EP1395786B1 - Condenseur pour refroidisseurs refroidis par air - Google Patents

Condenseur pour refroidisseurs refroidis par air Download PDF

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Publication number
EP1395786B1
EP1395786B1 EP02739443A EP02739443A EP1395786B1 EP 1395786 B1 EP1395786 B1 EP 1395786B1 EP 02739443 A EP02739443 A EP 02739443A EP 02739443 A EP02739443 A EP 02739443A EP 1395786 B1 EP1395786 B1 EP 1395786B1
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EP
European Patent Office
Prior art keywords
heat exchanger
flow paths
multiplicity
coil assembly
parallel
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.)
Expired - Lifetime
Application number
EP02739443A
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German (de)
English (en)
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EP1395786A1 (fr
Inventor
Michael L. Kraay
Paul R. Glamm
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.)
Trane International Inc
Original Assignee
American Standard International Inc
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Filing date
Publication date
Application filed by American Standard International Inc filed Critical American Standard International Inc
Publication of EP1395786A1 publication Critical patent/EP1395786A1/fr
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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
    • F28F1/02—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
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • 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

  • the present invention is directed to air cooled condensers for heating, ventilating and air conditioning (HVAC) systems. More specifically, the present invention is directed to aluminum heat exchangers for use in large air cooled air conditioning chillers, such chillers cooling a transport fluid for use in air conditioning elsewhere.
  • HVAC heating, ventilating and air conditioning
  • the present invention applies to a condenser using microchannel tubing, also known as parallel flow tubing or multi-path tubing.
  • HVAC condensers presently use fin and tube coils, primarily with copper tubes and aluminum fins. A significant weight reduction of the overall unit could be accomplished if the tubes were also formed of aluminum and then brazed or glued to the fins. Small sized brazed aluminum heat exchangers as microchannel tubing are used in the automotive industry. However, the application and the sizes are distinct. Automobile radiators are not as concerned about efficiency as the HVAC industry is. Also, simply resizing an automotive heat exchanger does not provide an optimum solution.
  • U. S. Patent 4,998,580 to Guntly et al. and U. S. Patent 5,372,188 to Dudley et al. are directed to a condenser with a small diameter hydraulic flow path where hydraulic diameter is conventionally defined as four times the cross sectional area of the flow path divided by the wetted perimeter of the flow path.
  • the Guntly et al. patent requires hydraulic diameters of about 0.07 inches and less while the Dudley et al. patent requires a hydraulic diameter in the range of 0.015 to 0.040 inches. This technology is used in the automotive industry and is not optimum for an air cooled chiller application.
  • GB 2 346 680 discloses a condenser for use in an air conditioning or refrigeration system having refrigerant flowpaths extending adjacent one another and grouped such that adjacent groups carry refrigerant passes in opposed directions across the condenser.
  • the arrangement of groups is such that the number of refrigerant passes across the condenser is five or above.
  • the refrigerant flowpaths may comprise tubes extending across the condenser.
  • EP 0 990 828 discloses a flat tube containing parallel flow channels, which have oval cross sections, and/or the outer tube surfaces have a corrugated contour corresponding to the flow channels.
  • the pipe In vertical direction, the pipe is thinner between two flow channels than in the area of a flow channel.
  • the large axis of the flow channels are at right angles or parallel to the transverse tube direction, or are angled relative to it.
  • US 5 967 228 discloses a heat exchanger for an air conditioner outdoor unit including tubing of the microchannel type which is internally partitioned into separate, parallel refrigerant flow passages and a wrapping of heat conductive flexible heat transfer material, commonly known as spine fin.
  • the heat exchanger provides for greater heat transfer and a more compact package. Further, such heat exchangers allow for a reduced refrigerant charge in the air conditioning unit in which they are used.
  • US 6 062 303 discloses a multiflow type condenser for an automobile air conditioner comprising: a pair of header pipes disposed in parallel with each other and arranged to have an inlet and an outlet; a plurality of flat tubes each connected to said header pipes at opposite ends thereof, each of said flat tubes having a plurality of inside fluid paths, a hydraulic diameter of said inside fluid paths being in the range of about 1 to 1.7 mm; a plurality of corrugated fins each disposed between adjacent flat tubes; at least a pair of baffles disposed in said header pipes one by one; each of said baffles having a projection inserted into a slit provided with each header pipes and dividing each header pipes into a plurality of chambers; at least one by-pass passageway formed in the baffles to route a vapor-abundant phase of said refrigerant from an upper chamber to a lower chamber within the same header pipes by providing a communication path between the adjacent chambers; a ratio of a hydraulic diameter of said by-pass passageway over
  • GB 2 133 525 discloses a flat tube of an evaporator for automotive air conditioners which is formed such that the upstream end portion of the tube with respect to the air stream flowing along the flat tube has a thicker wall than that of the remaining downstream portion of the same, thereby to cope with corrosive environments.
  • the thicker upstream end portion effectively prevents the same from being severely corroded when used in areas where the atmosphere includes relatively large amounts of salt and humidity.
  • US 5 067 560 discloses a condenser for an air conditioning or refrigeration system having first, second, third and fourth condenser coils arranged in a modified "W" arrangement.
  • the present invention is directed to solving the problem in the prior art systems.
  • the present invention provides a heat exchanger.
  • the heat exchanger comprises a first coil assembly including an inlet manifold, an outlet manifold parallel to and spaced from the inlet manifold; and a plurality of tubes each operably connected to and linking the inlet and the outlet manifolds.
  • Each tube has a multiplicity of flow paths and a hydraulic diameter in the range of 0.07 ⁇ to HD ⁇ 0. 30 inches (1.8 ⁇ HD ⁇ 7.6mm).
  • the present invention also provides an air conditioning system including a compressor, a first heat exchanger as defined above, a fan motivating air across the first heat exchanger, an expansion device and a second heat exchanger serially linked into an air conditioning cycle by tubing.
  • the present invention further provides a method of manufacturing an air cooled chiller.
  • the method further comprises the step of transferring heat through a wall enclosing said flow paths and to a fluid contained therein.
  • FIG. 1 shows an air conditioning system 10 including a compressor 12, a first heat exchanger 14 fimctioning as a condenser, an expansion device 16 such as an expansion valve, and a second heat exchanger 18 functioning as an evaporator.
  • the compressor 12, the first heat exchanger 14, the expansion device 16, and the second heat exchanger 18 are serially linked in an air conditioning cycle by tubing 20.
  • the first heat exchanger 14 functions as a condenser in releasing heat from the system, while the second heat exchanger 18 functions as an evaporator in cooling a fluid transported to and from the heat exchanger 18 by means of conduit 22.
  • Such systems are generally well known and are sold by The Trane Company, a Division of American Standard Inc., under the registered trademarks CenTraVac and Series R
  • the condenser 14 is preferably formed of aluminum and has an inlet manifold 30 receiving hot gaseous refrigerant from the conduit 20 and the compressor 12. This hot gaseous refrigerant is distributed by the inlet manifold 30 to a plurality of tubes 32. These tubes 32 conduct the hot gaseous refrigerant from the inlet manifold 30 through the tubes 32 to an outlet manifold 34. In the process, the hot gaseous refrigerant is condensed and returns to the conduit 20 as a liquid where it is modulated through the expansion device 16 to the second heat exchanger 18.
  • the tubes 32 are preferably microchannel or parallel flow tubing. Microchannel tubing is shown by U. S. 5,967,228.
  • Air is moved over the tubes 32 by an air moving device 36 such as a fan either to or away from the fan 36 as indicated by arrow 38.
  • an air moving device 36 such as a fan either to or away from the fan 36 as indicated by arrow 38.
  • fins 40 are provided to enhance the heat transfer. These fins 40 will be subsequently described with reference to Figure 4.
  • the preferred embodiment of the tubes 32 is shown in Figure 2 and an alternative embodiment is shown in Figure 3.
  • the heat transfer tube 32 shown in Figure 2 includes a multiplicity of adjacent flow paths 40, 42, 44, 46 and 48 throughout the length of the tube 32 and surrounded by a common tube wall 50.
  • the adjacent flow paths 40 through 48 are separated by barrier walls 52,54,56 and 58 respectively.
  • the flow paths 40 and 48 are of similar shape and cross sectional area and the flow paths 42, 44 and 46 are of similar shape and cross sectional area.
  • the flow paths 40,42,44,46 and 48 are sized and shaped to form a preferred hydraulic diameter HD within the range of: 0.07 ⁇ HD ⁇ 0.30 inches ( 1.8 ⁇ HD ⁇ 7.6 mm ) .
  • Empirical study shows that a 100 ton air cooled chiller should have a hydraulic diameter of at least 0.07 inches (1.8mm) whereas a 240 ton air cooled chiller should have a hydraulic diameter of about 0.14 inches (3.6mm).
  • Linear extrapolation shows that a 480 ton air cooled chiller should have a hydraulic diameter of about 0.26 inches (6.6mm).
  • the preferred range of hydraulic diameters is 0.07 ⁇ HD ⁇ 0.30 inches (1.8 ⁇ HD ⁇ 3.6 mm) with an intermediate range of 0.07 ⁇ HD ⁇ 0.26 inches (1.8 ⁇ HD ⁇ 6.6 mm).
  • An optimum range appears to be 0.07 ⁇ HD ⁇ 0.14 inches (1.8 ⁇ HD ⁇ 3.6 mm), with preferred hydraulic diameter of 0.14 inches (3.6mm).
  • the total cross sectional area of the flow paths 40, 42, 44, 46 and 48 is either measured or calculated, and the total wetted perimeter for those same flow paths is determined in a similar manner.
  • Figure 4a shows a first fin embodiment where a corrugated fin 40a is used.
  • Figure 4b shows the use of a sinusoidal fin 40b.
  • Figure 5 is directed to a multiple coil assembly embodiment of the invention in contrast to Figure 1 which shows a single coil assembly 70.
  • multiple coil assemblies 70,72,74 and 76 might be used.
  • the arrangement shown in Figure 5 is described in U.S. 5,067,560.
  • the control of such a condenser is described in U.S. 5,138,844.
  • the first coil assembly 70 is basically perpendicular to ground and a second coil assembly 76 is spaced from the first coil assembly 70 and is generally arranged in a parallel plane.
  • a third coil assembly 72 is positioned between the first and second coil assembly 70,76 and lying in a plane which is not parallel to the planes of first and second coil assemblies 70,76.
  • a fourth coil assembly 74 also lies between the first and second coil assembly 70,76 at a line in a plane which is not parallel to the planes of the first and second coil assembly 70,76.
  • the fourth coil assembly 74 preferably is at a complimentary angle to the third coil assembly 72.
  • the potential airflow paths are shown by arrows 80.

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

Claims (22)

  1. Echangeur de chaleur (14), comprenant :
    un premier ensemble de serpentins comprenant
    un collecteur d'entrée (30) ;
    un collecteur de sortie (34) parallèle au collecteur d'entrée et espacé de celui-ci ; et
    une pluralité de tubes (32), chacun étant raccordé de façon fonctionnelle aux collecteurs d'entrée (30) et de sortie (34), et les reliant, chaque tube (32) présentant une multitude de trajets de circulation selon un agencement parallèle, caractérisé par le fait que chaque trajet de la multitude de trajets de circulation présente au moins des première et seconde formes en section transversale et un diamètre hydraulique HD dans la plage de 0,07 < HD < 0,30 pouce (1,8 mm < HD < 7,6 mm) .
  2. Echangeur de chaleur (14) selon la revendication 1, dans lequel la multitude de trajets de circulation (40 à 48) sont disposés selon un agencement parallèle.
  3. Echangeur de chaleur (14) selon la revendication 2, comprenant en outre des ailettes (40) disposées dans une relation de transfert thermique entre des tubes adjacents parmi la pluralité de tubes.
  4. Echangeur de chaleur (14) selon la revendication 3, dans lequel les ailettes (40) présentent une forme sinusoïdale.
  5. Echangeur de chaleur selon la revendication 3, dans lequel les ailettes (40) présentent une forme ondulée.
  6. Echangeur de chaleur (14) selon la revendication 3, comprenant en outre un dispositif (36) déplaçant l'air au travers du premier ensemble de serpentins et l'échangeur de chaleur (14) est principalement formé d'aluminium.
  7. Echangeur de chaleur (14) selon la revendication 3, comprenant en outre un second ensemble de serpentins parallèle au premier ensemble de serpentins et espacé de celui-ci, chaque ensemble de serpentins étant situé dans des premier et second plans respectifs qui sont sensiblement parallèles l'un à l'autre.
  8. Echangeur de chaleur (14) selon la revendication 7, comprenant un troisième ensemble de serpentins situé entre les premier et second ensembles de serpentins et situé dans un troisième plan qui n'est pas parallèle aux premier et second plans.
  9. Echangeur de chaleur selon la revendication 8, comprenant en outre un quatrième ensemble de serpentins entre les premier et second ensembles de serpentins et situé dans un quatrième plan qui n'est pas parallèle aux premier et second plans où l'angle du quatrième plan et l'angle du troisième plan sont complémentaires.
  10. Système de conditionnement d'air comprenant :
    un compresseur (12),
    un premier échangeur de chaleur (14) selon l'une quelconque des revendications 1 à 11,
    un ventilateur (36) déplaçant l'air au travers du premier échangeur de chaleur (14),
    un dispositif de détente (16) et un second échangeur de chaleur (18) reliés en série dans un cycle de conditionnement d'air par des tubes.
  11. Système selon la revendication 10, dans lequel la multitude de trajets de circulation adjacents dans le premier échangeur de chaleur (14) sont formés d'aluminium.
  12. Système selon la revendication 10 ou 11, dans lequel le premier échangeur de chaleur (14) comprend des premier, second, troisième et quatrième ensembles de serpentins, chaque ensemble de serpentins comprenant la multitude de trajets de circulation, et lesdits premier, second, troisième et quatrième ensembles de serpentins présentant chacun une dimension plane de sorte que les ensembles de serpentins forment un profil en W lors d'une observation dans une direction perpendiculaire à un plan commun aux premier, second, troisième et quatrième ensembles de serpentins.
  13. Système selon les revendications 10 à 12, dans lequel la multitude de trajets de circulation présentent des première et seconde formes différentes.
  14. Système selon les revendications 10 à 13, dans lequel la première forme est rectangulaire et la seconde forme comprend une surface arquée.
  15. Procédé de fabrication d'un refroidisseur refroidi par air comprenant les étapes consistant à :
    former un premier échangeur de chaleur (14) destiné à inclure une multitude de trajets de circulation adjacents présentant au moins des première et seconde formes en section transversale, où les trajets de circulation sont dimensionnés et formés à un diamètre hydraulique HD préféré dans la plage de 0,07 < HD < 0,30 pouce (1,8 < HD < 7,6 mm) ;
    procurer un ventilateur (36) pour déplacer l'air au travers de la multitude de trajets de circulation adjacents (40 à 48) ;
    procurer un compresseur (12), un second échangeur de chaleur (18) et un dispositif de détente (16) ; et
    relier le compresseur (12), le premier échangeur de chaleur (14), le dispositif de détente (16) et le second échangeur de chaleur (18) en série dans un cycle de conditionnement d'air par des tubes.
  16. Procédé selon la revendication 15, comprenant l'étape supplémentaire consistant à :
    configurer de manière adaptative le second échangeur de chaleur (18) pour refroidir la température d'un liquide.
  17. Procédé selon la revendication 15, comprenant l'étape supplémentaire consistant à :
    former le premier échangeur de chaleur (14) à partir d'aluminium.
  18. Procédé selon la revendication 17, comprenant l'étape supplémentaire consistant à interconnecter des trajets adjacents parmi la multitude de trajets de circulation avec une ailette ondulée ou sinusoïdale (40).
  19. Procédé selon la revendication 18, comprenant l'étape consistant à agencer la multitude de trajets de circulation dans un plan commun.
  20. Procédé selon l'une quelconque des revendications 15 à 19, comprenant en outre l'étape consistant à transférer de la chaleur au travers d'une paroi enfermant lesdits trajets de circulation et vers un fluide contenu dans ceux-ci.
  21. Procédé selon la revendication 20, comprenant la formation de la paroi à partir d'aluminium.
  22. Procédé selon les revendications 15 à 21, comprenant la formation des trajets de circulation en des première et seconde formes en section transversale distinctes.
EP02739443A 2001-06-14 2002-05-24 Condenseur pour refroidisseurs refroidis par air Expired - Lifetime EP1395786B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US881638 1986-07-03
US09/881,638 US20020195240A1 (en) 2001-06-14 2001-06-14 Condenser for air cooled chillers
PCT/US2002/016725 WO2002103270A1 (fr) 2001-06-14 2002-05-24 Condenseur pour refroidisseurs refroidis par air

Publications (2)

Publication Number Publication Date
EP1395786A1 EP1395786A1 (fr) 2004-03-10
EP1395786B1 true EP1395786B1 (fr) 2006-04-26

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EP02739443A Expired - Lifetime EP1395786B1 (fr) 2001-06-14 2002-05-24 Condenseur pour refroidisseurs refroidis par air

Country Status (5)

Country Link
US (2) US20020195240A1 (fr)
EP (1) EP1395786B1 (fr)
CN (1) CN1295476C (fr)
CA (1) CA2450306C (fr)
WO (1) WO2002103270A1 (fr)

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Also Published As

Publication number Publication date
EP1395786A1 (fr) 2004-03-10
CA2450306C (fr) 2008-12-16
CA2450306A1 (fr) 2002-12-27
CN1295476C (zh) 2007-01-17
CN1516804A (zh) 2004-07-28
US20020195240A1 (en) 2002-12-26
WO2002103270A1 (fr) 2002-12-27
US20040134226A1 (en) 2004-07-15

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