EP2253921A2 - Nervure pour un caloporteur - Google Patents

Nervure pour un caloporteur Download PDF

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Publication number
EP2253921A2
EP2253921A2 EP10162268A EP10162268A EP2253921A2 EP 2253921 A2 EP2253921 A2 EP 2253921A2 EP 10162268 A EP10162268 A EP 10162268A EP 10162268 A EP10162268 A EP 10162268A EP 2253921 A2 EP2253921 A2 EP 2253921A2
Authority
EP
European Patent Office
Prior art keywords
rib
gill
gills
heat exchanger
rib according
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Withdrawn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
EP10162268A
Other languages
German (de)
English (en)
Other versions
EP2253921A3 (fr
Inventor
Michael Kohl
Christoph Kästle
Ying Fu
Isabel Munoz
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 Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2253921A2 publication Critical patent/EP2253921A2/fr
Publication of EP2253921A3 publication Critical patent/EP2253921A3/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Withdrawn legal-status Critical Current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
    • 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

Definitions

  • the invention relates to a rib for a heat exchanger according to the preamble of claim 1.
  • US 2005/0045314 A1 describes ribs for a heat exchanger, in which a corrugated, arranged between flat tubes fin plate is provided to improve the heat transfer with gills.
  • the gill angle is between 14 ° and 26 °. This optimized range of the gill angle can be combined with all depths of the girth, and more preferably with small girths of between 0.3 mm and 0.6 mm.
  • the Kiementiefe to further optimize the properties between 0.4 mm and 0.6 mm, more preferably between 0.45 mm and 0.55 mm.
  • the Kiementiefe for further optimization between 1.2 mm and 1.6 mm.
  • a rib density in the longitudinal direction is generally preferably between 70 Ri / dm and 120 Ri / dm.
  • the unit Ri / dm is to be understood as the number of rib flanks given by the corrugation per decimeter.
  • the rib flanks are regularly arranged at an angle to each other to improve the mechanical stability, but can also run parallel to each other depending on requirements.
  • a material thickness of the fin plate is approximately between 0.06 mm and 0.1 mm.
  • the inventive dimensioning of the gills is particularly suitable when the multiple gills follow each other directly. This means that between successive ribs no flat web of the remains, so that two gills are separated from each other by means of a single Einschitts in the sheet.
  • a first gill group and a second gill group are provided, wherein the gill angles KW of the gill groups have different orientations.
  • the gaseous fluid is first passed in one direction through the fin plate and subsequently in the opposite direction.
  • a rib height RH is preferably between 3 mm and 12 mm. In a particularly preferred detailed design, the rib height is between 4 mm and 8 mm.
  • a depth of the rib in the depth direction is between 15 mm and 80 mm, preferably between 15 mm and 45 mm.
  • a rib density in the longitudinal direction is not more than about 80 Ri / dm, and in a preferred detail design, the gill angle is at least 26 °. In an alternative embodiment, a rib density in the longitudinal direction is at least about 80 Ri / dm, in particular, the gill angle is not more than about 26 °. Overall, this allows a further optimization of the performance, taking into account the rib density, which can be predetermined depending on the application.
  • the object of the invention is also achieved for a heat exchanger according to claim 13 by providing a rib according to the invention.
  • the heat exchanger is designed as a heat exchanger of a motor vehicle, in particular as an electric radiator, liquid-operated radiator, evaporator or condenser of a vehicle air conditioning, intercooler or coolant radiator.
  • a motor vehicle in particular as an electric radiator, liquid-operated radiator, evaporator or condenser of a vehicle air conditioning, intercooler or coolant radiator.
  • the rib according to the invention is particularly suitable for use with a radiator, since it allows for a given air flow and given temperature difference a particularly small pressure drop. This reduces noise and makes it possible, for example, to make a heating fan particularly small.
  • the structures may also be flat tubes or round tubes in which, for example, heated coolant flows through an engine cooling circuit.
  • the in Fig. 1 shown heat exchanger is a radiator for a motor vehicle.
  • ribs 2 are respectively provided between structures in the form of parallel flat tubes 1, through which a heated coolant of an engine cooling circuit flows, so that overall a heat transfer network through which a gaseous fluid such as air flows is formed.
  • the flow direction of the air extends in the direction of a depth of the heat exchanger perpendicular to the plane of the drawing in Fig. 1 ,
  • the flat tubes 1 each open into a bottom 3 of a collector.
  • a height direction in the sense of the invention runs in the plane of the drawing Fig. 1 from left to right, ie perpendicular to the direction of the flat tubes and to the depth direction.
  • a longitudinal direction in the sense of the invention runs in the plane of the drawing Fig. 1 from top to bottom, ie parallel to the flat tubes.
  • the rib 2 are formed in their construction principle in a known manner as gill corrugated ribs of a corrugated in the longitudinal direction ribbed plate, wherein the individual ribs formed by the corrugation each having a plurality of gills 4.
  • the gills 4 are formed as a set-up opening of the ribbed plate and arranged one behind the other in the depth direction.
  • the gills are formed as a series of directly consecutive in the depth direction, so formed by means of only one incision of the rib sheet each other and angled webs.
  • the installation angle relative to the depth direction is defined as the gill angle KW.
  • the total length of a gill, measured in a plane with the depth direction, is defined as the kite depth KT.
  • the gills have according to Fig. 2 also a gill length KL, which is slightly smaller than a rib height RH, so that the bending of the ribbed plate is possible.
  • the rib height RH also corresponds to the free distance of adjacent flat tubes 1.
  • the gill length KL in optimized form is between 0.5 mm and 2 mm less than the rib height RH.
  • the number of rib flanks per unit length in the longitudinal direction is defined as the rib density RD (unit: Ri / dm).
  • the rib density RD is between 70 and 120 Ri / dm.
  • the total length of the ribs in the depth direction or flow direction of the air is defined as the rib depth RT and is typically between 15 mm and 80 mm, depending on the requirements.
  • the sectional view Fig. 3 shows that the gills 4 are provided in the depth direction as two successive gill panels 5.6 of each identical gills, the gill angle of the two fields 5, 6 is the same size, but inverted in the direction. Thus, the air is first passed in one direction and then in the reverse direction through the fin plate.
  • a respective peripheral girth 5a, 6a is provided, which has only half the height of a normal gill 4 above the plane of the sheet.
  • a roof gill 7 is provided in each case, which ensures a transfer between the differently directed gill fields 5, 6.
  • All of the belts 4,5a, 6a, 7 have in each case the same height above the plane of the sheet in all the present exemplary embodiments.
  • Fig. 5 shows the results of experiments on different rib densities with variation of the gill angle for a constant depth of girth of 1.5 mm, so a much greater Kiementiefe than in the prior art.
  • an air mass flow MS 3 kg / min was set.
  • the measured variable is the achieved temperature difference of the air as a function of the pressure drop.
  • the X-shaped mark shows the working point according to the above technique.
  • the set air mass flow is again 3 kg / min.
  • the explanation for the surprising effect is that due to the large depth of the kite, even at small gill angles (eg 22 °) enough air flows through the gills (see also Fig. 9 ). Due to the small gill angle, the detachments behind each gill are smaller than at large gill angles (27 °, state of the art). The air distribution perpendicular to the flow direction is thereby more homogeneous or it comes to more uniform air velocities.
  • Fig. 10 and Fig. 11 show speed profiles for different rib heights, namely 4.5 mm ( Fig. 10 ) and 6 mm ( Fig. 11 ). Clearly visible is the much more homogeneous velocity profile of variants 1 and 2 according to the present invention compared to the prior art.
  • the above-described preferred embodiments of a fin are applicable to various types of heat exchangers, particularly automobiles, such as coolant coolers, air conditioner evaporators, air conditioner condensers, intercoolers, or the like. Particularly preferred is an application in radiators of a motor vehicle, since the required power of a fan blower can be reduced here by the low pressure drop for a given performance and the overall homogeneous flow through the network.
  • the heat exchanger is designed as an electric heater, wherein the structures 1 are not flat tubes, but PTC elements which are heated by electric current.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP10162268.6A 2009-05-13 2010-05-07 Nervure pour un caloporteur Withdrawn EP2253921A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910021179 DE102009021179A1 (de) 2009-05-13 2009-05-13 Rippe für einen Wärmeübertrager

Publications (2)

Publication Number Publication Date
EP2253921A2 true EP2253921A2 (fr) 2010-11-24
EP2253921A3 EP2253921A3 (fr) 2014-04-09

Family

ID=42562534

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10162268.6A Withdrawn EP2253921A3 (fr) 2009-05-13 2010-05-07 Nervure pour un caloporteur

Country Status (2)

Country Link
EP (1) EP2253921A3 (fr)
DE (1) DE102009021179A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017200422A1 (de) 2017-01-12 2018-07-12 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Verfahren zur Herstellung eines Wärmeübertragers und Wärmeübertrager

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011004306A1 (de) 2011-02-17 2012-08-23 Behr Gmbh & Co. Kg Rippe für einen Wärmeübertrager
DE102014222983A1 (de) 2014-11-11 2016-05-12 Mahle International Gmbh Wellrippe für einen Wärmeübertrager
DE102016210159A1 (de) 2016-06-08 2017-12-14 Mahle International Gmbh Rippenelement für einen Wärmeübertrager
DE102022212358A1 (de) 2022-11-18 2024-05-23 Mahle International Gmbh Wellrippe für einen Wärmeübertrager

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050045314A1 (en) 2004-08-26 2005-03-03 Valeo, Inc. Aluminum heat exchanger and method of making thereof

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3050963C3 (de) * 1980-04-30 1995-11-09 Nippon Denso Co Wärmetauscher
JPS59107190A (ja) * 1982-12-10 1984-06-21 Nippon Radiator Co Ltd 熱交換器
US5329988A (en) * 1993-05-28 1994-07-19 The Allen Group, Inc. Heat exchanger
JP3775302B2 (ja) * 2002-01-23 2006-05-17 株式会社デンソー 熱交換器
US6805193B2 (en) * 2002-01-24 2004-10-19 Valeo, Inc. Fin louver design for heat exchanger
JP2003240470A (ja) * 2002-02-19 2003-08-27 Denso Corp 熱交換器
US7147047B2 (en) * 2002-03-09 2006-12-12 Behr Gmbh & Co. Kg Heat exchanger
DE10235038A1 (de) * 2002-07-31 2004-02-12 Behr Gmbh & Co. Flachrohr-Wärmeübertrager
AU2004239162A1 (en) * 2003-05-19 2004-11-25 Showa Denko K.K. Heat exchanger fin, heat exchanger, condensers, and evaporators
DE10360240B4 (de) * 2003-08-21 2005-09-01 Visteon Global Technologies, Inc., Dearborn Rippe für Wärmeübertrager mit paralleler Schichtung von flachen Wärmeübertragerrohren
JP2006207966A (ja) * 2005-01-31 2006-08-10 Denso Corp 熱交換器
JP2007212009A (ja) * 2006-02-07 2007-08-23 Sanden Corp 熱交換器
KR100821180B1 (ko) * 2006-11-28 2008-04-14 현대모비스 주식회사 열교환기용 방열핀

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050045314A1 (en) 2004-08-26 2005-03-03 Valeo, Inc. Aluminum heat exchanger and method of making thereof

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017200422A1 (de) 2017-01-12 2018-07-12 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Verfahren zur Herstellung eines Wärmeübertragers und Wärmeübertrager

Also Published As

Publication number Publication date
DE102009021179A1 (de) 2010-11-18
EP2253921A3 (fr) 2014-04-09

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