EP1664659A2 - Module a huile destine a un moteur a combustion interne - Google Patents

Module a huile destine a un moteur a combustion interne

Info

Publication number
EP1664659A2
EP1664659A2 EP04765448A EP04765448A EP1664659A2 EP 1664659 A2 EP1664659 A2 EP 1664659A2 EP 04765448 A EP04765448 A EP 04765448A EP 04765448 A EP04765448 A EP 04765448A EP 1664659 A2 EP1664659 A2 EP 1664659A2
Authority
EP
European Patent Office
Prior art keywords
oil
oil cooler
bypass channel
base plate
module 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.)
Granted
Application number
EP04765448A
Other languages
German (de)
English (en)
Other versions
EP1664659B1 (fr
Inventor
Rainer Gendermann
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.)
Ing Walter Hengst GmbH and Co KG
Original Assignee
Ing Walter Hengst 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 Ing Walter Hengst GmbH and Co KG filed Critical Ing Walter Hengst GmbH and Co KG
Publication of EP1664659A2 publication Critical patent/EP1664659A2/fr
Application granted granted Critical
Publication of EP1664659B1 publication Critical patent/EP1664659B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/03—Mounting or connecting of lubricant purifying means relative to the machine or engine; Details of lubricant purifying means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/08—Arrangements of lubricant coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the present invention relates to an oil module for an internal combustion engine, with a support part which can be flanged onto an engine block of the internal combustion engine and which carries at least one oil filter and an oil cooler, wherein channels are provided in the oil module for guiding oil and water, one channel of which is an oil cooler bypass channel that connects an oil inlet of the oil cooler with an oil outlet of the oil cooler.
  • An oil module of the type mentioned at the outset is known from EP 0 816 645 B1.
  • a bypass channel running exclusively within the carrier part for a throttled bypass to the oil guidance through the oil cooler is integrated in the carrier part.
  • This bypass ensures that when the oil is cold and therefore viscous, a relatively large part of the oil flows to the lubrication points of the internal combustion engine bypassing the oil cooler in order to ensure adequate lubrication even when the lubricating oil is still cold.
  • an increasingly greater proportion of the oil flows through the oil cooler, as a result of which the temperature of the oil is reduced in order to prevent thermal damage to the oil of the internal combustion engine due to excessive oil temperatures.
  • the object of the present invention is therefore to create an oil module of the type mentioned at the outset which avoids the disadvantages set out and in which an adaptation to different requirements, in particular a change in the passage cross section of the bypass channel, is possible with less effort and therefore at lower costs is.
  • This object is achieved according to the invention with an oil module of the type mentioned at the outset, which is characterized in that the oil cooler bypass channel extends over at least the greater part of its length through an oil cooler base plate which closes the oil cooler on the carrier part side or through an intermediate plate which is sealingly arranged between the oil cooler and the carrier part.
  • Essential to the invention is the oil according to the application module of the Olkühlerbypasskanal via the at least greater part of its length in the oil cooler base plate or in egg ⁇ ner intermediate plate, but not in the produced as a diecast carrier part.
  • Both the oil cooler base plate and the intermediate plate are very simple components in comparison to a die-cast part, which can be produced inexpensively and in which minor changes in shape can also be carried out with little effort and thus inexpensively.
  • the same carrier part can thus always be used for different designs of the associated internal combustion engine; the necessary adjustment is then made by simply changing or selecting the appropriate oil cooler base plate or intermediate plate. Complex and expensive changes to the injection mold for the carrier part are thus completely avoided.
  • the intermediate plate the oil cooler can also remain unchanged, which saves the production of different oil cooler designs. Only different intermediate plates then have to be manufactured and installed depending on the design of the associated internal combustion engine.
  • the oil cooler bypass channel in the oil cooler base plate or in the intermediate plate by at least one of the oil cooler base plate or the intermediate plate via their Entire thickness penetrating slot is formed, which is sealed on the oil cooler side by the remaining oil cooler and on the support part side by the support part to the external environment.
  • the design of the oil cooler bypass channel as a slot, which passes through the oil cooler base plate or the intermediate plate over its entire thickness, makes the production particularly simple since such a slot can be produced with little effort and its contour can also be changed with little effort if necessary.
  • the oil cooler bypass channel in the oil cooler base plate or in the intermediate plate be formed by at least one bead-side or oil cooler-side bead, pressed into the oil cooler base plate or the intermediate plate, or milled groove, which is formed by the carrier part or the oil cooler side is sealed off from the outside by the remaining oil cooler.
  • the oil cooler bypass channel is already closed on one side, which simplifies the sealing.
  • the oil cooler bypass channel runs over its entire length in the oil cooler base plate or in the intermediate plate.
  • An alternative embodiment of the oil module provides that a part of the oil cooler bypass channel lying in the oil cooler base plate or in the intermediate plate forms a central section of the oil cooler bypass channel and that two shorter end sections of the oil cooler bypass channel each run through the support part.
  • This design has the advantage that the oil cooler base plate or intermediate plate has a higher stability and dimensional stability because the part of the oil cooler bypass channel lying in the oil cooler base plate or intermediate plate does not take up the entire length between an oil inlet and an oil outlet in the form of openings in the oil cooler base plate or intermediate plate. Rather, in the vicinity of the openings for the oil inlet and the oil outlet, stabilizing material bridges remain in the oil cooler base plate or intermediate plate between the openings on the one hand and the central section of the oil cooler bypass channel on the other hand.
  • a further alternative embodiment of the oil module suggests that a part of the oil cooler bypass duct lying in the intermediate plate forms two end sections of the oil cooler bypass duct and that a shorter middle section of the oil cooler bypass duct runs through the carrier part.
  • This design has the advantage that in the area of the middle section of the oil cooler bypass channel the oil cooler base plate or intermediate plate can have a material bridge which, in the same way as in the previously described embodiment, ensures an increase in the stability and dimensional stability of the oil cooler base plate or intermediate plate.
  • the oil cooler bypass channel has a cross section that has a throttling effect.
  • a change in the throttle effect can be caused here a change in the cross section of the oil cooler bypass channel can be achieved overall.
  • the oil cooler bypass channel can have at least one cross-sectional constriction which has a throttling effect.
  • the flow resistance of the oil cooler bypass channel can be determined by a suitable design or change in the cross-sectional constriction.
  • cross-sectional constriction is formed by at least one nose protruding into the oil cooler bypass channel.
  • the cross-sectional constriction is formed by at least one overlap region between one end of the oil cooler bypass duct and a duct region on the carrier part side, which is connected to the oil inlet or oil outlet of the oil cooler.
  • a change in the flow resistance of the oil cooler bypass channel can be achieved here by changing the size of the overlap area, which can be done, for example, by changing the length of the overlap between the oil cooler bypass channel on the one hand and the channel area in the carrier part on the other.
  • the oil cooler base plate or the intermediate plate is a stamped part made of metal, in particular light metal, such as aluminum.
  • a stamped part is a particularly inexpensive component that can be manufactured contributes to low manufacturing costs of the oil module.
  • the use of metal, in particular light metal ensures good durability on the one hand and a low weight on the other hand with good thermal conductivity.
  • Aluminum is particularly suitable here.
  • the oil cooler base plate or the intermediate plate is manufactured by means of a punching tool with an exchangeable tool insert in the area of the oil cooler bypass channel.
  • a uniform basic punching tool can be used for the production of the oil cooler base plate or intermediate plate, in which case only one tool insert has to be exchanged when the plate is changed.
  • the invention proposes that a valve is arranged in the course of the oil cooler bypass channel, which is dependent on a pressure difference between the Oil inlet and the oil outlet of the oil cooler releases a variable passage cross-section, the passage cross-section being smaller at a lower differential pressure and the passage cross-section being larger at a higher differential pressure.
  • a low differential pressure occurs in particular when the oil is warm, so that there is then a higher cooling requirement for the oil and, accordingly, a larger proportion of the oil has to be passed through the oil cooler.
  • the valve is formed by a leaf spring which is arranged in the oil cooler bypass channel pointing in the direction of flow of the oil, the leaf spring not or not at all differential pressure-loaded condition runs obliquely through the oil cooler bypass duct and, in a more differential pressure-loaded state, is automatically adjustable from its position, which runs obliquely through the oil cooler bypass duct, to a position increasingly increasing in parallel to the oil cooler bypass duct and releasing an increasing cross-section.
  • the leaf spring consists of a bimetallic strip or comprises a bimetallic strip by means of which the position of the leaf spring in the oil cooler bypass channel can be adjusted automatically in a temperature-dependent manner, with an increasing temperature resulting in a reduction in the passage cross section Adjustment of the leaf spring leads.
  • a temperature-dependent adjustment of the leaf spring forming the valve is additionally achieved. This achieves an even more precise and needs-based division of the oil flow between the oil cooler and the oil cooler bypass duct.
  • FIG. 1 shows an oil module in a first embodiment in longitudinal section
  • FIG. 2 shows the oil module from FIG. 1 in plan view, partly in section
  • FIG. 4 the oil module in a second embodiment in a representation corresponding to FIGS. 1 and 2,
  • FIG. 6 the oil module in a third embodiment, again in the same representation as in FIGS. 1 and 2,
  • FIG. 7 and FIG. 8 the oil module in a fourth embodiment, again in the same representation as in FIGS. 1 and 2,
  • Figure 11 shows the detail circled in Figure 9 in an enlarged detail.
  • Figure 1 and Figure 2 show an oil module 1 in a first embodiment, in Figure 1 in longitudinal section and in Figure 2 in plan view, partly in section.
  • the oil module 1 consists of a carrier part 2, which is a die-cast part made of light metal, such as aluminum.
  • the carrier part 2 can here be connected to an internal combustion engine (not shown) by means of two connecting flanges 20, 20 ', an oil supply channel 22 being connected in the flange 20 and an oil discharge channel 24 being connected to the internal combustion engine in the flange 20'.
  • an oil conduit 23 runs through the carrier part 2 and is visible in section in FIG. 1.
  • the carrier part 2 On its side facing upwards in FIG. 1 and in FIG. 2 towards the viewer, the carrier part 2 has an oil cooler flange 29 to which an oil cooler 3 is sealingly attached. is flanged. A seal, not shown, is arranged in a circumferential sealing groove 29 ', which ensures a liquid-tight flange connection.
  • the oil cooler 3 is of a conventional type. On its side facing the carrier part 2, the oil cooler 3 has a base plate 30.
  • the base plate 30 has a plurality of fastening bores 31, which can be seen in FIG. 2 in a top view.
  • An oil inlet 32 and an oil outlet 33 each run through the oil cooler 3 and its base plate 30 as further channels of the oil module 1.
  • the oil inlet 32 is in flow connection with the oil supply channel 22.
  • the oil outlet 33 of the oil cooler 3 is in flow connection with the oil line channel 23.
  • the carrier part 2 has a filter receptacle 28 which is used to accommodate an exchangeable oil filter insert and which can be closed in a liquid-tight manner by means of a screw cap (not shown here).
  • the oil module 1 has an oil cooler bypass channel 4, which connects the oil inlet 32 of the oil cooler 3 with its oil outlet 33 bypassing the oil cooler 3.
  • the oil cooler bypass duct 4 runs over its entire length through the base plate 30 of the oil cooler 3.
  • the bypass duct 4 is designed as a slot penetrating the oil cooler base plate 30 over its entire thickness and preferably together with the remaining base plate 30 produced in one punching process.
  • the oil cooler bypass duct 4 has a cross-sectional constriction 40 approximately in the middle between the oil inlet 32 and the oil outlet 33, which is formed by two lugs in the base plate 30 which are to be pointed towards one another.
  • a defined flow resistance of the bypass channel 4 is set by this cross-sectional constriction 40.
  • the oil cooler 3 In addition to the oil inlet 32 and the oil outlet 33, the oil cooler 3 also has a water inlet 36 and a water outlet 37, which provide for the supply and discharge of cooling water which enters into heat exchange with the oil in the oil cooler 3 for cooling the oil.
  • the cooling water is fed here through a water supply duct 26 and discharged through a water discharge duct 27, which are partially recognizable in the background on the right in FIG. 2 and which are connected to further water pipes in the installed state on an internal combustion engine.
  • the fastening bores 31 are used, through which screws can be guided into the carrier part 2 and into the threaded bores provided there.
  • the oil module 1 as a whole can then be connected to the internal combustion engine (not shown) with further screws, these screws being guided through fastening bores 21 which pass through the carrier part 2.
  • lubricating oil coming from the oil pump of the internal combustion engine flows into the oil module 1 via the connecting flange 20 through the oil supply channel 22.
  • the oil flows to the oil inlet 32 of the oil cooler 3.
  • the oil flowing in through the oil line duct 23 flows radially away outside inwards through the filter insert and then through the oil discharge channel 24 via the second connection flange 20 'back to the internal combustion engine and in this to the lubrication points to be supplied with oil.
  • an oil drain channel 25 also runs through the second connecting flange 20 '. This oil drain channel 25 serves to empty the filter receptacle 28 of oil when the filter insert is changed.
  • the oil drain channel 25 opens into an unpressurized area within the internal combustion engine, for example into the oil pan.
  • Figures 3 and 4 show a second embodiment of the oil module 1.
  • an intermediate plate 5 is provided parallel to the oil cooler base plate 30, which is arranged sealingly between the oil cooler base plate 30 and the oil cooler flange 29 of the carrier part 2.
  • the oil cooler 3 is of a conventional type here, the oil cooler base plate 30 also being of a conventional type, in which the base plate 30 only has the openings for forming the oil inlet 32, oil outlet 33, water inlet 36 and water outlet 37.
  • the intermediate plate 5 has an outline which corresponds to the outline of the oil cooler base plate 30. Furthermore, the intermediate plate 5 with the openings in the oil cooler base plate 30 has identical openings which each form a section of the oil inlet 32, oil outlet 33, water inlet 36 and water outlet 37.
  • the oil cooler bypass duct 4 is provided entirely within the intermediate plate 5.
  • the intermediate plate 5 is provided with a preferably punched slot extending over its entire thickness, which connects the openings which form the oil inlet 32 and the oil outlet 33 to one another.
  • a cross-sectional constriction 40 is also provided here, which defines a defined flow resistance of the bypass duct 4. If a different flow resistance of the oil cooler bypass channel 4 is required, a simple and inexpensive change of the intermediate plate 5 is sufficient.
  • the oil cooler 3 and the carrier part 2 of the oil module 1 then do not need to be changed.
  • the oil module 1 according to FIGS. 3 and 4 corresponds to the oil module 1 according to the previously described FIGS. 1 and 2.
  • FIGS. 5 and 6 show the oil module 1 in a third embodiment. It is characteristic of this version of the oil module 1 that the oil cooler bypass duct 4 is divided into several duct sections. As FIGS. 5 and 6 illustrate, a longer middle section 41 of the oil cooler bypass channel 4 runs through the oil cooler base plate 30. Connected to this middle section 41 are two end sections 42, 43 of the bypass channel 4, each of which is considerably shorter in relation to the middle section 41 and each in the Carrier part 2 are formed. This ensures that the oil cooler base plate 30 in the area between its openings for the oil inlet 32 and the oil outlet 33 on the one hand and the central portion 41 of the bypass channel 4 on the other hand each has a material bridge which stabilizes the oil cooler base plate 30 and makes it more dimensionally stable. The risk of warping of the oil cooler base plate 30 is thus avoided particularly reliably.
  • a desired flow resistance of the oil cooler bypass channel 4 can here preferably be determined by the dimensions of the central section 41, in particular its width, and can be specifically changed if necessary by changing the width of the central section 41.
  • the oil module 1 corresponds to the previously explained exemplary embodiments according to FIGS. 1 to 4.
  • FIGS. 7 and 8 show an oil module 1 in an embodiment modified from FIGS. 5 and 6. Also in the example according to FIGS. 7 and 8, the oil cooler bypass duct 4 runs for the most part through the oil cooler base plate 30 and for a smaller part through the carrier part 2. The division here is chosen such that two overall longer end sections 42, 43 pass through the base plate 30 of the oil cooler 3 and a shorter middle section 41 of the bypass channel 4, which runs through the carrier part 2.
  • a desired flow resistance of the oil cooler bypass channel 4 can preferably be determined by setting a specific cross section of the end section 42, 43 or one of these two end sections 42, 43.
  • the oil module 1 corresponds to the previously explained exemplary embodiments.
  • FIGS. 9 and 10 show a fifth exemplary embodiment of the oil module 1, which in its basic version corresponds to the oil module according to FIGS. 5 and 6, but has an additional component.
  • This additional component is a valve 6 which is arranged in the oil cooler bypass duct 4.
  • the valve 6 is designed as a leaf valve with a leaf spring 60 and is arranged in the middle section 41 of the oil cooler bypass channel 4 which runs within the oil cooler base plate 30 and points in the direction of flow of the oil.
  • This valve 6 serves to divide the oil flow that flows through the oil supply channel 22 in a suitable manner between the oil cooler 3 and the oil cooler bypass channel 4.
  • the leaf spring 60 forming the valve 6 is included designed in such a way that, given a high differential pressure between the oil supply duct 22 and the oil supply duct 23, as is the case in particular with low oil temperatures and high oil viscosity, it is brought into an extended position on the two sides of the valve 6 on account of the pressure difference which arises is in which the valve 6 releases a larger cross section of the oil cooler bypass channel 4. At a lower pressure difference, the valve 6 reduces the cross section of the oil cooler bypass channel 4 due to the restoring force of the leaf spring 60, as shown in FIGS. 9 and 10, so that a larger proportion of the oil flow is then passed through the oil cooler 3 and cooled.
  • the oil module 1 in its remaining elements and in its remaining function, corresponds to the examples described above.
  • FIG. 11 shows the detail from the oil module 1 encircled in FIG. 9 in an enlarged representation.
  • the valve 6 in the form of the leaf spring 60 can be seen in the center of FIG. At the right end in FIG. 11, the leaf spring 60 is connected to the carrier part 2, for example pressed or riveted or welded.
  • FIG. 11 shows a state of the valve 6 as it is with a small pressure difference on the two sides of the valve 6. If the pressure difference is small or completely absent, the valve 6 assumes a closed or approximately closed position, as a result of which all or at least the largest part of the oil flow is then passed through the oil cooler 3. At a higher pressure difference, the free end of the leaf spring 60 pointing to the left in FIG. 11 moves downward within the central section 41 of the oil cooler bypass channel 4, where is released by an increasingly larger passage cross section and an increasingly larger part of the oil flow can flow through the oil cooler bypass channel 4.
  • the valve 6 can additionally either consist of a bimetal strip or comprise a bimetal strip in its course. With such a bimetallic strip it can also be achieved that the valve 6 is additionally adjusted automatically depending on the temperature of the oil.
  • the valve 6 is designed with a bimetallic spring so that the valve 6 releases a larger cross section at low temperature and a smaller cross section of the oil cooler bypass channel 4 at higher temperature.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)

Abstract

L'invention concerne un module à huile (1) destiné à un moteur à combustion interne, comportant une partie support (2) pouvant être bridée sur un bloc moteur du moteur à combustion interne, supportant au moins un filtre à huile et un radiateur à huile (3). Ledit module à huile (1) comporte des canaux (22, 23, 24, 25; 26, 27; 4) destinés à guider de l'huile et de l'eau, un de ces canaux étant un canal de dérivation de radiateur à huile (4) connectant une entrée d'huile (32) du radiateur à huile (3) à une sortie d'huile (33) du radiateur à huile (3). Sur ledit module à huile (1), le canal de dérivation de radiateur à huile (4) s'étend sur au moins la majeure partie de sa longueur au travers d'une plaque de base de radiateur à huile (30) délimitant le radiateur à huile (3) côté partie support, ou au travers d'une plaque intermédiaire (5) disposée de façon jointive entre le radiateur à huile (3) et la partie support (2).
EP04765448A 2003-09-23 2004-09-21 Module a huile destine a un moteur a combustion interne Not-in-force EP1664659B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20314687U DE20314687U1 (de) 2003-09-23 2003-09-23 Ölmodul für eine Brennkraftmaschine
PCT/EP2004/010572 WO2005031128A2 (fr) 2003-09-23 2004-09-21 Module a huile destine a un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1664659A2 true EP1664659A2 (fr) 2006-06-07
EP1664659B1 EP1664659B1 (fr) 2008-11-12

Family

ID=34202476

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04765448A Not-in-force EP1664659B1 (fr) 2003-09-23 2004-09-21 Module a huile destine a un moteur a combustion interne

Country Status (9)

Country Link
US (1) US8104581B2 (fr)
EP (1) EP1664659B1 (fr)
JP (1) JP4385051B2 (fr)
KR (1) KR100866004B1 (fr)
CN (2) CN101915141B (fr)
AT (1) ATE414254T1 (fr)
BR (1) BRPI0414692B1 (fr)
DE (2) DE20314687U1 (fr)
WO (1) WO2005031128A2 (fr)

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Also Published As

Publication number Publication date
BRPI0414692B1 (pt) 2015-12-29
US20070068737A1 (en) 2007-03-29
EP1664659B1 (fr) 2008-11-12
ATE414254T1 (de) 2008-11-15
US8104581B2 (en) 2012-01-31
WO2005031128A2 (fr) 2005-04-07
CN101915141A (zh) 2010-12-15
KR20070020190A (ko) 2007-02-20
CN1871492B (zh) 2010-08-25
KR100866004B1 (ko) 2008-10-29
CN101915141B (zh) 2013-03-27
JP2007506035A (ja) 2007-03-15
WO2005031128A3 (fr) 2005-06-23
DE20314687U1 (de) 2005-02-10
JP4385051B2 (ja) 2009-12-16
DE502004008454D1 (de) 2008-12-24
CN1871492A (zh) 2006-11-29
BRPI0414692A (pt) 2006-12-19

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