EP1395786B1 - Verflüssiger für luftgekühlte kühler - Google Patents

Verflüssiger für luftgekühlte kühler 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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English (en)
French (fr)
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EP1395786A1 (de
Inventor
Michael L. Kraay
Paul R. Glamm
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Trane International Inc
Original Assignee
American Standard International Inc
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Filing date
Publication date
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Publication of EP1395786A1 publication Critical patent/EP1395786A1/de
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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)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (22)

  1. Wärmetauscher (14), umfassend:
    eine ersten Spulenanordnung, umfassend
    einen Einlassverteiler (30);
    einen Auslassverteiler (34), welcher parallel zum Einlassverteiler liegt und zu diesem beabstandet ist; und
    eine Mehrzahl von Rohren (32), von denen jedes betriebsfähig mit dem Einlassverteiler (30) und dem Auslassverteiler (34) verbunden ist und die beiden miteinander verbindet, wobei jedes Rohr (32) eine Vielzahl von Flusspfaden in einer parallelen Anordnung aufweist, gekennzeichnet dadurch, dass jeder der Vielzahl der Flusspfade wenigstens eine erste und eine zweite Querschnittsform und einen hydraulischen Durchmesser HD im Bereich von 0,07 < HD < 0,30 Inch (1,8mm < HD < 7,6mm) aufweist.
  2. Wärmetauscher (14) gemäß Anspruch 1, wobei die Vielzahl der Flusspfade (40-48) in paralleler Anordnung vorliegt.
  3. Wärmetauscher (14) gemäß Anspruch 2, des Weiteren umfassend Kühlrippen (40), welche in Wärmeübertragungsbeziehung zwischen benachbarten Rohren der Mehrzahl von Rohren angeordnet sind.
  4. Wärmetauscher (14) gemäß Anspruch 3, wobei die Kühlrippen (40) eine sinusförmige Form aufweisen.
  5. Wärmetauscher gemäß Anspruch 3, wobei die Kühlrippen (40) eine gewellte Form aufweisen.
  6. Wärmetauscher (14) gemäß Anspruch 3, des Weiteren umfassend eine Vorrichtung (36), welche Luft über der ersten Spulenanordnung bewegt, und wobei der Wärmetauscher (14) in erster Linie aus Aluminium ausgebildet ist.
  7. Wärmetauscher (14) gemäß Anspruch 3, des Weiteren umfassend eine zweite Spulenanordnung, welche parallel zur ersten Spulenanordnung liegt und von dieser beabstandet ist, wobei jede Spulenanordnung in der jeweiligen ersten beziehungsweise zweiten Ebene liegt, welche im Wesentlichen parallel zueinander liegen.
  8. Wärmetauscher (14) gemäß Anspruch 7, umfassend eine dritte Spulenanordnung, welche zwischen der ersten und der zweiten Spulenanordnung angeordnet ist und in einer dritten Ebene liegt, die nicht parallel zur ersten und zur zweiten Ebene ist.
  9. Wärmetauscher gemäß Anspruch 8, umfassend eine vierte Spulenanordnung, welcher zwischen der ersten und der zweiten Spulenanordnung angeordnet ist und in einer vierten Ebene liegt, die nicht parallel zur ersten und zur zweiten Ebene liegt, wobei der Winkel der vierten Ebene komplementär zum Winkel der dritten Ebene ist.
  10. Klimatisierungssystem, umfassend:
    einen Verdichter (12),
    einen Wärmetauscher (14) gemäß einem der Ansprüche 1 bis 11,
    einen Ventilator (36), welcher Luft über der ersten Wärmetauscher (14) anregt,
    eine Ausdehnungsvorrichtung (16) und einen zweiten Hitzeaustauscher (18), welcher seriell in einen Klimatisierungszyklus durch Verrohrung eingebunden ist.
  11. System gemäß Anspruch 10, wobei die Vielzahl der benachbarten Flusspfade im ersten Wärmetauscher (14) aus Aluminium ausgebildet ist.
  12. System gemäß Anspruch 10 oder 11, wobei der erste Wärmetauscher (14) erste, zweite, dritte und vierte Spulenanordnungen umfasst, wobei jede Spulenanordnung eine Vielzahl von Flusspfaden umfasst, und die erste, die zweite, die dritte und die vierte Spulenanordnung jeweils eine ebene Abmessung aufweist, so dass die Spulenanordnungen eine W-Form aufweisen, wenn sie in einer Richtung betrachtet werden, die senkrecht zu einer allgemeinen Ebene für die erste, die zweite, die dritte und die vierte Spulenanordnung ist.
  13. System gemäß den Ansprüchen 10 bis 12, wobei die Vielzahl der Flusspfade in einer ersten und einer zweiten Form vorliegt.
  14. System gemäß den Ansprüchen 10 bis 13, wobei die erste Form rechteckig ist und die zweite Form eine gekrümmte Fläche aufweist.
  15. Verfahren zur Herstellung eines luftgekühlten Kühlers, umfassend die Schritte:
    Ausbilden eines ersten Wärmetauschers (14), um eine Vielzahl von benachbarten Flusspfaden zu umfassen, welche wenigstens erste und zweite Querschnittsformen aufweisen, wobei die Flusspfade für einen bevorzugten hydraulischen Durchmesser HD im Bereich von 0,07 < HD < 0,30 Inch (1,8mm < HD < 7,6mm) bemessen und geformt sind;
    Vorsehen eines Ventilators (36), um Luft über die Vielzahl der benachbarten Flusspfade (40-48) zu bewegen;
    Vorsehen eines Verdichters (12), eines zweiten Wärmetauschers (18) und einer Ausdehnungsvorrichtung (16); und
    Verbinden des Verdichters (12), des ersten Wärmetauschers (14), der Ausdehnungsvorrichtung (16) und des zweiten Wärmetauschers (18) seriell in einen Klimatisierungszyklus durch Verrohrung.
  16. Verfahren gemäß Anspruch 15, umfassend den weiteren Schritt:
    anpassendes Konfigurieren des zweiten Wärmetauschers (18), um die Temperatur einer Flüssigkeit abzukühlen.
  17. Verfahren gemäß Anspruch 15, umfassend den weiteren Schritt:
    Ausbilden des ersten Wärmetauschers (14) aus Aluminium.
  18. Verfahren gemäß Anspruch 17, umfassend den weiteren Schritt des Miteinanderverbindens benachbarter Flusspfade der Vielzahl an Flusspfaden mit einer gewellten oder sinusförmigen Kühlrippe (40).
  19. Verfahren gemäß Anspruch 18, umfassend den Schritt des Anordnens der Vielzahl von Flusspfaden in einer gemeinsamen Ebene.
  20. Verfahren gemäß einem der Ansprüche 15 bis 19, des Weiteren umfassend den weiteren Schritt des Übertragens von Wärme durch eine Wand, welche die Flusspfade umschließt, und auf ein Fluid, welches darin enthalten ist.
  21. Verfahren gemäß Anspruch 20, umfassend das Ausbilden der Wand aus Aluminium.
  22. Verfahren gemäß den Ansprüchen 15 bis 21, umfassend das Ausbilden der Flusspfade in eine erste und eine zweite unterschiedliche Querschnittsform.
EP02739443A 2001-06-14 2002-05-24 Verflüssiger für luftgekühlte kühler Expired - Lifetime EP1395786B1 (de)

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 (en) 2001-06-14 2002-05-24 Condenser for air cooled chillers

Publications (2)

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

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US (2) US20020195240A1 (de)
EP (1) EP1395786B1 (de)
CN (1) CN1295476C (de)
CA (1) CA2450306C (de)
WO (1) WO2002103270A1 (de)

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Also Published As

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

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