EP2956728A1 - Échangeur de chaleur à tubes plats et à faisceaux multiples - Google Patents

Échangeur de chaleur à tubes plats et à faisceaux multiples

Info

Publication number
EP2956728A1
EP2956728A1 EP13814690.7A EP13814690A EP2956728A1 EP 2956728 A1 EP2956728 A1 EP 2956728A1 EP 13814690 A EP13814690 A EP 13814690A EP 2956728 A1 EP2956728 A1 EP 2956728A1
Authority
EP
European Patent Office
Prior art keywords
fin
tube
heat exchange
bank
exchange 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.)
Granted
Application number
EP13814690.7A
Other languages
German (de)
English (en)
Other versions
EP2956728B1 (fr
Inventor
Michael F. Taras
Arindom Joardar
Tobias H. Sienel
Mel WOLDESEMAYAT
Bruce J. Poplawski
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP2956728A1 publication Critical patent/EP2956728A1/fr
Application granted granted Critical
Publication of EP2956728B1 publication Critical patent/EP2956728B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/32—Safety or protection arrangements; Arrangements for preventing malfunction for limiting movements, e.g. stops, locking means

Definitions

  • This invention relates generally to heat exchangers and, more particularly, to multiple tube bank, flattened tube, finned heat exchangers.
  • Heat exchangers have long been used as evaporators and condensers in heating, ventilating, air conditioning and refrigeration (HVACR) applications. Historically, these heat exchangers have been round tube and plate fin (RTPF) heat exchangers.
  • RTPF round tube and plate fin
  • all-aluminum flattened tube plate fin heat exchangers are finding increasingly wider use in industry, including the HVACR industry, due to their compactness, thermal-hydraulic performance, structural rigidity, lower weight and reduced refrigerant charge, in comparison to conventional RTPF heat exchangers.
  • Flattened tubes commonly used in HVACR applications typically have an interior subdivided into a plurality of parallel flow channels. Such flattened tubes are commonly referred to in the art as multi-channel tubes, mini-channel tubes or micro-channel tubes.
  • a typical flattened tube, finned heat exchanger includes a first manifold, a second manifold, and a single tube bank formed of a plurality of longitudinally extending flattened heat exchange tubes disposed in spaced parallel relationship and extending between the first manifold and the second manifold.
  • the first manifold, second manifold and tube bank assembly is commonly referred to in the heat exchanger art as a slab.
  • a plurality of fins are disposed between the neighboring pairs of heat exchange tubes for increasing heat transfer between a fluid, commonly air in HVACR applications, flowing over the outer surface of the flattened tubes and along the fin surfaces and a fluid, commonly refrigerant in HVACR applications, flowing inside the flattened tubes.
  • Such single tube bank heat exchangers also known as single slab heat exchangers, have a pure cross-flow configuration.
  • Double bank flattened tube and fin heat exchangers are also known in the art.
  • conventional double bank flattened tube and fin heat exchangers are typically formed of two conventional fin and tube slabs, one spaced behind the other.
  • a multiple bank, flattened tube and folded fin heat exchange unit wherein spacing between tube banks is achieved by a fin notch protruding outwardly from the fin caps of folded fin(s) into a gap between the trailing edges of the heat exchange tube segments of a first tube bank and the leading edges of the heat exchange tube segments of a second tube bank disposed next rearward of the first tube bank.
  • the fin notch has a notch width defining the desired depth of the gap to be maintained between the two tube banks.
  • the fin notch may have a notch height equal to at least one half of the thickness of the flattened tube heat exchange tube segments.
  • the fin notch may have a notch height in range from at least one half of the thickness of the flattened heat exchange tube segments to equal to the thickness of the flattened heat exchange tube segments. In an embodiment, the fin notch may have a notch height in range from at least one half of the thickness of the flattened heat exchange tube segments to less than the thickness of the flattened heat exchange tube segments.
  • FIG. 1 is a diagrammatic illustration of an embodiment of a multiple tube bank, flattened tube finned heat exchange unit as disclosed herein;
  • FIG. 2 is a top, plan view, partly in section, of the embodiment of the multiple tube bank, flattened tube finned heat exchange unit of FIG. 1;
  • FIG. 3 is a sectioned side elevation view of the embodiment of the multiple tube bank, flattened tube finned heat exchange unit of FIG. 1;
  • FIG. 4 is a diagrammatic frontal elevation view of a segment of an
  • FIG. 5 is a perspective view of a segment of the embodiment of the folded fin of FIG. 4;
  • FIG. 6 is a perspective view of a fin notch of the folded fin of FIG. 4;
  • FIG. 7 is an exploded view illustrating assembly of the multiple tube bank, flattened tube finned heat exchanger unit of FIG. 1 incorporating the embodiment of the folded fin of FIG. 4;
  • FIG. 8 is a perspective view of a segment of an embodiment of the folded fin of FIG. 3 having another embodiment of fin notches as disclosed herein;
  • FIG. 9 is a perspective view of a segment of an embodiment of a folded fin having another embodiment of fin notches as disclosed herein.
  • FIGs. 1, 2 and 3 An exemplary embodiment of a multiple bank flattened tube finned heat exchanger unit, generally designated 10, in accordance with the disclosure is depicted in FIGs. 1, 2 and 3.
  • the multiple bank flattened tube finned heat exchanger 10 includes a first tube bank 100 and a second tube bank 200 that is disposed behind the first tube bank 100, that is downstream with respect to the air flow, A, through the heat exchanger.
  • the first tube bank 100 may also be referred to herein as the front heat exchanger slab 100 and the second tube bank 200 may also be referred to herein as the rear heat exchanger slab 200.
  • the first tube bank 100 includes a first manifold 102, a second manifold 104 spaced apart from the first manifold 102, and a plurality of heat exchange tube segments 106, including at least a first and a second tube segment, extending longitudinally in spaced parallel relationship between and connecting the first manifold 102 and the second manifold 104 in fluid communication.
  • the second tube bank 200 includes a first manifold 202, a second manifold 204 spaced apart from the first manifold 202, and a plurality of heat exchange tube segments 206, including at least a first and a second tube segment, extending longitudinally in spaced parallel relationship between and connecting the first manifold 202 and the second manifold 204 in fluid communication.
  • the second tube bank 200 is disposed in alignment with the first tube bank 100 whereby the heat exchange tube segments 206 of the second tube bank 200 aligned with the heat exchange tube segments 106 of the first tube bank 100, for example as illustrated in FIG. 3.
  • each of the heat exchange tube segments 106, 206 comprises a flattened heat exchange tube having a leading edge 108, 208, a trailing edge 110, 210, an upper flat surface 112, 212, and a lower flat surface 114, 214.
  • the leading edge 108, 208 of each heat exchange tube segment 106, 206 is upstream of its respective trailing edge 110, 210 with respect to the airflow through the heat exchanger 10.
  • the respective leading and trailing portions of the flattened tube segments 106, 206 are rounded thereby providing blunt leading edges 108, 208 and trailing edges 110, 210.
  • the second tube bank 200 is spaced behind the first tube bank 100 with the leading edge 208 of each of the heat exchange tube segments 206 of the second tube bank 200 spaced from the trailing edge 110 of each of the heat exchange tube segments 106 of the first tube bank 100 at a desired spacing gap 15.
  • each of the heat exchange tube segments 106, 206 of the first and second tube banks 100, 200, respectively, may be divided by interior walls into a plurality of discrete flow channels 116, 216 that extend longitudinally the length of the tube from an inlet end of the tube to an outlet end of the tube and establish fluid
  • the flow channels 116, 216 provide a plurality of flow paths through which refrigerant, R, may pass between the manifolds 102, 104 and 202, 204, respectively, in heat exchange relationship with the air flow, A, passing over the outer surfaces of the heat exchange tube segments 106, 206.
  • the flow channels 116, 216 may have a circular cross-section, a rectangular cross-section or other non-circular cross-section. Also, the interior flow passages of the heat exchange tube segments 106, 206 may be divided into the same or into a different number of discrete flow channels 116, 216.
  • the heat exchange tube segments 106 of the first tube bank 100 have a depth, that is an expanse in a direction perpendicularly traverse to the longitudinal axes of the parallel heat exchange tube segmentsl06, 206, that is different, it this embodiment less than, than the depth of the heat exchange tube segments 206 of the second bank.
  • the depth of the heat exchange segments 106 and 206 may be the same, or the depth of the heat exchange tube segments 106 of the first tube bank 100 may be greater than the depth of the heat exchange segments 206 of the second tube bank 200.
  • the heat exchange tube segments 106, 206 comprise a plurality of parallel linear segments wherein each individual segment connects directing to a manifold at each end.
  • the tube banks 100, 200 could include serpentine tubes with the heat exchange tube segments 106, 206 being parallel linear tube segments connected by U-bends or hairpin turns to form a serpentine tube connected at its respective ends between the spaced manifolds of the tube bank.
  • the multiple bank, flattened tube heat exchanger 10 disclosed herein further includes a plurality of folded fins 20.
  • Each folded fin 20 is formed, for example by stamping a continuous sheet of fin material, such as for example aluminum or an aluminum alloy, in a serpentine, ribbon-like fashion thereby providing a plurality of fin faces 22 connected together by fin caps 24.
  • the folded fin 20 includes a plurality of spaced parallel fin faces 22
  • the fin faces 22 may extend obliquely, rather than parallel.
  • a longitudinally extending folded fin 20 is disposed between each pair of neighboring heat exchange tube segments 106 of the first tube bank 100 and an aligned pair of neighboring heat exchange tube segments 206 of the second tube bank 200.
  • Each folded fin 20 extends longitudinally, that is along the longitudinal axes of the heat exchange tube segments 106, 206, and transversely, that is perpendicularly to the longitudinal axes of the heat exchange tube segments 106, 206.
  • Folded fins 20 are disposed between each pair of neighboring heat exchange tubes 106, 206 across the width of the effective heat transfer area of the heat exchanger unit 10 whereby the air flow, A, passing through the heat exchanger unit 10 passes over the surfaces of the fin faces 22.
  • Each folded fin 20 is disposed between a respective pair of neighboring tube segments 106 and a respective pair of heat exchange tube segments 206 with the end caps 24 on opposite sides of the folded fin 20 in contact with the faces 112, 212 and 114, 214, respectively, of the heat exchange tube segments.
  • the fin faces 22 and the fin caps 24 of the folded fins 20 extend along the depth of the multiple bank, flattened tube heat exchanger 10 between a first heat exchange tube segment 106 and a second neighboring heat exchange tube segment 106 of the first tube bank 100, span the spacing gap 15 between the trailing edges 110 heat exchange tube segments 106 of the first tube bank 100 and the leading edges 208 of the heat exchange tube segments 206 of the second tube bank 200, and thence extend between a first heat exchange tube segment 206 and a neighboring second heat exchange tube segment 206 of the second tube bank 200.
  • the folded fin 20 may include a plurality of louvers 40 cut in the fin faces 22, for example as disclosed in International Patent Application No.
  • the fin faces 22 and the fin caps 24 of the folded fins 20 extend the full depth of the heat exchanger 10 from the leading edges 108 of the heat exchange tube segments 106 of the first (i.e. forward) tube bank 100 to the trailing edges 210 of the heat exchange tube segments 206 of the second (i.e. aft) tube bank 200.
  • the folded fins may overhang the leading edges 108 of the heat exchange tube segments 106 of the first tube bank 100 and/or overhang the trailing edges 210 of the heat exchange tube segments 206 of the second tube bank 200.
  • each folded fin 20 includes a plurality of fin notches 26 that protrude outwardly from the fin caps 24 of the folded fin 20 into the spacing gap 15 between the trailing edge 110 of the heat exchange tube segment 106 of the first tube bank 100 and the leading edge 208 of the heat exchange tube segment 206 of the second tube bank 200 aligned therewith.
  • the fin notches 26 extending into the spacing gap 15 defines the depth of the spacing gap 15 and maintains the spacing gap 15 at that depth during assembly and brazing of the heat exchanger unit 10.
  • an outwardly protruding fin notch 26 is provided on each fin cap 24.
  • some plurality of caps 24 less than all the caps 24 have a fin notch 26 formed therein.
  • each fin notch 26 has a dimension 28 defining the depth of the spacing gap 15 between the trailing edge 110 of the heat exchange tube segment 106 of the first tube bank 100 and the leading edge 208 of the heat exchange tube segment 206 of the second tube bank 200.
  • Each fin notch 26 has a height 30, that is a dimension defining the extent to which the fin notch 26 protrudes outwardly from the surface of the fin cap 24.
  • the fin height 30 is at least equal to one-half the thickness of the heat exchange tube segments 106, 206.
  • the fin height 30 may be in the range from at least one -half the thickness of the heat exchange tube segments 106, 206 to the full thickness of the heat exchange tube segments 106, 206.
  • each notch 26 is formed in a respective fin cap 24 as a unbroken tent- like notch that protrudes outwardly from the fin cap 24, having the desired fin height 30 as measured from the fin cap 24 to the apex of the unbroken fin notch 26.
  • the unbroken fin 26 may be formed simultaneously with formation of the folded fin 20 during a rolling process or a stamping process, or may be stamped in the fin caps 24 in a secondary operation after formation of folded fin 20. In the embodiments depicted in FIGs.
  • each notch 26 is formed in a respective fin cap 24 as a broken notch having two generally vertically, spaced, outwardly extending sides the protrude outwardly from the fin cap 24, the sides having the desired fin height 30.
  • the sides of the broken notch 26 have a dimension 28 extending along the fin cap 24 defining the depth of the spacing gap 15.
  • the sides of the broken notch 26 are spaced at a dimension 28 defining the depth of the spacing gap 15.
  • the broken notches 26 may be formed, for example, in a secondary operation, for example stamping, after the folded fin 20 has been formed in a rolling process.
  • the multiple tube bank assembly may be constructed by first laying down a base heat exchange tube segment 106 and a base heat exchange tube segment 206 in parallel spaced relationship at the desired spacing gap, then installing a folded fin 20 on the base heat exchange tube segments 106, 206, with the fin notches 26 protruding from the fin caps 24 on one side 32 of the folded fin 20 extending into the spacing gap 15.
  • a second aligned pair of heat exchange tube segments 106, 206 is laid upon the folded fin 20 with the trailing edge 110 of the heat exchange tube segment 106 and the leading edge 208 of the heat exchange tube segment 206 abutting the fin notches 26 protruding from the fin caps 24 on the other side 34 of folded fin 20.
  • the remainder of the tube bank assembly is built up of alternating folded fins 20 and aligned tubes 106, 206 in this manner.
  • the assembled tube bank is wrapped with wire or clipped by the frame clips to temporary hold the tube bank assembly together and the manifolds 102, 104, 202 and 204 are then mounted to the tube bank assembly.
  • a suitable brazing compound is applied as appropriate the various components of the assembly and the entire assembly is placed into and heated in a brazing furnace.
  • the folded fins 20 are metallurgically bonded to the heat exchange tube segments 106, 206 with the fin notches 26 establishing the desired spacing gap 15 between the heat exchange tube segments 106 of the first tube bank 100 and the heat exchange tube segments 206 of the second tube bank 200.
  • the fin notches 26 serve to maintain that desired spacing gap and provide additional structural rigidity during shipment, site installation, and operation of the multiple bank, flattened tube heat exchanger 10.
  • an opening 36 formed in the fin cap 24 upon stamping of the fin notch 26 provides a condensate/moisture drainage opening through which water collecting on the heat exchange tube segments 106 and fin faces 22 during application may drain from the heat exchanger 10.
  • the opening 36 formed in the fin cap 24 upon stamping of the fin notch 26 also interrupts a heat conductive flow path along the fin cap 24, thereby reducing heat conduction between the heat exchange tube segments 106 of the first tube bank 100 and the respective aligned heat exchange tube segments 206 of the second tube bank 200.
  • the multiple bank flattened tube heat exchanger 10 disclosed herein may include a third tube bank, or even more tube banks, incorporating folded fins 20 that extend across all tube banks of the multiple bank heat exchanger and include fin notches 26 on the end caps 24 that protrude outwardly into the spacing gaps between the respective trailing edge of each forward tube bank and the leading edge of the next aft tube bank.

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

Abstract

L'invention concerne un échangeur de chaleur à ailettes, à tubes plats et à faisceaux multiples qui comprend un premier faisceau de tubes comprenant une pluralité de segments de tube plat d'échange de chaleur s'étendant longitudinalement et disposés en réseau de manière espacée et parallèle entre un premier collecteur et un second collecteur et un second faisceau de tubes comprenant une pluralité de segments de tube plat s'étendant longitudinalement et disposés en réseau de manière espacée et parallèle entre un premier collecteur et un second collecteur, le second faisceau de tubes étant disposé de manière à être espacé du premier faisceau de tubes et à être derrière celui-ci. Une ailette repliée est disposée entre chaque ensemble de segments de tube d'échange de chaleur adjacents des premier et second faisceaux de tubes. Chaque ailette repliée s'étend entre un ensemble respectif de segments de tube d'échange de chaleur adjacents des premier et second faisceaux de tubes, embrassant l'écart d'espacement entre les faisceaux de tubes. Plusieurs encoches d'ailette font saillie vers l'extérieur à partir de chaque ailette repliée dans l'écart d'espacement.
EP13814690.7A 2013-02-13 2013-12-04 Échangeur de chaleur à tubes plats et à faisceaux multiples Not-in-force EP2956728B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201361764011P 2013-02-13 2013-02-13
PCT/US2013/073077 WO2014126634A1 (fr) 2013-02-13 2013-12-04 Échangeur de chaleur à tubes plats et à faisceaux multiples

Publications (2)

Publication Number Publication Date
EP2956728A1 true EP2956728A1 (fr) 2015-12-23
EP2956728B1 EP2956728B1 (fr) 2017-03-22

Family

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Application Number Title Priority Date Filing Date
EP13814690.7A Not-in-force EP2956728B1 (fr) 2013-02-13 2013-12-04 Échangeur de chaleur à tubes plats et à faisceaux multiples

Country Status (5)

Country Link
US (1) US20150377561A1 (fr)
EP (1) EP2956728B1 (fr)
CN (1) CN104995471A (fr)
ES (1) ES2627555T3 (fr)
WO (1) WO2014126634A1 (fr)

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CN107218822B (zh) * 2016-03-21 2019-04-19 丹佛斯微通道换热器（嘉兴）有限公司 换热器和空调系统
EP3428562A1 (fr) * 2017-07-14 2019-01-16 Nissens A/S Échangeur de chaleur comprenant des tubes de fluide ayant une première et une seconde paroi intérieure
CN109405621A (zh) * 2018-08-30 2019-03-01 纳百川控股有限公司 水箱翅片
TWI899355B (zh) * 2020-11-17 2025-10-01 德商威蘭 握克公司 管束熱交換器

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EP1840494A3 (fr) * 2006-03-29 2011-03-16 Erbslöh Aluminium GmbH Profilé d'échangeur de chaleur
JP4946348B2 (ja) * 2006-10-19 2012-06-06 ダイキン工業株式会社 空気熱交換器
JP5320846B2 (ja) * 2008-06-20 2013-10-23 ダイキン工業株式会社 熱交換器
CN101619950B (zh) * 2009-08-13 2011-05-04 三花丹佛斯（杭州）微通道换热器有限公司 翅片和具有该翅片的换热器
CN103270386A (zh) 2010-11-22 2013-08-28 开利公司 多管束扁平化管翅片式热交换器

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EP2956728B1 (fr) 2017-03-22
ES2627555T3 (es) 2017-07-28
US20150377561A1 (en) 2015-12-31
CN104995471A (zh) 2015-10-21

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