US20110284195A1 - Fabricated tube for an evaporator - Google Patents

Fabricated tube for an evaporator Download PDF

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Publication number
US20110284195A1
US20110284195A1 US13/107,045 US201113107045A US2011284195A1 US 20110284195 A1 US20110284195 A1 US 20110284195A1 US 201113107045 A US201113107045 A US 201113107045A US 2011284195 A1 US2011284195 A1 US 2011284195A1
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US
United States
Prior art keywords
ratio
evaporator
folded
tube
evaporator tube
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
US13/107,045
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English (en)
Inventor
Sourav Chowdhury
Prasad S. Kadle
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.)
Mahle International GmbH
Original Assignee
Delphi Technologies 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.)
Filing date
Publication date
Application filed by Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to US13/107,045 priority Critical patent/US20110284195A1/en
Assigned to DELPHI TECHNOLOGIES, INC. reassignment DELPHI TECHNOLOGIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KADLE, PRASAD S., CHOWDHURY, SOURAV
Priority to EP11166227.6A priority patent/EP2388545A3/en
Priority to CN2011202358111U priority patent/CN202216603U/zh
Publication of US20110284195A1 publication Critical patent/US20110284195A1/en
Priority to US14/734,148 priority patent/US20150360333A1/en
Assigned to MAHLE INTERNATIONAL GMBH reassignment MAHLE INTERNATIONAL GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DELPHI TECHNOLOGIES, INC.
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0391—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 plate-like or laminated conduits a single plate being bent to form one or more conduits
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits

Definitions

  • the present invention relates generally to a tube for a heat exchanger; specifically, to a fabricated tube for an evaporator; and more specifically, to a folded evaporator tube.
  • a heat exchanger assembly such as a radiator, condenser, or evaporator for use in a motor vehicle typically includes an inlet header, an outlet header, a plurality of tubes hydraulically connecting the headers for fluid flow therebetween, and external fins interconnecting the tubes.
  • the headers, tubes, and fins are typically assembled into a unitary structure and brazed to form the heat exchanger assembly.
  • a first heat transfer fluid such as a liquid coolant flows from the inlet header to the outlet header through the plurality of tubes.
  • the first heat transfer fluid is in contact with the interior surfaces of the tubes while a second heat transfer fluid, such as ambient air, is in contact with the exterior surfaces of the tubes.
  • a temperature difference exists between the first and second fluids, heat is transferred from the higher temperature fluid to the lower temperature fluid through the walls of the tubes.
  • the internal fins extend substantially the length of the tubes and define a plurality of channels or ports for the flow of a heat transfer fluid between the headers.
  • Heat exchanger tubes having a plurality of channels are also known as multi-port tubes.
  • a known method of manufacturing multi-port tubes is by extruding a billet of deformable heat conductive material through a die.
  • the extrusion process allows for the formation of the internal fins to have intricate geometric features to improve heat transfer efficiency that other known manufacturing process could not readily provide.
  • the extrusion process is known to be expensive because of the need to frequently replace the extrusion die in order to maintain the desired dimensions of the intricate geometric features.
  • Extruded tubes are also prone to corrosion attacks from road salt and acidic rain and require extensive corrosion inhibition coatings for motor vehicle applications, which add to the complexity of manufacturing and cost.
  • Another known method of forming multi-port tubes is by folding a sheet of pliable heat conductive material.
  • a flat elongated sheet of metallic material is folded to form a tube having multiple ports defined by internal corrugated folds.
  • the internal corrugated folds form the internal fins that define the shape and size of the ports.
  • Folded tubes provide numerous advantages over extruded tubes in terms of lower cost and ease of manufacturing for the tube itself as well as for the final assembly of the heat exchanger.
  • One advantage is that a folded tube can be formed from a sheet of clad aluminum that offers superior corrosion protection without the need for applying additional coatings.
  • headers due to the presence of cladding on the tube, other components of the heat exchanger, such as the headers and air fins, need not be cladded, thereby simplifying the material system for corrosion protection.
  • headers since the headers do not need to be cladded, the headers can be formed with extrusion technology to reduce the cost of manufacturing.
  • a shortcoming of a fold tube is that the thickness, or gage, of the sheet of heat conductive material limits the geometry and number of ports that the folding process can provide.
  • the geometry and number of ports are important factors for applications in evaporator type heat exchangers to meet heat transfer requirement within a given core package.
  • One aspect of the invention is an evaporator tube folded from a unitary strip of heat conductive material having a thickness (t).
  • the folded tube includes a cross sectional shape having a bottom wall with two opposing tube edges transitioning into a pair of top walls spaced from and substantially parallel to the bottom wall, a pair of abutted central walls bent substantially perpendicularly out of the top walls and extends toward the bottom wall, a corrugated portion extending substantially perpendicularly out of each of the central walls toward the corresponding tube edge.
  • the bottom wall includes a width (2w), the corrugated portion includes alternating flange segments abutting the interior surface of the tube and channel walls connecting the alternating flange segments; at least one of the alternating adjacent flange segments includes a length (a) cooperating with adjacent channel walls to define a channel having a width (b).
  • the evaporator tube includes a height (h) which is measured from the bottom exterior surface to the top exterior surface of the tube and a corner radius (r c ) defined by the transition radius from a flange segment to the channel wall.
  • PPMW ports per millimeter width
  • PS Port Shape
  • NDG non-dimensional gauge
  • NDCR non-dimensional corner radius
  • Another aspect of the invention is an evaporator assembly having a first header, a second header, at least two banks of evaporator tubes extending between and in hydraulic communication with the first and second headers.
  • At least one of the evaporator tube includes a unitary strip clad aluminum having a thickness (t) folded into a cross sectional shape having a bottom wall with two opposing tube edges transitioning into a pair of top walls spaced from and substantially parallel to the bottom wall, a pair of abutted central walls bent substantially perpendicularly out of the top walls and extend toward the bottom wall, and a corrugated portion extending substantially perpendicularly out of each of the central walls toward the corresponding tube edge.
  • the bottom wall includes a width (2w) and the corrugated portion includes alternating flange segments abutting the interior surface and channel walls connecting the alternating flange segments. At least one of the alternating adjacent flange segments includes a length (a) cooperating with adjacent channel walls to define a channel having a width (b).
  • the evaporator tube includes a height (h) measured from the bottom exterior surface to the top exterior surface and a corner radius (r c ) defined by the transition radius from the flange segment to the channel wall.
  • PPMW ports per millimeter width
  • PS Port Shape
  • NDG non-dimensional gauge
  • NDCR non-dimensional corner radius
  • Folded evaporator tube having the above critical parameters provide evaporators with improved heat transfer performance, reduced refrigerant pressure drop, increased burst strength, increased robustness of brazing process, and reduced heat exchanger mass per unit volume.
  • FIG. 1 is a perspective view of an evaporator having two banks of folded evaporator tubes for a motor vehicle.
  • FIG. 1A is a detail view of the evaporator of FIG. 1 .
  • FIGS. 2A-E show the intermediate stages in the formation of the folded evaporator tube for the evaporator of FIG. 1 .
  • FIG. 3 is a cross-section of a folded evaporator tube having geometric features of the present invention.
  • FIGS. 4A-D are graphs showing the effects of the ranges of the critical parameters of the folded evaporator tube on the operating characteristics of the evaporator shown in FIG. 1 .
  • FIG. 1 Shown in FIG. 1 is a perspective view of an evaporator 10 having dual banks 18 , 20 of evaporator tubes 16 for use in a motor vehicle.
  • the evaporator 10 is typically housed in a HVAC module of a motor vehicle and includes a plurality of evaporator tubes 16 hydraulically connecting two spaced apart headers 12 , 14 for a two-phase refrigerant flow therebetween.
  • the first header 12 is typically an inlet/out let header defining a cavity that includes a substantially center partition 13 extending the length of the first header 12 and separates the cavity into an inlet chamber 26 and an outlet chamber 28 .
  • the inlet chamber 26 is in hydraulic communication with an inlet port 30 and the outlet chamber 28 is in hydraulic communication with an outlet port 32 .
  • the first bank 18 of substantially parallel evaporator tubes 16 hydraulically connects the inlet chamber 26 to the return header 14 and a second bank 20 of evaporator tubes 16 connects the return header 14 to the outlet chamber 28 .
  • External fins 22 are disposed between and interconnect the evaporator tubes 16 to increase the surface area available for heat transfer.
  • the evaporator tubes 16 and fins 22 together define the core 34 of the evaporator 10 through which ambient air flows.
  • a partially expanded two-phase refrigerant flows into the inlet chamber 26 of the first header (inlet/outlet header) by way of the inlet port 30 and continues through the first bank 18 of evaporator tubes 16 to the second header (return header) 14 .
  • the two-phase refrigerant flows through the second bank 20 of evaporator tubes 16 to the outlet chamber 28 of the first header 12 and exits the outlet port 32 .
  • the two-phase refrigerant continues to expand into a vapor phase by absorbing heat from the ambient air.
  • the evaporator tubes 16 include internal geometric features having specific critical parameters that provide for improved performance of the evaporator 10 .
  • FIG. 1A Shown in FIG. 1A is a view of the evaporator 10 of FIG. 1 at detail section 1 A.
  • FIG. 1A shows dual banks of folded B-type evaporator tubes 16 .
  • the B-type evaporator tube 16 shown is typically formed by folding a sheet of heat conductive material to define a series of internal channels 36 for refrigerant flow.
  • the channel walls 72 formed from the folding of the sheet of heat conductive material act as internal fins to increase the area available for heat transfer.
  • FIGS. 2 A-E show the typical stages in the formation of a folded B-type evaporator tube.
  • FIG. 2A Shown in FIG. 2A is a partial sheet of heat conductive material strip 50 , preferably a continuous clad aluminum strip 50 , having a first surface 52 and a second surface 54 extending along a longitudinal A-axis.
  • the heat conductive material strip 50 is longitudinally fed into a multi-station roll forming apparatus having pairs of rollers arranged to symmetrically plastically deform the heat conductive material strip 50 to form a corrugated portion 56 on both sides of the A-axis.
  • Each of the corrugated portions 56 includes a series of alternating crests 57 and joining segments 63 .
  • the alternating crests 57 may be that of sharp corners to substantially flat surfaces that corresponds to the first and second surfaces 52 , 54 of the heat conductive material strip 50 , the significant of which will be discussed below.
  • the corrugated portion 56 is folded inward toward the second surface 54 such that the crests 57 on the same side as the second surface 54 are oriented toward and are in contact with the second surface 54 .
  • the fold of the corrugated portion 56 defines an abutting surface 58 .
  • the folded corrugated portion 56 is folded again toward the second surface 54 such that a portion of the first surface 52 defines an exterior tube edge 60 as shown in FIGS. 2C and 2D .
  • the abutting surfaces 58 of the corrugated portion 56 on either side of the A-axis are abutted upon each other and brazed forming the B type evaporator tube 16 having a center seam that runs the length of the tube as shown in FIG. 2E .
  • the continuous evaporator tube 16 is cut to the desired length.
  • FIG. 3 Shown in FIG. 3 is a cross sectional view of the folded B-type evaporator tube 16 of FIGS. 2A-E having a central wall 62 , two opposing tube edges 60 , a bottom wall 64 , and a pair of top walls 66 .
  • the folded evaporator tube 16 also has internal horizontal flange segments 68 , defined by the crests 57 of the folded material strip 50 , abutting the interior surface 70 of the folded tube and transitioning to channel walls 72 defined by the joining segments 63 .
  • the center walls 62 , tube edges 60 , bottom wall 64 , top walls 66 , and corrugated portions 56 are formed by folding a continuous strip 50 of clad aluminum.
  • the terms “bottom”, “upper”, and “horizontal” are arbitrary, as the evaporator tube could be in any orientation.
  • the central walls 62 need not be exactly in the center of the width of the cross section, but typically will be.
  • the B-type evaporator tube is preferably folded from a clad aluminum strip 50 having a stock thickness of (t) and includes a width (2w) that is measured from external tube edge 60 to external tube edge 60 .
  • a typical B-type evaporator tube for use in automotive applications has a width (2w) in the range from 10 mm to 30 mm for an evaporator 10 having a dual bank of evaporator tubes 16 .
  • the height (h) of the evaporator tube 16 is measured from the exterior surface of the bottom wall 64 to the exterior surface of the top wall 66 .
  • the length of the flange segments 68 abutting the interior surface 70 of the tube surface is shown as (a).
  • the distance of the channel 36 defined between the adjacent intersections of the channel walls 72 and interior surface 70 of the tube is shown as (b).
  • the angle between the channel wall 72 and the interior surface 70 is shown as ( ⁇ ).
  • the corner radius of the transition from the flange to the channel wall 72 is shown as (r c ).
  • the hydraulic parameter and the wetted parameter of the folded evaporator tube 16 is defined as:
  • evaporator tubes 16 having features with certain dimensional ranges, defined in terms of critical parameters offer improvements in heat transfer performance, reduced refrigerant pressure drop, increased burst strength, increased robustness of brazing process, and reduced heat exchanger mass per unit volume for evaporators.
  • the critical parameters are identified as follows: number of ports per unit millimeter width (PPMW); port shape ratio (PS ratio); Non-dimensional gauge (NDG ratio); and Non-dimensional Corner Radius (NDC ratio).
  • the formulas for the critical parameters for applications in evaporators 10 are provided in the Table 1 below:
  • FIGS. 4A-D are graphs showing the effects of the ranges of the critical parameters of the B-type evaporator tube 16 on the performance of the evaporator 10 .
  • Each of the graphs presents performance characteristics of evaporator 10 as illustrated by five curves labeled (1) through (5), corresponding to: (1) heat transfer performance, (2) refrigerant pressure drop, (3) burst strength of the tube, (4) the amount of braze contact across tube width for robustness of brazing process, and (5) heat exchanger mass per unit volume.
  • Each of the respective critical parameters is denoted on the X-axis and the relative change in performance of the evaporator 10 is denoted on the Y-axis.
  • the graphs show the relative changes in performance of the evaporator 10 with the corresponding changes in respective critical parameters.
  • the theoretical maximum number of ports can only be limited by the thickness (t) of the channel wall 72 or material gage. If the number of ports is too large, the cross-section of the tube is filled with a large number of vertical channel walls 72 which decreases the flow cross-section significantly.
  • ⁇ the number of ports
  • the PS ratio can be adjusted by changing both a and b, such that (a+b) must be kept constant to keep constant number of ports.
  • the port shape also changes with h.
  • changing h affects other critical parameters.
  • Changing port shape ratio relates to angle ⁇ and the hydraulic diameter D h , which will affect some of the performance characteristics listed above.
  • the shape of the port changes from a triangular cross section to a rectangular cross-section.
  • the performance characteristic curves ( 2 ) through ( 5 ) increased while performance characteristic curve ( 1 ) decreased.
  • gage is simpler to understand than that for other parameters.
  • the requirement for higher gage comes typically from the corrosion and mechanical strength issue.
  • the heat transfer is also affected by gage to some extent.
  • the webs defining the channels 36 do not conduct heat well and as a result has low fin efficiency. It also reduces burst strength.
  • the performance characteristic curves ( 2 ), ( 3 ), and ( 5 ) increased, while performance characteristic curve ( 4 ) remain substantially unchanged and performance characteristic curve ( 1 ) initially increased and then dropped significantly.
  • corner radius (r c ) is more on the manufacturing aspect of the tube rather than on the product characteristics. Nevertheless, this feature will have secondary impact on the performance characteristics as depicted below.
  • the largest corner radius is when the web as formed by a channel wall 72 and immediate adjacent flange segments 68 takes the shape of “S”.
  • the performance characteristic curve ( 1 ) slight dropped and then increased, performance characteristic curves ( 2 ), and ( 5 ) increased, while performance characteristic curve ( 4 ) remains unchanged, and performance characteristic curve ( 3 ) initially increased and then dropped.
  • Range Range Tube No. of ports per millimeter width 1/w-2/t 0.4-01.0 0.57 (PPMW) 2 Port Shape Ratio (PS ratio) 0.0-1.0 0.05-0.6 0.39 3 Non-dimensional gage (NDG ratio) 0.05-0.333 0.11-0.21 0.186 4 Non-dimensional corner radius 0-1.0 0.1-0.5 0.288 (NDCR)
  • An evaporator 10 having dual banks of B-type evaporator tubes 16 with critical parameters as provided herein has the advantage of having improved heat transfer performance, reduced refrigerant pressure drop, increased burst strength of the tube, increased robustness of brazing process, and reduced heat exchanger mass per unit volume for evaporators.
  • Evaporator tube 16 folded from a sheet of clad aluminum offers superior corrosion protection over that of extruded tubes.
  • the primary brazing alloy comes from the cladding. This cladding on the tube alone is sufficient to braze and adhere the primary components such as the evaporator tubes 16 , external fins 22 and headers 12 , 14 together.
  • headers 12 , 14 and cores 34 which offers both material cost saving and less complication in maintaining material quality and consistency. Also, this enables headers to be made by less costly extrusion process.
  • evaporator tube 16 as disclosed may be used for evaporators 10 having greater than two banks of evaporator tubes 16 and a plurality of refrigerant passes.
US13/107,045 2010-05-20 2011-05-13 Fabricated tube for an evaporator Abandoned US20110284195A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US13/107,045 US20110284195A1 (en) 2010-05-20 2011-05-13 Fabricated tube for an evaporator
EP11166227.6A EP2388545A3 (en) 2010-05-20 2011-05-16 Folded tube for an evaporator and evaporator assembly therewith
CN2011202358111U CN202216603U (zh) 2010-05-20 2011-05-17 折叠蒸发器管及蒸发器组件
US14/734,148 US20150360333A1 (en) 2010-05-20 2015-06-09 Method of fabricating a tube for an evaporator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US34652210P 2010-05-20 2010-05-20
US13/107,045 US20110284195A1 (en) 2010-05-20 2011-05-13 Fabricated tube for an evaporator

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US14/734,148 Continuation-In-Part US20150360333A1 (en) 2010-05-20 2015-06-09 Method of fabricating a tube for an evaporator

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EP (1) EP2388545A3 (zh)
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US20100327617A1 (en) * 2009-06-24 2010-12-30 Oriet Leo P Extruded Cornish Of A Motor Bus Body
US20140196877A1 (en) * 2013-01-14 2014-07-17 Halla Visteon Climate Control Corp. Tube for heat exchanger
US20150144309A1 (en) * 2013-03-13 2015-05-28 Brayton Energy, Llc Flattened Envelope Heat Exchanger
US20150375345A1 (en) * 2013-03-19 2015-12-31 Hydro Aluminium Rolled Products Gmbh Method for producing a roll-clad aluminum workpiece, roll-clad aluminum workpiece, and use therefor
JP2016038192A (ja) * 2014-08-11 2016-03-22 東芝キヤリア株式会社 パラレルフロー型熱交換器および空気調和機
US9874405B2 (en) 2013-02-27 2018-01-23 Mahle International Gmbh Heat exchanger
US11226161B2 (en) * 2017-12-21 2022-01-18 Hanon Systems Heat exchanger
US11566854B2 (en) 2015-12-28 2023-01-31 Carrier Corporation Folded conduit for heat exchanger applications

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CN106091781B (zh) * 2015-09-01 2018-06-26 赵炜 一种双圆弧形通道散热器

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US20100025025A1 (en) * 2006-09-28 2010-02-04 Kazuyoshi Tomochika Heat exchanger and manufacturing method of the same

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US20070119581A1 (en) * 2003-09-30 2007-05-31 Soichi Kato Heat exchanger tube
US20050045314A1 (en) * 2004-08-26 2005-03-03 Valeo, Inc. Aluminum heat exchanger and method of making thereof
US20100025025A1 (en) * 2006-09-28 2010-02-04 Kazuyoshi Tomochika Heat exchanger and manufacturing method of the same
US20090065184A1 (en) * 2007-09-06 2009-03-12 Denso Corporation Heat exchanger
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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100327617A1 (en) * 2009-06-24 2010-12-30 Oriet Leo P Extruded Cornish Of A Motor Bus Body
US8215707B2 (en) * 2009-06-24 2012-07-10 Navistar Canada, Inc. Extruded cornish of a motor bus body
US20140196877A1 (en) * 2013-01-14 2014-07-17 Halla Visteon Climate Control Corp. Tube for heat exchanger
US10113811B2 (en) * 2013-01-14 2018-10-30 Hanon Systems Tube for heat exchanger
US9874405B2 (en) 2013-02-27 2018-01-23 Mahle International Gmbh Heat exchanger
US20150144309A1 (en) * 2013-03-13 2015-05-28 Brayton Energy, Llc Flattened Envelope Heat Exchanger
US20150375345A1 (en) * 2013-03-19 2015-12-31 Hydro Aluminium Rolled Products Gmbh Method for producing a roll-clad aluminum workpiece, roll-clad aluminum workpiece, and use therefor
US10065271B2 (en) * 2013-03-19 2018-09-04 Hydro Aluminium Rolled Products Gmbh Method for producing a roll-clad aluminum workpiece, roll-clad aluminum workpiece, and use therefor
JP2016038192A (ja) * 2014-08-11 2016-03-22 東芝キヤリア株式会社 パラレルフロー型熱交換器および空気調和機
US11566854B2 (en) 2015-12-28 2023-01-31 Carrier Corporation Folded conduit for heat exchanger applications
US11226161B2 (en) * 2017-12-21 2022-01-18 Hanon Systems Heat exchanger

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Publication number Publication date
CN202216603U (zh) 2012-05-09
EP2388545A2 (en) 2011-11-23
EP2388545A3 (en) 2018-03-21

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