity of the external fluid varies in a wide flow velocity range, and a region in which the streams of the external fluid tend to separate from the tube of the finned tube and a region in which a wake is formed are variable.
  • the radial slits 13 may be formed in a specific circumferential range in the peripheral portion of the fin 12 as shown in Fig. 6 to form the bent portions 15 only in the specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube of the finned tube and a region in which a wake is formed.
  • bent portions 15 formed only in such a specific circumferential range in the peripheral portion of each fin 12 are effective in deflecting the flow of the external fluid toward the region directly behind the tube 11 in which a wake is liable to be formed, and the reduced number of the bent portions 15 limits pressure loss to the least unavoidable extent.
  • Figs. 7a and 7b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger in a second embodiment according to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 to a tube 11.
  • a plurality of slits 13 are formed in a peripheral portion of each fin 12 to divide the peripheral portion into a plurality of segments. Only one portion of each segment is bent to form a bent portion 15. The segments are bent alternately in opposite directions so that the bent portions 15 project alternately in opposite directions.
  • Fig. 8 is a perspective view of the bent portion 15.
  • bent portions 15 deflect streams of the external fluid flowing along upper and lower sections of the outer surface of the tube 11 toward a region directly behind the tube 11 so that the external fluid flows substantially along a downstream section of the outer surface of the tube 11 and a wake is scarcely formed behind the tube 11.
  • the flow velocity of the external fluid increases in the region behind the finned tube 10, whereby local external heat transfer coefficient is increased; that is, the entire surfaces of the fins 12 contribute to heat transfer, so that the effective heat transfer area of the fins 12 can be increased. Consequently, the flow velocity of the external fluid in the region behind the tube 11 increases, local external heat transfer coefficient is increased and hence the average external heat transfer coefficient is increased greatly.
  • the radial slits 13 may be formed in a specific circumferential range in the peripheral portion of the fin 12 as shown in Fig. 9 to form the bent portions 15 only in the specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10.
  • the bent portions 15 formed only in such a specific circumferential range in the peripheral portion of each fin 12 are effective in deflecting the flow of the external fluid toward the region directly behind the tube 11 in which a wake is liable to be formed and exercise the same effect as those previously mentioned in connection with the description of the first embodiment.
  • Figs. 10a and 10b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger in a third embodiment according to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 to a tube 11.
  • a plurality of slits 13 are formed in a peripheral portion of each fin 12 to divide the peripheral portion into a plurality of segments, and the segments are bent in the same direction to form bent portions 15 projecting from one of the surfaces of the fin 12.
  • the finned tube 10 is similar in other respects to the finned tube 10 employed in the heat exchanger in the second embodiment shown in Figs. 7a, 7b and 8 .
  • the radial slits 13 may be formed in a specific circumferential range in the peripheral portion of the fin 12 as shown in Fig. 11 to form the bent portions 15 only in the specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10.
  • Figs. 12a and 12b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger in a fourth embodiment according to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 to a tube 11.
  • a plurality of slits 13 are formed in a peripheral portion of each fin 12 to divide the peripheral portion into a plurality of segments.
  • Adjacent substantially triangular sections of the adjacent segments respectively on the opposite sides of each radial slit 13 (Fig. 2) are bent in the same direction to form a pair of bent portions 15. as shown in Fig. 13.
  • the pairs of adjacent substantially triangular sections of the segments are bent alternately in opposite directions so that the pairs of bent portions project alternately in opposite directions from one of the surfaces of the fin 12 and from the other surface of the same.
  • the radial slits 13 may be formed in a specific circumferential range in the peripheral portion of the fin 12 as shown in Fig. 14 to form the bent portions 15 only in the specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10.
  • Figs. 15a and 15b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger in a fifth embodiment according to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 to a tube 11.
  • a plurality of slits 13 are formed in a peripheral portion of each fin 12 to divide the peripheral portion into a plurality of segments. Substantially triangular sections of the segments are bent in the same direction to form bent portions 15. as shown in Fig. 13.
  • the radial slits 13 may be formed in a specific circumferential range in the peripheral portion of the fin 12 as-shown in Fig. 16 to form the bent portions 15 only in the specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10.
  • Figs. 17a and 17b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger relevant to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 having the shape of a circular plate to the outer surface of a tube 11.
  • the fin 12 has bent portions 15 of a shape different from those of the finned tubes 10 employed in the foregoing embodiments.
  • a plurality of radial slits 13 are formed in a peripheral portion of the fin 12 to divide the peripheral portion into a plurality of segments, and the segments are bent in the same direction along bending lines 17 to form bent portions 18 as shown in Fig. 19.
  • each bending line 17 extends between a first point a on one of the radial slit 13 and a second point a' on another radial slit 13' adjacent to the former radial slit 13.
  • the first point a and the second point a' are on the same circle R having its center on the center axis of the finned tube 10.
  • a substantially quadrangular portion of the segment defined by the radial slits 13 and 13', the bending line 17, and a section of the circumference of the fin 12 corresponding to the segment is bent along the bending line 17 perpendicularly to the surface of the fin 12 to form the bent portion 18.
  • the substantially quadrangular portions of the alternate segments are bent in the same direction so that the bent portions 18 project in the same direction from one of the surfaces of the fin 12 and the adjacent bent portions 18 may not be continuous.
  • the bent portions 18 may be formed only in a specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10 as shown in Fig. 20 if the flow velocity of the external fluid varies in a fixed range of flow velocity, and the region in which the streams of the external fluid tend to separate from the tube 11 and the condition of a wake are invariable.
  • Figs. 21a and 21b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger relevant to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 having the shape of a circular plate to the outer surface of a tube 11.
  • the fin 12 has substantially quadrangular bent portions 16 of a shape different from those of the finned tubes 10 employed in the foregoing embodiments.
  • a plurality of radial slits 13 are formed in a peripheral portion of the fin 12 to divide the peripheral portion into a plurality of segments, and the segments are bent substantially perpendicularly to the surface of the fin 12 in the same direction along bending lines 17 to form the bent portions 16 as shown in Fig. 23.
  • each bending line 17 extends between a first point a on one of the radial slit 13 and a second point c on another radial slit 13' adjacent to the former radial slit 13.
  • the first point a and the second point c are not on the same circle R having its center on the center axis of the finned tube 10. That is, the points a and c are on different concentric circles of different diameters, respectively.
  • a substantially quadrangular portion of the segment defined by the radial slits 13', the bending line 17, and a section of the circumference of the fin 12 corresponding to the segment is bent along the bending line 17 substantially perpendicularly to the surface of the fin 12 to form the bent portion 16.
  • the finned tube 10 exercises the same effect as that exercised by the finned tube 10 employed in the first embodiment.
  • the bent portions 16 may be formed only in a specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10 as shown in Fig. 25 if the flow velocity of the external fluid varies in a fixed range of flow velocity, and the region in which the streams of the external fluid tend to separate from the tube 11 and the condition of a wake are invariable.
  • Figs. 26a and 26b are sectional view and a side view, respectively, of a finned tube 10 employed in a heat exchanger relevant to the present invention.
  • the finned tube 10 is fabricated by attaching fins 12 having the shape of a circular plate to the outer surface of a tube 11, and each fin 12 has bent portions 16 projected alternately in opposite directions from one of the surfaces of the fin 12 and from the other surface of the same.
  • the finned tube 10 employed in the eighth embodiment is similar in other respects to the finned tube 10 shown in Figs. 21a, 21b and 22 employed in the seventh embodiment.
  • the bent portions 16 may be formed only in a specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10 as shown in Fig. 28.
  • Figs. 29a, 29b and 30 show a finned tube employed in a heat exchanger relevant to the present invention.
  • the finned tube is formed by attaching fins 12 to the outer surface of a tube 11.
  • Each fin 12 has bent portions 18 projected alternately in opposite directions from one of the surfaces of the fin 12 and from the other surface of the same.
  • the finned tube employed in the ninth embodiment is similar in other respects to the finned tube 10 shown in Figs. 17a, 17b and 18.
  • the bent portions 18 may be formed only in a specific circumferential range in the peripheral portion of the fin 12 corresponding to a region in which the streams of the external fluid tend to separate from the tube 11 of the finned tube 10 as shown in Fig. 31.
  • the length of the radial slits and the height of the bent portions may be determined properly taking into consideration the type, temperature, pressure and flow velocity of the external fluid, intervals between the fins, required heat exchange rate, allowable pressure loss and such.
  • the respective lengths of the radial slits 13 may be varied sequentially to form the successive bent portions 15 in gradually varying heights, respectively, so that the bent portions 15 in a region in which streams of the external fluid tend to separate from the tube 11 have a maximum height as shown in Fig. 32.
  • the fins of the finned tubes illustrated in the drawings are continuous fins formed by helically winding a strip around a tube, the fins may be separate rings attached separately to the outer surface of a tube.
  • each of the fins of the finned tube has the plurality of bent portions on its outer circumference, and each bent portion is formed by bending each of the segments formed by dividing the peripheral portion of the fin by the radial slits in an axial direction of the tube along the bending line extending from a point on one of the radial slit.
  • the bent portions have a high degree of freedom of design and can be formed in an optimum shape capable of effectively suppressing the separation of streams of the external fluid from the finned tube.
  • the region in which a wake is formed due to the separation of streams of the external fluid from the tube of the finned tube can be reduced, so that the local external heat transfer coefficient of the downstream section of the finned tube is enhanced, the heat transfer area of the finned tube can be effectively increased and, consequently, the heat exchanging performance of a heat exchanger employing the finned tube of the present invention can be improved.

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

Claims (5)

  1. Wärmetauscher, umfassend:
    ein Rohr (11), das eine Achse besitzt, die eine Strömungsrichtung eines externen Fluids schneidet; und
    Rippen (12), die an einer äußeren Fläche des Rohrs (11) angebracht sind; worin jede Rippe (12) in einem Randabschnitt davon mit einer Mehrzahl geknickter Abschnitte (15) ausgestattet ist, wobei die geknickten Abschnitte (15) gebildet sind durch Bilden radialer Schlitze (13) in dem Randabschnitt der Rippe (12), um den Randabschnitt in eine Mehrzahl von Segmenten zu teilen, und Knicken jedes Segments im wesentlichen senkrecht zu der Fläche der Rippe (12), dadurch gekennzeichnet, dass das Knicken entlang einer Knicklinie ausgeführt ist, die sich zwischen einem Punkt an dem Radialschlitz (13) und einem Punkt (b) an einem äußeren Umfang der Rippe (12) erstreckt.
  2. Wärmetauscher nach Anspruch 1, worin die geknickten Abschnitte (15) durch Knicken der durch Teilen des Randabschnitts der Rippe (12) durch die radialen Schlitze (13) gebildeten Segmente in derselben Richtung gebildet sind.
  3. Wärmetauscher nach Anspruch 1, worin die geknickten Abschnitte (15) durch Knicken der durch Teilen des Randabschnitts der Rippe (12) durch die radialen Schlitze (13) gebildeten Segmente in abwechselnd entgegengesetzten Richtung gebildet sind.
  4. Wärmetauscher nach Anspruch 1, worin die geknickten Abschnitte durch abwechselndes Knicken der durch Teilen des Randabschnitts der Rippe (12) durch die radialen Schlitze (13) gebildeten Segmente gebildet sind.
  5. Wärmetauscher nach einem der vorhergehenden Ansprüche, worin die geknickten Abschnitte (15) nur in einem bestimmten Umfangsbereich in dem Randabschnitt jeder Rippe (12) entsprechend einer Region gebildet sind, in welcher sich Ströme des externen Fluids von dem Rohr (11) trennen.
EP98100889A 1997-01-20 1998-01-20 Wärmetauscher Expired - Lifetime EP0854344B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP9007378A JPH10206059A (ja) 1997-01-20 1997-01-20 熱交換器
JP737897 1997-01-20
JP7378/97 1997-01-20

Publications (3)

Publication Number Publication Date
EP0854344A2 EP0854344A2 (de) 1998-07-22
EP0854344A3 EP0854344A3 (de) 2000-01-26
EP0854344B1 true EP0854344B1 (de) 2003-07-23

Family

ID=11664298

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98100889A Expired - Lifetime EP0854344B1 (de) 1997-01-20 1998-01-20 Wärmetauscher

Country Status (5)

Country Link
EP (1) EP0854344B1 (de)
JP (1) JPH10206059A (de)
KR (1) KR100283314B1 (de)
CN (1) CN1135358C (de)
AT (1) ATE245793T1 (de)

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JP5461756B2 (ja) * 2006-04-25 2014-04-02 住友精密工業株式会社 蒸発器
US20100282456A1 (en) * 2009-05-06 2010-11-11 General Electric Company Finned tube heat exchanger
KR101114468B1 (ko) * 2009-07-08 2012-02-24 군산대학교 산학협력단 핀 튜브 열교환기
EP2784426A1 (de) 2013-03-27 2014-10-01 GEA Batignolles Technologies Thermiques Rohrwärmetauscher mit optimierten thermohydraulischen Merkmalen
WO2018044319A1 (en) 2016-09-02 2018-03-08 General Electric Company Finned tube heat exchanger with enhanced serrated fins and method of assembling same
CN107192294B (zh) * 2017-07-05 2022-12-06 江苏萃隆精密铜管股份有限公司 高翅片热交换管
CN107401861A (zh) * 2017-08-17 2017-11-28 河南科隆集团有限公司 一种翅片蒸发器及其制造方法
US11499747B2 (en) * 2019-10-04 2022-11-15 Rheem Manufacturing Company Heat exchanger tubes and tube assembly configurations

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JPS5866794A (ja) * 1981-10-16 1983-04-21 Yamaguchi Kikai Kenkyusho:Kk 熱交換器用フイン付き管
JPS5986896A (ja) * 1982-11-09 1984-05-19 Seiichi Konaka 小ビレ付フイン管熱交換装置
US4787442A (en) * 1987-12-04 1988-11-29 Carrier Corporation Delta wing and ramp wing enhanced plate fin
US5240070A (en) * 1992-08-10 1993-08-31 Fintube Limited Partnership Enhanced serrated fin for finned tube

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016003374A1 (en) * 2014-07-03 2016-01-07 King Mongkut's University Of Technology Thonburi Mixed louver spiral fin

Also Published As

Publication number Publication date
EP0854344A2 (de) 1998-07-22
ATE245793T1 (de) 2003-08-15
EP0854344A3 (de) 2000-01-26
CN1135358C (zh) 2004-01-21
CN1188890A (zh) 1998-07-29
KR19980070602A (ko) 1998-10-26
JPH10206059A (ja) 1998-08-07
KR100283314B1 (ko) 2001-03-02

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