EP1746377A1 - Connection entre la paroi d'une boîte collectrice et un tuyau pour une perte de charge minimale dans un échangeur de chaleur - Google Patents

Connection entre la paroi d'une boîte collectrice et un tuyau pour une perte de charge minimale dans un échangeur de chaleur Download PDF

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Publication number
EP1746377A1
EP1746377A1 EP06076270A EP06076270A EP1746377A1 EP 1746377 A1 EP1746377 A1 EP 1746377A1 EP 06076270 A EP06076270 A EP 06076270A EP 06076270 A EP06076270 A EP 06076270A EP 1746377 A1 EP1746377 A1 EP 1746377A1
Authority
EP
European Patent Office
Prior art keywords
pipe
assembly
set forth
collar
header wall
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.)
Withdrawn
Application number
EP06076270A
Other languages
German (de)
English (en)
Inventor
Henry Earl Beamer
Chris A. Calhoun
Khalid El Moutamid
Lin-Jie Huang
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.)
Delphi Technologies Inc
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
Publication of EP1746377A1 publication Critical patent/EP1746377A1/fr
Withdrawn legal-status Critical Current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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0234—Header boxes; End plates having a second heat exchanger disposed there within, e.g. oil cooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/067—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines

Definitions

  • This invention relates to automotive heat exchangers in general, and specifically to a liquid flow heat exchanger, such as a radiator, with a novel in tank structure for reducing the pressure drop caused by flow turning losses.
  • Automotive heat exchangers that use a pumped, liquid heat exchange medium, as opposed to a compressed gaseous/liquid heat exchange medium, include radiators and heaters.
  • these include two elongated manifolds or header tanks, one on each side of the heat exchanger, with a central core consisting of a plurality of evenly spaced, flattened flow tubes and interleaved corrugated air fins running between the two tanks.
  • Each tank is generally box shaped, with parallel side walls, a back wall joining the side walls, two axially opposed ends, and an open area opposite the back wall, which is eventually closed off when it is fixed leak tight to one side of the core.
  • Each header tank distributes pumped liquid to or from the flow tubes in the core, and is in turn filled or drained by an inlet or outlet pipe opening into the header tank at a discrete location.
  • the inlet or outlet pipe to the header tank is oriented both transversely to the length of the tank and to the flow tubes. Coolant flow entering the inlet pipe must, therefore, turn through a substantial angle toward the two ends of the tank before as well as turning substantially again to flow out of the tank interior and into the flow tubes. The converse is true for coolant exiting the return tank through the outlet pipe.
  • An example of a recent radiator with molded plastic, box shaped header tanks may be seen in U.S. Pat. No.
  • the design of a radiator or any cross flow heat exchanger with a liquid medium flowing in one direction through flow tubes, and with air blown perpendicularly across the flow tubes, is a compromise between heat exchange efficiency between the two flowing media, and the pressure or pumping losses of the two media.
  • decreasing the flow passage cross sectional area will present relatively more surface area of the fluid medium within the flow passage to the air blowing over the flow tube, increasing the heat transfer efficiency from fluid to air.
  • a tube that is smaller on the inside is also thinner on the outside, and so presents less obstruction the air blown over the outside of it, decreasing the air side pressure loss through the core.
  • a thinner flow tube creates more fluid pressure loss through the tube, end to end.
  • radiator header tanks become smaller, and the parallel sidewalls become closer.
  • Flow exiting the opening of the inlet pipe (through the first side wall) impinges on the proximate, opposed second side wall, creating turbulence and pressure loss before it can be distributed toward the opposite ends of the tank and into the flow tubes.
  • the other liquid medium heat exchanger typically found in an automobile, the heater core, has a similar cross flow configuration, but faces a different problem.
  • the inlet pipe generally opens through the back wall of the header tank, in line with, rather than perpendicular to, the flow tubes.
  • the flow thus impinges directly onto the ends of the nearest aligned flow tubes, rather than against a sidewall of the tank, which would theoretically be positive, in terms of direct flow into the tubes with minimal pressure loss.
  • the fact that the ends of the nearest tubes are in line with the inlet pipe is a detriment, because the force of the impinging flow against the near tube ends causes erosion and damage.
  • Plate type oil coolers are frequently incorporated in radiator tanks to provide engine and transmission oil cooling. Due to packaging constraints, it is common for oil coolers to straddle the coolant inlet/outlet pipes. This flow blockage increases coolant pressure drop and creates local regions of high coolant velocity that can cause erosion corrosion of the oil cooler. In a typical cross flow radiator, the tanks and oil cooler represent 50% of the total coolant pressure drop. The penalty due to the oil cooler blockage is 35-40% of the tank pressure drop ( ⁇ 20% of total pressure drop).
  • the most common method used to limit the oil cooler coolant pressure drop penalty is the spacing (stand off height) of the oil cooler from the inside tank wall.
  • the pressure drop penalty typically it is not practical to reduce the pressure drop penalty below the levels described above because the increased stand off height required will reduce the size of oil cooler that can be installed in the tank, or a larger tank must be used with increased packaging space, mass, and cost penalties.
  • the internal juncture between the pipe and tank is typically sharp edged. Due to the joint design, the pipe is frequently extended into the tank to allow secure clinching of the pipe to the tank. Both the sharp edge and pipe extension act to increase coolant pressure drop.
  • the subject invention provides a radiator header tank to pipe joint that reduces coolant pressure drop by reducing turning losses at the transition between the pipe and the header tank wall.
  • the heat exchanger assembly of the subject invention is distinguished by a transition between the header wall and the pipe extending transition completely around the opening to present an expanding flow control surface between from the header wall to the pipe for conveying the heat exchange medium closely over the control surface between the tank interior and the pipe to reduce turbulence and pressure loss at the transition between the tank interior the said pipe.
  • This invention provides a transition to significantly reduce the oil cooler pressure drop penalty and/or reduce the size of the tank.
  • a method of determining the required feature size and practical designs are provided for integrally molded or fabricated sheet metal tanks. Several configurations are shown that incorporate an internal radius or chamfer to eliminate the pipe extension inside the tank.
  • a heat exchanger assembly constructed in accordance with the subject invention is generally shown at 20 in Figures 1 and 2.
  • the assembly 20 includes a core comprising a plurality of flow tubes 22 having heat exchange fins 24 extending therebetween.
  • a header tank 26 distributes a flowing liquid heat exchange medium to and from the flow tubes 22 and presents a header wall 28 with an interior surface.
  • a pipe 30 is disposed in an opening through the header wall 28.
  • a joint extends between the pipe 30 and the header wall 28 to define an endless transition completely around the opening to present an expanding flow control surface between the pipe 30 and the interior surface 32 of the header wall 28 for conveying the heat exchange medium closely over the control surface between the interior surface and the pipe 30 to reduce turbulence and pressure loss at the transition between the interior surface and the pipe 30.
  • a typical pipe to header wall joint is shown in Figure 3 wherein a sharp edged corner is presented annularly about the opening into the header wall 28.
  • the pipe is formed in a cylindrical shape to define entry flow into the header as cylindrical.
  • the cylindrical pipe could be flattened into an oval, elliptical, or other shape at the joint.
  • the joint of the subject invention presents an expanding flow control surface with a rounded radius 32 or a straight or conical shaped chamfer 34 as illustrated in Figure 4.
  • the use of a chamfer 34 is slightly more effective than the radius 32 due to increased entrance flow area for the same size pipe flow area as shown in Figure 5.
  • the typical pipe/tank juncture is a sharp edged corner as illustrated in Figure 3.
  • the limiting entrance flow area into the pipe is a cylinder.
  • This invention replaces the sharp corner with a radius or chamfer to increase entrance flow area and facilitate turning of the flow into the pipe.
  • Flow streamlines for both sharp and chamfered geometry's are shown in figures 3 and 4.
  • Use of a chamfer is slightly more effective than a radius due to increased entrance flow area for the same size feature as shown in Figures 5 and 7.
  • the optimum chamfer angle was found to be 45° as shown in Figure 8.
  • radius/chamfer size is similar through out the practical range of pipe and standoff sizes.
  • a radius/chamfer of 2.0 mm yields approximately 50% of the total savings possible as shown in Figures 9 and 10. Therefore this invention claims the use of a radius or 30/60° chamfer equal to or greater than 2.0 mm.
  • the pipe 30 is cylindrical about an axis and the flow control surface expands radially as it opens axially into the interior surface 32 of the header wall 28, it expanding through a radius or through a cone shaped chamfer.
  • the header wall 28 presents a planar disk-like portion immediately adjacent to and extending radially from the opening in the header wall 28 to define the interior surface 32 in a radial plane.
  • the control surface blends into the planar disk-like portion to present a smooth transition of the control surface from the pipe 30 into the interior surface 32 of the header wall 28. It is important that the control surface blend into the planar interior surface 32 to present a smooth transition of the control surface from the pipe 30 into the interior surface 32 of the header wall 28.
  • control surface may extend through a radius 32 or through a cone to define a chamfer 34.
  • the pipe 30 is integrally formed of plastic material with the header wall 28 define the chamfered control surface 34 that expands to the radial plane of the interior surface 32 of the header wall 28.
  • An oil cooler 36 is disposed opposite to the pipe 30. The chamfer 34 significantly reduces the pressure drop caused by the imposition of the oil cooler 36.
  • the header wall 28 defines the control surface and the control surface expands from a cylindrical collar 40 to the radial plane of the interior surface 32. Said another way, the header wall 28 extends through a transition control surface into a cylindrical collar 40, which receives the pipe 30.
  • the pipe 30 extends within the opening of the collar 40 and terminates in an annular edge 38.
  • the header wall 28 extends into the axially extending collar 40 to surround and engage the pipe 30.
  • the pipe 30 includes a bead 42 abutting the open end of the collar 40.
  • the pipe 30 has an end which terminates in spaced relationship to the radial plane in the header wall 28.
  • the pipe 30 is disposed about the exterior of the collar 40.
  • the pipe 30 is flared 48 outwardly into a flare to engage the exterior of the collar 40 defining the control surface.
  • the pipe 30 includes an enlarged end 50 defining a shoulder 52 for surrounding and engaging the exterior of the collar 40 with the shoulder 52 abutting the collar 40.
  • the only difference in Figure 15 is that the pipe 30 and the collar 40 are forced radially into one another to create a mechanically overlapping connection in the axial direction.
  • the pipe 30 and the collar 40 include mating undulations 54 extending annularly thereabout for locking the pipe 30 to the collar 40 to create a mechanically overlapping connection in the axial direction.
  • the various embodiments may employ the radius 32 shown in Figures 12-14 and 16 or the chamfer 34 shown in Figures 11 and 15 and that either may be used with the various species of Figures 11-16.
  • the joint may be formed with a radiused or chamfered flange and may be secured by fixturing, staking, tack weld, or spin welding, prior to final bonding.
  • the pipe 30 end may be expanded to engage the outside surface of the collar or flange 40 as illustrated in Figures 11-12. A feature can be added to the end of the pipe 30 to provide lead in.
  • the pipe 30 and the header wall 28 may be molded of an organic polymeric material (plastic) or formed of sheet metal, when of metal, the pipe 30 may be secured to the tank 26 prior to brazing by expanding the collar 40 into the pipe 30.
  • the pipe 30 can be a press fit on to the collar 40, or can be shrunk onto the collar 40. Either the collar 40 or the pipe 30 can be tapered to control the press fit characteristics.
  • the collar 40 can be expanded into the pipe 30 or the pipe 30 shrunk on to the collar 40.
  • the bead 42 may be formed into the pipe 30 and the collar expanded into the bead 42. All configurations allow the use of an unclad pipe 30 and externally clad tank 26.
  • All configurations are designed to allow brazing of the pipe 30 and collar.
  • clad material is used for the tank 26 body and bare material for the pipe 30, but either or both parts can be clad.
  • a separate source of braze material can be used such as a braze ring or braze paste.
  • Some of the configurations could also be spin welded.
  • the pipe 30 may be mechanically attached or bonded to the collar 40, as by an adhesive, fusion or spin welding or integrally molded.
  • the collar 40 and the pipe 30 may be bonded together by brazing, soldering, welding or an adhesive, depending upon the composition of the components.
  • the pipe 30 may be secured prior to bonding to the collar 40 by fixturing, a press fit, e.g., expanding or shrinking, staking, forming undulations, etc.
  • the pipe 30 and/or collar 40 may include a lead-in such as a taper, or the locating bead 42 or shoulder 52.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP06076270A 2005-07-19 2006-06-20 Connection entre la paroi d'une boîte collectrice et un tuyau pour une perte de charge minimale dans un échangeur de chaleur Withdrawn EP1746377A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/184,478 US20070017664A1 (en) 2005-07-19 2005-07-19 Sheet metal pipe geometry for minimum pressure drop in a heat exchanger

Publications (1)

Publication Number Publication Date
EP1746377A1 true EP1746377A1 (fr) 2007-01-24

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EP06076270A Withdrawn EP1746377A1 (fr) 2005-07-19 2006-06-20 Connection entre la paroi d'une boîte collectrice et un tuyau pour une perte de charge minimale dans un échangeur de chaleur

Country Status (2)

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US (1) US20070017664A1 (fr)
EP (1) EP1746377A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402694A1 (fr) * 2010-06-30 2012-01-04 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile et echangeur de chaleur equipe d'un tel condenseur
CN106482367A (zh) * 2016-12-01 2017-03-08 浙江鸿乐光热科技有限公司 一种太阳能热水器水管座导流接头
EP3943860A1 (fr) * 2020-07-23 2022-01-26 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006003317B4 (de) 2006-01-23 2008-10-02 Alstom Technology Ltd. Rohrbündel-Wärmetauscher
WO2008083220A1 (fr) * 2006-12-27 2008-07-10 Johnson Controls Technology Company Distribution de réfrigérant de condenseur
US8166776B2 (en) * 2007-07-27 2012-05-01 Johnson Controls Technology Company Multichannel heat exchanger
US9557119B2 (en) 2009-05-08 2017-01-31 Arvos Inc. Heat transfer sheet for rotary regenerative heat exchanger
JP2013507263A (ja) * 2009-10-09 2013-03-04 ノアグレン ゲゼルシャフト ミット ベシュレンクテル ハフツング ブロー成形システムのバルブ・ブロック・アセンブリ
US8439104B2 (en) * 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution
US9200853B2 (en) 2012-08-23 2015-12-01 Arvos Technology Limited Heat transfer assembly for rotary regenerative preheater
JP2014126284A (ja) * 2012-12-26 2014-07-07 Daikin Ind Ltd 冷凍装置
US10175006B2 (en) 2013-11-25 2019-01-08 Arvos Ljungstrom Llc Heat transfer elements for a closed channel rotary regenerative air preheater
US10094626B2 (en) 2015-10-07 2018-10-09 Arvos Ljungstrom Llc Alternating notch configuration for spacing heat transfer sheets
US10240874B2 (en) 2017-08-04 2019-03-26 Denso International America, Inc. Radiator tank
US11098966B2 (en) 2018-08-08 2021-08-24 Denso International America, Inc. Header tank for heat exchanger

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Publication number Priority date Publication date Assignee Title
JPH06241614A (ja) * 1993-02-12 1994-09-02 Sharp Corp 熱交換器
EP0702201A1 (fr) * 1994-09-14 1996-03-20 General Motors Corporation Noyau d'échangeur de chaleur avec conduit d'alimentation débouchant à l'intérieur
JPH0989491A (ja) * 1995-09-21 1997-04-04 Usui Internatl Ind Co Ltd Ｅｇｒガス冷却装置
FR2750483A1 (fr) * 1996-06-27 1998-01-02 Valeo Climatizzazione Spa Radiateur a securite amelioree pour le chauffage de l'habitacle d'un vehicule automobile
US5762130A (en) 1996-12-09 1998-06-09 General Motors Corporation Down flow, two pass radiator with air venting means
DE19849574A1 (de) * 1998-10-27 2000-05-11 Valeo Klimatech Gmbh & Co Kg Rohrverbindung zwischen einem Sammler eines Kraftfahrzeugwärmetauschers und einer äußeren Rohrleitung für das innere Wärmetauschfluid und Verfahren zum Herstellen der Rohrverbindung
US6116335A (en) 1999-08-30 2000-09-12 Delphi Technologies, Inc. Fluid flow heat exchanger with reduced pressure drop
US6283200B1 (en) 1998-12-03 2001-09-04 Denso Corporation Heat exchanger having header tank increased in volume in the vicinity of pipe connected thereto
JP2002181486A (ja) * 2000-12-15 2002-06-26 Denso Corp 熱交換器
FR2844346A1 (fr) * 2002-09-10 2004-03-12 Valeo Climatisation Echangeur de chaleur comportant au moins une tubulure de racordement
JP2005156000A (ja) * 2003-11-25 2005-06-16 Denso Corp 熱交換器

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JPS5531204A (en) * 1978-08-23 1980-03-05 Diesel Kiki Co Ltd Heat exchanger
US4544030A (en) * 1983-08-15 1985-10-01 American Standard Inc. Shell nozzle
JPH0271097A (ja) * 1988-09-06 1990-03-09 Diesel Kiki Co Ltd 熱交換器
US5513700A (en) * 1994-07-29 1996-05-07 Ford Motor Company Automotive evaporator manifold
SE9702420L (sv) * 1997-06-25 1998-12-26 Alfa Laval Ab Plattvärmeväxlare
DE10203521A1 (de) * 2002-01-30 2003-07-31 Modine Mfg Co Schnellverschlusskupplung

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06241614A (ja) * 1993-02-12 1994-09-02 Sharp Corp 熱交換器
EP0702201A1 (fr) * 1994-09-14 1996-03-20 General Motors Corporation Noyau d'échangeur de chaleur avec conduit d'alimentation débouchant à l'intérieur
JPH0989491A (ja) * 1995-09-21 1997-04-04 Usui Internatl Ind Co Ltd Ｅｇｒガス冷却装置
FR2750483A1 (fr) * 1996-06-27 1998-01-02 Valeo Climatizzazione Spa Radiateur a securite amelioree pour le chauffage de l'habitacle d'un vehicule automobile
US5762130A (en) 1996-12-09 1998-06-09 General Motors Corporation Down flow, two pass radiator with air venting means
DE19849574A1 (de) * 1998-10-27 2000-05-11 Valeo Klimatech Gmbh & Co Kg Rohrverbindung zwischen einem Sammler eines Kraftfahrzeugwärmetauschers und einer äußeren Rohrleitung für das innere Wärmetauschfluid und Verfahren zum Herstellen der Rohrverbindung
US6283200B1 (en) 1998-12-03 2001-09-04 Denso Corporation Heat exchanger having header tank increased in volume in the vicinity of pipe connected thereto
US6116335A (en) 1999-08-30 2000-09-12 Delphi Technologies, Inc. Fluid flow heat exchanger with reduced pressure drop
JP2002181486A (ja) * 2000-12-15 2002-06-26 Denso Corp 熱交換器
FR2844346A1 (fr) * 2002-09-10 2004-03-12 Valeo Climatisation Echangeur de chaleur comportant au moins une tubulure de racordement
JP2005156000A (ja) * 2003-11-25 2005-06-16 Denso Corp 熱交換器

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402694A1 (fr) * 2010-06-30 2012-01-04 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile et echangeur de chaleur equipe d'un tel condenseur
FR2962199A1 (fr) * 2010-06-30 2012-01-06 Valeo Systemes Thermiques Condenseur, notamment pour systeme de climatisation d'un vehicule automobile.
CN106482367A (zh) * 2016-12-01 2017-03-08 浙江鸿乐光热科技有限公司 一种太阳能热水器水管座导流接头
EP3943860A1 (fr) * 2020-07-23 2022-01-26 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
WO2022017751A1 (fr) * 2020-07-23 2022-01-27 Valeo Autosystemy Sp. Z O.O. Échangeur de chaleur

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