EP0219974B1 - Verflüssiger mit einen kleinen hydraulischen Durchmesser aufweisender Strömungsbahn - Google Patents

Verflüssiger mit einen kleinen hydraulischen Durchmesser aufweisender Strömungsbahn Download PDF

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Publication number
EP0219974B1
EP0219974B1 EP86307161A EP86307161A EP0219974B1 EP 0219974 B1 EP0219974 B1 EP 0219974B1 EP 86307161 A EP86307161 A EP 86307161A EP 86307161 A EP86307161 A EP 86307161A EP 0219974 B1 EP0219974 B1 EP 0219974B1
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EP
European Patent Office
Prior art keywords
condenser
tubes
tube
headers
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.)
Revoked
Application number
EP86307161A
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English (en)
French (fr)
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EP0219974A3 (de
EP0219974A2 (de
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
Priority to EP93202885A priority Critical patent/EP0583851B1/de
Publication of EP0219974A2 publication Critical patent/EP0219974A2/de
Publication of EP0219974A3 publication Critical patent/EP0219974A3/de
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Publication of EP0219974B1 publication Critical patent/EP0219974B1/de
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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 condenser, and more particularly to a condenser for use in an air conditioning or refrigeration system for condensing a refrigerant.
  • the large tube size of such condensers means that 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 air cooled condenser suitable for use in a refrigeration or air conditioning system to condense a refrigerant vapour into a refrigerant liquid, comprises a pair of spaced headers for receiving refrigerant vapour and collecting condensed refrigerant; and a plurality of tubes extending in hydraulic parallel between said headers, each tube being in fluid communication with each said header and being elongate in transverse cross-section with the minor dimension of the cross-section aligned substantially perpendicular to the direction of air flow through the condenser is characterised in that each said tube defines a plurality of discrete hydraulically parallel fluid flow paths, each said fluid flow path having a hydraulic diameter in the range of 0.381 to 1.778mm (0.015 to 0.070 inches).
  • the preferred embodiment of the invention provides a condenser which has a lesser frontal area on the air side that is blocked by tubes allowing an increase in the air side heat exchange surface area without increasing air side pressure drop and without increasing vapour and/or condensate side pressure drop.
  • the tubes are flat tubes.
  • the plurality of flow paths in each tube are defined by an undulating spacer contained within the tube.
  • 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 may be defined by generally cylindrical tubes having facing openings, such as slots, for receiving respective ends of the condenser tubes.
  • FIG. 1 An exemplary embodiment of a condenser made according to the invention is illustrated in Figure 1 and is seen to include opposed, spaced, generally parallel headers 10 and 12.
  • the headers 10 and 12 are 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 US-A-4615385 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 vapour 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 parallel to 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 Figure 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 described embodiment of the invention, however, the desired support in a serpentine fin heat exchanger is accomplished by the fact that the spacer 40 and the crests thereof are bonded along its entire length to 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.
  • 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 0.381 to 1.778mm (0.015 to 0.070 inches). Given current assembly techniques known in the art, a hydraulic diameter of approximately 0.889mm (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 Figure 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 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 vapour and/or conduit side.
  • Figure 3 for example, on the right-hand side, plots the heat transfer rate against the cavity or hydraulic diameter at air flows varying from 12.74 to 90.61m 3 (450 to 3200 Standard Cubic Feet) per minute for production condenser cores made by the applicant. Heat transfer rate is plotted in kW (thousands of BTU per hour) and the hydraulic diameter is plotted in mm (inches).
  • the left of such data are computer generated curves based on a heat transfer model for a core made according to the present invention, the model constructed using empirically obtained data. Various points on the curves have been confirmed by actual tests.
  • the curves designated "A" represent heat transfer at the stated air flows for a core such as shown in Figure 1 having a frontal area of 0.186m- (two square feet) utilizing tubes approximately 0.61m (24 inches) long and having a 0.381mm (0.015 inch) tube wall thickness, a 13.51mm (0.532 inch) tube major dimension, 43.3°C (110°F) inlet air, 82.2°C (180°F) inlet temperature and 1.619 MPa (235 psig) pressure for R-12 and assuming 1.1 degree C (2 degree F) of subcooling of the exiting refrigerant after condensation.
  • the core was provided with 18 fins per 25.4mm (inch) between tubes and the fins were 15.88mm (0.625 inches) by 13.72mm (0.540 inches by 0.152mm (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 Figure 4, a heat transfer rate of 7.62kW (26,000 BTU per hour) at an air flow of 50.97m 3 (1800 Standard Cubic Feet) per minute.
  • the actual observed equivalence of the two cores occurred at 8.21kW (28,000 BTU per hour) and 56.63m 3 (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 an embodiment of the subject invention illustrate a considerable difference in the pressure drop of the refrigerant across the condenser.
  • a core made according to an embodiment of the invention when compared with the conventional core, holds less refrigerant.
  • the core of embodiment 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.
  • Figure 5 compares, at various air velocities, the heat transfer rate per unit mass of core of the conventional condenser (curve "K") versus heat transfer per unit mass of core of a condenser made according to the invention (curve “L").
  • heat transfer rate per unit mass is plotted in W kg -1 (BTU per pound) and air flow is plotted in m 3 (Standard Cubic Feet) per minute.
  • W kg -1 BTU per pound
  • m 3 Standard Cubic Feet
  • FIG. 6 in curve "M” thereon, illustrates the air side pressure drop, plotted in Pa (inches of water), for a conventional core and for a core according to the invention for various air flows plotted in m 3 (Standard Cubic Feet) per minute.
  • 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.

Claims (6)

  1. Luftgekühlter Kondensator, der sich zum Einsatz in einem Kühl- oder Klimasystem zum Kondensieren eines Kühlmitteldampfes zu einer Kühlmittelflüssigkeit eignet, wobei der Kondensator ein Paar beabstandeter Sammelrohre (10,12) zur Aufnahme von Kühlmitteldampf und zum Sammeln von kondensiertem Kühlmittel umfaßt; sowie eine Vielzahl von Röhren (20), die hydraulisch parallel zwischen den Sammelrohren verlaufen, wobei jede Röhre mit jedem der Sammelrohre in Fluidverbindung steht und im Querschnitt länglich ist, wobei die kleinere Abmessung des Querschnitts im wesentlichen senkrecht zur Richtung des Luftstroms durch den Kondensator ausgerichtet ist, dadurch gekennzeichnet, daß jede der Röhren eine Vielzahl getrennter, hydraulisch paralleler Fluidströmungswege aufweist, wobei jeder der Fluidströmungswege einen hydraulischen Durchmesser im Bereich von 0,381 bis 1,778 mm (0,015 bis 0,071 inch) aufweist.
  2. Kondensator nach Anspruch 1, wobei die Röhren abgeflachte Röhren sind und die Vielzahl von Strömungswegen in jeder Röhre durch einen wellenförmigen Abstandhalter (40) gebildet wird, der in der Röhre enthalten ist.
  3. Kondensator nach Anspruch 1 oder Anspruch 2, der des weiteren Rippen (34) an den Außenseiten der Kondensatorröhren enthält.
  4. Kondensator nach einem der vorangehenden Ansprüche, der Rippen (34) enthält, die sich zwischen den Außenseiten benachbarter Kondensatorröhren erstrecken.
  5. Kondensator nach einem der vorangehenden Ansprüche, wobei die Sammelrohre durch im allgemeinen zylindrische Röhren gebildet werden und einander zugewandte Öffnungen (14) aufweisen, die entsprechende Enden (16, 18) der Kondensatorröhren aufnehmen.
  6. Kondensator nach Anspruch 5, wobei die Öffnungen eine Reihe länglicher Schlitze (14) sind, wobei die Schlitze an einem Sammelrohr den Schlitzen an dem anderen Sammelrohr zugewandt sind; und wobei die Kondensatorröhren abgeflachte Röhren (20) mit einander gegenüberliegenden Enden (16, 18) sind, die den Schlitzen entsprechend angeordnet sind.
EP86307161A 1985-10-02 1986-09-17 Verflüssiger mit einen kleinen hydraulischen Durchmesser aufweisender Strömungsbahn Revoked EP0219974B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP93202885A EP0583851B1 (de) 1985-10-02 1986-09-17 Wärmetauscher

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US78308785A 1985-10-02 1985-10-02
US90269786A 1986-09-05 1986-09-05
US902697 1986-09-05
US783087 2001-02-15

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP93202885.5 Division-Into 1986-09-17
EP93202885A Division EP0583851B1 (de) 1985-10-02 1986-09-17 Wärmetauscher

Publications (3)

Publication Number Publication Date
EP0219974A2 EP0219974A2 (de) 1987-04-29
EP0219974A3 EP0219974A3 (de) 1989-08-02
EP0219974B1 true EP0219974B1 (de) 1996-11-06

Family

ID=27120095

Family Applications (2)

Application Number Title Priority Date Filing Date
EP86307161A Revoked EP0219974B1 (de) 1985-10-02 1986-09-17 Verflüssiger mit einen kleinen hydraulischen Durchmesser aufweisender Strömungsbahn
EP93202885A Revoked EP0583851B1 (de) 1985-10-02 1986-09-17 Wärmetauscher

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP93202885A Revoked EP0583851B1 (de) 1985-10-02 1986-09-17 Wärmetauscher

Country Status (9)

Country Link
EP (2) EP0219974B1 (de)
JP (1) JPS62175588A (de)
KR (1) KR950007282B1 (de)
AT (2) ATE160441T1 (de)
BR (1) BR8604768A (de)
CA (1) CA1317772C (de)
DE (2) DE3650648T2 (de)
ES (1) ES2002789A6 (de)
MX (1) MX167593B (de)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0255313A2 (de) * 1986-07-29 1988-02-03 Showa Aluminum Kabushiki Kaisha Verflüssiger
EP0374896A2 (de) * 1988-12-22 1990-06-27 THERMAL-WERKE Wärme-, Kälte-, Klimatechnik GmbH Flachrohrverflüssiger, Herstellungsverfahren und Anwendungen
DE3843305A1 (de) * 1988-12-22 1990-06-28 Thermal Waerme Kaelte Klima Verfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
US5099576A (en) * 1989-08-29 1992-03-31 Sanden Corporation Heat exchanger and method for manufacturing the heat exchanger
EP0499390A1 (de) * 1991-02-11 1992-08-19 Modine Manufacturing Company Wärmetauscher mit reduzierter Kerntiefe
WO1992015833A1 (en) * 1991-03-11 1992-09-17 Modine Manufacturing Company Condenser with small hydraulic diameter flow path
US5190100A (en) * 1986-07-29 1993-03-02 Showa Aluminum Corporation Condenser for use in a car cooling system
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5458190A (en) * 1986-07-29 1995-10-17 Showa Aluminum Corporation Condenser
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
USRE35742E (en) * 1986-07-29 1998-03-17 Showa Aluminum Corporation Condenser for use in a car cooling system
EP0990828A2 (de) 1998-10-01 2000-04-05 Behr GmbH & Co. Mehrkanal-Flachrohr
DE10025486A1 (de) * 2000-05-23 2001-11-29 Behr Gmbh & Co Wärmeübertragerblock
US6622785B2 (en) 2001-04-28 2003-09-23 Behr Gmbh & Co. Folded multi-passageway flat tube
US8166776B2 (en) 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger
US8281615B2 (en) 2006-11-22 2012-10-09 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1317772C (en) * 1985-10-02 1993-05-18 Leon A. Guntly Condenser with small hydraulic diameter flow path
US4688311A (en) * 1986-03-03 1987-08-25 Modine Manufacturing Company Method of making a heat exchanger
JPH0544679Y2 (de) * 1988-07-12 1993-11-12
DE3843306A1 (de) * 1988-12-22 1990-06-28 Thermal Waerme Kaelte Klima Flachrohrverfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
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
US6016864A (en) * 1996-04-19 2000-01-25 Heatcraft Inc. Heat exchanger with relatively flat fluid conduits
EP1223391B8 (de) 1996-12-25 2005-12-21 Calsonic Kansei Corporation Kondensatoraufbaustruktur
GB2346680A (en) 1999-02-11 2000-08-16 Llanelli Radiators Ltd Condenser
EP1065454A1 (de) 1999-07-02 2001-01-03 Modine Manufacturing Company Luftgekühlter Kondensator
DE10054158A1 (de) 2000-11-02 2002-05-08 Behr Gmbh Mehrkammerrohr mit kreisförmigen Strömungskanälen
JP2002318086A (ja) * 2001-04-16 2002-10-31 Japan Climate Systems Corp 熱交換器用チューブ
EP1265046B1 (de) 2001-06-07 2005-11-23 Behr GmbH & Co. KG Rippe, Rohr und Wärmetauscher
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US8281615B2 (en) 2006-11-22 2012-10-09 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
US8166776B2 (en) 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger

Also Published As

Publication number Publication date
DE3650658T2 (de) 1998-05-14
EP0583851B1 (de) 1997-11-19
MX167593B (es) 1993-03-31
EP0219974A3 (de) 1989-08-02
DE3650658D1 (de) 1998-01-02
EP0583851A3 (de) 1994-03-09
ATE160441T1 (de) 1997-12-15
EP0219974A2 (de) 1987-04-29
JPS62175588A (ja) 1987-08-01
KR880004284A (ko) 1988-06-03
ATE145051T1 (de) 1996-11-15
KR950007282B1 (ko) 1995-07-07
CA1317772C (en) 1993-05-18
EP0583851A2 (de) 1994-02-23
DE3650648D1 (de) 1997-10-30
ES2002789A6 (es) 1988-10-01
BR8604768A (pt) 1987-06-30
DE3650648T2 (de) 1999-04-15
JPH0587752B2 (de) 1993-12-17

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