US20070163751A1 - Metal side-plate for a radiator - Google Patents

Metal side-plate for a radiator Download PDF

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Publication number
US20070163751A1
US20070163751A1 US10/587,357 US58735705A US2007163751A1 US 20070163751 A1 US20070163751 A1 US 20070163751A1 US 58735705 A US58735705 A US 58735705A US 2007163751 A1 US2007163751 A1 US 2007163751A1
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US
United States
Prior art keywords
plate
metal side
penetrations
radiator
way
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
US10/587,357
Inventor
Sinan Balci
Reinhard Kull
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
Assigned to BEHR GMBH & CO. KG reassignment BEHR GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BALCI, SINAN, KULL, REINHARD
Publication of US20070163751A1 publication Critical patent/US20070163751A1/en
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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements

Definitions

  • the present invention relates to a metal side-plate for radiators, in particular for tubular radiators such as those which find an application in vehicles with internal combustion engines.
  • Radiators of this kind exhibit a radiator body, in which tubes extend in the longitudinal direction, in conjunction with which heat exchanger surfaces are embodied between the tubes. What is more, the radiator is enclosed by at least one pair of metal side-plates situated to either side of the radiator body.
  • the metal side-plates in this case extend along or across the direction in which the tubes of the tubular radiator extend. They delimit in particular the heat exchanger surfaces, are utilized for the purposes of assembly, for example, and also prevent the ingress of undesired contamination into the area between the heat exchanger surfaces and in so doing prevent impairment of the heat exchange performance of the heat exchanger.
  • the length of the tubes and the heat exchanger surfaces changes in the presence of fluctuations in the operating temperature of the tubular radiator, so that a loading due to thermal stress can make its effect felt on the metal side-plate.
  • the object of the invention is to make available a metal side-plate that is executed in such a way that stresses arising from various kinds of thermal expansion of the metal side-plate and tubular radiator are prevented. This object is achieved by a metal side-plate in accordance with the independent claim.
  • a metal side-plate of this kind which can find an application in particular for tubular radiators, is intended to be used in radiator bodies in which tubes extend in the longitudinal direction and in which heat exchanger surfaces are arranged between the tubes, in conjunction with which the metal side-plates are intended to close off the radiator on at least one pair of opposing sides.
  • the metal side-plates are characterized in that they exhibit a weakened area, in conjunction with which the material of the metal side-plate in this area is weakened in such a way as to allow compensation for the thermal expansion corresponding to that of the radiator body.
  • This weakening of the material enables the thermal expansion of the metal side-plate to be adapted to that of the radiator body and thereby permits the permanent retention of the metal side-plate on both sides of the radiator body.
  • the occurrence of stresses, both in the metal side-plate and in the radiator body, due to different thermal expansion is avoided at the same time.
  • the weakening of a weakened area is effected by penetrations in the material of the metal side-plate. It is particularly advantageous if the penetrations are embodied in such a way that a network of webs is formed. The adoption of this measure ensures that high mechanical flexibility of the lateral part is achieved, which is able to compensate for thermal expansion deviating from the thermal expansion of the radiator body. It is especially favorable if the penetrations are executed in such a way that the network of webs forms lozenges standing on their tips in the longitudinal extent of the metal side-plate, that is to say in the longitudinal direction.
  • the webs which delimit the penetrations in each case run with a directional component in the longitudinal direction of the metal side-plate, in which the different thermal expansion produces its effect, and also at all times in a directional component transversely thereto, so that a certain rigidity and dimensional stability of the metal side-plate nevertheless continue to be assured.
  • An alternative embodiment is provided if the network of webs delimits honeycomb-shaped penetrations. What is more, the honeycomb-shaped penetrations can be formed both by penetrations having a hexagonal form and by penetrations having an octagonal form.
  • Hexagonal, honeycomb-shaped penetrations have the advantage that they are able to form a closed surface, whereas in the case of octagonal honeycombs, lozenge-shaped intermediate surfaces occur repeatedly, with the result that a uniform, transcurrent pattern is not produced.
  • octagonal honeycombs repeatedly form areas of material running in the longitudinal direction and in the transverse direction of the metal side-plate, whereas hexagonal honeycombs only exhibit areas of material running either in the longitudinal direction or in the transverse direction of the metal side-plate. It is accordingly possible in this case for a different longitudinal rigidity to result in relation to the transverse rigidity of the metal side-plate.
  • a weakened area is produced in the form of a plurality of rows of penetrations, in conjunction with which the rows of penetrations are preferably arranged off-set in relation to one another, and the number of rows can be selected in such a way that, when viewed in the direction in which the metal side-plate extends, the length of the penetrations added together at each point transversely to the direction of its extent amounts to at least 1.5 times, and preferably at least two to three times, the maximum length of a penetration in the direction of its extent.
  • the adoption of this measure ensures that a certain length of material is free over the entire width of the metal side-plate when viewed in the longitudinal direction, so that a specific, defined minimum weakening of the longitudinal rigidity of the insert plate is achieved over its entire width.
  • this is bent in its cross section, at least in the area of weakening, and is preferably of a u-shaped embodiment.
  • Such a design of the cross section, including in the area of weakening, increases the connecting rigidity of the insert plate and guarantees dimensional stability.
  • FIG. 1 depicts a radiator that is delimited on its mutually opposing sides by an insert plate in accordance with the invention
  • FIG. 2 depicts an insert plate in accordance with the invention
  • FIG. 3 depicts an insert plate in accordance with the invention with a weakened area as an enlarged representation.
  • FIG. 1 depicts a radiator 10 , in which tubes extending in the longitudinal direction of the radiator are surrounded by heat exchanger surfaces 11 .
  • Two mutually opposing sides of the radiator are delimited by metal side-plates 12 , which are securely retained to other components connected to the radiator and are also aligned in the longitudinal direction.
  • each of the metal side-plates 12 exhibits two weakened areas 13 , each of which, in particular in the final one third, and preferably in the final one quarter of the metal side-plate, are executed all the way to the edge.
  • FIG. 2 depicts an oblique representation of such a metal side-plate 12 having two weakened areas 13 , in conjunction with which each of the weakened areas 13 is formed by penetrations 14 in the material of the metal side-plate.
  • FIG. 3 depicts an enlarged representation of such a weakened area 13 .
  • the penetrations are executed adjacent to one another in such a way that a network of webs 15 is produced between them.
  • the webs 15 are executed in such a way that they delimit lozenge-shaped penetrations in each case.
  • the penetrations 14 are arranged in a plurality of rows 16 .
  • Four rows of penetrations 14 which form the weakened area 13 , are executed one after the other in the illustrative embodiment represented here.
  • the rows are offset in relation to one another in such a way that a material-free section is produced over the entire width of the metal side-plate 12 , the overall length of which is greater than twice the maximum length of a penetration in the direction in which it extends.
  • the use of a lozenge-shaped form for the penetrations ensures that a compact, contiguous arrangement of the penetrations can be achieved over the entire surface.
  • a constant width of the webs 15 between two penetrations is maintained throughout, so that the rigidity of the metal side-plate is capable of being determined accurately in the area of the penetration.
  • the metal side-plate 12 is of u-shaped execution in its cross section, in conjunction with which the cross-sectional form is also maintained in the weakened area 13 . It is ensured by this means that a corresponding weakening of the material is also provided in this peripheral area and, at the same time, that a basic measure of torsional rigidity and dimensional stability of the metal side-plate is also assured in the weakened area 13 .

Abstract

The invention relates to a metal side-plate (12) for a radiator, particularly a tubular radiator, such as those used in motor vehicles with combustion engines. The aim of the invention is to provide a meal side-plate (12) which is embodied in such a way that stresses arising from various types of thermal expansion of the metal side-plate (12) and tubular radiator (10) can be prevented. The metal side-plates (12) are characterized in that they have a weakened area (13) in which the material of the metal side-plate is weakened in order to compensate heat expansion according to that of the cooling body.

Description

  • The present invention relates to a metal side-plate for radiators, in particular for tubular radiators such as those which find an application in vehicles with internal combustion engines.
  • Radiators of this kind exhibit a radiator body, in which tubes extend in the longitudinal direction, in conjunction with which heat exchanger surfaces are embodied between the tubes. What is more, the radiator is enclosed by at least one pair of metal side-plates situated to either side of the radiator body. The metal side-plates in this case extend along or across the direction in which the tubes of the tubular radiator extend. They delimit in particular the heat exchanger surfaces, are utilized for the purposes of assembly, for example, and also prevent the ingress of undesired contamination into the area between the heat exchanger surfaces and in so doing prevent impairment of the heat exchange performance of the heat exchanger.
  • The length of the tubes and the heat exchanger surfaces changes in the presence of fluctuations in the operating temperature of the tubular radiator, so that a loading due to thermal stress can make its effect felt on the metal side-plate.
  • The object of the invention is to make available a metal side-plate that is executed in such a way that stresses arising from various kinds of thermal expansion of the metal side-plate and tubular radiator are prevented. This object is achieved by a metal side-plate in accordance with the independent claim.
  • A metal side-plate of this kind, which can find an application in particular for tubular radiators, is intended to be used in radiator bodies in which tubes extend in the longitudinal direction and in which heat exchanger surfaces are arranged between the tubes, in conjunction with which the metal side-plates are intended to close off the radiator on at least one pair of opposing sides. What is more, the metal side-plates are characterized in that they exhibit a weakened area, in conjunction with which the material of the metal side-plate in this area is weakened in such a way as to allow compensation for the thermal expansion corresponding to that of the radiator body.
  • This weakening of the material enables the thermal expansion of the metal side-plate to be adapted to that of the radiator body and thereby permits the permanent retention of the metal side-plate on both sides of the radiator body. The occurrence of stresses, both in the metal side-plate and in the radiator body, due to different thermal expansion is avoided at the same time.
  • According to a preferred embodiment of the invention, the weakening of a weakened area is effected by penetrations in the material of the metal side-plate. It is particularly advantageous if the penetrations are embodied in such a way that a network of webs is formed. The adoption of this measure ensures that high mechanical flexibility of the lateral part is achieved, which is able to compensate for thermal expansion deviating from the thermal expansion of the radiator body. It is especially favorable if the penetrations are executed in such a way that the network of webs forms lozenges standing on their tips in the longitudinal extent of the metal side-plate, that is to say in the longitudinal direction. In this way, the webs which delimit the penetrations in each case run with a directional component in the longitudinal direction of the metal side-plate, in which the different thermal expansion produces its effect, and also at all times in a directional component transversely thereto, so that a certain rigidity and dimensional stability of the metal side-plate nevertheless continue to be assured. An alternative embodiment is provided if the network of webs delimits honeycomb-shaped penetrations. What is more, the honeycomb-shaped penetrations can be formed both by penetrations having a hexagonal form and by penetrations having an octagonal form. Hexagonal, honeycomb-shaped penetrations have the advantage that they are able to form a closed surface, whereas in the case of octagonal honeycombs, lozenge-shaped intermediate surfaces occur repeatedly, with the result that a uniform, transcurrent pattern is not produced. What is more, octagonal honeycombs repeatedly form areas of material running in the longitudinal direction and in the transverse direction of the metal side-plate, whereas hexagonal honeycombs only exhibit areas of material running either in the longitudinal direction or in the transverse direction of the metal side-plate. It is accordingly possible in this case for a different longitudinal rigidity to result in relation to the transverse rigidity of the metal side-plate.
  • According to embodiments of the invention, a weakened area is produced in the form of a plurality of rows of penetrations, in conjunction with which the rows of penetrations are preferably arranged off-set in relation to one another, and the number of rows can be selected in such a way that, when viewed in the direction in which the metal side-plate extends, the length of the penetrations added together at each point transversely to the direction of its extent amounts to at least 1.5 times, and preferably at least two to three times, the maximum length of a penetration in the direction of its extent. The adoption of this measure ensures that a certain length of material is free over the entire width of the metal side-plate when viewed in the longitudinal direction, so that a specific, defined minimum weakening of the longitudinal rigidity of the insert plate is achieved over its entire width.
  • According to a preferred embodiment of the insert plate, this is bent in its cross section, at least in the area of weakening, and is preferably of a u-shaped embodiment. Such a design of the cross section, including in the area of weakening, increases the connecting rigidity of the insert plate and guarantees dimensional stability.
  • Moreover, the invention is explained in greater detail below with reference to the illustrative embodiment depicted in the drawing. In the drawing:
  • FIG. 1 depicts a radiator that is delimited on its mutually opposing sides by an insert plate in accordance with the invention;
  • FIG. 2 depicts an insert plate in accordance with the invention;
  • FIG. 3 depicts an insert plate in accordance with the invention with a weakened area as an enlarged representation.
  • FIG. 1 depicts a radiator 10, in which tubes extending in the longitudinal direction of the radiator are surrounded by heat exchanger surfaces 11. Two mutually opposing sides of the radiator are delimited by metal side-plates 12, which are securely retained to other components connected to the radiator and are also aligned in the longitudinal direction. What is more, each of the metal side-plates 12 exhibits two weakened areas 13, each of which, in particular in the final one third, and preferably in the final one quarter of the metal side-plate, are executed all the way to the edge.
  • FIG. 2 depicts an oblique representation of such a metal side-plate 12 having two weakened areas 13, in conjunction with which each of the weakened areas 13 is formed by penetrations 14 in the material of the metal side-plate.
  • FIG. 3 depicts an enlarged representation of such a weakened area 13. It can be appreciated in this case that the penetrations are executed adjacent to one another in such a way that a network of webs 15 is produced between them. In the embodiment represented here, the webs 15 are executed in such a way that they delimit lozenge-shaped penetrations in each case. What is more, the penetrations 14 are arranged in a plurality of rows 16. Four rows of penetrations 14, which form the weakened area 13, are executed one after the other in the illustrative embodiment represented here. What is more, the rows are offset in relation to one another in such a way that a material-free section is produced over the entire width of the metal side-plate 12, the overall length of which is greater than twice the maximum length of a penetration in the direction in which it extends. The use of a lozenge-shaped form for the penetrations ensures that a compact, contiguous arrangement of the penetrations can be achieved over the entire surface. A constant width of the webs 15 between two penetrations is maintained throughout, so that the rigidity of the metal side-plate is capable of being determined accurately in the area of the penetration.
  • As can also be appreciated from FIGS. 2 and 3, the metal side-plate 12 is of u-shaped execution in its cross section, in conjunction with which the cross-sectional form is also maintained in the weakened area 13. It is ensured by this means that a corresponding weakening of the material is also provided in this peripheral area and, at the same time, that a basic measure of torsional rigidity and dimensional stability of the metal side-plate is also assured in the weakened area 13.

Claims (8)

1. A metal side-plate for radiators, in particular tubular radiators, in which the radiator body exhibits tubes and heat exchanger surfaces extending between the tubes, in which the radiator is enclosed by at least one metal side-plate arranged laterally on the radiator or at least one pair of metal side-plates arranged on either side of the radiator,
wherein
at least one metal side-plate exhibits at least one weakened area, in which the material of the metal side-plate is weakened in such a way as to allow compensation for the thermal expansion corresponding to that of the radiator body.
2. The metal side-plate as claimed in claim 1, wherein the weakening of a weakened area is effected by perforations in the material of the metal side-plate.
3. The metal side-plate as claimed in claim 2, wherein the penetrations are embodied in such a way that a network of webs is formed.
4. The metal side-plate as claimed in claim 3, wherein the network of webs delimits lozenges standing on their tips as penetrations in the longitudinal extent of the metal side-plate.
5. The metal side-plate as claimed in claim 3, wherein the network of webs delimits honeycomb-shaped penetrations.
6. The metal side-plate as claimed in claim 5, wherein a plurality of rows of penetrations is provided, in conjunction with which the rows of penetrations are preferably arranged off-set in relation to one another, and the number of rows is preferably selected in such a way that, viewed in the direction in which the insert plate extends, the length of the penetrations added together at each point transversely to the direction of their extent amounts to at least 1.5 times, and preferably at least two to three times, the maximum length of a penetration in the direction of its extent.
7. The metal side-plate as claimed in claim 1, wherein the insert plate is bent, at least in the area of weakening, and is preferably of a u-shaped execution.
8. A heat exchanger having at least one metal side-plate as claimed in claim 1.
US10/587,357 2004-02-02 2005-02-02 Metal side-plate for a radiator Abandoned US20070163751A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004005177 2004-02-02
DE102004005177.1 2004-02-02
PCT/EP2005/001025 WO2005073661A1 (en) 2004-02-02 2005-02-02 Metal side-plate for a radiator

Publications (1)

Publication Number Publication Date
US20070163751A1 true US20070163751A1 (en) 2007-07-19

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US10/587,357 Abandoned US20070163751A1 (en) 2004-02-02 2005-02-02 Metal side-plate for a radiator

Country Status (9)

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US (1) US20070163751A1 (en)
EP (1) EP1716378B1 (en)
JP (1) JP2007519883A (en)
CN (1) CN1914472A (en)
AT (1) ATE386915T1 (en)
BR (1) BRPI0507276A (en)
DE (2) DE502005002920D1 (en)
ES (1) ES2303224T3 (en)
WO (1) WO2005073661A1 (en)

Cited By (6)

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US20080190596A1 (en) * 2005-04-05 2008-08-14 Dieter Bachner Heat Exchanger, in Particular for a Motor Vehicle
US20100065262A1 (en) * 2008-09-18 2010-03-18 Multistack Llc Double inlet heat exchanger
US20100218914A1 (en) * 2007-11-12 2010-09-02 Behr Gmbh & Co. Kg Exhaust gas cooler for a motor vehicle
US20110024081A1 (en) * 2009-07-29 2011-02-03 Christian Riondet End plate with area of weakness for a heat exchanger
US20140202670A1 (en) * 2013-01-21 2014-07-24 Denso International America, Inc. Stamped thermal expansion relief feature for heat exchangers
US11137210B2 (en) 2019-08-07 2021-10-05 Denso International America, Inc. Heat exchanger

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FR2873434B1 (en) * 2004-07-20 2017-12-29 Valeo Thermique Moteur Sa HEAT EXCHANGER WITH JOUES
JP4984813B2 (en) * 2006-06-06 2012-07-25 株式会社デンソー Heat exchanger
DE102006017610B4 (en) 2006-04-12 2020-08-06 Mahle International Gmbh Heat exchanger for charge air cooling for motor vehicles, system
EP1921412B1 (en) * 2006-11-09 2018-02-28 VALEO AUTOSYSTEMY Sp. Z. o.o. Heat exchanger provided with improved side plates
DE102007003100A1 (en) 2007-01-16 2008-07-17 Oesterle, Hans-Joachim, Dipl.-Ing. Tubular cooler used in automobile, comprises tube block with sides overlapping tube plates and joined by seam-welding using industrial robot
DE102007003099A1 (en) 2007-01-16 2008-07-17 Oesterle, Hans-Joachim, Dipl.-Ing. Cooler e. g. for vehicles with internal combustion engines, has cooler body with cooling pipe arranged between two levels which are arranged with cooling pipes
DE102007004679A1 (en) 2007-01-25 2008-07-31 Oesterle, Hans-Joachim, Dipl.-Ing. Lamella-less tubular radiator for vehicle, has radiator body with cooling tube arranged between two tubing bases, where cooling tube has expansion compensator arranged between cooling tube parts
FR2916836B1 (en) * 2007-05-30 2015-06-26 Valeo Systemes Thermiques HEAT EXCHANGER WITH PERFORATED JOUES
DE102009050887A1 (en) 2009-10-27 2011-04-28 Behr Gmbh & Co. Kg Heat exchanger i.e. coolant radiator, for cooling or warming up fluid in internal combustion engine of motor vehicle, has side part with axis aligned parallel to axis of pipe, where side part is partially built from honeycomb structure
CN102261864A (en) * 2010-05-28 2011-11-30 扬州英谛车材实业有限公司 Core support plate of novel heat radiator
EP2522845A1 (en) * 2011-05-11 2012-11-14 Borgwarner Emission Systems Spain, S.L. Heat exchanger for cooling a gas
CN104930903A (en) * 2014-03-21 2015-09-23 泰安鼎鑫冷却器有限公司 Guard board for energy-absorbing heat sink and processing method thereof
CN105020001A (en) * 2014-05-02 2015-11-04 泰安鼎鑫冷却器有限公司 Energy-absorbing type protective plate for intercooler
DE102014219210A1 (en) * 2014-09-22 2016-03-24 Mahle International Gmbh Heat exchanger
CN107388877A (en) * 2017-06-15 2017-11-24 苏州吉利不锈钢制品有限公司 A kind of radiator shell structure

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US20040251002A1 (en) * 2002-04-09 2004-12-16 Frank Reichle Heat transfer unit, especially for a motor vehicle
US7198095B2 (en) * 2002-04-23 2007-04-03 Behr Gmbh & Co. Kg Heat exchanger, especially a heat exchanging module, for a motor vehicle

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US6065500A (en) * 1996-12-13 2000-05-23 Petroline Wellsystems Limited Expandable tubing
US20020029869A1 (en) * 1998-11-10 2002-03-14 Kodumudi Magesh V. Side member for heat exchanger and heat exchanger incorporating side plate
US6736193B2 (en) * 1998-11-10 2004-05-18 Valeo Thermique Moteur Side member for heat exchanger and heat exchanger incorporating side plate
US6260612B1 (en) * 1999-05-20 2001-07-17 Toyo Radiator Co., Ltd. “Stacked” type heat exchanger
US6412547B1 (en) * 2000-10-04 2002-07-02 Modine Manufacturing Company Heat exchanger and method of making the same
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080190596A1 (en) * 2005-04-05 2008-08-14 Dieter Bachner Heat Exchanger, in Particular for a Motor Vehicle
US20100218914A1 (en) * 2007-11-12 2010-09-02 Behr Gmbh & Co. Kg Exhaust gas cooler for a motor vehicle
US8794300B2 (en) 2007-11-12 2014-08-05 Behr Gmbh & Co. Kg Exhaust gas cooler for a motor vehicle
US20100065262A1 (en) * 2008-09-18 2010-03-18 Multistack Llc Double inlet heat exchanger
US8844610B2 (en) * 2008-09-18 2014-09-30 Multistack, LLC Double inlet heat exchanger
US20110024081A1 (en) * 2009-07-29 2011-02-03 Christian Riondet End plate with area of weakness for a heat exchanger
US20140202670A1 (en) * 2013-01-21 2014-07-24 Denso International America, Inc. Stamped thermal expansion relief feature for heat exchangers
US10393451B2 (en) * 2013-01-21 2019-08-27 Denso International America, Inc. Stamped thermal expansion relief feature for heat exchangers
US11137210B2 (en) 2019-08-07 2021-10-05 Denso International America, Inc. Heat exchanger

Also Published As

Publication number Publication date
DE102005004907A1 (en) 2005-08-18
WO2005073661A1 (en) 2005-08-11
DE502005002920D1 (en) 2008-04-03
JP2007519883A (en) 2007-07-19
ATE386915T1 (en) 2008-03-15
BRPI0507276A (en) 2007-06-26
ES2303224T3 (en) 2008-08-01
CN1914472A (en) 2007-02-14
EP1716378B1 (en) 2008-02-20
EP1716378A1 (en) 2006-11-02

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