US20030102113A1 - Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle - Google Patents

Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle Download PDF

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Publication number
US20030102113A1
US20030102113A1 US10/013,018 US1301801A US2003102113A1 US 20030102113 A1 US20030102113 A1 US 20030102113A1 US 1301801 A US1301801 A US 1301801A US 2003102113 A1 US2003102113 A1 US 2003102113A1
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US
United States
Prior art keywords
tubes
headers
parallel
heat exchanger
fins
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.)
Abandoned
Application number
US10/013,018
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English (en)
Inventor
Stephen Memory
C. Rogers
Gregory Hughes
Frank Grippe
Rifiquat Cheema
William Markusen
Kenneth Ritt
Frank Vetter
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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
Application filed by Modine Manufacturing Co filed Critical Modine Manufacturing Co
Priority to US10/013,018 priority Critical patent/US20030102113A1/en
Priority to RU2004117856/06A priority patent/RU2319094C2/ru
Priority to MXPA04004660A priority patent/MXPA04004660A/es
Priority to AU2002365762A priority patent/AU2002365762B2/en
Priority to CA002467137A priority patent/CA2467137A1/en
Priority to PCT/US2002/034606 priority patent/WO2003048670A1/en
Priority to JP2003549821A priority patent/JP2005512009A/ja
Priority to CNB028236556A priority patent/CN100380081C/zh
Priority to KR1020047008270A priority patent/KR20050058253A/ko
Priority to EP02804409A priority patent/EP1448945A1/en
Priority to BR0214479-4A priority patent/BR0214479A/pt
Priority to CNA2007101049458A priority patent/CN101089533A/zh
Priority to TW091133260A priority patent/TW200301815A/zh
Priority to ARP020104527A priority patent/AR037428A1/es
Publication of US20030102113A1 publication Critical patent/US20030102113A1/en
Assigned to MODINE MANUFACTURING COMPANY reassignment MODINE MANUFACTURING COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHEEMA, RIFIQUAT, GRIPPE, FRANK M., HUGHES, GREGORY G., MARKUSEN, WILLIAM, MEMORY, STEPHEN, RITT, KENNETH, ROGERS, C. JAMES, VETTER, FRANK R.
Abandoned legal-status Critical Current

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    • 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
    • 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
    • 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
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

Definitions

  • This invention relates to heat exchangers, and more particularly, to heat exchangers that provide supercritical cooling of a working fluid in a transcritical cooling cycle.
  • One common form of a heat exchanger includes a so called “core” made up of tubes and interconnecting fins. One fluid is passed through the tubes of the core while a second fluid is passed through the core itself in the spaces between the fins and tubes.
  • the opposite ends of the tubes are connected to a pair of parallel manifolds or “tanks”, with one of the manifolds being an inlet manifold and the other manifold being an outlet manifold which direct one of the fluids into and out of the tubes, respectively.
  • Heat exchangers of this general type are used for a large variety of purposes, such as radiators, condensers, evaporators, charge air coolers, oil coolers, etc., all of which may be utilized in a vehicle.
  • One common form of this type of heat exchanger is known as a parallel flow heat exchanger wherein flat, multi-port tubes direct a refrigerant through the heat exchanger.
  • the flat tubes are straight and the manifolds are spaced on opposite sides of the heat exchanger to receive the opposite ends of the tubes.
  • it is known to bend the flat tubes so that each tube is shaped as a so called “hair pin” tube having two parallel legs, with the inlet and outlet manifold positioned next to each other to receive the ends of the tubes.
  • An exemplary embodiment of the invention achieves at least some of the foregoing objects in a heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle.
  • the heat exchanger includes a pair of elongated headers having longitudinal axis disposed substantially parallel to each other, a plurality of elongated tubes spaced in side by side relation along the longitudinal axis of the headers, with each of the tubes being folded upon itself to define at least two parallel legs of the tube so that the working fluid flows serially through at least two parallel passes from one of the headers to the other, and serpentine fins extending between adjacent pairs of the tubes, with each of the fins having a length extending parallel to the parallel legs of the adjacent tubes.
  • Each of the tubes has a flat cross-section with a major dimension and a minor dimension.
  • the major dimensions of the parallel legs of each of the tubes lie in a common plane that is substantially transverse to the longitudinal axes of the headers.
  • Each of the tubes has a first end connected to one of the headers and a second end connected to the other header to transfer the working fluid between the headers.
  • each of the serpentine fins has a transverse width extending across the parallel legs of the adjacent tubes.
  • Each of the fins includes a plurality of alternating tabs and elongated separations extending parallel to the parallel legs, with the tabs and separations located between the parallel legs of the adjacent tubes to divide the width of each fin into a plurality of discrete fin elements that are connected to each other by the tabs.
  • Each of the fin elements corresponds to and extends along one of the parallel legs of each of the adjacent tubes.
  • the parallel legs of each of the tubes are spaced from each other.
  • each of the tubes is folded upon itself at least twice to define at least three parallel legs of the tube so that the working fluid flows serially through at least three parallel fluid passes from one of the headers to the other.
  • each of the tubes is a multi-port tube with a hydraulic diameter in the range of 0.015 inch to 0.040 inch.
  • the major dimension of each of the tubes is no greater than 0.500 inch and the minor dimension is no greater than 0.100 inch.
  • each of the fins has a fin height extending from one of the tubes to an adjacent one of the tubes, parallel to the longitudinal axes of the headers, and the major dimension of the tubes is no greater than the fin height.
  • the major dimensions of the tubes extend parallel to the longitudinal axes of the headers at the location where the tube end is connected to the header.
  • FIG. 1 is a somewhat diagrammatic elevation view of a cooling system including a heat exchanger embodying the present invention
  • FIG. 2 is an elevation view of the heat exchanger shown in FIG. 1;
  • FIG. 3 is a side view of the heat exchanger shown in FIG. 2;
  • FIG. 4 is a top view of the heat exchanger shown in FIG. 2;
  • FIG. 5 is an enlarged, partial section view taken along line 5 - 5 in FIG. 3;
  • FIG. 6 is an enlarged, partial view of a tube employed in the heat exchanger shown in FIGS. 1 - 5 ;
  • FIG. 7 is a perspective view showing a tube and a fin utilized in a heat exchanger embodying the invention.
  • a heat exchanger 10 embodying the present invention is shown in connection with a basic cooling system 12 that operates a transcritical cooling cycle.
  • the heat exchanger 10 is shown in the form of a gas cooler 13 that provides supercritical cooling to the working fluid or refrigerant, such as CO 2 , of the cooling system 12 by rejecting heat to a medium, such as an air flow A, on the fin side of the heat exchanger 10 .
  • the cooling system 12 includes the heat exchanger 10 , a compressor 14 , that compresses gaseous phase refrigerants to a supercritical pressure for delivery to the heat exchanger 10 , an expansion device 16 , that reduces the pressure in the refrigerant received from the heat exchanger 10 so at least some of the refrigerant enters the liquid phase, an evaporator 17 that transfers heat from one medium into the refrigerant to change the refrigerant from the liquid phase to the gaseous phase, an accumulator 18 (optional), and a suction line heat exchanger 19 that transfers heat from the refrigerant exiting the heat exchanger 10 into the refrigerant exiting the evaporator 17 , or accumulator 18 if used.
  • the heat exchanger 10 may find use in other types of cooling systems, and in other configurations of cooling systems that perform a transcritical cooling cycle, and is not limited to use with the specific cooling system shown in FIG. 1 unless specifically recited in the claims. Further, while the disclosed heat exchanger 10 can provide distinct advantages when used as a gas cooler 13 , it may also prove advantageous when used for other purposes, such as a condenser or an evaporator, regardless of whether it is used in connection with a transcritical cooling cycle.
  • the heat exchanger 10 includes a pair of elongated tubular headers 20 and 22 having longitudinal axes 24 and 26 , respectively, disposed substantially parallel to each other; a plurality of elongated tubes 28 spaced in side-by-side relations along the longitudinal axes 24 , 26 of the headers 20 , 22 ; and serpentine fins 30 extending between adjacent pairs of the tubes 28 .
  • each fin 30 extends over a length L of the tubes 28 , but the middle portions of the lengths are not shown in FIG. 2 for convenience of illustration.
  • the fins 30 are louvered.
  • each of the tubes 28 has a first end 31 connected to the header 20 and a second end 32 connected to the header 22 to transfer the refrigerant between the headers 20 , 22 .
  • Each of the tubes 28 has a flattened cross-section with a major dimension D and a minor dimension d, as best seen in FIG. 5.
  • Each of the tubes 28 is preferably a multi-port tube and, in highly preferred embodiments, a multi-port tube having a hydraulic diameter in the range of 0.015 inch to 0.045 inch.
  • FIG. 5 shows six ports 34 , it may be beneficial in some applications to include more than, or less than, six ports 34 in each of the multi-port tubes 28 .
  • each of the tubes has four ports 34 .
  • the tubes are configured to withstand a burst pressure of at least 6500 PSI, at 70° F. ambient, such as may be required for operation as a gas cooler in a transcritical CO 2 cooling system.
  • the major dimension D of each of the tubes 28 is nominally no greater than 0.500 inch and the minor dimension d is nominally no greater than 0.100 inch, while in some highly preferred embodiments the minor dimension d is nominally no greater than 0.060 inch and the major dimension D is nominally no greater than 0.320 inch.
  • reducing the major dimension D can offer a number of advantages. For example, because each of the tubes 28 includes at least two parallel legs 36 , the depth of the heat exchanger 10 becomes highly dependent upon the size of the major dimension D and will be reduced with the reduction in the major dimension D.
  • the diameter of the headers 20 , 22 can be reduced in a construction where the major dimension D of the tube ends 31 , 32 extends transverse to the longitudinal axes 24 , 26 of the headers 20 , 22 at the locations where the ends 31 , 32 are connected to the headers 20 , 22 , rather than the parallel construction shown in FIGS. 1 - 4 .
  • the length of the headers 20 , 22 can be reduced in a construction wherein the major dimension D of the tube ends 31 , 32 extend parallel to the longitudinal axes 24 , 26 of the headers 20 , 22 , such as shown in FIGS. 1 - 4 .
  • a reduction in the major dimension D can allow for a reduction in the fin height in some preferred embodiments. However, it should be understood that larger fin heights may offer advantages with respect to air side efficiency.
  • each of the tubes 28 is folded upon itself to define at least two parallel legs 36 of the tube 28 so that the refrigerant flows serially through at least two parallel fluid passes 38 from the header 20 to the header 22 .
  • the inlet and outlet headers 20 , 22 be selected so that the heat exchanger 10 operates in a cross-counterflow configuration relative to the fluid flow on the fin side of the heat exchanger 10 when operating as a gas cooler.
  • Each pair of the parallel legs is joined by a fold 39 that is twisted 90° relative to the legs 36 at the location of the fold 39 so that the major dimension D extends parallel to the axes 26 , 24 at the location of the fold 39 , rather than transverse.
  • the fold 39 is formed by first twisting the legs 36 90° relative to the portion of the tube 28 at the location of the fold 39 , and then bending the tube through approximately 180° at the location of the fold 39 to form the fold 39 .
  • the 90° twist of each of the legs 36 relative to the fold 39 can be in the same direction as shown in FIGS. 3 and 6, or in opposite, directions, depending upon which configuration offers the most advantage for a particular application of the heat exchanger 10 .
  • the parallel legs 36 of each of the tubes 28 are preferably spaced from each other by a distance X, with the major dimension D of each of the parallel legs 36 lying in a common plane, illustrated by dashed line P in FIGS.
  • the spacing X reduces heat conduction from one leg 36 to the other, which can be advantageous when the heat exchanger 10 is providing supercritical cooling because the temperature of the refrigerant can vary substantially as it flows through the tube 28 from one header 20 to the other header 22 .
  • the distance X is sufficient to minimize or prevent the closing of the space between adjacent parallel legs 36 by braze material during brazing of the heat exchanger 10 , but not so large so as to unduly increase the depth of the heat exchanger 10 . While it is preferred that the adjacent parallel legs 36 of each tube 28 be spaced from each other, in some applications this spacing may not be required and/or desirable.
  • each of the fins 30 has a fin height H equal to the spacing between adjacent tubes 28 , i.e. a fin height H extending from one of the tubes 28 to an adjacent tube 28 parallel to the longitudinal axes 24 , 26 of the headers 20 , 22 .
  • the major dimension D of the tubes 28 is no greater than the fin height H. This allows a construction wherein each of the tube ends 31 , 32 can be twisted 90° relative to the parallel legs 36 from which they extend so that the major dimension D of the end 31 , 32 extends parallel to the longitudinal axes 24 , 26 of the headers 20 , 22 at the location where the tube ends 31 and 32 are connected to the headers 20 and 22 , as seen in FIG.
  • the major dimension D of the tube ends 31 , 32 extend parallel to the longitudinal axes 24 , 26 of the headers 20 , 22 at the location where the tube ends 31 , 32 are connected to the headers 20 , 22
  • other orientations of the major dimension D at these locations may be advantageous in some applications.
  • the major dimension D of the tube ends 31 , 32 may be advantageous in some applications for the major dimension D of the tube ends 31 , 32 to extend transverse to the longitudinal axes 24 , 26 at the location where the tube ends 31 , 32 are connected to the headers 20 , 22 .
  • each of the serpentine fins 30 has a length L extending parallel to the parallel legs 36 of the adjacent tubes 28 and, as best seen in FIG. 4, a transverse width W extending across the parallel legs 36 of the adjacent tubes 28 .
  • FIG. 5 shows three legs 36 of the tubes 28 and
  • FIG. 7 shows a fin 30 for use with a heat exchanger construction 10 wherein each of the tubes 28 has only two parallel legs 36 .
  • each of the fins 30 includes a plurality of alternating tabs 40 and elongated separations 42 extending parallel to the parallel legs 36 and located between the parallel legs 36 of the adjacent tubes 28 to divide the width W of each fin 30 into two or more discrete fin strips or elements 44 that are connected to each other by the tabs 40 .
  • Each of the fin elements 44 corresponds to and extends along one of the parallel legs 36 of each of the adjacent tubes 28 .
  • the separations 42 are generally straight line and have opposed edges 45 that face one another and are generally transverse to the direction of the medium flow through the fins 30 . While FIG.
  • each of the fins 30 preferably extends across all of the parallel legs 36 with a fin element 44 corresponding to and extending along each of the parallel legs 36 of each of the adjacent tubes 28 , and the tabs 40 and separations 42 provided between each of the fin elements 44 .
  • the alternating tabs 40 in each of the fins 30 serve to restrict movement of the fin elements 44 relative to each other so that each fin 30 remains a unitary component during the assembly of the heat exchanger 10 and, furthermore, to better maintain the fin elements 44 in alignment with each other to minimize the pressure drop on the fin side of the heat exchanger.
  • the purpose of the elongated separations 42 is to minimize the heat conduction from each of the parallel legs 36 to any adjacent parallel leg 36 of each tube 28 by interrupting, and thus minimizing, the heat conduction between the fin elements 44 associated with each of the parallel legs 36 . This is desirable in applications, such as the gas cooler 13 of FIGS.
  • each of the elongated separations 42 it is desirable for each of the elongated separations 42 to extend uninterrupted as far as possible along the length of the fin 30 and for the number and size of the tabs 40 to be minimized to that which is required to prevent each of the fin elements 44 from separating during assembly and to maintain an acceptable degree of alignment between the fin elements 44 of each of the fins 30 during assembly.
  • each of the tabs 40 extends approximately 0.020 inch along the length of the fin 30 and each of the elongated separations 42 of a fin 30 made of aluminum extends approximately 8.0 inches along the length of the unfolded fin 30 .
  • the tabs 40 and the separations 44 have lengths extending parallel with the length of the fin 30 in the unfolded state and the ratio of the length of the separations 42 to the length of the tabs 40 is in the range of 200 to 600.
  • each of the elongated separations 42 extends uninterrupted from one of the tabs 40 over 10 to 14 of the folds 46 to the next tab 40 with the fin 30 in the folded condition.
  • the tabs 40 and the separations 42 can be formed in a number of ways, it is preferred that the separations 42 be formed as cuts or slits in the fin material that do not require removal of fin material during formation in the fin 30 .
  • One way of achieving such slits or cuts is to use a splitter disk in the fin roll die to create a simple cut in the fin 30 as the fin 30 is formed from a strip of sheet material. The split could be eliminated for a small portion of the disk in every revolution to form the tabs 40 to ensure that each fin element 44 stays attached to the adjoining fin element 44 of the fin 30 . This provides a physical cut or slit in the fin 30 , with no loss of fin surface.
  • edges 45 are virtually, but not quite, in abutment with each other.
  • One concern is that the fin elements 44 might braze together during the brazing process.
  • One approach to minimize this concern is to locate the braze material on the side walls of the tube legs 36 that abut the fins 30 , rather than cladding the braze material onto the fins 30 .
  • Another approach to minimize this concern is to offset adjacent fin elements 44 of the fin 30 at locations remote from the tab 40 , which may allow for clad fins.
  • Another approach would be to bend the edges 45 formed by the slits slightly apart, forming a very small louver, which may also allow for clad fins.
  • Yet another approach is to coin each of the tab portions 40 to further separate the fin elements 44 from each other.
  • this last approach may allow for clad fins. While slits are preferred, in some applications it may be advantageous for the separations 42 to be formed as slots that do require removal of fin material when formed in the fins 30 . In this regard, it would probably be sufficient for the slots to have a width of a few thousands of an inch parallel to the width W of the fin 30 .
  • the fins 30 include the tabs 40 and separations 44 , in some applications the tabs 40 and separations 42 may not be desirable and/or required.
  • the fins 30 be louvered, many forms of which are known.
  • the exact configuration of the louvers will be highly dependent on the parameters of the particular application such as, for example, the fluid on the fin side of the heat exchanger 10 , the available pressure drop on the fin side of the heat exchanger 10 , the number of parallel legs 36 in each of the tubes 28 , and whether there is an odd or even number of parallel legs 36 in each of the tubes 28 .
  • the heat exchanger 10 when operating as a gas cooler 13 in the system 12 , the heat exchanger 10 will typically provide supercritical cooling of the refrigerant; however, there may be some conditions of operation wherein the ambient temperature is below the critical temperature, in which case the heat exchanger 10 will operate as a condenser that provides subcritical cooling for the refrigerant.
  • the illustrated heat exchanger 10 includes 12 parallel legs 36 for each of the tubes 28 .
  • the optimum number of parallel legs for each application of the heat exchanger 10 will be highly dependent upon the specific parameters for the particular application such as, for example, the working fluid of the system 12 , the envelope and environment into which the heat exchanger 10 must be packaged, and the function of the heat exchanger, i.e., as a gas cooler, condenser, or evaporator for use in either an AC or heat pump system.
  • one or more baffles can be provided within either or both of the headers 20 , 22 to direct the refrigerant from the header 20 through a subset of the tubes 28 to the header 22 and then back through a different subset of the tubes 28 to the header 20 and so on for as many passes from one header to the other as may be needed to provide the performance dictated by each particular application.
  • headers 20 , 22 , tubes 28 , and fins 30 are all made of aluminum and brazed with an appropriate braze material. However, it should be understood that in some applications other suitable materials made be employed for these components as dictated by the parameters of the particular application.
  • FIGS. 1 - 3 it should also be understood that while the heat exchanger 10 illustrated in FIGS. 1 - 3 is shown so that the longitudinal axes 24 , 26 of the headers 20 , 22 extend in a horizontal direction, and the parallel legs 36 of the tubes 28 extend in a vertical direction, it may be desirable in some applications for a heat exchanger 10 to have a different orientation, such as, for an example, an orientation wherein the axes 24 , 26 extend in a vertical direction and the parallel legs 36 extend in a horizontal direction. Further, while the headers 20 , 22 of the heat exchanger 10 illustrated in FIGS.
  • headers 20 , 22 are located on the same side of the heat exchanger 10 , it may be desirable in some applications for the headers 20 , 22 to be located on opposite sides of the heat exchanger 10 .
  • a construction with the headers 20 , 22 on the same side of the heat exchanger will typically result in an even number of parallel legs 36 for each of the tubes 28
  • a construction with the headers 20 , 22 on opposite sides of the heat exchanger 10 will typically result in a odd number of parallel legs 36 for each of the tubes 28 .
  • header plates fitted with tanks could be employed in lieu of the tubular headers 20 , 22 if desired for a particular application.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US10/013,018 2001-11-30 2001-11-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle Abandoned US20030102113A1 (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US10/013,018 US20030102113A1 (en) 2001-11-30 2001-11-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
RU2004117856/06A RU2319094C2 (ru) 2001-11-30 2002-10-30 Теплообменник для сверхкритического охлаждения рабочей среды в транскритическом холодильном цикле (варианты)
MXPA04004660A MXPA04004660A (es) 2001-11-30 2002-10-30 Intercambiador termico para proporcionar enfriamiento supercritico de un fluido de trabajo en un ciclo de enfriamiento transcritico.
AU2002365762A AU2002365762B2 (en) 2001-11-30 2002-10-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
CA002467137A CA2467137A1 (en) 2001-11-30 2002-10-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
PCT/US2002/034606 WO2003048670A1 (en) 2001-11-30 2002-10-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
JP2003549821A JP2005512009A (ja) 2001-11-30 2002-10-30 トランスクリティカル冷却サイクルにおいて作業流体の超臨界冷却を与えるための熱交換器
CNB028236556A CN100380081C (zh) 2001-11-30 2002-10-30 用于在跨临界冷却循环中提供工作流体的超临界冷却的热交换器
KR1020047008270A KR20050058253A (ko) 2001-11-30 2002-10-30 넘김 고비 냉각 사이클에서 작동유를 초임계 냉각시키는열교환기
EP02804409A EP1448945A1 (en) 2001-11-30 2002-10-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
BR0214479-4A BR0214479A (pt) 2001-11-30 2002-10-30 Trocador de calor para propiciar refrigeração supercrìtica de um fluìdo de trabalho em um ciclo de refrigeração transcrìtico
CNA2007101049458A CN101089533A (zh) 2001-11-30 2002-10-30 用于在跨临界冷却循环中提供工作流体的超临界冷却的热交换器
TW091133260A TW200301815A (en) 2001-11-30 2002-11-13 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
ARP020104527A AR037428A1 (es) 2001-11-30 2002-11-25 Intercambiador de calor para proporcionar enfriamiento supercritico de un fluido de operacion en un ciclo de enfriamiento transcritico

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US10/013,018 US20030102113A1 (en) 2001-11-30 2001-11-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle

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US20030102113A1 true US20030102113A1 (en) 2003-06-05

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US10/013,018 Abandoned US20030102113A1 (en) 2001-11-30 2001-11-30 Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle

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US (1) US20030102113A1 (ru)
EP (1) EP1448945A1 (ru)
JP (1) JP2005512009A (ru)
KR (1) KR20050058253A (ru)
CN (2) CN100380081C (ru)
AR (1) AR037428A1 (ru)
AU (1) AU2002365762B2 (ru)
BR (1) BR0214479A (ru)
CA (1) CA2467137A1 (ru)
MX (1) MXPA04004660A (ru)
RU (1) RU2319094C2 (ru)
TW (1) TW200301815A (ru)
WO (1) WO2003048670A1 (ru)

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US20050109486A1 (en) * 2003-11-20 2005-05-26 Memory Stephen B. Suction line heat exchanger for CO2 cooling system
US20050155749A1 (en) * 2004-01-20 2005-07-21 Memory Stephen B. Brazed plate high pressure heat exchanger
WO2005066565A1 (de) * 2004-01-12 2005-07-21 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für überkritischen kältekreislauf
US20050223738A1 (en) * 2002-07-26 2005-10-13 Behr Gmbh & Co. Kg Device for heat exchange
WO2006056360A1 (de) * 2004-11-23 2006-06-01 Behr Gmbh & Co. Kg Dimensionsoptimierte vorrichtung zum austausch von wärme und verfahren zur optimierung der dimensionen von vorrichtungen zum austausch von wärme
US20060124288A1 (en) * 2002-11-07 2006-06-15 Behr Gmbh & Co. Kg Heat exchanger
US20060243432A1 (en) * 2003-02-18 2006-11-02 Behr Gmbh & Co. Kg Flat pipe comprising a return bend section and a heat exchanger constructed therewith
FR2894656A1 (fr) * 2005-12-14 2007-06-15 Valeo Systemes Thermiques Boite collectrice perfectionnee pour un echangeur de chaleur d'un circuit de climatisation
US20080173434A1 (en) * 2007-01-23 2008-07-24 Matter Jerome A Heat exchanger and method
US20090086169A1 (en) * 2007-09-28 2009-04-02 Sanyo Electric Co., Ltd. Projection type image display device
US20090113903A1 (en) * 2007-11-02 2009-05-07 Babkin Alexei V Cooling methods and systems using supercritical fluids
US20110132586A1 (en) * 2009-12-08 2011-06-09 Visteon Global Technologies, Inc. Heat exchanger with tube bundle
US20110247791A1 (en) * 2010-04-13 2011-10-13 Danfoss Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Heat exchanger
US20110314846A1 (en) * 2004-08-09 2011-12-29 Linde Kaltetechnik Gmbh Refrigeration Circuit and Method for Operating a Refrigeration Circuit
US9939208B2 (en) 2014-03-24 2018-04-10 Denso Corporation Heat exchanger
US10436156B2 (en) 2016-12-01 2019-10-08 Modine Manufacturing Company Air fin for a heat exchanger, and method of making the same
US11519356B2 (en) * 2020-10-22 2022-12-06 Southwest Research Institute Techniques for engine cooling using supercritical fluids and a combustion engine system implementing the same
US11692479B2 (en) 2019-10-03 2023-07-04 General Electric Company Heat exchanger with active buffer layer

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CN1333228C (zh) * 2005-01-26 2007-08-22 清华大学 用于跨临界co2制冷循环的微通道板翅式内部换热器
FR2907887B1 (fr) * 2006-10-25 2013-12-20 Valeo Systemes Thermiques Echangeur de chaleur protege vis-a-vis des ponts thermiques et procede de fabrication d'un tel echangeur
CN101776357B (zh) * 2009-01-09 2011-12-28 三花丹佛斯（杭州）微通道换热器有限公司 一种热交换器
CN101776403B (zh) * 2009-01-13 2012-07-04 三花丹佛斯（杭州）微通道换热器有限公司 一种热交换器
EP2962055B1 (en) * 2013-03-01 2018-05-23 Sapa AS Fin solution related to micro channel based heat exchanger
RU2693946C2 (ru) * 2014-11-26 2019-07-08 Кэрриер Корпорейшн Стойкий к образованию инея микроканальный теплообменник
CN106643263B (zh) * 2015-07-29 2019-02-15 丹佛斯微通道换热器（嘉兴）有限公司 用于换热器的翅片组件和具有该翅片组件的换热器

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Cited By (32)

* Cited by examiner, † Cited by third party
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US20050223738A1 (en) * 2002-07-26 2005-10-13 Behr Gmbh & Co. Kg Device for heat exchange
US7347063B2 (en) * 2002-07-26 2008-03-25 Behr Gmbh & Co. Kg Device for heat exchange
US20060124288A1 (en) * 2002-11-07 2006-06-15 Behr Gmbh & Co. Kg Heat exchanger
US20060243432A1 (en) * 2003-02-18 2006-11-02 Behr Gmbh & Co. Kg Flat pipe comprising a return bend section and a heat exchanger constructed therewith
US20050109486A1 (en) * 2003-11-20 2005-05-26 Memory Stephen B. Suction line heat exchanger for CO2 cooling system
US7261151B2 (en) * 2003-11-20 2007-08-28 Modine Manufacturing Company Suction line heat exchanger for CO2 cooling system
WO2005066565A1 (de) * 2004-01-12 2005-07-21 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für überkritischen kältekreislauf
US7343965B2 (en) * 2004-01-20 2008-03-18 Modine Manufacturing Company Brazed plate high pressure heat exchanger
US20050155749A1 (en) * 2004-01-20 2005-07-21 Memory Stephen B. Brazed plate high pressure heat exchanger
US9494345B2 (en) 2004-08-09 2016-11-15 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US9476614B2 (en) 2004-08-09 2016-10-25 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US8844303B2 (en) * 2004-08-09 2014-09-30 Carrier Corporation Refrigeration circuit and method for operating a refrigeration circuit
US20110314846A1 (en) * 2004-08-09 2011-12-29 Linde Kaltetechnik Gmbh Refrigeration Circuit and Method for Operating a Refrigeration Circuit
CN101065635B (zh) * 2004-11-23 2010-10-13 贝洱两合公司 尺寸优化的热交换装置及热交换装置的尺寸优化的方法
WO2006056360A1 (de) * 2004-11-23 2006-06-01 Behr Gmbh & Co. Kg Dimensionsoptimierte vorrichtung zum austausch von wärme und verfahren zur optimierung der dimensionen von vorrichtungen zum austausch von wärme
US20080029242A1 (en) * 2004-11-23 2008-02-07 Behr Gmbh & Co., Kg Dimensionally-Optimized Device For The Exchange Of Heat And Method For Optimisation Of The Dimensions Of Devices For The Exchange Of Heat
FR2894656A1 (fr) * 2005-12-14 2007-06-15 Valeo Systemes Thermiques Boite collectrice perfectionnee pour un echangeur de chaleur d'un circuit de climatisation
EP1798510A1 (fr) * 2005-12-14 2007-06-20 Valeo Systemes Thermiques Boîte collectrice perfectionnée pour un échangeur de chaleur d'un circuit de climatisation
US20080173434A1 (en) * 2007-01-23 2008-07-24 Matter Jerome A Heat exchanger and method
US7921904B2 (en) 2007-01-23 2011-04-12 Modine Manufacturing Company Heat exchanger and method
US20090086169A1 (en) * 2007-09-28 2009-04-02 Sanyo Electric Co., Ltd. Projection type image display device
US8002415B2 (en) * 2007-09-28 2011-08-23 Sanyo Electric Co., Ltd. Projection-type image display device with cooling mechanism
US20090113903A1 (en) * 2007-11-02 2009-05-07 Babkin Alexei V Cooling methods and systems using supercritical fluids
US8087256B2 (en) 2007-11-02 2012-01-03 Cryomechanics, LLC Cooling methods and systems using supercritical fluids
US20110132586A1 (en) * 2009-12-08 2011-06-09 Visteon Global Technologies, Inc. Heat exchanger with tube bundle
US20110247791A1 (en) * 2010-04-13 2011-10-13 Danfoss Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Heat exchanger
US9528770B2 (en) * 2010-04-13 2016-12-27 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co. Heat exchanger
US9939208B2 (en) 2014-03-24 2018-04-10 Denso Corporation Heat exchanger
US10436156B2 (en) 2016-12-01 2019-10-08 Modine Manufacturing Company Air fin for a heat exchanger, and method of making the same
US11162742B2 (en) 2016-12-01 2021-11-02 Modine Manufacturing Company Air fin for a heat exchanger
US11692479B2 (en) 2019-10-03 2023-07-04 General Electric Company Heat exchanger with active buffer layer
US11519356B2 (en) * 2020-10-22 2022-12-06 Southwest Research Institute Techniques for engine cooling using supercritical fluids and a combustion engine system implementing the same

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RU2004117856A (ru) 2005-04-27
CA2467137A1 (en) 2003-06-12
AR037428A1 (es) 2004-11-10
CN101089533A (zh) 2007-12-19
BR0214479A (pt) 2004-09-14
AU2002365762B2 (en) 2008-02-21
TW200301815A (en) 2003-07-16
CN100380081C (zh) 2008-04-09
CN1596360A (zh) 2005-03-16
EP1448945A1 (en) 2004-08-25
JP2005512009A (ja) 2005-04-28
MXPA04004660A (es) 2004-08-13
WO2003048670A1 (en) 2003-06-12
AU2002365762A1 (en) 2003-06-17
KR20050058253A (ko) 2005-06-16
RU2319094C2 (ru) 2008-03-10

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