WO2002103270A1 - Condenser for air cooled chillers - Google Patents
Condenser for air cooled chillers Download PDFInfo
- Publication number
- WO2002103270A1 WO2002103270A1 PCT/US2002/016725 US0216725W WO02103270A1 WO 2002103270 A1 WO2002103270 A1 WO 2002103270A1 US 0216725 W US0216725 W US 0216725W WO 02103270 A1 WO02103270 A1 WO 02103270A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat exchanger
- flow paths
- multiplicity
- coil assembly
- hydraulic diameter
- Prior art date
Links
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. In particular the present invention applies to a condenser using microchannel tubing, also known as parallel flow tubing or multi-path tubing.
- HVAC heating, ventilating and air conditioning
- 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.
- the present invention is directed to solving the problem in the prior art systems . It is an object, feature and advantage of the present invention to provide an aluminum heat exchanger with multiple parallel flow paths for use in a large chiller for air conditioning purposes. It is a further object, feature and an advantage of the present invention to significantly reduce the weight of a large chiller. It is an object, feature and advantage of the present invention to provide a heat exchanger with multiple parallel flow paths having a hydraulic diameter greater than 0.07 inches and less than 0.30 inches. It is a further object, feature and advantage of the present invention to provide a hydraulic diameter in the range greater than 0.07 inches and less than or equal to 0.26 inches.
- 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 0.05 ⁇ to HD ⁇ 0.30.
- the present invention also provides an air conditioning system including a compressor, a first heat exchanger, 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 first heat exchanger includes an inlet manifold, an outlet manifold, and a multiplicity of adjacent flow paths surrounded by a common tube wall and interconnecting the inlet manifold with the outlet manifold.
- the present invention further provides a method of manufacturing an air cooled chiller.
- the present invention still further provides a method of transferring heat in a heat exchanger.
- the method comprises the steps of: forming a first heat exchanger to include a multiplicity of adjacent flow paths wherein the flow paths are sized and shaped to a preferred hydraulic diameter HD within the range of 0.7 ⁇ HD ⁇ 0.30 inches where hydraulic diameter HD as defined as four times a cross sectional area divided by a total wetted perimeter; and transferring heat thru a wall enclosing said flow paths and to a fluid contained therein.
- FIG. 1 is a block diagram of an air cooled chiller system in accordance with the present invention.
- Figure 2 shows a first preferred embodiment of the present invention taken along lines 2-2 of Figure 1.
- Figure 3 is an alternative embodiment of the multi- path tubes shown in Figure .
- Figures 4a and 4b are diagrams of fins used in the heat exchanger shown in Figure 1.
- Figure 5 is a block diagram of a multiple coil assembly configuration as a preferred embodiment of Figure 1.
- FIG. 1 shows an air conditioning system 10 including a compressor 12, a first heat exchanger 14 functioning 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
- 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 present invention is directed to an improved condenser 14.
- This improved 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.
- 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 applicant's U.S. Patent 5,967,228 to Bergman et al . which is assigned to the assignee of the present invention and hereby incorporated by reference.
- 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:
- Hydraulic diameter is conventionally calculated according to the following formula:
- Hydraulic Diameter (HD) cross sectional area X 4 total wetted perimeter
- Empirical study shows that a 100 ton air cooled chiller should have a hydraulic diameter of at least 0.07 whereas a 240 ton air cooled chiller should have a hydraulic diameter of about 0.14 inches.
- Linear extrapolation shows that a 480 ton air cooled chiller should have a hydraulic diameter of about 0.26 inches.
- the preferred range of hydraulic diameters is 0.07 ⁇ HD ⁇ 0.30 with an intermediate range of 0.07 ⁇ HD ⁇ 0.26.
- An optimum range appears to be 0.07 ⁇ HD ⁇ 0.14, with preferred hydraulic diameter of 0.14.
- 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.
- exemplary calculations are performed for the alternative embodiment shown in Figure 3.
- like reference numerals are used to denote like elements.
- each of the multiplicity of flow paths has an identical size and shape 60.
- the cross sectional area for these multiplicity of flow paths 60 can be determined by taking an individual flow path 60a, determining a height 62 and a width 64, and multiplying the height 62 and width 64 together to determine an area for a single flow path 60a.
- the total cross sectional area for the tube 32 is determined by multiplying by the number of flow paths, in this case 5, by the cross-sectional area per flow path leading to the calculation that the total cross sectional area equals 5 times the height 62 time the width 64.
- the wetted perimeter for any individual flow path 60 can be calculated as two heights (62) plus two widths (64) .
- Total wetted perimeter can be determined by multiplying the wetted perimeter for any particular flow path by the number of individual flow paths 60, in this case 5, to result in a total wetted perimeter of 5 times (2H plus 2 ) . This results in a hydraulic diameter according to the following formula:
- HD 10 (HXW) X 4 /20 (H+ )
- 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 applicant's previous U.S. Patent 5,067,560 to Carey et al . which is assigned to the assignee of the present invention and hereby incorporated by reference.
- the control of such a condenser is described in applicant's U.S. Patent 5,138,844 to Clanin et al . which is assigned to the assignee of the present invention and also incorporated by reference .
- 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.
Landscapes
- 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)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA002450306A CA2450306C (en) | 2001-06-14 | 2002-05-24 | Condenser for air cooled chillers |
EP02739443A EP1395786B1 (en) | 2001-06-14 | 2002-05-24 | Condenser for air cooled chillers |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/881,638 | 2001-06-14 | ||
US09/881,638 US20020195240A1 (en) | 2001-06-14 | 2001-06-14 | Condenser for air cooled chillers |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002103270A1 true WO2002103270A1 (en) | 2002-12-27 |
Family
ID=25378876
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2002/016725 WO2002103270A1 (en) | 2001-06-14 | 2002-05-24 | Condenser for air cooled chillers |
Country Status (5)
Country | Link |
---|---|
US (2) | US20020195240A1 (en) |
EP (1) | EP1395786B1 (en) |
CN (1) | CN1295476C (en) |
CA (1) | CA2450306C (en) |
WO (1) | WO2002103270A1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
US8166776B2 (en) | 2007-07-27 | 2012-05-01 | Johnson Controls Technology Company | Multichannel heat exchanger |
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 |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
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US7337832B2 (en) * | 2003-04-30 | 2008-03-04 | Valeo, Inc. | Heat exchanger |
US6988538B2 (en) * | 2004-01-22 | 2006-01-24 | Hussmann Corporation | Microchannel condenser assembly |
US7281387B2 (en) * | 2004-04-29 | 2007-10-16 | Carrier Commercial Refrigeration Inc. | Foul-resistant condenser using microchannel tubing |
US20060130517A1 (en) * | 2004-12-22 | 2006-06-22 | Hussmann Corporation | Microchannnel evaporator assembly |
US7937963B1 (en) * | 2006-10-02 | 2011-05-10 | Thomas Middleton Semmes | Architecturally enhanced chiller unit |
CN101631996A (en) * | 2006-10-13 | 2010-01-20 | 开利公司 | The refrigerating plant that comprises micro channel heat exchanger |
WO2008064247A1 (en) * | 2006-11-22 | 2008-05-29 | Johnson Controls Technology Company | Multi-function multichannel heat exchanger |
US20080216493A1 (en) * | 2007-03-08 | 2008-09-11 | Liebert Corporation | Microchannel cooling condenser for precision cooling applications |
US20110126559A1 (en) * | 2007-08-24 | 2011-06-02 | Johnson Controls Technology Company | Control system |
AU2008357596A1 (en) * | 2008-06-09 | 2009-12-17 | A-Heat Allied Heat Exchange Technology Ag | Heat exchanger block, and a method for wetting a heat exchanger block |
US20100011803A1 (en) * | 2008-07-15 | 2010-01-21 | Johnson Controls Technology Company | Horizontal discharge air conditioning unit |
US20110168362A1 (en) * | 2008-09-30 | 2011-07-14 | Muller Industries Australia Pty Ltd. | Cooling system with microchannel heat exchanger |
AU2009301278B2 (en) * | 2008-10-08 | 2015-11-19 | A-Heat Allied Heat Exchange Technology Ag | Heat exchanger assembly and method for the operation thereof |
US20110219790A1 (en) * | 2010-03-14 | 2011-09-15 | Trane International Inc. | System and Method For Charging HVAC System |
USD763417S1 (en) * | 2012-08-02 | 2016-08-09 | Mitsubishi Electric Corporation | Heat exchanger tube |
US20140224460A1 (en) * | 2013-02-08 | 2014-08-14 | Trane International Inc. | Microchannel Heat Exchanger |
US9546807B2 (en) | 2013-12-17 | 2017-01-17 | Lennox Industries Inc. | Managing high pressure events in air conditioners |
US10222106B2 (en) | 2015-03-31 | 2019-03-05 | The Boeing Company | Condenser apparatus and method |
CN104949548A (en) * | 2015-07-03 | 2015-09-30 | 湖南省中达换热装备有限公司 | Combined type air cooler |
US20200333077A1 (en) * | 2019-04-18 | 2020-10-22 | The Babcock & Wilcox Company | Perturbing air cooled condenser fin |
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2002
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- 2002-05-24 CN CNB028119681A patent/CN1295476C/en not_active Expired - Lifetime
- 2002-05-24 EP EP02739443A patent/EP1395786B1/en not_active Expired - Lifetime
- 2002-05-24 CA CA002450306A patent/CA2450306C/en not_active Expired - Lifetime
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Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7677057B2 (en) | 2006-11-22 | 2010-03-16 | Johnson Controls Technology Company | Multichannel heat exchanger with dissimilar tube spacing |
US7757753B2 (en) | 2006-11-22 | 2010-07-20 | Johnson Controls Technology Company | Multichannel heat exchanger with dissimilar multichannel tubes |
US7802439B2 (en) | 2006-11-22 | 2010-09-28 | Johnson Controls Technology Company | Multichannel evaporator with flow mixing 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 |
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 |
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 |
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EP1395786A1 (en) | 2004-03-10 |
CA2450306A1 (en) | 2002-12-27 |
US20020195240A1 (en) | 2002-12-26 |
CA2450306C (en) | 2008-12-16 |
CN1295476C (en) | 2007-01-17 |
EP1395786B1 (en) | 2006-04-26 |
CN1516804A (en) | 2004-07-28 |
US20040134226A1 (en) | 2004-07-15 |
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