WO2004083762A1 - Tuyaux echangeurs de chaleur - Google Patents

Tuyaux echangeurs de chaleur Download PDF

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Publication number
WO2004083762A1
WO2004083762A1 PCT/GB2004/001215 GB2004001215W WO2004083762A1 WO 2004083762 A1 WO2004083762 A1 WO 2004083762A1 GB 2004001215 W GB2004001215 W GB 2004001215W WO 2004083762 A1 WO2004083762 A1 WO 2004083762A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
channels
tube according
channel
ratio
Prior art date
Application number
PCT/GB2004/001215
Other languages
English (en)
Inventor
Youming Yuan
Original Assignee
Calsonic Kansei Uk Limited
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 Limited filed Critical Calsonic Kansei Uk Limited
Priority to EP04721949A priority Critical patent/EP1608928B1/fr
Priority to DE602004029338T priority patent/DE602004029338D1/de
Publication of WO2004083762A1 publication Critical patent/WO2004083762A1/fr

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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F28F1/045—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular with assemblies of stacked elements
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the present invention relates to heat exchanger tub&s, and in particular to heat exchanger tubes for use in automotive heat exchangers, particularly ⁇ automotive HVAC heat exchangers.
  • Carbon dioxide has been shown to be one of the most promising candidates for an environmentally friendly refrigerant.
  • CO 2 has " been used before the adoption of CFC refrigerant and it is still used as a refrigerant in deep freezing industry today. Due to the particular thermophysical properties of carbon dio xide (its low critical temperature of about 31 °C), however, when used for mobile air conditioning, it has to be operated, in a transcritical cycle in most mobile air conditioning usage, when the ambient air temperature is likely to be high. Thus in a mobile C0 2 air conditioning system, the heat exchanger that dissipates heat to the ambient air (also known as gas cooler) has to operate in a high pressure supercritical state, usually over 10O " bar.
  • the present invention provides a substantially flat tube for an automotive heat exchanger, the tube comprising a plurality of flow channels extending in ttie longitudinal direction of the tube, the channels having substantially non-circular cros s- sectional geometry.
  • the present invention provides flat tube designs with non-circular cross-section channel geometry, that are narrow to reduce airside pressure drop, strong to withstand high pressur-e, of light weight and that also offer higher heat conductance and lower pressure drop compared to flat tube with circular cross-section channel with the same tube cross-section size.
  • the tube is extruded, the channels preferably being formed in the extrusion process.
  • the tube is preferably used in an HVAC gas cooler having a working fluid operating in a substantially supercritical state.
  • the tube material is aluminium.
  • thue refrigerant is C0 2 .
  • the ratio of the maximum channel dimension in section in the tube minor axis direction to the txibe minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress: H/Ltminor ⁇ A ⁇ yeild /( ⁇ yeild + Pburst);
  • .A is a safety factor and A ⁇ 1.
  • the ratio of the sum of the length of all the channel widths to the tube major axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
  • B is a safety factor and B ⁇ 1.
  • Figure 1 is a schematic sectional view of a tube in accordance with a first embodiment of tlie invention (triangular cross-section channels);
  • Figure 2 is a graphic representation of effects on channel width on performance compared with a comparable circular section channel tube
  • Figure 3 is a schematic sectional view of a tube in accordance with a second embodiment of the invention (rectangular cross-section channels);
  • Figure 4 is a graphic representation of effect on channel width for the second embodiment of tube (rectangular section channels) compared with a comparable circular section channel tub «;
  • Figure 5 is a schematic sectional view of a tube in accordance with a further embodiment of the invention (waisted rectangular cross-section channel);
  • Figure 6 is a graphic representation of effect on channel width for the further embodiment of the invention compared to a comparable circular section channel tube; and Figure 7 is a graphic comparison between refrigerant temperature in a triangular cross-section channel tube and a comparable circular cross-section channel tube.
  • a heat exchange tube (1) typically of extruded aluminium material is provided with a series of substantially parallel working fluid (refrigerant) channels 2.
  • working fluid typically the tubes extend between headers and are stacked in a row having air-gaps between adjacent tubes.
  • An airway or fin matrix may be provided in thermal contact with adjacent spaced tubes in order to maximise heat transfer.
  • the heat exchanger is brazed together.
  • One of the prefened realisations of the indention is a flat tube 1 with multiple channels 2 of triangular cross-section.
  • the second realisation is a flat tube of multiple channels of rectangular cross-section and yet a third realisation is a flat tube of multiple channels with a shape modified from rectangular cross-section.
  • the performance of the three realisations are compared to the benchmark round channel flat tubes under the same overall tube cross-section size.
  • the maximum channel dimension in the tube minor axis direction is fixed as the same as the round channel diameter.
  • the variation of the total heat conductance for each tube, incorporating a typical airside surface design and airside flow condition, and of the pressure drop through one tube, for a fixed tube length, are calculated with the variation of the channel width.
  • the merits of each design are judged by these two performance parameters compared to the benchmark circular cro ss-section channel flat tube.
  • the maximisation of total channel cross- section area needs also to result in a tube design having sufficient structural robustness. Therefore, the maximum dimension of the channel in the tube minor axis direction should be no more than a fixed fraction of the tube minor axis dimension. Similarly, over any intersection line between the tube end surface and any plane perpendicular to the tube end surface, the ratio of the total length falling into the channels to the total line length should not be greater than a fixed fraction. The exact value of these fraction numbers should ideally be a function of the desired burst pressure an trie yield stress of the tube material.
  • Figure 7 shows the result of the refrigerant temperatures in a flat tube of prefened triangular channel and in a benchmark circular cross-section channel flat tube. It can be seen that prefened triangular channel tube is more effective and cools the refrigerant to the same extent as a circular cross-section channel tube of a third longer length. For the same length, the new triangular channel tube will give a heat transfer rate about 7°/ ⁇ higher.
  • Figure 3 shows the second realisation with rectangular channel.
  • the total channel cross-section area is increased by 27% compared to the benchmark round channel case and conespondingly the weight of the tube is reduced significantly.
  • the limitation on the two ratios as discussed in first realisation still t ⁇ olds.
  • the performance of the flat tube of the second realisation versus the channel width, compared again to the benchmark round channel tube is shown in Figure 4.
  • the optimal performance range, offering better or equivalent under the same or much lower pressure drop, is 0.5 ⁇ w H ⁇ 2.2.
  • a further and third realisation is schematically shown in Figure 5.
  • the rectangular channel in the second realisation is modified to improve structural robustness of the rectangular channel. This design still offers weight reduction compared to the benchmark round channel flat tube. To maintain the structural robustness, again the limitation on the two ratios a_s discussed in first realisation still holds.
  • the ratio of the maximum channel dimension in section in the tube minor axis direction to the tube minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
  • A is a safety factor and A ⁇ 1.
  • the ratio of the sum of the length of alL the channel widths to the tube major axis dimension is less than a factor of the ratio between. the bursting pressure and the tube material yield stress:
  • B is a safety factor and B ⁇ 1.

Landscapes

  • 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 tuyau sensiblement plat (1) pour un échangeur thermique d'automobile, ce tuyau (1) comprenant plusieurs canaux d'écoulement (2) s'étendant dans la direction longitudinale du tuyau (1), ces canaux (2) possédant une forme non circulaire en section transversale.
PCT/GB2004/001215 2003-03-19 2004-03-19 Tuyaux echangeurs de chaleur WO2004083762A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP04721949A EP1608928B1 (fr) 2003-03-19 2004-03-19 Procédé pour la configuration de tubes plats pour échangeur de chaleur de véhicule automobile
DE602004029338T DE602004029338D1 (de) 2003-03-19 2004-03-19 Verfahren zur auslegung von flachrohren für kraftfahrzeug-wärmetauscher

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0306269A GB2399623A (en) 2003-03-19 2003-03-19 Flat tube heat exchanger for a vehicle air conditioning system
GB0306269.2 2003-03-19

Publications (1)

Publication Number Publication Date
WO2004083762A1 true WO2004083762A1 (fr) 2004-09-30

Family

ID=9955060

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2004/001215 WO2004083762A1 (fr) 2003-03-19 2004-03-19 Tuyaux echangeurs de chaleur

Country Status (4)

Country Link
EP (1) EP1608928B1 (fr)
DE (1) DE602004029338D1 (fr)
GB (1) GB2399623A (fr)
WO (1) WO2004083762A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006105823A1 (fr) * 2005-04-08 2006-10-12 Behr Gmbh & Co. Kg Tube plat a plusieurs canaux

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1983272A1 (fr) * 2007-04-18 2008-10-22 Aic S.A. Faisceau d'échangeur thermique à combustible
US20190162455A1 (en) * 2017-11-29 2019-05-30 Lennox Industries, Inc. Microchannel heat exchanger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0596507A1 (fr) * 1992-11-05 1994-05-11 Nippondenso Co., Ltd. Matrice d'extrusion de tube multicanaux et tube multicanaux fabriqué avec cette matrice
US5476141A (en) * 1993-04-19 1995-12-19 Sanden Corporation Flat-type refrigerant tube having an improved pressure-resistant strength
EP0881448A2 (fr) 1997-05-30 1998-12-02 Showa Aluminum Corporation Tube plat à passages multiples pour échangeur de chaleur et échangeur de chaleur utilisant de tels tubes
EP0990828A2 (fr) 1998-10-01 2000-04-05 Behr GmbH & Co. Tuyau plat avec canaux multiples
DE19921407A1 (de) * 1999-05-08 2000-11-09 Behr Gmbh & Co Stranggepreßtes Mehrkammerrohr, insbesondere für einen Wärmeübertrager

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2694080B1 (fr) * 1992-07-24 1996-06-21 Furukawa Electric Co Ltd Tube condenseur plat et poreux.
JPH0972680A (ja) * 1995-09-05 1997-03-18 Akutoronikusu Kk 多孔扁平管の構造とその製造方法
US6216776B1 (en) * 1998-02-16 2001-04-17 Denso Corporation Heat exchanger
JP2000046421A (ja) * 1998-07-27 2000-02-18 Calsonic Corp 二酸化炭素冷凍サイクル用熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0596507A1 (fr) * 1992-11-05 1994-05-11 Nippondenso Co., Ltd. Matrice d'extrusion de tube multicanaux et tube multicanaux fabriqué avec cette matrice
US5476141A (en) * 1993-04-19 1995-12-19 Sanden Corporation Flat-type refrigerant tube having an improved pressure-resistant strength
EP0881448A2 (fr) 1997-05-30 1998-12-02 Showa Aluminum Corporation Tube plat à passages multiples pour échangeur de chaleur et échangeur de chaleur utilisant de tels tubes
EP0990828A2 (fr) 1998-10-01 2000-04-05 Behr GmbH & Co. Tuyau plat avec canaux multiples
DE19921407A1 (de) * 1999-05-08 2000-11-09 Behr Gmbh & Co Stranggepreßtes Mehrkammerrohr, insbesondere für einen Wärmeübertrager

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006105823A1 (fr) * 2005-04-08 2006-10-12 Behr Gmbh & Co. Kg Tube plat a plusieurs canaux

Also Published As

Publication number Publication date
EP1608928A1 (fr) 2005-12-28
DE602004029338D1 (de) 2010-11-11
GB2399623A (en) 2004-09-22
EP1608928B1 (fr) 2010-09-29
GB0306269D0 (en) 2003-04-23

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