EP3956623A1 - Ailette de condenseur refroidie par de l'air turbulent - Google Patents

Ailette de condenseur refroidie par de l'air turbulent

Info

Publication number
EP3956623A1
EP3956623A1 EP20791300.5A EP20791300A EP3956623A1 EP 3956623 A1 EP3956623 A1 EP 3956623A1 EP 20791300 A EP20791300 A EP 20791300A EP 3956623 A1 EP3956623 A1 EP 3956623A1
Authority
EP
European Patent Office
Prior art keywords
flow channel
air
cooled condenser
fin
air cooled
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
EP20791300.5A
Other languages
German (de)
English (en)
Other versions
EP3956623A4 (fr
Inventor
Ted L. Thome
Tony F. Habib
JR. Billy G. SPRINGER
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.)
Babcock and Wilcox Co
Original Assignee
Babcock and Wilcox Co
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 Babcock and Wilcox Co filed Critical Babcock and Wilcox Co
Publication of EP3956623A1 publication Critical patent/EP3956623A1/fr
Publication of EP3956623A4 publication Critical patent/EP3956623A4/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • 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
    • F28F1/24—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 transversely
    • F28F1/30—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 transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/38—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 being staggered to form tortuous fluid passages
    • 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
    • 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
    • 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
    • F28F2215/08—Fins with openings, e.g. louvers
    • 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
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the following relates to air cooled condensers, heat exchanger fins and arrays thereof for air cooled condensers, and so forth.
  • a known modification of the straight fin design is to include perforations in the fins to disturb air flow with the flow channel, i.e. pressed or cut perforations. They offer cross channel flow paths and are commonly used in automotive applications. The perforations, while effective at disturbing the fluid boundary layer increasing heat transfer, can be impractical in certain applications as they increase the pressure drop of the air flow.
  • Another known fin design employs offset fins.
  • the straight path is cyclically offset within a channel to disturb the boundary layer.
  • This design as with the perforations, increase heat transfer capability but in doing so also increases pressure drop.
  • Another known fin design employs wavy or ruffled fins.
  • the straight fins are curved to form sinusoidal waves.
  • the periodic waves enables disruption of the fluid boundary layer.
  • Swer, U.S. Patent No. 5,209,289 issued May 1 1 , 1993 discloses a modified fin array incorporating wavy offsets in a unique combination.
  • Bugler et al. U.S. Publication No. 2018/0023901 A1 published January 25, 2018, discloses a heat exchange tube fin design in which a plurality of arrowhead shapes are pressed into or embossed onto each fin.
  • the pressed arrowhead shapes are grouped into nested pairs, and one of the arrowheads in a pair is pressed as a positive relative to the fin plane and the other of the pair is pressed as a negative relative to the fin plane.
  • the arrowhead pairs are placed in rows parallel to the air flow direction and arrowhead pairs in one row are preferably staggered relative to the arrowhead pairs in the adjacent row along the fin in the air flow direction.
  • an air cooled condenser fin comprises flow channel walls defining an air flow channel.
  • the flow channel walls include planar sections separated by intermittent flow interruptions which are spaced apart along the air flow channel. The intermittent flow interruptions are defined by the flow channel walls.
  • the intermittent flow interruptions comprise splits formed by a staggered arrangement in which the planar sections of the flow channel walls before and after each split are staggered.
  • the staggering of the flow channel walls after each split is about one-half of a width of the air flow channel.
  • the intermittent flow interruptions comprise intermittent sinusoidal waves formed into the flow channel walls.
  • the intermittent flow interruptions comprise louvers formed into the flow channel walls to create openings passing through the flow channel walls at the louvers.
  • the louvers are angled between 1 degree and 30 degrees to an air flow direction of the air flow channel.
  • the flow channel walls are secured to a tube of an air cooled condenser.
  • the intermittent flow interruptions are in some more specific embodiments spaced between 5 hydraulic diameters and 10 hydraulic diameters apart along the air flow channel.
  • the intermittent flow interruptions are in some more specific embodiments spaced apart along the air flow channel by at least 5 hydraulic diameters.
  • a plurality of air cooled condenser fins as set forth in any of the preceding paragraphs is provided, in which the air flow channels of the air cooled condenser fins are arranged in parallel.
  • an air cooled condenser comprises steam/condensate tubes and fins attached to the steam/condensate tubes.
  • the fins comprise flow channel walls defining parallel air flow channels.
  • the flow channel walls include planar sections separated by intermittent flow interruptions which are spaced apart along the air flow channels.
  • the interm ittent flow interruptions are defined by the flow channel walls.
  • the intermittent flow interruptions in some embodiments comprise splits formed by a staggered arrangement in which the planar sections of the flow channel walls before and after each split are staggered.
  • the staggering of the flow channel walls after each split is, in some more specific embodiments, about one-half of a width of the air flow channel.
  • the intermittent flow interruptions in some embodiments comprise intermittent sinusoidal waves formed into the flow channel walls.
  • the intermittent flow interruptions in some embodiments comprise louvers formed into the flow channel walls to create openings passing through the flow channel walls at the louvers.
  • the louvers are, in some more specific embodiments, angled between 1 degree and 30 degrees to an air flow direction of the air flow channel.
  • the intermittent flow interruptions may in some more specific embodiments be spaced between 5 hydraulic diameters and 10 hydraulic diameters apart along the air flow channel.
  • the intermittent flow interruptions may in some more specific embodiments be spaced apart along the air flow channel by at least 5 hydraulic diameters.
  • an air cooled condenser as set forth in the immediately preceding paragraph further comprise distribution headers connected to feed steam into the steam/condensate tubes, and an air moving system comprising a fan arranged to drive an airflow across the fins attached to the steam/condensate tubes.
  • Some more specific embodiments further include risers connected to feed the steam into the distribution headers, wherein the steam/condensate tubes, the distribution headers, the risers, and the air moving system are arranged to form the air cooled condenser as an A-frame type air cooled condenser or other types.
  • a method of cooling using an air cooled condenser fin comprises flowing air through an air flow channel defined by flow channel walls, and interrupting the flowing of air at intermittent flow interruptions defined by the flow channel walls which are spaced apart along the air flow channel.
  • the intermittent flow interruptions are placed at locations where a boundary layer of the flowing air has normalized.
  • the intermittent flow interruptions are spaced apart along the air flow channel by at least 5 hydraulic diameters.
  • the invention may take form in various components and arrangements of components, and in various process operations and arrangements of process operations.
  • the drawings are only for purposes of illustrating preferred embodiments and are not to be construed as limiting the invention. This disclosure includes the following drawings.
  • FIGURE 1 diagrammatically shows differential temperature versus length for a planar fin.
  • FIGURE 2 diagrammatically shows heat transfer coefficient versus length for a planar fin.
  • FIGURE 3 diagrammatically shows incremental air pressure drop versus length for a planar fin.
  • FIGURE 4 diagrammatically shows a perspective view of a portion of an air cooled condenser fin having a single split-fin.
  • FIGURE 5 diagrammatically shows a top view of a portion of an air cooled condenser fin array including a plurality of splits of the type shown in FIGURE 4.
  • FIGURE 6 diagrammatically shows a perspective view air flow velocity map for the split fin air flow.
  • FIGURE 7 diagrammatically shows a perspective view of a portion of an air cooled condenser fin having intermittent sinusoidal waves.
  • FIGURE 8 diagrammatically shows a perspective view of a portion of an air cooled condenser fin having louvers.
  • FIGURE 9 diagrammatically shows a top view of a portion of an air cooled condenser fin array including a plurality of louvers of the type shown in FIGURE 8.
  • FIGURE 10 plots heat transfer coefficient of an air cooled condenser fin with splits, versus position.
  • FIGURE 1 1 plots heat transfer coefficient of an air cooled condenser fin with intermittent sinusoidal waves, versus position.
  • FIGURE 12 diagrammatically shows a typical air cooled condenser application of the disclosed improved fins, where the illustrative air cooled condenser is of the forced draft A-frame type.
  • Air-cooled condenser applications have some requirements regarding the steam flow area and resultant pressure drop that places constraints on the minimum sizing of the heat exchanger fin tube base.
  • Use of existing non-planar fin designs (Louvered, Offset, Wavy, etc.) requires additional power input (larger air mover sizing) to apply the fin to the required tube geometry. Further, redesigning tube geometry to incorporate a non-planar fin design in a lower power input design is often uneconomical.
  • Flow on the air-side of an air-cooled condenser generally operates in the laminar regime, which is defined by Reynolds numbers less than 2000.
  • momentum and energy transport occur via the mechanism of molecular diffusion, which is driven by gradients in the velocity profile.
  • the velocity gradients near the fin wall are especially important in determining the momentum and energy transport rates in the local region as the air flows through the fin channel.
  • extremely high velocity gradients result, based on the large velocity differential between the entering air velocity and the zero- velocity condition at the fin wall. This results in large friction factors and heat transfer coefficients at the lead edge of the fin.
  • the velocity profile approaches the fully developed profile (generally parabolic).
  • the entrance region of the fin is therefore more effective in terms of heat transfer than the remainder of the fin, although the increase in heat transfer comes at the cost of added pressure drop.
  • FIGURES 1 -3 numerical simulations of differential temperature versus length (FIGURE 1 ), heat transfer coefficient versus length (FIGURE 2), and incremental air pressure drop versus length (FIGURE 3) are shown for a planar fin.
  • FIGURES 1 , 2, and 3 the entrance region is to the left, with the air flow proceeding along the channel of length L to the exit side of the fin on the right of the curve.
  • the most effective region of heat transfer in a planar fin of an air cooled condenser is at the air entrance into the fin channel. This is evident in FIGURE 2 where the heat transfer coefficient decreases rapidly as air flows along the channel length.
  • FIGURE 4 is a graphic representation showing a single split-fin 10 as disclosed herein.
  • the split-fin takes advantage of the enhanced heat transfer which occurs at the lead edge of a fin channel entrance to reduce the total surface area of the overall fin assembly.
  • the split-fin arrangement of FIGURE 4 comprises a straight fin section 12 having a fin channel 14 that is subsequently split into two fin channels 16, 18 at a split point 20 along the length of the fin channel 14.
  • the split 20 preferably occurs at or around the point where air flow has fully developed in the first channel section 14. As air flow (indicated by arrows F in FIGURE 4) enters the staggered fin arrangement 20, it is split into subsequent sections, i.e. split air flows 16, 18.
  • the fin wall of the downstream fin section 22 is located at or near the center of the upstream flow path or channel 14 (in other words, the staggering of the fin walls after the split is about one-half of a width of the air flow channel), thereby being exposed to high velocity gradients near the wall, similar to what occurs at the entrance of the first fin section 12. This process is repeated at each flow split, resulting in increased heat transfer at the lead edge region of every fin section 12, 22.
  • a more compact fin assembly configuration results; requiring less fin surface area and comparatively less material needed to construct the fin array than traditional designs.
  • FIGURE 5 illustrates a fin array including successive illustrated fin sections 12a, 12b, 12c with respective channels 14a, 14b, 14c, with fin split point 20ab at the junction of fin sections 12a, 12b and fin split point 20bc at the junction of fin sections 12b, 12c. This is repeated for as many fin split sections exist in the assembly.
  • the local increases in friction factor result in an increase in pressure drop, which is generally undesirable. Fleat transfer from the fin to the air depends on two factors, the local heat transfer coefficient, and the local bulk air-to-fin temperature difference.
  • the flow splits 20 increase the local heat transfer coefficient, which is beneficial. As with friction factor, the local increase in heat transfer coefficient resulting from each flow split 20 is consistent throughout the fin assembly. However, as the air flow F proceeds through the assembly, the temperature difference between the air and the fin is continuously reduced. Therefore, the effectiveness of the flow splits 20 with respect to increased local heat transfer decreases the farther the particular flow split is from the fin assembly entrance. For this reason, it is beneficial to cluster the flow splits 20 near the entrance to the assembly and use a more continuous section at the trail end of a fin assembly comprising multiple split-fins.
  • an air cooled condenser utilizes single row finned tubes and includes a split-feature within the air flow channel which disturbs the boundary layer along the flow channel wall.
  • FIGURE 6 shows a perspective view air flow velocity map for the split fin air flow.
  • split-fins may be repeating or intermediate.
  • Flow channel walls may be discontinuous or continuous.
  • Flow along the wall of a planar fin may be perturbed by the channel being cut, and a new channel formed with the opening offset from the outlet of the original channel.
  • Fin channels may consist of single or multiple splits.
  • Channel length of the fin sections 12 is preferably determined by finding the point along the wall in which the airflow boundary layer approaches fully developed profile. In one embodiment having multiple splits the splits are spaced between about 5 hydraulic diameters and about 10 hydraulic diameters apart.
  • one or more fin channels in the fin array may include intermittent sinusoidal waves.
  • a graphic representation of a fin 30 having a channel 34 with an intermittent sinusoidal wave 32 is shown in FIGURE 7.
  • Flow F along the wall of the channel 34 is redirected by the sinusoidal wave 32 in the transverse direction of air flow F.
  • Wave geometry of the sinusoidal wave 32 is designed to optimize full channel recirculation downstream from the disturbance.
  • Planar fin wall is placed between the multiple waves 32 until boundary layer normalizes to reduce pressure drop.
  • the sinusoidal waves 32 are preferably spaced between about 5 hydraulic diameters and about 10 hydraulic diameters apart.
  • louvered fins 40 are disclosed.
  • openings 42 between adjacent fin channels 44 are used. Openings may take the form of louvers 46 angled between about 1 and about 30 degrees to the direction of flow.
  • Figures 8 and 9 provide graphic representations of the openings 42 between adjacent fin channels 44. As seen in FIGURE 8, the openings 42 do not comprise the entirely of the flow channel wall. While FIGURES 8 and 9 show alignment between openings in adjacent channels, such alignment is not present in some embodiments; rather, in these embodiments the opening may alternatively be offset.
  • FIGURE 8 also illustrates the louvered fins 40 soldered (or otherwise attached) to a tube 48 as is common in the case of an air cooled condenser (where the steam or other fluid being condensed flows through the tube 48).
  • FIGURES 8 and 9 show the louvers in the“pointing downstream” configuration. In this configuration the tips of the louvers are pointing roughly in the direction of the flow from upstream to downstream. In a variant embodiment, the louvers may be reversed, so as to point“into” the flow in the upstream direction. Either configuration can be employed effectively.
  • the innovations disclosed herein may be used on a single channel, a combination of channels, and/or combined with one another to form new and unique fin arrays that improve heat transfer over a variety of tube geometries that may be subject to space constraints and otherwise have limitations on ability to overcome pressure drop concerns. Further advantageous is the reduction in materials requirements for fin arrays enabled by the approaches disclosed herein.
  • FIGURES 10 and 1 1 plots show simulated data relating to heat transfer coefficient of the split-fin and intermittent wave, respectively, against position. As shown in these figures, the heat transfer peaks at the location of the flow interruption and decreases along the length of the channel as the boundary layer is reestablished and the difference in temperature between the two fluids, air and steam, is gradually reduced.
  • FIGURE 12 a typical air cooled condenser application of the disclosed improved fins is shown.
  • An illustrative air cooled condenser shown in FIGURE 12 is of the forced draft A-frame type.
  • An electric power generator 52 is driven by a steam turbine 54 using steam 56.
  • Exhaust steam 58 discharged from the steam turbine 54 flows into a main steam duct 60 and a distribution manifold 62, that distributes the steam to a set of air cooled condensers, an illustrative one of which is shown in FIGURE 12.
  • the steam flows up through risers 64 which are connected to feed the steam into distribution headers 66 which in turn are connected to feed the steam into bundles 70 that include steam/condensate tubes (e.g., the illustrative steam/condensate tube 48 shown in FIGURE 8) with fins (such as split fins 10 as shown in FIGURES 4-6; or fins 30 with intermittent sinusoidal waves 32 as shown in FIGURE 7; or fins 40 with louvers 46 as shown in FIGURES 8 and 9) soldered or otherwise attached to the steam/condensate tubes.
  • An air moving system 72 such as a fan, drives an airflow across the fins of the bundles 70 in order to cool and condense the steam in the tubes to form condensate.
  • FIGURE 12 further shows the condenser superstructure including a fan deck 74 supported by support structure 76 and bracing 78, and a windwall structure 80 atop the fan deck 74. While the illustrative air cooled condenser is of the forced draft A-frame type, the disclosed improved fins are suitably employed in conjunction with air cooled condensers of other types, such as an induced draft V-frame condenser type, a flat condenser type, or so forth.
  • the inventors have performed computer simulations of the performance of various designs of split fins 10 (FIGURES 4-6), fins 30 with intermittent sinusoidal waves 32 (FIGURE 7), and fins 40 with louvers 46 (FIGURES 8 and 9).
  • the fins were modeled as rectangular channels with rectangular dimension Hf in being the fin height (that is, the distance the fin extends away from the steam/condensate tube to which it is soldered) and dimension S fin being the separation between the fin walls defining the air flow channel.
  • the simulations were for a design of the bundles 70 that included 1 1 fins per inch.
  • the simulations also modeled the energy (in horsepower which is related to pressure loss across a bundle) of the air moving system (e.g. fan) 72 and the bundle tube length 82.
  • the air moving system e.g. fan
  • the intermittent flow interruptions can be fin splits 20 (as in the embodiments of FIGURES 4-6), intermittent sinusoidal waves 32 (as in the embodiment of FIGURE 7), louvers 46 (as in the embodiments of FIGURES 8 and 9), or more generally any other type of intermittent interruption.
  • the simulations also found that placing the intermittent flow interruptions nearer the entrance side of the fin maximizes the heat transfer benefit while imposing the least additional pressure drop.
  • at least 70% of the intermittent flow interruptions are positioned within the first one-half of the fin length L (that is, within the half-fin length closest to the entrance side of the fin).
  • at least 80% of the intermittent flow interruptions are positioned within the first one-third of the fin length L (that is, within the first third of the fin length that is closest to the entrance side of the fin).
  • planar fin is used herein in its usual and ordinary meaning in the art, as a fin that channels air flow principally along a single planar channel.
  • the flow channel walls defining the air flow channel may have some deviations from geometrically perfect planar form, for example due to unintended manufacturing-induced variations, dimples, wall curvature, or so forth. Such a imperfections typically do not have a meaningful impact on air flow and hence are considered“planar” fin sections as used herein.
  • the term “intermittent flow interruption” as used herein is an intentional (i.e.

Landscapes

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

Abstract

La présente invention concerne une ailette de condenseur refroidie par de l'air qui comprend des parois de canal d'écoulement définissant un canal d'écoulement d'air. Les parois de canal d'écoulement comprennent des sections planes séparées par des interruptions d'écoulement intermittentes qui sont espacées le long du canal d'écoulement d'air. Des interruptions d'écoulement intermittentes sont définies par les parois de canal d'écoulement. Des interruptions d'écoulement intermittentes peuvent par exemple comprendre des divisions formées par un agencement en quinconce dans lequel les sections planes des parois de canal d'écoulement avant et après chaque division sont décalées ; ou des ondes sinusoïdales intermittentes formées dans les parois de canal d'écoulement ; ou des persiennes formées dans les parois de canal d'écoulement pour créer des ouvertures passant à travers les parois de canal d'écoulement au niveau des persiennes. Des interruptions d'écoulement intermittentes peuvent être espacées le long du canal d'écoulement d'air d'au moins 5 diamètres hydrauliques et, dans certains modes de réalisation, de 5 à 10 diamètres hydrauliques. Une pluralité de telles ailettes de condenseur refroidies par de l'air sont utilisées de manière appropriée avec les canaux d'écoulement d'air agencés en parallèle.
EP20791300.5A 2019-04-18 2020-04-17 Ailette de condenseur refroidie par de l'air turbulent Pending EP3956623A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US201962835706P 2019-04-18 2019-04-18
US16/850,673 US20200333077A1 (en) 2019-04-18 2020-04-16 Perturbing air cooled condenser fin
PCT/US2020/028659 WO2020214902A1 (fr) 2019-04-18 2020-04-17 Ailette de condenseur refroidie par de l'air turbulent

Publications (2)

Publication Number Publication Date
EP3956623A1 true EP3956623A1 (fr) 2022-02-23
EP3956623A4 EP3956623A4 (fr) 2022-12-21

Family

ID=72829569

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20791300.5A Pending EP3956623A4 (fr) 2019-04-18 2020-04-17 Ailette de condenseur refroidie par de l'air turbulent

Country Status (3)

Country Link
US (1) US20200333077A1 (fr)
EP (1) EP3956623A4 (fr)
WO (1) WO2020214902A1 (fr)

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1044125B (de) * 1956-02-15 1958-11-20 Gea Luftkuehler Ges M B H Durch einen zwanglaeufig bewegten Luftstrom gekuehlter Oberflaechenkondensator
US3810509A (en) * 1971-10-15 1974-05-14 Union Carbide Corp Cross flow heat exchanger
JPH09105566A (ja) * 1995-10-09 1997-04-22 Hitachi Ltd 熱交換器
KR20020030431A (ko) * 2000-10-17 2002-04-25 장철수 방열판
US20020195240A1 (en) * 2001-06-14 2002-12-26 Kraay Michael L. Condenser for air cooled chillers
DE602005016897D1 (de) * 2004-01-12 2009-11-12 Litelaser L L C Laserkühlsystem und laserkühlverfahren
DE102004006276A1 (de) * 2004-02-09 2005-08-25 Linde Kältetechnik GmbH & Co. KG Teilstrukturierte Wärmetauscherlamellen
CN102580593A (zh) * 2004-11-17 2012-07-18 万罗赛斯公司 使用微通道处理技术的乳化方法
KR20080108545A (ko) * 2006-03-16 2008-12-15 베헤르 게엠베하 운트 콤파니 카게 자동차용 열교환기
US9513059B2 (en) * 2011-02-04 2016-12-06 Lockheed Martin Corporation Radial-flow heat exchanger with foam heat exchange fins
US20150027679A1 (en) * 2012-01-18 2015-01-29 Holtec International Finned tube assemblies for heat exchangers
KR101569829B1 (ko) * 2014-06-13 2015-11-19 주식회사 코렌스 Egr 가스 차압 저감용 웨이브 핀 플레이트를 갖는 열교환기
EP3359902B2 (fr) * 2015-10-08 2023-06-28 Linde GmbH Procédé de fabrication d'une lamelle et un échangeur de chaleur à plaque avec une lamelle fabriquée à l'aide d'un tel procédé
JP6952703B2 (ja) * 2016-02-04 2021-10-20 エバプコ・インコーポレイテッドＥｖａｐｃｏ， Ｉｎｃ． 熱交換チューブのための矢じりフィン
US10024600B2 (en) * 2016-06-21 2018-07-17 Evapco, Inc. Mini-tube air cooled industrial steam condenser

Also Published As

Publication number Publication date
EP3956623A4 (fr) 2022-12-21
US20200333077A1 (en) 2020-10-22
WO2020214902A1 (fr) 2020-10-22

Similar Documents

Publication Publication Date Title
US9599410B2 (en) Plate-like air-cooled engine surface cooler with fluid channel and varying fin geometry
KR100990309B1 (ko) 열교환기
CN101441041B (zh) 热交换器
KR101177726B1 (ko) 홈이 형성된 핀을 구비한 튜브를 포함하는 열교환기
US5395212A (en) Member having internal cooling passage
US12025387B2 (en) Turning vanes and heat exchangers and methods of making the same
US6725912B1 (en) Wind tunnel and heat exchanger therefor
CN106052462B (zh) 一种矿井空冷器用波纹翅片换热结构及其设计方法
US8292578B2 (en) Material having internal cooling passage and method for cooling material having internal cooling passage
CN107314699B (zh) 一种用于换热器的高性能换热片及其换热器
US20130153184A1 (en) Heat exchanger
EP2784426A1 (fr) Échangeur de chaleur de tube à caractéristiques thermo-hydrauliques optimisées
US20120205068A1 (en) High efficiency cascade-style heat exchanger
US20150047820A1 (en) Bendable heat exchanger
US20170157722A1 (en) Cross flow ceramic heat exchanger and method for manufacturing
CN104142084B (zh) 一种用于电站百万机组间接空冷系统的换热器
US20160252311A1 (en) Wavy Fin Structure and Flat Tube Heat Exchanger Having the Same
US20200333077A1 (en) Perturbing air cooled condenser fin
US20070169921A1 (en) Fin and tube heat exchanger
KR101795039B1 (ko) 핀 및 튜브 열교환기
US20200400377A1 (en) Heat exchanger closure bar
RU2790404C1 (ru) Ребро газоохладителя с возмущённым воздушным охлаждением
JPS6346357B2 (fr)
CN104729329B (zh) 一种用于海勒式间接空冷系统的非均匀翅片散热器
WO2000071956A1 (fr) Soufflerie et echangeur de chaleur associe

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20211011

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20221122

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 3/02 20060101ALI20221116BHEP

Ipc: F28B 1/06 20060101ALI20221116BHEP

Ipc: F24F 13/08 20060101ALI20221116BHEP

Ipc: F28F 3/04 20060101AFI20221116BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20240611