EP2096397B1 - Ailette pour un échangeur thermique - Google Patents

Ailette pour un échangeur thermique Download PDF

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Publication number
EP2096397B1
EP2096397B1 EP08017257.0A EP08017257A EP2096397B1 EP 2096397 B1 EP2096397 B1 EP 2096397B1 EP 08017257 A EP08017257 A EP 08017257A EP 2096397 B1 EP2096397 B1 EP 2096397B1
Authority
EP
European Patent Office
Prior art keywords
edge
fin
approximately
face
heat exchanger
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.)
Ceased
Application number
EP08017257.0A
Other languages
German (de)
English (en)
Other versions
EP2096397A3 (fr
EP2096397A2 (fr
Inventor
Hermann Knaus
Florian Schmidt
Werner Oswald
Jens Paulik
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 EP2096397A2 publication Critical patent/EP2096397A2/fr
Publication of EP2096397A3 publication Critical patent/EP2096397A3/fr
Application granted granted Critical
Publication of EP2096397B1 publication Critical patent/EP2096397B1/fr
Ceased legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0082—Charged air coolers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making

Definitions

  • ribs in fluid-flow channels are provided to improve the heat exchanger performance.
  • Such ribs may be formed, for example, as smooth ribs, gill ribs or ribbed ribs.
  • Bar ribs show a particularly significant improvement of the heat exchange performance given the size, but also mean an often undesirably large pressure drop across the flow channel.
  • Web ribs are used inter alia in intercoolers of motor vehicles, and mainly on the side of the charge air.
  • DD 0 152 187 describes a strip-shaped tube installation element for shell and tube heat exchangers in the field of the petrochemical industry, in which trapezoidal louvers are provided for generating turbulence.
  • the louvers have a variable width in the direction of flow, the lugs being bent out of the strip by an angle of greater than 30 ° about a longer of two parallel edges of the trapezoid.
  • the WO 2009/015805 A1 discloses a rib for a heat exchanger in which a tab is disclosed.
  • the first edge, at least one end edge of the at least one side wall and a second straight edge of the wall surface form an opening oriented essentially perpendicular to the flow direction and permeable by the first fluid, which has a substantially triangular shape.
  • the tab surface is connected via a third edge to the wall surface, wherein the tab surface is angled over the third edge to the wall surface and the angle is advantageously between about eight degrees and about sixteen degrees, in particular about twelve degrees.
  • the length of the third edge is advantageously between about twice and about four times, in particular about three times the length of the first edge. Overall, this is a hood-like leaching provided with very low pressure drop with good heat transfer of the air flowing through, as has been shown by experiments.
  • a rib according to the invention can also be made of steel or another material which is suitable depending on the requirements.
  • the shape of the tab surface starting from the first edge has approximately the parameterization [0; 2,500], [0.805; 2,470], [1.610; 2,290], [2,420; 1,910], [3,220; 1.540], [4.030; 1,210], [4,840; 0.980], [5.640; 0.780], [6.440; 0.590], [7.240; 0.400], [8.050; 0.210], the first value indicating the distance from the first edge in the flow direction, and the second value respectively indicating the distance of the side wall from the third edge.
  • Such a shape corresponds in plan view of the tab surface approximately one on its central axis halved "NACA air inlet" according to the aforementioned research report number RM A9L29.
  • a width of the tab surface decreases with increasing distance from the first edge, so that a nozzle effect for flowing along the leaching air flows.
  • the curvature of the at least one side wall in its course at least one inflection point with respect to the direction of curvature, whereby a particularly good modulation of the air flow to improve the heat transfer is achieved at the same time low pressure drop.
  • the inclination of the tab surface relative to the wall surface is between about five degrees and about ten degrees, in particular about seven degrees.
  • the rib in the flow direction on several successively arranged leaching resulting in particular in long ribs a meaningful arrangement for the purpose of multiple deflection of the air over the ribs. Otherwise, the Air flow only affects part of the rib on advantageous way through the leaching.
  • At least one of the plurality of louvers is particularly preferably arranged in the reverse orientation, with an overall effect of the leaching on the fluid flow being largely independent of its direction.
  • the rib can be installed without impact in both orientations.
  • At least two latches are provided with different opening direction or Ausstellraum with respect to the wall surface.
  • the angle W3 is not less than about 10 °, in particular between about 15 ° and about 20 °.
  • the angle of inclination of the wall allows sufficiently large or deep structures in the wall surface to affect the flow of the fluid in a desired manner and, secondly, the wall surface is still sufficiently steep in terms of mechanical strength.
  • the wall surface may form a tie rod between the walls of a high-pressure fluid flat tube, such as in the case of using the rib as an inner corrugated fin of an intercooler.
  • the rib is produced as a quasi-endless molded part from a sheet-metal strip by means of longitudinal rolling in the flow direction A.
  • the rib can be formed particularly cost-effective with high production speed.
  • the folding of the wall surfaces of the rib as well as the structures in the wall surfaces can be produced.
  • a quasi-endless rib can be easily cut to the length of particularly large heat exchangers. In this way it is avoided that a plurality of individual ribs have to be plugged into an exchanger tube in order to provide it with ribs over the entire length.
  • the rib consists of a sheet having a thickness between about 0.05 mm and about 0.35 mm, in particular between about 0.1 mm and about 0.15 mm.
  • the material is expediently an aluminum alloy, wherein due to the good formability of the aluminum in conjunction with the selected sheet thicknesses, a longitudinal rolling of the rib as a production method is particularly well possible.
  • the structure may be formed as an embossing and / or incision and / or offset in the wall surface.
  • dislocations in the flow are particularly effective on the flow of the first fluid Wall surface, so that the fluid can partially pass through the wall surface in an adjacent flow space.
  • the rib next to the inclined by the angle W3 wall surface also has a substantially perpendicular to the plane wall surface.
  • These wall surfaces can be present in particular alternately.
  • the vertical wall surfaces cause a particularly good mechanical stiffness of the rib against tensile and compressive forces.
  • no structure is preferably provided in the wall surface perpendicular to the plane.
  • all wall surfaces can be inclined and in particular provided with structures.
  • the rib is designed as an inner corrugated rib of a charge air cooler.
  • the rib is designed as an inner corrugated rib of a charge air cooler.
  • intercoolers of high power density structured wall surfaces are favorable in contrast to conventional smooth ribs.
  • the invention also relates to a heat exchanger having at least one rib according to the invention as claimed in any one of claims 1 to 9.
  • the heat exchanger is preferably a heat exchanger for a motor vehicle, in particular a heat exchanger from the group of coolant coolers, climatic heat exchangers or intercoolers. Especially in motor vehicles and especially passenger cars, there is an increasing lack of space, so that the related to the size transmission capacity of a heat exchanger is of great importance. Due to the inventive design of the ribs of the heat exchanger, the heat exchanger performance can be improved with the same size.
  • the angle is not less than about 10 °, in particular between about 15 ° and about 20 °.
  • the rib is produced as a quasi-endless molded part from a sheet-metal strip by means of longitudinal rolling in the flow direction.
  • the rib consists of a sheet having a thickness between about 0.05 mm and about 0.35 mm, in particular between about 0.1 mm and about 0.15 mm.
  • the structure is formed as an embossing and / or incision and / or offset in the wall surface.
  • the rib has a wall surface which is substantially perpendicular to the plane.
  • the rib is designed as an inner corrugated rib of a charge air cooler.
  • This in Fig. 1 shown embodiment of the invention comprises a rib 1 made of a multi-bent aluminum sheet. Between two mutually inclined wall surfaces 1a, 1b, a flow channel 2 is formed through which a first fluid of the heat exchanger, in the present case air, flows in the direction of the arrow A.
  • the angle of inclination W3 of the wall surfaces 1a, 1b to each other is about 14 degrees, wherein the one wall surface 1a is inclined relative to a plane E of the heat exchanger by an angle W2 of about 12 degrees and the other wall surface accordingly by an angle W3-W2 of about 2 degrees (please refer Fig. 2 ).
  • the heat exchanger is constructed such that a plurality of the ribs 1 are arranged side by side to form parallel adjacent flow channels 2. Above and below the ribs 1 are exchanger tubes or partitions (not shown), which delimit a second fluid, surface connected to the ribs 1, in particular soldered flat. For this purpose, the rib has a contact region 1c.
  • At least one of the side walls 1a of the rib 1 a lashing 3 is arranged with a substantially smooth and against the side wall 1a with respect to the flow direction A inclined tab surface. 4
  • the inclination angle in the flow direction is about 7 degrees.
  • the geometric shape is identical.
  • the lashing 3 is arranged only in each case different orientation in the wall surface 1a.
  • the leaching is exposed to the same side with respect to the wall surface 1a, but the orientation with respect to the direction of the fluid flow A is inverted.
  • the versions c and d the same applies, with the lashing being issued in relation to the wall surface 1a in the opposite orientation compared to the versions a and b respectively.
  • the tab surface 4 has a first straight edge 5, it extends perpendicular to the flow direction A and at an angle of about 12 degrees to the wall surface 1 a.
  • the tab surface 4 is connected via a curved extending side wall 7 with the wall surface 1a of the rib.
  • the side wall 7 of the lashing 3 is approximately perpendicular to the wall surface 1a of the rib 1. According to the inclination of the tab surface 4 in the flow direction A, the height of the side wall 7 in the flow direction A increases.
  • a front edge 7a of maximum height of the side wall 7 is formed, which lies together with the first edge 5 and the second edge 6 in a plane perpendicular to the wall surface 1a, wherein the three edges 5, 6 and 7a a triangular, perpendicular to the Form wall surface 1a standing opening or opening 9.
  • the triangle 9 has two long sides, formed by the edges 5 and 6, which enclose an acute angle W1 of 12 degrees (see Fig. 2 ) and an acute angle opposite short side, which is formed by the front edge 7a of the side wall 7.
  • the tab surface 7 merges into the wall surface 1a in a third edge 8 which is approximately parallel to the direction of flow, wherein the third edge forms a kink, via which the tab surface 4 is angled relative to the wall surface 1a.
  • the curved side wall 7 has at its beginning, as viewed in the flow direction A according to Fig. 1a , First, a smallest distance from the third edge 8, in the present example, approximately a distance of zero, wherein the distance over the length L of the tab surface grows monotonically. Both at the beginning of their course as well as at the end of the sidewall is almost parallel to the third edge. 8
  • the length L of the tab surface 4 is approximately eight times the maximum height of the side wall. 7
  • the side wall 7 changes its direction of curvature on approximately half of its course, so that the curvature has exactly one turning point.
  • a parameterization of the course of the side walls of the preferred embodiment is: [0; 2,500], [0.805; 2,470], [1.610; 2,290], [2,420; 1,910], [3,220; 1.540], [4.030; 1,210], [4,840; 0.980], [5.640; 0.780], [6.440; 0.590], [7.240; 0.400], [8.050; 0.210].
  • the first digit of a coordinate pair [x; y] the distance in the direction of the third edge 8, starting from the first edge 5, ie opposite to the flow direction A.
  • the second digit y describes at this point the vertical distance of the side wall 7 of the third edge 8.
  • Side wall 7 has a maximum height of about 1.0 and the maximum width B of the tab surface 4, which runs along the first straight edge, corresponding to 2.5.
  • any sequence of orientation of the louvers 3 in a rib according to the invention is possible.
  • the production of the rib takes place in the present embodiment of a thin aluminum sheet, in which first the leaching by material deformation such as deep drawing are introduced and the following is bent to the rib shown.
  • the rib is formed objectively as in the preceding embodiments and is produced by means of a longitudinal rolling process.
  • a quasi-endless sheet-metal strip of aluminum of a thickness of about 0.1 mm to about 0.15 mm (depending on the requirements and thicker or thinner sheets can be used) fed in a feed direction and over several in the feed direction successively following stations reshaped the rib.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (11)

  1. Ailette pour un échangeur de chaleur, comprenant un corps d'ailette (1) s'étendant dans une direction d'écoulement (A) d'un premier fluide et ayant une surface de paroi (1a) baignée des deux côtés par le premier fluide,
    où il est prévu, dans la surface de paroi (1a), au moins une languette saillante (3) à travers laquelle est formée une ouverture (9) de la surface de paroi (1a) pouvant être traversée par le premier fluide,
    où une première arête (5) de la languette saillante (3) est disposée, pour la formation de l'ouverture (9), en étant à distance de la surface de paroi (1a),
    où la languette saillante (3) présente une surface de languette (4) inclinée par rapport à la surface de paroi (1a), laquelle surface de languette se termine par la première arête (5),
    caractérisée en ce que
    la surface de languette (4) est reliée à la surface de paroi (1a) par au moins une paroi latérale (7) de la languette saillante (3), paroi latérale qui s'étend de façon incurvée et qui, en partant de la première arête (5), présente une hauteur diminuant de façon correspondant à l'inclinaison de la surface de languette (4), où la première arête (5), au moins une arête d'extrémité (7a) de la paroi latérale (7) au moins au nombre de un, et une deuxième arête (6) de la surface de paroi (1a), forment une ouverture (9) orientée en étant sensiblement perpendiculaire a la direction d'écoulement (A) et pouvant être traversée par le premier fluide, et ou l'ouverture (9) a une forme sensiblement triangulaire, où la surface de languette (4) est reliée à la surface de paroi (1a) par une troisième arête (8), la surface de languette (4) est coudée par la troisième arête (8), par rapport a la surface de paroi (1a), et une largeur de la surface de languette (4) se réduit avec une distance qui augmente par rapport à la première arête (5).
  2. Ailette selon la revendication 1, caractérisée en ce que l'angle formé est compris entre huit degrés environ et seize degrés environ, étant en particulier de douze degrés environ.
  3. Ailette selon l'une des revendications 1 ou 2, caractérisée en ce que la longueur (L) de la troisième arête (8) est comprise entre à peu près le double et à peu près le quadruple, étant en particulier à peu près égale au triple d'une longueur de la première arête (5).
  4. Ailette selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la forme de la surface de languette (4) présente, en partant de la première arête (5), sensiblement le paramétrage [0 ; 2,500], [0,805 ; 2,470], [1,610 ; 2,2901, [2,420 ; 1,910], [3,220 ; 1,540], [4,030 ; 1,210], [4,840 ; 0,980], [5,640 ; 0,780], [6,440 ; 0,590], [7,240 ; 0,400], [8,050 ; 0,210], où la première valeur indique a chaque fois la distance par rapport à la première arête (5) dans la direction d'écoulement (A), la seconde valeur indiquant à chaque fois la distance de la paroi Latérale (7) par rapport à la troisième arête (8).
  5. Ailette selon l'une quelconque des revendications précédentes, caractérisée en ce que la courbure de la paroi latérale (7) au moins au nombre de un présente, dans son profil, au moins un point d'inflexion par rapport à la direction de courbure.
  6. Ailette selon l'une quelconque des revendications précédentes, caractérisée en ce que l'inclinaison de la surface de languette par rapport à la surface de paroi (1a) est, dans la direction d'écoulement (A), comprise entre cinq degrés environ et dix degrés environ, étant en particulier de sept degrés environ.
  7. Ailette selon l'une quelconque des revendications précédentes, caractérisée en ce que l'ailette (1) présente, dans la direction d'écoulement, plusieurs languettes saillantes (3) qui se suivent.
  8. Ailette selon la revendication 7, caractérisée en ce qu'au moins l'une parmi la pluralité de languettes saillantes (3) est disposée suivant une orientation inversée, où en particulier un effet d'ensemble des languettes saillantes (3), sur le flux de fluide, est dans une large mesure indépendant de la direction dudit flux de fluide.
  9. Ailette selon au moins l'une quelconque des revendications précédentes, comprenant un corps d'ailette (1) s'étendant dans une direction d'écoulement (A) d'un premier fluide et ayant une surface de paroi (1a) baignée des deux côtés par le premier fluide,
    ou il est prévu, dans la surface de paroi (1a), au moins une structure (3) par laquelle peut être influencé un écoulement du premier fluide,
    où le corps d'ailette s'étend dans un plan, caractérisée en ce que La surface de paroi (1a) est inclinée par rapport a une perpendiculaire du plan, suivant un angle (W3) qui est compris entre 2° environ et 45° environ.
  10. Echangeur de chaleur comprenant au moins une ailette selon l'une quelconque des revendications 1 à 9.
  11. Echangeur de chaleur selon la revendication 10, caractérisé en ce que l'échangeur de chaleur est un échangeur de chaleur pour un véhicule automobile, en particulier un échangeur de chaleur faisant partie du groupe comprenant un radiateur à liquide de refroidissement, un échangeur de chaleur de climatisation ou un refroidisseur d'air de suralimentation.
EP08017257.0A 2007-10-08 2008-10-01 Ailette pour un échangeur thermique Ceased EP2096397B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007048307 2007-10-08

Publications (3)

Publication Number Publication Date
EP2096397A2 EP2096397A2 (fr) 2009-09-02
EP2096397A3 EP2096397A3 (fr) 2013-07-17
EP2096397B1 true EP2096397B1 (fr) 2015-01-21

Family

ID=40522281

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Application Number Title Priority Date Filing Date
EP08017257.0A Ceased EP2096397B1 (fr) 2007-10-08 2008-10-01 Ailette pour un échangeur thermique

Country Status (3)

Country Link
US (1) US8267161B2 (fr)
EP (1) EP2096397B1 (fr)
DE (1) DE102008049851A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007036308A1 (de) * 2007-07-31 2009-02-05 Behr Gmbh & Co. Kg Rippe für einen Wärmetauscher
DE102009005038A1 (de) * 2009-01-17 2010-07-22 Mahle International Gmbh Turbulenzblech
JP5884055B2 (ja) * 2014-05-09 2016-03-15 パナソニックＩｐマネジメント株式会社 熱交換器および熱交換器用オフセットフィン
DE102014222983A1 (de) 2014-11-11 2016-05-12 Mahle International Gmbh Wellrippe für einen Wärmeübertrager
JP2015180852A (ja) * 2015-07-24 2015-10-15 株式会社小松製作所 コルゲートフィンおよびそれを備える熱交換器
DE102017208324A1 (de) * 2017-05-17 2018-11-22 Mahle International Gmbh Wärmeübertrager

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1116621A (en) * 1963-12-27 1968-06-12 Ass Eng Ltd Improvements in or relating to heat exchangers
US3584682A (en) 1968-07-29 1971-06-15 Borg Warner Tubular heat transfer device
DD152187A1 (de) 1980-07-23 1981-11-18 Ernst Roth Streifenfoermiges rohreinbauelement
US4501321A (en) * 1982-11-10 1985-02-26 Blackstone Corporation After cooler, charge air cooler and turbulator assemblies and methods of making the same
JPS62112997A (ja) * 1985-11-08 1987-05-23 Matsushita Refrig Co 熱交換器
DE19511665A1 (de) 1995-03-30 1996-10-02 Abb Management Ag Verfahren und Vorrichtung zur Luftkühlung von Hubkolben-Verbrennungskraftmaschinen
US5669438A (en) * 1996-08-30 1997-09-23 General Motors Corporation Corrugated cooling fin with louvers
US6170565B1 (en) * 1996-12-04 2001-01-09 Zexel Corporation Heat exchanger
JP2002277180A (ja) * 2001-03-16 2002-09-25 Calsonic Kansei Corp 一体型熱交換器のコア部構造
JP2006078035A (ja) * 2004-09-08 2006-03-23 Denso Corp 熱交換装置
DE102007036308A1 (de) * 2007-07-31 2009-02-05 Behr Gmbh & Co. Kg Rippe für einen Wärmetauscher

Also Published As

Publication number Publication date
EP2096397A3 (fr) 2013-07-17
US8267161B2 (en) 2012-09-18
DE102008049851A1 (de) 2009-07-02
US20090090497A1 (en) 2009-04-09
EP2096397A2 (fr) 2009-09-02

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