EP1384038A1 - Systeme echangeur de chaleur - Google Patents

Systeme echangeur de chaleur

Info

Publication number
EP1384038A1
EP1384038A1 EP02720306A EP02720306A EP1384038A1 EP 1384038 A1 EP1384038 A1 EP 1384038A1 EP 02720306 A EP02720306 A EP 02720306A EP 02720306 A EP02720306 A EP 02720306A EP 1384038 A1 EP1384038 A1 EP 1384038A1
Authority
EP
European Patent Office
Prior art keywords
tubes
heat exchanger
strip
slots
exchanger system
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.)
Withdrawn
Application number
EP02720306A
Other languages
German (de)
English (en)
Inventor
Gwyn Thomas
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.)
Marelli Automotive Systems UK Ltd
Original Assignee
Calsonic Kansei UK Ltd
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 Calsonic Kansei UK Ltd filed Critical Calsonic Kansei UK Ltd
Publication of EP1384038A1 publication Critical patent/EP1384038A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F28F1/24—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
    • F28F1/32—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 having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the present invention relates to heat exchanger systems, and in particular to heat exchanger systems for automotive use.
  • Heat exchanger systems comprising arrays of tubes for carrying a first heat exchange fluid between spaced headers.
  • a fin matrix (typically airside for vehicle radiators or condensers) forms a path for a second heat exchange fluid (for example air) .
  • the fin matrix comprises elongate serpentine metallic strips extending in the longitudinal direction of the tubes and in thermal bonded contact with adjacent spaced tubes.
  • the tubes and fin airway strips are of aluminium material clad with a brazing alloy. The tubes and airway matrix are assembled, secured by jigging clamps and brazed in a one shot brazing process.
  • the present invention provides a heat exchanger system comprising:
  • a matrix for directing flow of a heat exchange fluid through the heat exchanger system externally of the tubes comprising a plurality of spaced spacing strips, respective strips including:
  • a plurality of receiving portions for receiving a respective plurality tubes in the bank of tubes .
  • the strips are preferably arranged spaced face adjacent face, and desirably orientated transversely to the tubes.
  • the tube bank and strip matrix are preferably fused together to form a unitary heat exchanger unit.
  • the system is preferably of brazed aluminium construction, the tubes and strips beneficially comprising aluminium material components (typically clad with a brazing alloy) .
  • the tube bank and strip matrix are typically fused together in an aluminium brazing process following assembly.
  • the receiving portions preferably comprise void portions shaped and dimensioned to accommodate the thickness of a respective tube.
  • the void portions preferably comprise slots, the slots beneficially intersecting an edge of the respective spacing strip.
  • the slots intersect opposed edges of the respective strip.
  • the slots beneficially have respective closed ends opposed to the slot open end intersecting the strip edge.
  • the spacing strips are preferably laid up to be spaced from one another and face to face spaced adjacent one another.
  • the spacing between adjacent strips is preferably substantially in the range 1mm - 2mm.
  • the tubes in the bank are for optimum performance preferably spaced from adjacent tubes by a spacing distance substantially within the range 4mm - 12mm.
  • the above preferred ranges give a preferred hydraulic diameter for the heat exchanger design substantially in the range 1.5 to 3.5.
  • the system is effectively self jigging for the fusing/brazing process. This is because the tubes are retained securely in the matched up receiving portions of the strips such that clamping is not required. This gives significant cost reductions. Typically 30% or more of the heat supplied in an aluminium brazing furnace is used merely in wasteful heating of the securing jigging clamps.
  • the arrangement also provides for highly automated assembly for bonding.
  • the tubes may be inserted simultaneously through the open slot ends in a direction transverse to the longitudinal direction of the tubes.
  • One or mor tab portions are preferably provided proximate the edge of a respective slot, the respective tab portion beneficially extending generally transversely to the major surface of the strip.
  • the tab portions serve as spacers to contact and provide consistent spacing between adjacent strips in the matrix.
  • the respective tab portions are preferably provided proximate spaced opposed edges of a respective slot.
  • the transverse extent of the tab portion is substantially of 50% or greater of the width of the slot (more preferably of 70% or greater of the width of the slot, most preferably substantially equal to the width of the slot) .
  • the respective tab portions are preferably formed from material comprising the strip, the tab being turned outwardly to leave a void defining the slot.
  • Tabs are preferably formed from adjacent portions of material turned outwardly to leave a void defining the slot, the adjacent tab forming portions preferably being connected at opposed edges of the slot .
  • the tabs may also provide a greater surface area for bonding (for example by brazing) to the external wall of the tube.
  • the free outer edge of a respective tab includes a seat portion extending transversely to the general surface of the respective tab.
  • the seat portion of a tab of a respective slot in a first strip beneficially rests against the edge material (underside) of a respective slot in a second adjacently laying strip in the matrix.
  • the seat portion avoids the tab of one strip inadvertently extending into a matched up slot of the adjacent laying strip.
  • the receiving portions of the spacing strips are configured such that, when receiving tubes, adjacent tubes overlap widthwise preferably by substantially 50% or greater.
  • the spanning portions are preferably provided with boundary layer disruptive formations such as louvres, slits, slots or the like. This arrangement effectively provides for a single bank of tubes, adjacent tubes being respectively staggered or displaced depending upon the degree of widthwise overlap of adjacent tubes.
  • Such a staggered tube configuration may provide improved heat transfer characteristics per unit core depth due to improved airflow adhesion to the tubes (for example where the matrix strips define airways) .
  • the heat exchanger system may comprise:
  • a first heat exchanger arrangement comprising a first bank of heat exchanger tubes, adjacent tubes having spaces therebetween;
  • a second heat exchanger arrangement comprising a second bank of heat exchanger tubes, adjacent tubes having spaces therebetween, the first and second banks of tubes being substantially side by side the tubes extending in a common general direction;
  • respective spacing strips comprising the matrix including a first row of spaced tube receiving slots intersecting a first edge of the strip and a second row of spaced tube receiving slots intersecting a second edge of the strip.
  • the first row of spaced tube receiving slots in a respective strip preferably receives tubes from a respective one of the first and second banks of tubes, the second row of spaced tube receiving slots in a respective strip receiving tubes from the other respective one of the first and second banks of tubes.
  • the arrangement defined enables the system to be used as a dual or unified heat exchanger such as for example a unified condenser radiator as described in general terms in EP-A-0367078.
  • the tubes in the first tube bank may advantageously be orientated in side by side, in-line, configuration with respective tubes in the second tube bank.
  • the slots in the first row are in match-up relationship with slots in the second row.
  • Tubes in the first tube bank are orientated in offset/staggered relationship with respective tubes in the second tube bank.
  • the slots in the first row are in correspondingly offset/staggered relationship with slots in the second row.
  • Such a staggered tube configuration may provide improved heat transfer characteristics per unit core depth due to improved airflow adhesion to the tubes (for example where the matrix strips define airways) and also managed airflow resulting from venturi effect generated between the two tube banks .
  • Respective strips in the matrix preferably include one or more (preferably a series of) zones of reduced thermal conductivity inhibiting heat transfer via the strip between the banks of tubes.
  • a zone of reduced conductivity may comprise an aperture (such as a slot or slit) in the strip positioned intermediate respective slots in the first and second rows.
  • a zone of reduced conductivity may comprise a gauge reduction portion (such as a groove, channel or notch) in the strip positioned intermediate respective slots in the first and second rows.
  • the tubes in the first bank may contain a heat exchange fluid associated with a first heat exchange circuit, the heat exchange tubes in the second bank containing a heat exchange fluid associated with a second heat exchange circuit .
  • one of the first and second heat exchanger arrangements may beneficially comprise a condenser of a refrigerant circuit of an vehicle air conditioning arrangement, the other of the first and second heat exchanger comprising a part of the engine coolant circuit.
  • the present invention provides a fin strip for spacing tubes in a heat exchanger system, the fin strip including:
  • the invention provides a method of manufacturing a heat exchanger system comprising:
  • a fin matrix comprising a plurality of fin strips as herein defined arranged in face adjacent face spaced configuration such that tube receiving slots in respective adjacent strips are in match-up relationship;
  • the slots in the strips beneficially intersect a respective longitudinal edge of the strips, the tubes preferably being mated by insertion in the direction of the tube width into the matched-up slots through the mouths of respective slots .
  • the slots in the strips may intersect two opposed longitudinally running edges of a respective strip, in which case the tubes are preferably mated by insertion in the direction of the tube width into the matched-up slots through the mouths of respective slots in both longitudinally running edges of the strips (preferably simultaneously) .
  • the strips and tubes are preferably of aluminium material, the tubes and strips being bonded in a one shot brazing process in which a brazed connection is formed between tubes and strips at the interface between the slots and the outer tube walls.
  • the invention provides a heat exchanger system including:
  • a second bank of heat exchanger tubes adjacent tubes having spaces therebetween, the first and second banks of tubes being substantially side by side, the tubes extending in a common general direction, wherein tubes in the first tube bank are orientated in offset/staggered relationship with respective tubes in the second tube bank.
  • Figure 1 is a plan view of an airway matrix strip according to the invention for use in a heat exchanger system in accordance with the invention
  • Figure 2 is a more detailed view of the part of strip of Figure 1 ;
  • Figure 3 is a section along A-A in Figure 2 ;
  • Figure 4 is a section along B-B in Figure 2;
  • Figure 5 is a perspective view of a portion of the strip of Figures 1 to 4 showing the upstanding tabs;
  • Figure 6 is a plan view of the portion of the strip of Figure 5 prior to folding out the tabs ;
  • Figure 7A and 7B are plan and side views respectively of a strip in accordance with the invention.
  • FIGS 8A, 8B and 9A, 9B are plan and side views respectively of alternative configurations of airway matrix strips according to the invention for use in heat exchanger systems in accordance with the invention;
  • Figure 10 is a plan view of a further alternative configuration of airway matrix strip.
  • Figure 11 is a schematic perspective view of a part of a heat exchanger system according to the invention.
  • an airway matrix fin strip 1 for use in a heat exchanger system.
  • the airway fin is formed of a thin strip of aluminium material clad with an aluminium brazing alloy.
  • the strip is typically of gauge 0.12mm - 0.05mm.
  • the fins are set up overlaying one adjacent the other, being spaced by means of tabs 9 upstanding from the general surface of the respective strips 1 as will be described hereinafter below.
  • the fins are built up face adjacent face spaced by tabs 9 in stacks of two to eight hundred deep.
  • the tabs 9 are shaped dimension to provide a fin pitched spacing of, typically, 1mm - 2mm.
  • Each fin strip 1 comprises a spanning portion 2 (provided with an airflow slit louvered portion 3) and, either side of respective spanning portions 2, a series of slots 4A, 4B.
  • slots 4A have open ends intersecting a first longitudinal edge of the strip 1 alternating with slots 4B having open ends interconnecting with the other longitudinally running edge of strip 1.
  • Slots 4A, 4B are shaped dimension to receive (extending transversely thereto i.e. into the paper in Figure 1) heat exchange fluid tubes (not shown) to be positioned in a bank spaced from one another by spanning portions 2 and extending in the same longitudinal tube direction.
  • the tubes are positioned in a batch adjacent the relevant slots 4A, 4B and introduced simultaneously by sideways movement (directions of arrow A and arrow B) to be received in the array formed by the stack of airways 1.
  • the tubes are generally clad with aluminium brazing alloy and the design is such that when the tubes are received in respective slots 4A, 4B in the stack of strips 1, the arrangement is self supporting (i.e. no further jigging or clamping is required) .
  • the assembly will then be introduced into the brazing furnace for brazing.
  • header tanks (not shown) are mounted to the opposed open ends of the tubes prior to brazing.
  • Figure 11 shows how tubes 101 and fin strips 1 are laid up.
  • a significant advantage of the present invention is that the self-jigging construction provides increased productivity. In other designs, jigging is required, and typically the jigging clamps may use up 30 percent of the furnace power in heating.
  • Tabs 9 are positioned around the periphery of respective slots 4A, 4B and standing proud of the surface of the strip 1. The tabs 9 are shown most conveniently in Figures 3, 4 and 5.
  • Each tab 9 includes a dart or seat formation 8 extending transversely to the general surface of tab 9.
  • the dart or seat 8 ensures that the next adjacent strip 1 in the stack rests conveniently upon the outwardly splayed dart or seat 8 at the uppermost position of the relevant tabs 9. This arrangement results in consistent spacing of the strips 1 in the stack.
  • an important feature of the tabs 9 is that they have, when oriented in an upstanding direction, a height dimension greater than 50 percent of the width of the slot.
  • the tabs are formed from the material of the strip such than, when deformed to extend transversely to the general surface of the strip 1, void portions defining the slot remain. In order to ensure that adjacent strips in the stack are sufficiently spaced, it is important that the height dimension is 50 percent or greater of the width of slots 4A, 4B.
  • FIG. 1A to 7A result in a heat exchanger having tubes in a single bank substantially in parallel, but adjacent tubes having a slightly staggered overlap relationship.
  • the widthwise overlap of adjacent tubes is 50% or greater.
  • the louvred tube spacing portions 3 of strip 1 are positioned intermediate adjacent tubes .
  • the resulting heat exchanger system has tubes in two side-by- side banks.
  • the tubes in the separate banks may be connected to separate headers to provide, for example, separate side-by-side heat exchanger units such as units currently becoming in vogue, for example, unified or combined condenser radiators for vehicles .
  • a general arrangement for such a unified or combined heat exchanger is disclosed for example in EP-A- 0367078.
  • separate tube banks are defined by rows of slots 4A, 4B respectively.
  • the tubes are retained in slots 4A, 4B in a respectively staggered or offset relationship between the two banks of tubes.
  • staggered tube configuration provides improved heat transfer performance with respect to equivalent heat exchanger core depth for matched up or aligned tubes in respective banks. This is due to the improved airflow adhesion to the tubes for the staggered tube banks and the managed airflow resulting from the venturi effect generated between the two tube banks .
  • the conduction path is reduced by means of providing apertures 11 in the path between the spaced banks of slots 4A, 4B in the respective strip 1.
  • gauge reduction portions such as grooves, notches, slits, channels or the like may be provided intermediately between slots 4A, 4B receiving the tubes in respective spaced banks .
  • each bank of tubes are substantially parallel to one another and matched up one to one.
  • the reduced heat transfer path between the tube holding slot banks 4A, 4B are provided, again, by apertures 11.
  • optimum heat exchanger performance has been found to be achieved, with a strip 1 spacing (x) substantially in the range 1mm - 2mm and a tube spacing (y) substantially in the range 4mm - 12mm.
  • the preferred hydraulic diameter for the systems of the invention are therefore preferably substantially in the range 1.5 to 3.5.
  • the heat exchanger system according to the invention combines ease of construction and economic advantage in terms of constructions costs together with versatility of design for use in differing applications. Benefits are envisaged in multi-core heat exchanger designs having spaced banks of tubes, in particular, in such arrangements where the tubes in respective banks can be offset or staggered with respect to one another.
  • the present invention enables such heat exchanger systems to be readily and conveniently achieved.

Landscapes

  • 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)

Abstract

La présente invention se rapporte à un système échangeur de chaleur (conçu particulièrement pour des automobiles) comportant une rangée de tubes échangeurs de chaleur espacés et une matrice conçue pour diriger le flux de fluide d'échange thermique à travers le système échangeur de chaleur, à l'extérieur des tubes espacés, ladite matrice comprenant des bandes d'espacement (1) qui comprennent des parties de travée (2) écartant les tubes respectifs dans la rangée ainsi que des parties de réception conçues pour recevoir les tubes respectifs.
EP02720306A 2001-05-04 2002-05-03 Systeme echangeur de chaleur Withdrawn EP1384038A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0111153 2001-05-04
GB0111153A GB2375164B (en) 2001-05-04 2001-05-04 Heat exchanger system
PCT/GB2002/002058 WO2002090856A1 (fr) 2001-05-04 2002-05-03 Systeme echangeur de chaleur

Publications (1)

Publication Number Publication Date
EP1384038A1 true EP1384038A1 (fr) 2004-01-28

Family

ID=9914173

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02720306A Withdrawn EP1384038A1 (fr) 2001-05-04 2002-05-03 Systeme echangeur de chaleur

Country Status (3)

Country Link
EP (1) EP1384038A1 (fr)
GB (2) GB2375164B (fr)
WO (1) WO2002090856A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2445575A (en) * 2007-01-12 2008-07-16 Kuan-Yin Chou Radiating structure
JP5573698B2 (ja) * 2011-01-21 2014-08-20 ダイキン工業株式会社 熱交換器および空気調和機
KR20140042093A (ko) * 2012-09-27 2014-04-07 삼성전자주식회사 열교환기
WO2014091536A1 (fr) * 2012-12-10 2014-06-19 三菱電機株式会社 Dispositif d'échange de chaleur à tube plat
KR20190124820A (ko) 2014-09-08 2019-11-05 미쓰비시덴키 가부시키가이샤 열교환기
JP6569525B2 (ja) * 2015-12-28 2019-09-04 株式会社富士通ゼネラル 熱交換器
JP6233540B2 (ja) * 2016-04-20 2017-11-22 ダイキン工業株式会社 熱交換器及び空調機
JP6925242B2 (ja) * 2017-11-13 2021-08-25 三菱電機株式会社 管挿入装置及び管挿入方法
JP6656279B2 (ja) * 2018-02-15 2020-03-04 三菱電機株式会社 熱交換器

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3771595A (en) * 1971-09-22 1973-11-13 Modine Mfg Co Heat exchange device

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Publication number Priority date Publication date Assignee Title
GB448815A (en) * 1935-06-04 1936-06-16 Arthur Bernard Modine Radiator core for cooling liquids
GB561026A (en) * 1942-10-29 1944-05-02 Edwin James Bowman Improvements in radiators for cooling liquids
US3863451A (en) * 1972-10-06 1975-02-04 Maschf Augsburg Nuernberg Ag Heater apparatus of a hot gas external combustion piston engine
GB2088034B (en) * 1980-11-22 1984-05-31 Serck Industries Ltd Heat exchangers and a method of manufacturing same
HU184377B (en) * 1981-02-05 1984-08-28 Huetoegepgyar Motor cooler
US4607690A (en) * 1985-11-29 1986-08-26 Foster Wheeler Energy Corporation Tube and support system for a heat exchanger
JPS62166294A (ja) * 1986-01-16 1987-07-22 Nippon Denso Co Ltd 熱交換器
GB2223301B (en) * 1988-07-08 1992-12-16 H E T Limited Heat exchange device and method of manufacture therefor
JPH02154987A (ja) * 1988-12-06 1990-06-14 Matsushita Refrig Co Ltd フィン付熱交換器
JP2819802B2 (ja) * 1990-08-10 1998-11-05 株式会社デンソー 積層型熱交換器のコア部構造
IT1284735B1 (it) * 1996-08-07 1998-05-21 Magneti Marelli Climat Srl Condensatore per impianti di condizionamento d'aria per veicoli
WO2000019162A1 (fr) * 1998-09-30 2000-04-06 Norsk Hydro Asa Ailette d'echangeur de chaleur
FR2812081B1 (fr) * 2000-07-18 2003-01-24 Valeo Thermique Moteur Sa Module d'echange de chaleur, notamment pour vehicule automobile, et procede de fabrication de ce module

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3771595A (en) * 1971-09-22 1973-11-13 Modine Mfg Co Heat exchange device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO02090856A1 *

Also Published As

Publication number Publication date
GB2375164B (en) 2005-11-30
GB2375164A (en) 2002-11-06
GB2409511A (en) 2005-06-29
GB2409511B (en) 2005-11-30
WO2002090856A1 (fr) 2002-11-14
GB0111153D0 (en) 2001-06-27
GB0504941D0 (en) 2005-04-20

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