EP1828488A1 - Dieselhammer - Google Patents
DieselhammerInfo
- Publication number
- EP1828488A1 EP1828488A1 EP05822549A EP05822549A EP1828488A1 EP 1828488 A1 EP1828488 A1 EP 1828488A1 EP 05822549 A EP05822549 A EP 05822549A EP 05822549 A EP05822549 A EP 05822549A EP 1828488 A1 EP1828488 A1 EP 1828488A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- piston
- cylinder
- injection
- diesel hammer
- 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
Links
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
- E02D7/02—Placing by driving
- E02D7/06—Power-driven drivers
- E02D7/12—Drivers with explosion chambers
- E02D7/125—Diesel drivers
Definitions
- the invention relates to a diesel hammer with
- a fuel supply device through which a given amount of fuel, in particular diesel oil, can be introduced into the working space during each working cycle.
- Such diesel hammers which are also referred to as diesel bears, are used in particular for foundation work in the construction industry for driving piles of all kinds, such as concrete pillars, iron girders, sheet pile wall elements or the like, into a ground.
- the piston With the aid of a Auskl inking device is pulled up and released at a certain height, whereupon he falls under the action of gravity down.
- the piston actuates a fuel pump when falling, thereby
- the released explosion energy hurls on the one hand the piston to a new duty cycle back up and drives the other hand, the pile in the ground.
- the high-pressure injection the fuel is injected during the compression of the air by the falling piston at high pressure usually in the form of a finely atomized fuel spray into the working space of the cylinder. This mist together with the air forms an ignitable mixture.
- the fuel ignites in the high-pressure injection already during the compression process, as soon as the compressed air reaches a temperature sufficient to ignite the fuel mixture.
- diesel hammers using high pressure injection are less suitable for ramming heavy pile or difficult soil conditions with hard layers.
- Advantages of the high pressure injection are a good, relatively residue-free combustion and a good starting behavior of the diesel hammer as well as a good ramming effect on soft soil layers.
- the second type of injection is so-called impact atomization, which, in contrast to high-pressure injection, can also be referred to as low-pressure injection.
- the fuel is introduced at the beginning of the compression process with lower pressure, usually in the form of a fuel jet, in the working space and is then first as a fuel surface on the upper face of the hammer.
- Diesel hammers that use a low-pressure injection are less well suited to be used at low resistors, Bodenwi- '. In these cases, the compression is reduced due to the lower resistance of the soil, because even the building up compression pressure is transmitted via the downwardly moving hammer on the Rammgut. The working space is actually enlarged, which in turn at the expense of compression pressure.
- Combustion is therefore of reduced quality in soft soils, which can lead to undesirable residues (soot, unburnt fuel in the combustion gases) that pollute the environment.
- An advantage of the impact atomization is that the kinetic energy of the piston is used effectively, since the piston strikes hard on the hammer.
- a diesel hammer with impact atomization is less likely to overheat, is less prone to failure, and easier to operate than a high-pressure injection diesel hammer.
- a diesel hammer is to be created, which can be used in different soil conditions with good impact efficiency with good combustion quality.
- the fuel supply device is designed such that the fuel in a first injection as atomized fuel mist and in a second Injection as fuel jet is injected into the working space.
- the fuel spray of the first injection type flows into the working space substantially perpendicularly to the direction of movement of the piston in the vicinity of the upper end surface of the striking piece.
- a good distribution of the fuel spray is achieved in the working space, resulting in an overall good and effective combustion of the resulting fuel / air mixture
- the fuel spray of the second type of injection is injected into the working space of the cylinder such that it impinges obliquely on the piston-side end face of the striking piece. This ensures that the liquid fuel spreads well over the face, which leads to a better atomization when the piston hits the hammer and thus to a good and effective combustion.
- a structurally simple to implement diesel hammer results from derj enigen embodiment in which the fuel supply device comprises at least one high-pressure injection device and at least one low-pressure injection device, which in each case a line through at least one fuel pump, whose inlet communicates with a fuel tank, at any given cycle of the diesel hammer a certain amount of fuel is supplied.
- the jet can in each case be adjusted via a high-pressure injection device and the fuel quantity fed in each case via a low-pressure injection device, preferably via the fuel pump itself.
- the impact intensity of the diesel hammer can be adapted to different ground conditions, depending on the hardness of the ground.
- steerbarer chokes or in the opening time controllable valves is possible.
- a well functioning and timely injection of the fuel matched to a duty cycle of the diesel hammer is achieved when the falling piston controls or actuates the fuel pump or an injector.
- a combustion chamber ensuring effective combustion is provided when the end face of the piston delimiting the working chamber of the cylinder is set down by a circumferential radially outward step. So is the combustion chamber, which is formed when the
- End face of the piston rests on the inner end face of the hammer, toroidal and has a relatively small volume.
- the fuel is injected in a third injection as both atomized fuel mist and as a fuel jet in the working space of the cylinder.
- FIG. 2 shows a low-pressure injection device with and 3 fuel pump, whose actuating tappet is shown in different initial positions;
- Figure 4 schematically shows an electronic control of the amount of fuel which is supplied to the working space.
- FIG. 1 shows a diesel hammer 10 with a cylinder 12 which is open on both sides and in practice has a length of 5 to 10 m and a diameter of 0.5 to 1 m can.
- a piston 14 runs.
- a coaxial to this impact piece 16 engages slidably in the open lower end of the cylinder 12 a.
- the lower end of the cylinder 12 carries a by means of screws, of which in the figure is designated by the reference numeral 18, fixed annular bearing unit 20.
- a central shaft portion 22 of the striking piece 16 is guided tightly and slidably, the one opposite
- Inner diameter of the cylinder 12 has reduced outer diameter.
- a striking plate 24 is formed below the cylinder, the outer lower convex boundary surface 26 cooperates in operation with the upper end of a driven pile material such as a concrete pile, an iron carrier, a sheet pile element or the like.
- a piston portion 28 is formed with a plurality of circumferential, axially spaced sealing rings 30 which run on the inner circumferential surface 32 of the cylinder 12.
- the top of the piston portion 28 defines together with the underside of the piston 14 and the peripheral wall of the cylinder 12 a working space 34.
- the working space 34 of the cylinder 12 facing end face 36 of the hammer 16 is ground flat with a flat fuel recess 37.
- damping ring 38 is arranged between the striking plate 24 of the hammer 16 and the bearing unit 20 of the cylinder 12.
- Another damping ring 40 is in the vicinity of the bearing unit 20 between the top the bearing unit 20 and the underside of the piston portion 28 of the hammer 16 effective.
- a lower working end 44 of the piston 14 which is provided with circumferential, axially spaced sealing rings 42, runs above the striking piece 16.
- the lower free plan ground end face 46 of the piston 14 is offset by a radially outer circumferential step 48, so that a toroidal shape of the combustion chamber is formed when the end face 46 of the piston 14 rests on the end face 36 of the striking piece 16.
- the working end 44 of the piston 14 is formed on a mass portion 50 thereof, which extends into the upper portion of the cylinder 12, not shown here.
- the mass portion 50 has a driving shoulder, not shown here, on which a releasable hook of a lifting device also not shown here can attack.
- a high pressure injector 52 is arranged with a schematically indicated fuel pump 53 and a high pressure injector 54.
- the injection nozzle 54 of the high-pressure injector 52 opens just above the end face 36 of the hammer 16 in the working space 34 of the cylinder 12th
- further high-pressure injection nozzles may be arranged distributed evenly in the peripheral wall of the cylinder 12.
- the high-pressure injection nozzle 54 is connected via a line 58 to the outlet of the fuel pump 53 arranged on the outside of the cylinder 12, the inlet of which communicates with a fuel tank 55 filled with diesel oil.
- the fuel pump 53 is actuated via an actuating tappet 57 when the piston 14 falls down.
- the high-pressure injection device 52 in particular its injection nozzle 54, is An oilbilet so that it injects the diesel oil supplied to it at high pressure substantially as finely atomized mist 16 in the working chamber 34 of the cylinder 12.
- the injection nozzle 54 is aligned so that the diesel oil is injected substantially perpendicular to the direction of movement of the piston 14.
- a further fuel pump 60 which is driven by a biased into the interior of the cylinder 12 actuating plunger 61 upon falling of the piston 14, is connected on the delivery side via a line 64 with a low-pressure injector 66 and forms with this a low-pressure injector 68th Die Fuel pump 60 communicates with a fuel tank 62 filled with diesel oil.
- Low-pressure injector 68 is axially spaced from high-pressure injector 52 toward the upper end of cylinder 12 at and in the peripheral wall of cylinder 12. Its injection nozzle 66 is designed and aligned such that the discharged fuel in a substantially hanging jet is sprayed approximately centrally on the end face 36 of the hammering piece 16.
- additional additional low-pressure injection nozzles can preferably be located at the same height as the
- Low-pressure injector 66 may be distributed around the circumference of the cylinder 12.
- the fuel pumps 53 and 60 are independently adjustable in their flow rate, so that the high-pressure injector 54 and the low-pressure injector 66 supplied fuels is continuously variable, as will be explained below.
- the peripheral wall of the cylinder 12 is penetrated by obliquely upwardly extending working nozzle 70 and 72, as can be seen from the figure. About them combustion air is sucked in and combustion gases are discharged.
- Figures 2 and 3 show the fuel pump 60 of the low-pressure injector 68, wherein its actuating plunger 61 in two different starting positions is shown.
- the actuating tappet 61 extends through the circumferential wall of the cylinder 12. It terminates externally in a pump piston 80 and in the interior of the cylinder 12 in a wedge-shaped actuating portion 82 running in a mating recess 81 in the peripheral wall of the cylinder 12 and connected to each other via a piston rod 84.
- a concave actuating surface 86 of the actuating portion 82 facing the interior of the cylinder 12 has a curvature corresponding to that of the inner circumferential surface 32 of the cylinder 12 and is inclined upwardly and radially outwardly.
- an upwardly facing stop plate 88 which cooperates with a radially adjustable housing-fixed stop plate 90 a Hubeinstell noticed 92.
- the stop plate 90 passes through a threaded bore 94 on a radially outwardly extending threaded spindle 96, which can be rotated via a servo motor 98, which is indicated only schematically in the drawing.
- the pump piston 80 runs in a pump cylinder 100 disposed externally on the peripheral wall of the cylinder 12, which has a fuel outlet 102 communicating with the injector 66 and a fuel inlet 104 in fluid communication with the fuel tank 62.
- the actuating plunger 61 is always pressed by a spring 106 in the direction of the interior of the cylinder 12, so that the stop plate 88 abuts in the initial position against the stop plate 90 of Hubeinstellvorraum 92.
- FIG. 2 shows the position of the stop plate 90 in which the pump piston 80 has its largest stroke. This means that in this position, the stop plate 90, the amount of fuel delivered by the fuel pump 60 per stroke fuel quantity is maximum.
- the high pressure injector 52 may be configured according to the above-explained embodiment of the low pressure injector 68. Components of the high-pressure injection device 52 are provided in Figures 2 and 3 with corresponding reference numerals.
- FIG. 4 shows an electronic control of the working Room 32 of the cylinder 12 supplied amount of fuel, wherein thejenden of the Figures 1 to 3 corresponding components are identified by the same reference numerals.
- the high-pressure injector 54 and the low-pressure injector 66 are in each case in fluid communication with a spring-loaded solenoid valve 110.
- the latter in each case communicate with a pressurized fuel reservoir 112, which is fed by the corresponding fuel pumps 53 and 60 via check valves 113.
- the amount of fuel to be supplied to the high pressure injector 54 and the low pressure injector 66, respectively, is input to a computer 114 having a display monitor 116 via a keyboard 118.
- Information about the present ground conditions is also possible as input parameters, on the basis of which suitable data for the high-pressure injection device 52 and the low-pressure injection device 68 are then calculated by appropriate software.
- the computer 114 calculates from the input data denj enigen period over which the solenoid valves 110 are opened, whereby according to the opening duration of a certain amount of fuel through the high pressure injector 54 and. is injected through the low pressure injector 66 into the working space 32 of the cylinder 12.
- Control unit 120 transmits these as control signals to each time a controllable monoflop 122 of the high-pressure injector 52 and. the low pressure injector 68 passes.
- the monostables 122 are on the input side via contact terminals 124 in FIG. 4 only schematically indicated in the piston web projecting actuating tappets 126 in conjunction and are activated upon movement of the actuating plunger 126.
- non-contact sensors can be used, which respond when the piston 14 reaches a predetermined position when falling.
- the monoflops 122 are in each case connected to an amplifier 128 which supplies the amplified signal of the
- Monoflops 122 passes to the corresponding solenoid valve 110, whereupon this takes its open position in accordance with the pulse width of the monoflop 122 set in each case. Is the switching time of the two monoflops 110, for the high-pressure injector 52 and for the
- Low pressure injector 68 can be selected differently, achieved, the solenoid valves 110 are transferred by spring force back into its closed position.
- a solenoid valve 110, a fuel reservoir 112 and a monostable 122 together form a controllable in the flow rate fuel source.
- the diesel hammer 10 described above operates as follows:
- the piston 12 In the initial state, the piston 12 is raised by the already mentioned holding device, not shown, in an upper position. After notching it falls from there under the action of gravity down, closes the work socket 70 and 72 and actuates with its end face 46, the actuating plunger 57, 61 of the high pressure injection device 52 and. the low pressure injector 68. If the embodiment of the injection devices 52 and 68 shown in FIGS. 2 and 3 is used, this means that the piston 14 strikes the actuating surface 86 of the actuating section 82 of the actuating member 61 from above. Upon further dropping of the piston 14, this is moved to the left in FIGS. 2 and 3.
- the pump piston 80 is displaced in the direction of the outlet 102 of the pump cylinder 100, whereby the fuel located in the working space 108 is conveyed to the injection nozzle 54 or 66 and injected into the working chamber 34 of the cylinder.
- the injection nozzles 54 and 66 will now individually or in combination, j e after adjustment of the fuel pumps 53 and 60, inject a certain amount of diesel oil in the above-mentioned manner in the working space 34 of the cylinder 12. If one of the injection devices 52, 68 does not inject fuel into the working chamber 34 of the cylinder 12, its actuating tappet 57 or 61 is displaced radially outward by control of the servomotor 98 until the respective actuating section 86 no longer penetrates into the interior of the motor Cylinder 12 sticks out.
- the desired parameters are programmed via the computer 114. If one of the two injectors 52, 68 injects no fuel into the working space 34 of the cylinder 12, then in this case the corresponding monostable 122 is controlled to pulse width zero, so that the corresponding solenoid valve 110 is not opened when the piston 14 falls. With the impact of the piston 14 on the hammer 16 and / or on the gas cushion between the piston and hammer a downwardly directed force is exerted on the hammer and this on the pile material, which drives the pile further into the ground.
- the diesel hammer can thus optionally only by means of the high-pressure injector 52 in a first injection as atomized fuel mist, only by means of the low-pressure injector 68 in a second injection as a fuel jet or by a combination of both in a third injection as both atomized fuel mist also be operated as a fuel jet. This makes it adaptable to different soil conditions.
- the low-pressure injector 68 can be supplied with a small amount of fuel, so that the already explained impact atomization supports the application.
- the proportion of low-pressure injection can be increased by corresponding change in the allocated amount of fuel through the low-pressure injector 68, whereby the direct power transmission of the piston 14 on the hammer 16 and thus on the Rammgut is increased, as already explained.
- the ratio of the quantities of fuel supplied by the injectors 52 and 68 can be adjusted accordingly.
- an individual adjustment of the working and mode of action of the diesel hammer 10 to different and changing soil conditions is possible, with a good and complete combustion of the diesel oil is guaranteed.
- the high pressure injector 52 will continue to operate on hard soil strata utilizing the principle of impact sputtering for each low duty cycle work cycle.
- the fuel pump 53 of the high-pressure injector 52 thus supplies a minimum amount of fuel at each operating cycle of the high-pressure injector 54. This avoids that the usually very finely formed injection nozzle 54 of the high-pressure injection device 52 is added by combustion residues or other impurities such as lubricating oil residues and no longer works.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Mining & Mineral Resources (AREA)
- Paleontology (AREA)
- Civil Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Structural Engineering (AREA)
- Fuel-Injection Apparatus (AREA)
- Diaphragms For Electromechanical Transducers (AREA)
- Saccharide Compounds (AREA)
- Toys (AREA)
- Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004062043A DE102004062043A1 (de) | 2004-12-23 | 2004-12-23 | Dieselhammer |
PCT/EP2005/012791 WO2006072297A1 (de) | 2004-12-23 | 2005-12-01 | Dieselhammer |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1828488A1 true EP1828488A1 (de) | 2007-09-05 |
EP1828488B1 EP1828488B1 (de) | 2008-07-23 |
Family
ID=36169102
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05822549A Not-in-force EP1828488B1 (de) | 2004-12-23 | 2005-12-01 | Dieselhammer |
Country Status (7)
Country | Link |
---|---|
US (1) | US20090071672A1 (de) |
EP (1) | EP1828488B1 (de) |
CN (1) | CN100582381C (de) |
AT (1) | ATE402293T1 (de) |
CA (1) | CA2591927A1 (de) |
DE (2) | DE102004062043A1 (de) |
WO (1) | WO2006072297A1 (de) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE531337C2 (sv) * | 2007-07-03 | 2009-02-24 | Atlas Copco Constr Tools Ab | Bränsledriven brytmaskin |
US20120292062A1 (en) * | 2011-05-20 | 2012-11-22 | American Piledriving Equipment, Inc. | Systems and methods for controlling diesel hammers |
EP2767636B1 (de) * | 2013-02-15 | 2015-05-20 | UTM Universal Tiefbau Maschinen Verwaltungs- und Beteiligungsgesellschaft mbH | Dieselramme |
DE102013101550A1 (de) * | 2013-02-15 | 2014-08-21 | UTM Universal Tiefbau Maschinen Verwaltungs- und Beteiligungsgesellschaft mbH | Dieselramme |
EP2871288B1 (de) * | 2013-11-12 | 2016-03-16 | Delmag GmbH & Co. KG | Dieselramme |
EP2871286B1 (de) * | 2013-11-12 | 2016-03-23 | Delmag GmbH & Co. KG | Rammhammer |
EP2871287B1 (de) * | 2013-11-12 | 2016-06-08 | Delmag GmbH & Co. KG | Dieselramme |
EP2924170A1 (de) * | 2014-03-28 | 2015-09-30 | Delmag GmbH & Co. KG | Rammhammer |
EP2924172B1 (de) * | 2014-03-28 | 2016-06-22 | Delmag GmbH & Co. KG | Rammhammer |
EP2924171B1 (de) * | 2014-03-28 | 2016-07-13 | Delmag GmbH & Co. KG | Rammhammer |
EP2995721B1 (de) * | 2014-09-10 | 2016-09-07 | Delmag GmbH & Co. KG | Rammhammer |
AU2015391736A1 (en) * | 2015-04-17 | 2017-11-02 | Junttan Oy | A method for pile-driving |
CN105442603B (zh) * | 2016-01-21 | 2017-10-10 | 永康市嘉宏工具制造有限公司 | 打桩机的打桩机构以及打桩机 |
DE102022128360A1 (de) | 2022-10-26 | 2024-05-02 | Rws Gmbh | Pyrotechnische Schlagramme, Kartuschenbausatz und Verfahren zum Bestimmen einer Pyrotechnikmaterialmenge zum pyrotechnischen Eintreiben eines Rammguts in einen Untergrund |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2305772A (en) * | 1939-08-09 | 1942-12-22 | Haage Konrad | Diesel power ram |
US2633832A (en) * | 1949-07-22 | 1953-04-07 | Syntron Co | Diesel hammer |
US2740385A (en) * | 1950-06-24 | 1956-04-03 | Haage Konrad | Hammer and starting device therefor |
US2755783A (en) * | 1953-06-18 | 1956-07-24 | Mckiernan Terry Corp | Free piston internal combustion pile hammer |
US2804856A (en) * | 1954-12-22 | 1957-09-03 | Syntron Co | Diesel hammer starting device |
US2857888A (en) * | 1957-05-17 | 1958-10-28 | Syntron Co | Portable internal combustion percussion tools |
US3161184A (en) * | 1962-05-10 | 1964-12-15 | Link Belt Co | Diesel pile hammer starting device |
US3679005A (en) * | 1969-10-24 | 1972-07-25 | Ishikawajima Harima Heavy Ind | Diesel hammer |
BE771087A (fr) * | 1970-08-18 | 1971-12-16 | Delmag Maschinenfabrik | Mouton diesel a pulverisation par percussion |
US3923017A (en) * | 1971-11-06 | 1975-12-02 | Delmag Maschinenfabrik | Arrangement for injection nozzle and exhaust openings in a diesel assisted ram |
US3967688A (en) * | 1973-08-14 | 1976-07-06 | Mitsubishi Jukogyo Kabushiki Kaisha | Fuel injection device for an impact atomization-type diesel pile hammer |
NL172579C (nl) * | 1974-03-13 | 1983-09-16 | Delmag Maschinenfabrik | Dieselheiblok met slagverstuiving van de brandstof tussen heiblokzuiger en slagstuk. |
NL162443C (nl) * | 1974-12-10 | 1980-05-16 | Kooten Bv V | Werkwijze voor het doen verbranden van brandstof in een dieselheiblok met slagverstuiving. |
GB1572349A (en) * | 1976-05-21 | 1980-07-30 | Bsp Int Foundation | Drop hammers |
US4473123A (en) * | 1982-08-05 | 1984-09-25 | Raymond International Builders, Inc. | Diesel hammer capable of delivering uplift blows and method of using same |
US4580641A (en) * | 1983-04-28 | 1986-04-08 | Raymond International Builders, Inc. | Method and apparatus for starting diesel type hammers |
DE3545880A1 (de) * | 1985-12-23 | 1987-06-25 | Lindenmeyer Gmbh & Co Geb | Dieselramme |
DE19529538A1 (de) * | 1995-08-11 | 1997-02-13 | Delmag Maschinenfabrik | Ramme |
DE10115681A1 (de) * | 2001-03-29 | 2002-10-10 | Delmag Gmbh & Co Kg | Dieselbär |
US6736218B1 (en) * | 2001-04-16 | 2004-05-18 | American Piledriving Equipment, Inc. | Diesel hammer systems and methods |
-
2004
- 2004-12-23 DE DE102004062043A patent/DE102004062043A1/de not_active Withdrawn
-
2005
- 2005-12-01 US US11/722,414 patent/US20090071672A1/en not_active Abandoned
- 2005-12-01 EP EP05822549A patent/EP1828488B1/de not_active Not-in-force
- 2005-12-01 CA CA002591927A patent/CA2591927A1/en not_active Abandoned
- 2005-12-01 WO PCT/EP2005/012791 patent/WO2006072297A1/de active Application Filing
- 2005-12-01 DE DE502005004846T patent/DE502005004846D1/de active Active
- 2005-12-01 CN CN200580044737A patent/CN100582381C/zh not_active Expired - Fee Related
- 2005-12-01 AT AT05822549T patent/ATE402293T1/de not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO2006072297A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN100582381C (zh) | 2010-01-20 |
US20090071672A1 (en) | 2009-03-19 |
DE102004062043A1 (de) | 2006-07-13 |
DE502005004846D1 (de) | 2008-09-04 |
WO2006072297A1 (de) | 2006-07-13 |
CA2591927A1 (en) | 2006-07-13 |
EP1828488B1 (de) | 2008-07-23 |
CN101087919A (zh) | 2007-12-12 |
ATE402293T1 (de) | 2008-08-15 |
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