EP0583851A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0583851A2
EP0583851A2 EP93202885A EP93202885A EP0583851A2 EP 0583851 A2 EP0583851 A2 EP 0583851A2 EP 93202885 A EP93202885 A EP 93202885A EP 93202885 A EP93202885 A EP 93202885A EP 0583851 A2 EP0583851 A2 EP 0583851A2
Authority
EP
European Patent Office
Prior art keywords
headers
tubes
condenser
flow paths
refrigerant
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
EP93202885A
Other languages
German (de)
English (en)
Other versions
EP0583851B1 (fr
EP0583851A3 (fr
Inventor
Leon Arnold Guntly
Jack C. Dudley
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.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing 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
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Application filed by Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of EP0583851A2 publication Critical patent/EP0583851A2/fr
Publication of EP0583851A3 publication Critical patent/EP0583851A3/fr
Application granted granted Critical
Publication of EP0583851B1 publication Critical patent/EP0583851B1/fr
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag 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
    • F28F1/02—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
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • This invention relates to a heat exchanger suitable for use in a refrigeration or air conditioning system for cooling the refrigerant.
  • the invention is particularly applicable to a condenser for condensing a refrigerant using ambient air as a cooling medium.
  • the air side of the tubes will be relatively large in size.
  • the relatively large size of the tubes on the air side results in a relatively large portion of the frontal area of the air side being blocked by the tube and less area available in which air side fins may be disposed to enhance heat transfer.
  • the present invention is directed to overcoming the above problems.
  • An exemplary embodiment of the invention achieves the foregoing objects in a condenser comprising a pair of spaced headers, one of the headers having a vapor inlet and the other of the headers having a condensate outlet.
  • a condenser tube extends between the headers and is in fluid communication with each.
  • the tube defines a plurality of hydraulically parallel substantially discrete fluid flow paths between the headers and each of the fluid flow paths has a hydraulic diameter in the range of about 0.015 to 0.040 inches.
  • the invention contemplates that the tubes be flattened tubes.
  • the invention contemplates that the plurality of flow paths in each tube be defined by an undulating spacer contained within the tubes.
  • Fins may be disposed on the exterior of the condenser tube and extend between the exteriors of adjacent ones of the condenser tubes.
  • the headers be defined by generally cylindrical tubes having facing openings, such as slots, for receiving respective ends of the condenser tubes.
  • a condenser made according to the invention is illustrated in Fig. 1 and is seen to include opposed, spaced, generally parallel headers 10 and 12.
  • the headers 10 and 12 are preferably made up from generally cylindrical tubing. On their facing sides, they are provided with a series of generally parallel slots or openings 14 for receipt of corresponding ends 16 and 18 of condenser tubes 20.
  • each of the headers 10 and 12 is provided with a somewhat spherical dome to improve resistance to pressure as explained more fully in the commonly assigned, copending application of Saperstein et al, entitled “Heat Exchanger” U.S. application Ser. No. 722,653, filed April 12, 1985, the details of which are herein incorporated by reference.
  • the header 10 has one end closed by a cap 24 brazed or welded thereto. Brazed or welded to the opposite end is a fitting 26 to which a tube 28 may be connected.
  • the lower end of the header 12 is closed by a welded or brazed cap 30 similar to the cap 24 while its upper end is provided with a welded or brazed in place fitting 32.
  • a welded or brazed cap 30 similar to the cap 24 while its upper end is provided with a welded or brazed in place fitting 32.
  • one of the fittings 26 and 32 serves as a vapor inlet while the other serves as a condensate outlet.
  • the fitting 26 will serve as a condensate outlet.
  • a plurality of the tubes 20 extend between the headers 10 and 12 and are in fluid communication therewith.
  • the tubes 20 are geometrically in parallel with each other and hydraulically in parallel as well.
  • Disposed between adjacent ones of the tubes 20 are serpentine fins 34 although plate fins could be used if desired.
  • Upper and lower channels 36 and 38 extend between and are bonded by any suitable means to the headers 10 and 12 to provide rigidity to the system.
  • each of the tubes 20 is a flattened tube and within its interior includes an undulating spacer 40.
  • the spacer 40 appears as shown in Fig. 2 and it will be seen that alternating crests are in contact along their entire length with the interior wall 42 or the tube 20 and bonded thereto by fillets 44 of solder or braze metal.
  • a plurality of substantially discrete hydraulically parallel fluid flow paths 46, 48, 50, 52, 54, 56, 58 and 60 are provided within each of the tubes 20. That is to say, there is virtually no fluid communication from one of such flow paths to the adjacent flow paths on each side.
  • This effectively means that each of the walls separating adjacent fluid flow paths 46, 48, 50, 52, 54, 56, 58 and 60 are bonded to both of sides of the flattened tube 20 along their entire length.
  • a second advantage resides in the fact the condensers such as that of the present invention are employed on the outlet side of a compressor and therefore are subjected to extremely high pressure. Conventionally, this high pressure will be applied to the interior of the tubes 20. Where so-called "plate" fins are utilized in lieu of the serpentine fins 34 illustrated in the drawings, the same tend to confine the tubes 20 and support them against the internal pressure employed in a condenser application. Conversely, serpentine fins such as those shown at 34 are incapable of supporting the tubes 20 against substantial internal pressure. According to the invention, however, the desired support in a serpentine fin heat exchanger is accomplished by the fact that the spacer 40 and the crest thereof is bonded along its entire length in the interior wall 42 of each tube 20. This bond results in various parts of the spacer 40 being placed in tension when the tube 20 is pressurized to absorb the force resulting from internal pressure within the tube 20 tending to expand the tube 20.
  • tubes 20 with accompanying inserts 40 may be formed in the commonly assigned U.S. application of Saperstein, entitled “Tube and Spacer Construction For Use In Heat Exchangers", Serial No. 740,000, filed May 31, 1985, the details of which are herein incorporated by reference.
  • a highly preferred means by which the tubes 20 with accompanying inserts 40 may be formed is disclosed in the commonly U.S. assigned application of Saperstein et al, entitled “Method of Making a Heat Exchanger", Serial No. 887,223, filed July 21, 1986, the details of which are also herein incorporated by reference.
  • each of the flow paths 48, 50, 52, 54, 56 and 58, and to the extent possible depending upon the shape of the insert 40, the flow paths 46 and 60 as well, have a hydraulic diameter in the range of about 0.015 to 0.040 inches. Given current assembly techniques known in the art, a hydraulic diameter of approximately 0.035 inches optimizes ultimate heat transfer efficiency and ease of construction. Hydraulic diameter is as conventionally defined, namely, the cross-sectional area of each of the flow paths multiplied by four and in turn divided by the wetted perimeter of the corresponding flow path.
  • the tube dimension across the direction of air flow through the core is desirable to make the tube dimension across the direction of air flow through the core as small as possible. This in turn will provide more frontal area in which fins, such as the fins 34, may be disposed in the core without adversely increasing air side pressure drop to obtain a better rate of heat transfer.
  • one or more additional rows of the tubes can be included.
  • the preferred embodiment contemplates that tubes with separate spacers such as illustrated in Fig. 2 be employed as opposed to extruded tubes having passages of the requisite hydraulic diameter.
  • Current extrusion techniques that are economically feasible at the present for large scale manufacture of condensers generally result in a tube wall thickness that is greater than that that is required to support a given pressure using a tube and spacer as disclosed herein.
  • the overall tube width of such extruded tubes is somewhat greater for a given hydraulic diameter than a tube and spacer combination, which is undesirable for the reasons stated immediately preceding. Nonetheless, the invention contemplates the use of extruded tubes having passages with a hydraulic diameter within the stated range.
  • the ratio of the outside tube periphery to the wetted periphery within the tube be made as small as possible so long as the flow path does not become sufficiently small that the refrigerant cannot readily pass therethrough. This will lessen the resistance to heat transfer on the vapor and/or conduit side.
  • Fig. 3 plots the heat transfer rate against the cavity or hydraulic diameter in inches at air flows varying from 450 to 3200 standard cubic feet per minute for production condenser cores made by the assignee of the instant application.
  • the curves designated "A" represent heat transfer at the stated air flows for a core such as shown in Fig. 1 having a frontal area of two square feet utilizing tubes approximately 24 inches long and having a 0.015 inch tube wall thickness, a 0.532 tube major dimension, 110°F. inlet air, 180°F. inlet temperature and 235 psig pressure for R-12 and assuming 2°F. of subcooling of the exiting refrigerant after condensation.
  • the core was provided with 18 fins per inch between tubes and the fins were 0.625 inches by 0.540 inches by 0.006 inches.
  • Both the core made according to the invention and the conventional core have the same design point which is, as shown in Fig. 4, a heat transfer rate of 26,000 BTU per hour at an air flow of 1800 standard cubic feet per minute.
  • the actual observed equivalence of the two cores occurred at 28,000 BTU per hour and 2,000 standard cubic feet per minute; and those parameters may be utilized for comparative purposes.
  • Curves "H” and "J" respectively for the conventional condenser and the condenser of the subject invention illustrate a considerable difference in the pressure drop of the refrigerant across the condenser.
  • a core made according to the invention when compared with the conventional core, holds less refrigerant.
  • the core of the invention reduces the system requirement for refrigerant.
  • there is lesser space required for installation of the inventive core because of its lesser depth.
  • Fig. 5 compares, at various air velocities, the heat transfer rate per pound of core of the conventional condenser (curve "K") versus heat transfer per pound of core of a condenser made according to the invention (curve "L").
  • Fig. 5 demonstrates a considerable weight savings in a system may be obtained without sacrificing heat transferability by using the core of the present invention.
  • Fig. 6 in curve “M” thereon, illustrates the air side pressure drop for a conventional core for various air flows.
  • Curve “N” illustrates the air side pressure drop for the core of the present invention. It will be appreciated that the air side pressure drop, and thus fan energy, is reduced when a core made according to the invention is utilized.
EP93202885A 1985-10-02 1986-09-17 Echangeur de chaleur Revoked EP0583851B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US78308785A 1985-10-02 1985-10-02
US783087 1985-10-02
US90269786A 1986-09-05 1986-09-05
US902697 1986-09-05
EP86307161A EP0219974B1 (fr) 1985-10-02 1986-09-17 Condenseur à branche d'écoulement à petit diamètre hydraulique

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP86307161A Division EP0219974B1 (fr) 1985-10-02 1986-09-17 Condenseur à branche d'écoulement à petit diamètre hydraulique
EP86307161.9 Division 1986-09-17

Publications (3)

Publication Number Publication Date
EP0583851A2 true EP0583851A2 (fr) 1994-02-23
EP0583851A3 EP0583851A3 (fr) 1994-03-09
EP0583851B1 EP0583851B1 (fr) 1997-11-19

Family

ID=27120095

Family Applications (2)

Application Number Title Priority Date Filing Date
EP86307161A Revoked EP0219974B1 (fr) 1985-10-02 1986-09-17 Condenseur à branche d'écoulement à petit diamètre hydraulique
EP93202885A Revoked EP0583851B1 (fr) 1985-10-02 1986-09-17 Echangeur de chaleur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP86307161A Revoked EP0219974B1 (fr) 1985-10-02 1986-09-17 Condenseur à branche d'écoulement à petit diamètre hydraulique

Country Status (9)

Country Link
EP (2) EP0219974B1 (fr)
JP (1) JPS62175588A (fr)
KR (1) KR950007282B1 (fr)
AT (2) ATE145051T1 (fr)
BR (1) BR8604768A (fr)
CA (1) CA1317772C (fr)
DE (2) DE3650648T2 (fr)
ES (1) ES2002789A6 (fr)
MX (1) MX167593B (fr)

Cited By (8)

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Publication number Priority date Publication date Assignee Title
US6302193B1 (en) * 1996-12-25 2001-10-16 Calsonic Kansei Corporation Condenser assembly structure
DE10054158A1 (de) * 2000-11-02 2002-05-08 Behr Gmbh Mehrkammerrohr mit kreisförmigen Strömungskanälen
US7677057B2 (en) 2006-11-22 2010-03-16 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar tube spacing
US7802439B2 (en) 2006-11-22 2010-09-28 Johnson Controls Technology Company Multichannel evaporator with flow mixing multichannel tubes
US8234881B2 (en) 2008-08-28 2012-08-07 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US8439104B2 (en) 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution
US8713963B2 (en) 2007-07-27 2014-05-06 Johnson Controls Technology Company Economized vapor compression circuit
EP1992891B1 (fr) 2002-10-31 2017-06-21 Valeo Systemes Thermiques Condenseur, notamment pour un circuit de climatisation de véhicule automobile, et circuit comprenant ce condenseur

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CA1317772C (fr) * 1985-10-02 1993-05-18 Leon A. Guntly Condenseur a circuit d'ecoulement de faible diametre hydraulique
US4688311A (en) * 1986-03-03 1987-08-25 Modine Manufacturing Company Method of making a heat exchanger
US4936379A (en) * 1986-07-29 1990-06-26 Showa Aluminum Kabushiki Kaisha Condenser for use in a car cooling system
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
EP0360362B1 (fr) * 1986-07-29 1992-07-22 Showa Aluminum Kabushiki Kaisha Condenseur
US5458190A (en) * 1986-07-29 1995-10-17 Showa Aluminum Corporation Condenser
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5190100B1 (en) * 1986-07-29 1994-08-30 Showa Aluminum Corp Condenser for use in a car cooling system
JPH0544679Y2 (fr) * 1988-07-12 1993-11-12
DE3843306A1 (de) * 1988-12-22 1990-06-28 Thermal Waerme Kaelte Klima Flachrohrverfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
DE3843305A1 (de) * 1988-12-22 1990-06-28 Thermal Waerme Kaelte Klima Verfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
DE3918312A1 (de) * 1988-12-22 1990-12-06 Thermal Waerme Kaelte Klima Flachrohrverfluessiger, herstellungsverfahren und anwendung
DE3923936C2 (de) * 1989-07-19 1996-07-11 Laengerer & Reich Kuehler Wärmeaustauscher, insbesondere Ölkühler
JPH0363497A (ja) * 1989-07-28 1991-03-19 Matsushita Refrig Co Ltd 伝熱管
US5099576A (en) * 1989-08-29 1992-03-31 Sanden Corporation Heat exchanger and method for manufacturing the heat exchanger
US5197539A (en) * 1991-02-11 1993-03-30 Modine Manufacturing Company Heat exchanger with reduced core depth
WO1992015833A1 (fr) * 1991-03-11 1992-09-17 Modine Manufacturing Company Condenseur a passage d'ecoulement de diametre hydraulique reduit
US6016864A (en) * 1996-04-19 2000-01-25 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
DE19845336A1 (de) 1998-10-01 2000-04-06 Behr Gmbh & Co Mehrkanal-Flachrohr
GB2346680A (en) 1999-02-11 2000-08-16 Llanelli Radiators Ltd Condenser
EP1065454A1 (fr) 1999-07-02 2001-01-03 Modine Manufacturing Company condenseur à refroidissement par air
DE10025486A1 (de) 2000-05-23 2001-11-29 Behr Gmbh & Co Wärmeübertragerblock
JP2002318086A (ja) * 2001-04-16 2002-10-31 Japan Climate Systems Corp 熱交換器用チューブ
DE50207354D1 (de) 2001-04-28 2006-08-10 Behr Gmbh & Co Kg Gefalztes Mehrkammerflachrohr
EP1265046B1 (fr) 2001-06-07 2005-11-23 Behr GmbH & Co. KG Ailette, tube et échangeur de chaleur
DE10137907A1 (de) 2001-08-02 2003-02-20 Modine Mfg Co Luftgekühlte Wärmeübertragungsanordnung
DE10212249A1 (de) * 2002-03-20 2003-10-02 Behr Gmbh & Co Wärmetauscher und Kühlsytem
DE10223712C1 (de) * 2002-05-28 2003-10-30 Thermo King Deutschland Gmbh Anordnung zum Klimatisieren eines Fahrzeugs
DE20208337U1 (de) * 2002-05-28 2003-10-16 Thermo King Deutschland Gmbh Anordnung zum Klimatisieren eines Fahrzeugs
EP1503164B1 (fr) * 2003-07-28 2019-05-01 Mahle Behr France Rouffach S.A.S Échangeur de chaleur
GB0326443D0 (en) 2003-11-13 2003-12-17 Calsonic Kansei Uk Ltd Condenser
DE102006062261A1 (de) * 2006-12-22 2008-06-26 Konvekta Ag Klimaanlage für Fahrzeuge mit Wärmetauschereinheit mit mindestens einem nicht modular zusammengesetzten Wärmetauscher
WO2009018150A1 (fr) 2007-07-27 2009-02-05 Johnson Controls Technology Company Echangeur thermique a multiples canaux
KR20130065174A (ko) * 2011-12-09 2013-06-19 현대자동차주식회사 차량용 열교환기
DE102015210231A1 (de) * 2015-06-03 2016-12-08 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher für ein Kühlsystem, Kühlsystem sowie Baugruppe
CN107709915A (zh) 2015-06-29 2018-02-16 开利公司 微型管热交换器
CN113091380A (zh) * 2020-01-08 2021-07-09 青岛海尔电冰箱有限公司 冷凝系统及冰箱

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6302193B1 (en) * 1996-12-25 2001-10-16 Calsonic Kansei Corporation Condenser assembly structure
US6546997B2 (en) 1996-12-25 2003-04-15 Calsonic Kansei Corporation Condenser assembly structure
DE10054158A1 (de) * 2000-11-02 2002-05-08 Behr Gmbh Mehrkammerrohr mit kreisförmigen Strömungskanälen
EP1203922A2 (fr) 2000-11-02 2002-05-08 Behr GmbH & Co. Condenseur et tube pour celui-ci
EP1992891B1 (fr) 2002-10-31 2017-06-21 Valeo Systemes Thermiques Condenseur, notamment pour un circuit de climatisation de véhicule automobile, et circuit comprenant ce condenseur
US7802439B2 (en) 2006-11-22 2010-09-28 Johnson Controls Technology Company Multichannel evaporator with flow mixing multichannel tubes
US7757753B2 (en) 2006-11-22 2010-07-20 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar multichannel tubes
US7832231B2 (en) 2006-11-22 2010-11-16 Johnson Controls Technology Company Multichannel evaporator with flow separating manifold
US7895860B2 (en) 2006-11-22 2011-03-01 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
US7980094B2 (en) 2006-11-22 2011-07-19 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar tube spacing
US7677057B2 (en) 2006-11-22 2010-03-16 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar tube spacing
US8713963B2 (en) 2007-07-27 2014-05-06 Johnson Controls Technology Company Economized vapor compression circuit
US8234881B2 (en) 2008-08-28 2012-08-07 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US8938988B2 (en) 2008-08-28 2015-01-27 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US8439104B2 (en) 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution

Also Published As

Publication number Publication date
DE3650658D1 (de) 1998-01-02
CA1317772C (fr) 1993-05-18
EP0219974A3 (fr) 1989-08-02
JPH0587752B2 (fr) 1993-12-17
EP0219974B1 (fr) 1996-11-06
EP0219974A2 (fr) 1987-04-29
ATE145051T1 (de) 1996-11-15
DE3650658T2 (de) 1998-05-14
EP0583851B1 (fr) 1997-11-19
JPS62175588A (ja) 1987-08-01
KR880004284A (ko) 1988-06-03
MX167593B (es) 1993-03-31
DE3650648T2 (de) 1999-04-15
ATE160441T1 (de) 1997-12-15
ES2002789A6 (es) 1988-10-01
KR950007282B1 (ko) 1995-07-07
BR8604768A (pt) 1987-06-30
DE3650648D1 (de) 1997-10-30
EP0583851A3 (fr) 1994-03-09

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