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US20090308585A1 - Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby - Google Patents

Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby Download PDF

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Publication number
US20090308585A1
US20090308585A1 US12/484,895 US48489509A US2009308585A1 US 20090308585 A1 US20090308585 A1 US 20090308585A1 US 48489509 A US48489509 A US 48489509A US 2009308585 A1 US2009308585 A1 US 2009308585A1
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United States
Prior art keywords
vanes
fin
apertures
sheet
row
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
US12/484,895
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English (en)
Inventor
Pei Pei Chen
Russell Tharp
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.)
Goodman Global Inc
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Goodman Global Inc
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.)
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Publication date
Application filed by Goodman Global Inc filed Critical Goodman Global Inc
Priority to US12/484,895 priority Critical patent/US20090308585A1/en
Assigned to GOODMAN GLOBAL, INC. reassignment GOODMAN GLOBAL, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHEN, PEI PEI, THARP, RUSSELL
Publication of US20090308585A1 publication Critical patent/US20090308585A1/en
Assigned to JPMORGAN CHASE BANK, N.A., AS COLLATERAL AGENT reassignment JPMORGAN CHASE BANK, N.A., AS COLLATERAL AGENT SECURITY AGREEMENT Assignors: Goodman Company, L.P., GOODMAN GLOBAL, INC., GOODMAN MANUFACTURING COMPANY, L.P.
Assigned to JPMORGAN CHASE BANK, N.A., AS COLLATERAL AGENT reassignment JPMORGAN CHASE BANK, N.A., AS COLLATERAL AGENT SECURITY AGREEMENT Assignors: Goodman Company, L.P., GOODMAN GLOBAL, INC., GOODMAN MANUFACTURING COMPANY, L.P.
Assigned to GOODMAN MANUFACTURING COMPANY, L.P., Goodman Company, L.P., GOODMAN GLOBAL, INC. reassignment GOODMAN MANUFACTURING COMPANY, L.P. RELEASE Assignors: JPMORGAN CHASE BANK, N.A.
Assigned to GOODMAN MANUFACTURING COMPANY, L.P., Goodman Company, L.P., GOODMAN GLOBAL, INC. reassignment GOODMAN MANUFACTURING COMPANY, L.P. RELEASE Assignors: JPMORGAN CHASE BANK, N.A.
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • 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
    • F28D1/0475—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 having a single U-bend
    • 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
    • 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
    • F28F1/14—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 and extending longitudinally
    • F28F1/22—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 and extending longitudinally the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • This invention relates generally to tube and fin heat exchangers, and in particular, to a novel fin design for tube and fin heat exchangers.
  • a typical tube and fin heat exchanger ( 10 ) consists of a stack of generally planar metallic fins ( 12 ) sandwiched between a top end plate ( 14 ) and a bottom end plate ( 16 ).
  • the terms “top” and “bottom” used for designating heat exchanger end plates are derived based on the heat exchanger orientation during expansion in a vertical hairpin expander press and are not necessarily indicative of the heat exchanger orientation in any particular installation.
  • the fins ( 12 ) have a number of collared holes ( 18 ) formed therethrough, and the top and bottom end plates ( 14 , 16 ) have corresponding holes ( 20 ) formed therethrough.
  • the holes ( 18 , 20 ) are in axial alignment for receiving a number of U-shaped hairpin tubes (“hairpins”) ( 22 ) through the stack.
  • Hairpins ( 22 ) are formed by bending lengths of small tubes, typically copper, aluminum, steel or titanium, 180 degrees around a small diameter mandrel.
  • the hairpin tubes ( 22 ) are fed, or laced, through the loosely-stacked assembly of fins from the bottom end plate ( 16 ) so that the open ends ( 26 ) of the hairpin tubes ( 22 ) extend beyond the top end plate ( 14 ).
  • the top end plate ( 14 ) is slipped over the open ends ( 26 ) of the hairpins ( 22 ), and the hairpins ( 22 ) are mechanically expanded from within to create a tight fit with the fins ( 12 ).
  • return bend fittings ( 24 ) are soldered or brazed to the open ends ( 26 ) of the hairpin tubes ( 22 ) to create a serpentine fluid circuit through the stack of fins ( 12 ).
  • hairpin tubing of very small diameter in order to maximize heat transfer area within a given heat exchanger size and geometry.
  • Smaller tubes increase the overall heat transfer area and heat transfer coefficient at the refrigerant side of the heat exchanger, which significantly enhances system efficiency.
  • smaller tubing diameter reduces the air flow wake effect behind the heat tube, which reduces the pressure loss due to the presence of the tube facing the incoming air. Lower pressure loss at the air side reduces the fan motor power requirement and increases the fin area to further improve the system heat transfer efficiency.
  • the larger the tube diameter the thicker the tube wall thickness must be in order to withstand a given pressure differential. Therefore, smaller tube diameters allow thinner tube walls for a given refrigerant pressure, which reduces material costs.
  • HVAC heating, ventilation, and air conditioning
  • the industry desires to manufacture heat exchanger coils of smaller diameter, manufacturing techniques of prior art have restricted such coils to short lengths, with the result that small diameter coils have had limited commercial success.
  • the source of the problem is that when the hairpin tubing becomes too small, the lacing process becomes exceedingly difficult, prohibiting commercially viable manufacturing of any but the shortest heat exchangers. For example, heat exchangers six or more feet in length are readily manufactured using 3 ⁇ 8 inch copper tubing.
  • the prior art tube-fin exchanger characterized by 7 mm to 3 ⁇ 8 inch tubing, generally employ fins with a fin width between 19 mm and 22 mm, and a transverse tube pitch ranging between 19 mm and 25.4 mm. Fins of these prior art fin dimensions do not deliver optimized performance for smaller diameter, e.g., 5 mm, tubes. It is also desirable, therefore, to provide a heat exchanger fin that has enhanced thermodynamic performance optimized for small diameter tubing, which results in heat exchanger systems that occupies less space.
  • a primary object of the invention is to provide a manufacturing process for producing stiffer fins to promote the lacing of tube and fin heat exchangers of large size with 5 mm or smaller tubing.
  • Another object of the invention is to provide a heat exchanger manufacturing process in which heat exchanger fins having a plurality of longitudinal ribs are utilized to enhance the lacing process.
  • Another object of the invention is to provide a heat exchanger fin that is designed and arranged for use with 5 mm or smaller tubing to maximize thermodynamic heat transfer.
  • Another object of the invention is to provide a heat exchanger fin that promotes condensation flow from the fin.
  • an improved method for manufacturing tube and fin heat exchangers that, according to a preferred embodiment, includes a process for increasing the stiffness and rigidity of heat exchanger fins.
  • Stiffer fins have a greater tendency to maintain proper alignment within a stack of fins, which aids in lacing long stacks of fins with small (e.g., 5 mm) diameter tubing.
  • fin stiffness is increased by forming a plurality of longitudinal ribs within the fin during the fin stamping process. More preferably still, two ribs for each longitudinal row of collared holes are provided.
  • the preferred embodiment of the invention also includes a slotted heat exchanger fin that is dimensioned and arranged for optimized thermodynamic performance when used with small diameter tubing, thus reducing the space required for a given heat exchanger system.
  • the fin preferably includes slits with ends having a 30 degree incident angle with respect to the airflow, which helps to re-direct the airflow from the tube passing through the collared hole to avoid the wake region behind the tube and provides for a more effective air mixture in parallel slits.
  • the angled slit ends also create turbulence at the area of the fin that has largest distance to neighboring tubes, which enhances the heat transfer over that area.
  • FIG. 1 is a perspective exploded diagram of a typical tube and fin heat exchanger of prior art
  • FIG. 2 is a perspective view of a portion of a heat exchanger fin arranged for a single longitudinal row of 5 mm hairpin tubes according to a first embodiment of the invention, showing a preferred slot pattern, which is repeated between pairs of collared holes, and a pair of longitudinal ribs formed in the fin, which bounds the collared holes;
  • FIG. 3 is a top view of the portion of the single hairpin row heat exchanger fin of FIG. 2 ;
  • FIG. 4 is a perspective view of a portion of a heat exchanger fin arranged for two longitudinal rows of 5 mm hairpin tubes according to a second embodiment of the invention, showing a preferred slot pattern, which is repeated between pairs of collared holes, and two pairs of longitudinal ribs formed in the fin, which bounds the two longitudinal rows of collared holes;
  • FIG. 5 is a top view of the portion of the heat exchanger fin of FIG. 4 ;
  • FIG. 6 is a bottom view of the portion of the heat exchanger fin of FIG. 4 ;
  • FIG. 7 is an enlarged cross section view of the heat exchanger fin of FIG. 4 taken along lines 7 - 7 of FIG. 5 , shown with the collared holes in hidden line to reveal the detail of the raised slots;
  • FIG. 8 is a left side view (with the front of the fin defined by the incident air flow) of the portion of the heat exchanger fin of FIG. 4 ;
  • FIG. 9 is an enlarged cross section view of a longitudinal rib of the portion of heat exchanger fin of FIG. 4 taken along lines 9 - 9 of FIG. 5 ;
  • FIG. 10 is a top view of a portion of the heat exchanger fin of FIG. 4 showing the detail and preferred dimensions of pattern of raised slots for optimizing thermodynamic performance with 5 mm hairpin tubes;
  • FIG. 11 is an enlarged cross section view of a raised vane taken along lines 11 - 11 of FIG. 11 .
  • FIGS. 2-12 illustrate a fin 12 ′ dimensioned for small tubing, e.g. 5 mm outer diameter or less, optimized for use with a condenser or evaporator of a conventional air conditioner.
  • FIGS. 2 and 3 illustrate a heat exchanger fin 12 ′ according to a first embodiment of the invention that is characterized by a single longitudinal row of collared holes 18 ′ for use in a single-row coil assembly.
  • FIGS. 4-8 illustrate a heat exchanger fin 12 ′ according to a second embodiment of the invention that contains two longitudinal rows of collared holes 18 ′ for use in a double-row coil assembly.
  • fins 12 ′ may be arranged for three, four, five, and six or more rows of coils according to the invention.
  • the leading and trailing edges of fin 12 ′ preferably have corrugated edges.
  • a 5 mm or smaller tube and fin heat exchanger manufacturing process includes a novel and unobvious processing step in forming the heat exchanger fins.
  • fins 12 ′ are formed by a stamping process in a fin press, such as those produced by Burr Oak Tool, Inc. of Sturgis, Mich. Fin stock is delivered to a press in a roll of sheet metal. Various metals, heat treatments, and thicknesses may be used, but aluminum is the general industry selection. Fin stock is paid out from an uncoiler, lubricated, then fed through a press, where a die draws, details, punches collared holes, and cuts fins to a desired length and width. Stamping generally occurs in several stages.
  • the fin press includes a die that forms two longitudinal ribs 100 into fin 12 ′ for each longitudinal row of collared holes 18 ′.
  • the purpose of the lengthwise strengthening ribs 100 is to aid in the fabrication of the coil assembly.
  • Stiffer fins have a greater tendency to maintain proper alignment on a lacing table within a stack of fins, which aids in lacing long stacks of fins with small (e.g., 5 mm) diameter tubing.
  • Each longitudinal row of collared holes 18 ′ is disposed between its own pair of longitudinal ribs 100 .
  • fin 12 ′ has two ribs 100 ( FIGS. 2-3 ), and for a double-row coil arrangement, fin 12 ′ has four ribs 100 ( FIGS. 4-6 ).
  • the height h r ( FIG. 9 ) of rib 100 above surface 103 of fin 12 ′ is between 0.05 and 0.25 mm. More preferably, h r is about 0.125 mm.
  • Ribs 100 are also beneficial in the removal of condensate that forms on the fin during the refrigerant evaporation process. Ribs 100 function to provide a path for condensate to follow between tubing rows in multiple-coil arrangements. In single row coil arrangements, ribs 100 provide flow paths for condensate on both the leading and trailing edges of the fin (with respect to the airflow over the fin). Ribs 100 promote the draining of condensate from the fin 12 ′, thus minimizing the potential for condensate carry-over, i.e., condensate blowing off of the fin and becoming entrained in the stream of air flowing across the fins 12 ′.
  • Heat exchanger capacity and efficiency are determined by both fin area and tube area.
  • An optimized heat exchanger must properly balance the utilization of fin and tube area to create the best heat transfer between the refrigerant side and the air side in a cost-effective manner.
  • the combination of smaller diameter tubes, e.g., 5 mm or smaller, with fins 12 ′ according to the preferred embodiment of the invention provides optimal heat transfer efficiency and cost-effectiveness.
  • a plurality of slits 110 are disposed at spaces between the collared holes 18 ′ within a given longitudinal row.
  • Each slit 110 forms a projecting or raised ribbon-like segment or vane 112 , which is parallel to fin surface 103 and is connected at its two longitudinal ends 113 to the surface 103 of fin 12 ′.
  • Segment 112 defines an open portion 114 between the raised vane 112 and the fin surface 103 that separates the incoming air flow.
  • the slit depth dimension d v (along the direction of airflow) ( FIGS. 8 , 9 ) is optimized to reduce the boundary layer development on the segment 112 , which improves heat transfer ability.
  • d v ranges between 0.5 and 1.5 mm. More preferably, d v equals about 1.0 mm.
  • the interval depth d i ( FIG. 8 ) of the fin between adjacent vanes 112 is also preferably equal to the vane depth d v .
  • slits 110 are arranged in an ‘X’-shaped pattern 105 , with each pattern 105 of slits 110 repeating between each pair of collared holes 18 ′ within a given longitudinal row.
  • the slits 110 are ideally grouped by five longitudinal rows 120 , 122 , 124 , 126 , 128 , respectively.
  • the leading two rows (on the basis of the direction of air flow) 120 , 122 , and the trailing two rows 126 , 128 each preferably employ two slits 110 , for which the connecting ends 113 are preferably formed at an angle ⁇ between 15 and 45 degrees with respect to the normal direction of airflow (airflow being assumed to be perpendicular to the longitudinal direction of the fin). Ideally, ⁇ is 30 degrees.
  • the center row 124 preferably employs a single slit 110 with ends 113 formed parallel to the incident airflow. By the nature of the tube and fin heat exchanger, the center portion of fin 12 ′ that has largest distance to neighboring tubes has the lowest heat transfer efficiency.
  • Pattern 105 is designed to guide the airflow to create more turbulence, which enhances the heat transfer over the area.
  • the angled ends 113 of the slits 110 in first, second, fourth and fifth rows 120 , 122 , 126 , 128 create vortices and corresponding turbulence.
  • fin 12 ′ also provides an optimized and balanced tube distance and fin width for 5 mm tubing.
  • Prior art tube-fin exchangers arranged for 7 mm to 3 ⁇ 8 inch diameter tubing have fin widths typically ranging between 19 mm and 22 mm and transverse tube pitches ranging between 19 mm and 25.4 mm.
  • These prior art fins 12 do not deliver optimized performance for the smaller tube size, which results in a larger space for the heat exchanger system than is necessary using the fins 12 ′ according to the preferred embodiment of the invention.
  • Fin 12 ′ has a reduced fin width dimension p w (i.e., the distance from center to center between two adjacent collared holes 18 ′ within a single longitudinal row) between 12 and 18 mm and a transverse tube pitch dimension p t (i.e., the perpendicular distance between the centerline of two adjacent longitudinal rows of collared holes 18 ′) between 10 and 15 mm to give optimized heat transfer capacity and efficiency with minimal use of fin and heat tube material, which results in a space efficient product. More preferably, p w is 16 mm and p t is 13.86 mm.
  • the height h v from the top surface of vane 112 ′ to the top surface 103 of fin 12 ′ preferably ranges from 0.25 to 0.75 mm. More preferably still, h v is about 0.5 mm.

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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)
US12/484,895 2008-06-13 2009-06-15 Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby Abandoned US20090308585A1 (en)

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US6149808P 2008-06-13 2008-06-13
US12/484,895 US20090308585A1 (en) 2008-06-13 2009-06-15 Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby

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US (1) US20090308585A1 (ko)
EP (1) EP2313728A1 (ko)
KR (1) KR20110033198A (ko)
CN (1) CN102216714A (ko)
CA (1) CA2727671A1 (ko)
MX (1) MX2010013776A (ko)
WO (1) WO2009152514A1 (ko)

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US20070215330A1 (en) * 2006-03-20 2007-09-20 Ishikawajima-Harima Heavy Industries Co., Ltd. Heat exchanger
US20100000726A1 (en) * 2008-07-04 2010-01-07 Sang Yeul Lee Heat exchanger
US20120103582A1 (en) * 2010-10-28 2012-05-03 Samsung Electronics Co., Ltd. Heat exchanger and micro-channel tube thereof
US20120103583A1 (en) * 2010-10-28 2012-05-03 Samsung Electronics Co., Ltd. Heat exchanger and fin for the same
JP2012172860A (ja) * 2011-02-17 2012-09-10 Mitsubishi Heavy Ind Ltd 熱交換器
CN103273295A (zh) * 2013-05-10 2013-09-04 丹佛斯微通道换热器（嘉兴）有限公司 换热器和换热器制造方法
US20130284414A1 (en) * 2012-04-26 2013-10-31 Lg Electronics Inc. Heat exchanger
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US20140034272A1 (en) * 2012-08-01 2014-02-06 Lg Electronics Inc. Heat exchanger
WO2016031032A1 (ja) * 2014-08-29 2016-03-03 日立アプライアンス株式会社 熱交換器および空気調和装置
US20160245594A1 (en) * 2015-02-24 2016-08-25 Heatcraft Refrigeration Products Llc Heat exchanger with louvered fins
USD800282S1 (en) * 2016-03-03 2017-10-17 Lennox Industries Inc. Heat exchanger fin
US20180252475A1 (en) * 2015-08-25 2018-09-06 Danfoss Micro Channel Heat Exchanger (Jiaxing) Co., Ltd. Heat exchange tube for heat exchanger, heat exchanger and assembly method thereof
US20180266772A1 (en) * 2015-07-17 2018-09-20 Valeo Systemes Thermiques Fin heat exchanger comprising improved louvres
US20210123691A1 (en) * 2018-06-20 2021-04-29 Lg Electronics Inc. Outdoor unit of air conditioner
US20220088693A1 (en) * 2019-08-01 2022-03-24 Benteler Automobiltechnik Gmbh Process for producing a plate heat exchanger and plate heat exchanger
US20220235947A1 (en) * 2020-12-11 2022-07-28 Guangdong Midea White Home Appliance Technology Innovation Center Co., Ltd. Air Conditioner Indoor Unit and Air Conditioner
US11561014B2 (en) * 2016-03-16 2023-01-24 Samsung Electronics Co., Ltd. Air conditioner including a heat exchanger
US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger

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CN103453793A (zh) * 2013-07-29 2013-12-18 姚福良 管翅一体式热传输单元及其热交换器
CN109737791B (zh) * 2018-12-29 2020-04-10 西安交通大学 一种梯形波纹与异形环管结构复合翅片

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