EP1488184B1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP1488184B1
EP1488184B1 EP03720308A EP03720308A EP1488184B1 EP 1488184 B1 EP1488184 B1 EP 1488184B1 EP 03720308 A EP03720308 A EP 03720308A EP 03720308 A EP03720308 A EP 03720308A EP 1488184 B1 EP1488184 B1 EP 1488184B1
Authority
EP
European Patent Office
Prior art keywords
fluid
heat exchanger
flow
corrugated
offset
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.)
Expired - Lifetime
Application number
EP03720308A
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German (de)
English (en)
Other versions
EP1488184A1 (fr
Inventor
Gerrit WÖLK
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
Priority claimed from DE10249451A external-priority patent/DE10249451A1/de
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1488184A1 publication Critical patent/EP1488184A1/fr
Application granted granted Critical
Publication of EP1488184B1 publication Critical patent/EP1488184B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
    • Y10S165/471—Plural parallel conduits joined by manifold
    • Y10S165/486—Corrugated fins disposed between adjacent conduits
    • Y10S165/487—Louvered

Definitions

  • the invention relates to a heat exchanger, in particular for motor vehicles, having the features of the preamble of claim 1.
  • a heat exchanger is for example from the DE 198 13 989 A1 known.
  • This heat exchanger can be designed, for example, as a condenser of an air conditioning system for motor vehicles.
  • the heat exchanger may be formed, for example, as a coolant radiator, which serves for cooling coolant of a coolant circuit in a motor vehicle.
  • the heat exchanger has a number of juxtaposed, parallel to each other flat tubes, ie tubes whose cross-section is substantially rectangular on.
  • a first fluid for example, a coolant in the case of a coolant cooler or a gaseous refrigerant to be condensed in the case of a capacitor one Air conditioning.
  • the flat tubes are connected to manifolds and manifolds and exposed to the flow of a second fluid, such as ambient air, to effect heat transfer between the fluids. Between the individual, spaced-apart flat tubes flow paths for the second fluid are formed.
  • the cooling fins As a result, a considerable flow resistance is opposed to the second fluid.
  • the flow velocity of the second fluid should be selectively reduced. On the one hand, this increases the residence time of the second fluid during the flow through the heat exchanger, ie the time in which the second fluid absorbs heat from the first fluid or can transfer it to it. On the other hand, however, is limited by the low flow rate of the second fluid, the transferable between the first and the second fluid amount of heat, ie the heat exchanger performance.
  • Another heat exchanger with cooling fins is for example from the US 4,676,304 known.
  • the cooling fins are in Substantially parallel to the flow direction of the second fluid (here: air).
  • the second fluid here: air
  • This problem is particularly significant when the heat exchanger in the direction of flow of the second fluid has small dimensions. In this case, a high mass flow rate of the second fluid does not necessarily cause a high heat transfer performance.
  • the available temperature difference between the first and the second fluid is used only to a relatively small extent.
  • the invention has for its object to provide a heat exchanger with flat tubes, especially for motor vehicles, with cooling fins, which are designed particularly streamlined and at the same time ensure a high heat transfer performance.
  • a heat exchanger having the features of claim 1.
  • the heat exchanger of a first fluid flow-through flat tubes which are externally acted upon by a second fluid and arranged substantially parallel to the flow direction of the second fluid in parallel to each other, in that flow paths are formed for the second fluid, in which cooling fins are arranged, which each extend between adjacent flat tubes.
  • the cooling fins are in each case formed as corrugated ribs, wherein a plurality of corrugated fins are arranged one behind the other in the flow direction of the second fluid and these laterally, ie in the flow direction of the first fluid, are offset from each other.
  • corrugated fins are formed from a common band.
  • the corrugated ribs including the gills are in particular produced by rolling from a metal strip.
  • the corrugated fins have gills for guiding the second fluid.
  • start-up flow forming on the gills which has a high temperature gradient in a region of the corrugated fin, an improved heat transfer between the second fluid and the corrugated ribs is ensured.
  • a streamlined design of the corrugated fins is preferably achieved in that their surfaces are substantially parallel to the flow direction of the second fluid, i. the surface normals of the corrugated fins are substantially at right angles to the flow direction of the second fluid.
  • the aerodynamic design of the corrugated fins is ensured by the lateral offset successively arranged corrugated fins that only a smaller proportion of the second fluid unused, i. without appreciable heat transfer, flows between the flat tubes than without such an offset.
  • This advantage is more pronounced the higher the rib spacing b between two ribs.
  • two or three similarly shaped corrugated ribs are offset from each other in succession.
  • the individual corrugated fins are preferably directly adjacent to each other, i. arranged without a distance in the flow direction of the second fluid. As a result, a large heat exchanger surface is given.
  • a spaced arrangement of the narrower in this case corrugated fins be provided.
  • all the gills of a rib section enclosed between two flat tubes of a corrugated fin are inclined in the same direction with respect to the flow direction of the second fluid.
  • a similar inclination of the gills within a rib section has the advantage that, if appropriate, the flow is specifically directed to a downstream rib section.
  • the gills offset successively arranged rib portions are preferably inclined in opposite directions, so that the heat exchanger through the flowing second fluid is given a longer flow path.
  • the gills of two adjacent gill panels can also be placed obliquely in the same direction, it may then be advantageous if the gills of the two adjacent gill fields upstream or downstream gills are inclined in opposite directions to the gills of the two adjacent gill panels.
  • Uniform coverage of the flow cross-section through which the second fluid flows is preferably achieved by displaced rib sections arranged one behind the other running parallel to one another.
  • the mutually offset rib sections are preferably perpendicular to the flat tubes. If the rib surfaces deviate slightly (up to about 6 degrees) from the parallelism, in which case they are still to be regarded as substantially parallel in the context of the invention, the thermodynamic advantages of the mutually offset ribs are scarcely impaired as a result. Likewise, the use of so-called V-ribs or even arbitrarily rounded ribs is conceivable.
  • the rib geometry according to the invention is particularly applicable to automotive heat exchangers such as coolant radiators, radiators, condensers and evaporators.
  • FIG. 1a, 1b and 2a, 2b show a detail of a heat exchanger 1 with parallel arranged flat tubes 2, which are flowed through by a first fluid FL1 in a first flow direction S1.
  • the flat tubes 2 are equipped with flow guide 2a and (not shown).
  • the fluid FL1 is for example a cooling liquid or a refrigerant condensing in the heat exchanger 1.
  • corrugated fins 3 are arranged as cooling fins. Embodiments with a higher number of corrugated fins 3 are also feasible.
  • the corrugated fins 3 are meander-shaped bent from a metal sheet, with each one adjacent to a flat tube 2 rib section 4a with a two adjacent flat tubes 2 connecting rib section 4b alternates.
  • the voltage applied to the flat tubes 2 rib portions 4a are thermally conductively connected to the flat tubes 2, in particular soldered.
  • the two adjacent flat tubes 2 connecting rib sections 4b are perpendicular to the flat tubes 2 and form flow paths for a second fluid FL2, for example, air, which flows through the heat exchanger 1 in the flow direction S2.
  • the second fluid FL2 flows substantially parallel to the surface 5 of the corrugated fins 3, i.
  • the second fluid FL2 initially strikes only the narrow end faces 6 of the corrugated fins 3.
  • the second fluid FL2 can thereby flow through the heat exchanger 1 at high speed and correspondingly high mass flow rate.
  • gills 7, which extend transversely to the flow direction S2 of the second fluid FL2 and transversely to the flow direction S1 of the first fluid FL1, are formed from the rib sections 4b.
  • the gills 7 within a rib portion 4b cause on the one hand a particularly good heat transfer between the second fluid FL2 and this rib portion 4b, on the other hand a targeted guidance of the second fluid FL2 to the flow direction S2 obliquely behind it arranged rib portion 4b.
  • the mass flow of the second fluid FL2 flowing through the heat exchanger 1 is almost completely utilized with high utilization of the temperature difference between the first fluid FL1 and the second fluid FL2 for heat transfer.
  • Two corrugated fins 3 arranged one behind the other between two flat tubes 2 are offset from one another by half the width b between adjacent fin sections 4b.
  • an offset of b / 3 is preferably selectable, although other values for the offset are conceivable.
  • Two or three adjacent corrugated fins 3, which extend across the depth T of the heat exchanger 1, are produced by rolling from a belt 8.
  • the band 8 is cut in the region of the respective offset between the two (FIG. 1a, 1b, FIG. 3) and three (FIG. 2a, 2b, FIG. 4) corrugated ribs 3 and the gills 7 are cut into the corrugated ribs 3 cut.
  • a simple (Fig. 1a, 1b, Fig. 3, Fig. 5c) and double (Fig. 2a, 2b, Fig. 4, Fig. 5d) offset or higher order order (Fig. 5e, 5f, 5g) the corrugated fins 3 Alternatively, it can be produced by arranging similar separate corrugated fins 3 with an offset between 0.1 mm and b / 2, where b is the distance between two adjacent flat tubes 2.
  • FIG. 5 shows corrugated ribs 10a, b... J each with a plurality of gill fields in cross-sectional view.
  • cooling fins with flow-conducting Lamellae (gills) in the individual ribs usually have a rib between two tubes in the main flow direction of the second fluid exclusively in a plane without offset (FIGS. 5a, 5b).
  • These cooling fins have at least two so-called gill panels 11, 12 and 13, 14, which are separated by a web of different design.
  • the orientation of the flow-conducting lamellae (gills) of adjacent gill fields is usually in opposite directions.
  • two, three or more similarly shaped corrugated fins (cooling fins) offset from each other are arranged one behind the other, ie, the one corrugated fin with flow-conducting fins (gills) can be offset in several planes to each other.
  • the number of corrugated fins, which are arranged one behind the other viewed in the direction of flow of the second fluid, depending on the depth of the heat exchanger and / or the depth of the corrugated fins are selected.
  • 2, 3 or more rows can be used; for example, 2, 3, 4 or more rows can be used for a depth of up to 24 mm; for example, 2, 3 can be used for a depth of up to 30 mm , 4, 5 or more rows are used, with a depth of up to 36 mm, for example, 2, 3, 4, 5, 6 or more rows can be used, with a depth of up to 42 mm, for example, 2, 3, 4, 5, 6 , 7 or more rows use find, with a depth up to 48 mm, for example, 2, 3, 4, 5, 6, 7, 8 or more rows use, with a depth up to 54 mm, for example, 2, 3, 4, 5, 6, 7, 8 2, 3, 4, 5, 6, 7, 8, 9, 10 or more rows can be used with a construction depth of up to 60 mm; for a construction depth of up to 66 mm, for example 2, 3 , 4, 5, 6, 7, 8, 9, 10, 11 or more rows.
  • FIG. 5c An exemplary embodiment for 2 rows 15 and 16 is shown in FIG. 5c in a cross-sectional view.
  • FIG. 5d An exemplary embodiment for 3 rows 17, 18 and 19 is shown in FIG. 5d in a cross-sectional view.
  • FIG. 5e An exemplary embodiment for 4 rows 20, 21, 22 and 23 is shown in FIG. 5e in a cross-sectional view.
  • FIG. 5f An exemplary embodiment for 5 rows 24, 25, 26, 27 and 28 is shown in FIG. 5f in a cross-sectional view.
  • FIG. 5g An embodiment for 5 rows 29, 30, 31, 32 and 33 is shown in FIG. 5g in a cross-sectional view.
  • FIG. 5h An exemplary embodiment for 5 rows 34, 35, 36, 37 and 38 is shown in FIG. 5h in a cross-sectional view.
  • More than two mutually offset rows can preferably be distributed over a total of two staggered planes as in the embodiments in Figures 5d, 5e and 5g. However, they can also be distributed over three or more different levels as in the embodiments in FIGS. 5f and 5h, wherein the distances between each two levels may be the same or different.
  • the corrugated rib 10i or 10j has no gill. This embodiment also causes an influence of the temperature boundary layer on the tube walls and / or an improved flow through the lamellae.
  • the number of gills per row is for example between 2 and 30 gills depending on the number of rows and the depth of the heat exchanger.
  • the number of gills per gill field from an engineering point of view in odd number of rows that is not identical at 3, 5, 7, 9 or 11 rows. If the number is even Rows may be identical to the number of gills per gill panel, but this is not necessary.
  • a corrugated fin in a row i. E. without offset, consisting of a row with two gill panels, which are separated by a ridge in the form of a roof, considered (prior art).
  • a corrugated fin with 2 rows and a corrugated fin with 3 rows is considered.
  • the simulation determines the mass flow through the individual fin openings as well as the radiation power from the pipe to the cooling air.
  • FIG. 6 shows the flow field of the air at an air inlet speed V air of 3 m / s into a heat exchanger 51 with corrugated fins 52, 53 under the boundary conditions described above in the area between two gill fields 54, 55 and 56, 57.
  • the webs 58 and 59, respectively between each two gill fields have this a roof shape.
  • the Arrows 60 show the main flow path of the air particles, which flow through the last fin opening 61 in front of the web 59, then undergo a flow deflection and flow through the fin openings 62, 63 in the adjacent gill field 57.
  • the figure shows that only the second slat opening 62 of the gill field 57 is again flowed through by a larger number of air particles, whereby only the speed field through the third slat opening 63 corresponds approximately to the Geschwindkeitstruck in the previous gill field 56 again.
  • FIG. 7 shows the flow field of the air at an air inlet speed V air of 3 m / s into a heat exchanger 71 with corrugated ribs 72, 73 under the boundary conditions described above in the region of an offset point 74 or 75 between two gill arrays 76, 77 and 78, 79, respectively
  • the arrows 80 show the main flow path of the air particles before the offset 75, on the one hand through the last fin opening 81 before the offset and the other through the offset opening 75.
  • the air particles experience after the flow through the displacement opening 75, a flow deflection, wherein the air particles passing through then flow through the offset opening, then mainly through the first and second fin opening 82, 83 of the adjacent gill field 79 to flow.
  • the air particles that flow through the last fin opening 81 before the offset flow, after also having a flow deflection have experienced, mainly through the third slat opening 84 of the subsequent gill field 79th
  • the percentage air mass flow in the two corrugated fin configurations with two or three rows is always above 9%, whereas in corrugated fins in a plane / row of air mass flow at the two fin openings in the connection at the land area falls below 8% with a minimum of about 4%. If the air mass flow at the corrugated rib consisting of a plane at the slat opening in front of the web area drops from approximately 12% to approximately 10%, the mass flow through the last slat opening in front of the offset point of approximately 12 takes place in the corrugated rib consisting of two levels / rows to about 13% too.
  • the percentage air mass flow is in the two corrugated fin configurations with two or three rows (one or two offset points) always above 12%, whereas in corrugated fins in a plane / row of air mass flow at the two fin openings in the connection at the land area falls below 11% with a minimum of about 4.5%. If the air mass flow in the corrugated rib consisting of a level at the Lammellenö réelle before the web area of about 16.5% to about 15%, so takes in the corrugated rib consisting of two levels / rows here the mass flow through the last lamellar opening in front of the offset point of about 16.5 to about 18% too.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Claims (9)

  1. Échangeur de chaleur, en particulier pour véhicules automobiles, comprenant des tubes aplatis (2) à l'intérieur desquels peut circuler un premier fluide (FL1), à l'extérieur desquels peut circuler un deuxième fluide (FL2), qui sont disposés essentiellement transversalement au sens d'écoulement (S2) du deuxième fluide (FL2) et parallèlement les uns aux autres, et qui sont espacés les uns des autres et forment ainsi des chemins d'écoulement pour le deuxième fluide (FL2) traversant l'échangeur de chaleur, dans lequel des ailettes de refroidissement sont disposées dans les chemins d'écoulement, lesquelles s'étendent chacune entre des tubes aplatis adjacents (2), dans lequel sont prévues, en tant qu'ailettes de refroidissement, à chaque fois plusieurs ailettes ondulées (3) disposées les unes derrière les autres dans le sens d'écoulement (S2) du deuxième fluide (FL2), lesquelles sont formées à partir d'un ruban commun (8), dans lequel plusieurs ailettes ondulées (3) disposées les unes derrière les autres sont décalées latéralement les unes par rapport aux autres en formant des ouvertures décalées (75), caractérisé en ce que les ailettes ondulées (3) présentent des ouïes (7) pour guider le deuxième fluide (FL2).
  2. Échangeur de chaleur selon la revendication 1, caractérisé en ce que les surfaces (5) des ailettes ondulées (3) sont disposées essentiellement parallèlement au sens d'écoulement (S2) du deuxième fluide (FL2).
  3. Échangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que plusieurs ailettes ondulées (3) décalées les unes par rapport aux autres ont une forme similaire.
  4. Échangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que toutes les ouïes (7) d'un segment d'ailette (4b) délimité par deux tubes aplatis (2) sont inclinées dans le même sens par rapport au sens d'écoulement (S2) du deuxième fluide (FL2).
  5. Échangeur de chaleur selon la revendication 4, caractérisé en ce que les ouïes (7) de deux segments d'ailette (4b) placés en décalage l'un derrière l'autre sont inclinées dans le même sens.
  6. Échangeur de chaleur selon la revendication 4, caractérisé en ce que les ouïes (7) de deux segments d'ailette (4b) placés en décalage l'un derrière l'autre sont inclinées en sens inverse.
  7. Échangeur de chaleur selon l'une quelconque des revendications 1 à 6, caractérisé en ce que deux segments d'ailette (4b) placés en décalage l'un derrière l'autre sont essentiellement parallèles l'un à l'autre.
  8. Échangeur de chaleur selon la revendication 7, caractérisé en ce que les segments d'ailette (4b) sont disposés essentiellement perpendiculairement aux tubes aplatis (2).
  9. Échangeur de chaleur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les ailettes ondulées (3), dans le sens d'écoulement principal du deuxième fluide, présentent une extension identique ou similaire.
EP03720308A 2002-03-09 2003-02-24 Echangeur de chaleur Expired - Lifetime EP1488184B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10210458 2002-03-09
DE10210458 2002-03-09
DE10249451 2002-10-24
DE10249451A DE10249451A1 (de) 2002-03-09 2002-10-24 Wärmetauscher
PCT/EP2003/001852 WO2003076860A1 (fr) 2002-03-09 2003-02-24 Echangeur de chaleur

Publications (2)

Publication Number Publication Date
EP1488184A1 EP1488184A1 (fr) 2004-12-22
EP1488184B1 true EP1488184B1 (fr) 2007-12-05

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EP03720308A Expired - Lifetime EP1488184B1 (fr) 2002-03-09 2003-02-24 Echangeur de chaleur

Country Status (8)

Country Link
US (1) US7147047B2 (fr)
EP (1) EP1488184B1 (fr)
JP (1) JP2005520113A (fr)
CN (1) CN100354592C (fr)
AT (1) ATE380324T1 (fr)
AU (1) AU2003223946A1 (fr)
DE (1) DE50308729D1 (fr)
WO (1) WO2003076860A1 (fr)

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WO2024023908A1 (fr) * 2022-07-26 2024-02-01 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

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AU2003223946A1 (en) 2003-09-22
CN1639533A (zh) 2005-07-13
WO2003076860A1 (fr) 2003-09-18
CN100354592C (zh) 2007-12-12
JP2005520113A (ja) 2005-07-07
ATE380324T1 (de) 2007-12-15
WO2003076860A8 (fr) 2005-05-12
EP1488184A1 (fr) 2004-12-22
US20050126767A1 (en) 2005-06-16
US7147047B2 (en) 2006-12-12
DE50308729D1 (de) 2008-01-17

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