EP1355822B1 - Schiffsantrieb - Google Patents

Schiffsantrieb Download PDF

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Publication number
EP1355822B1
EP1355822B1 EP02706725A EP02706725A EP1355822B1 EP 1355822 B1 EP1355822 B1 EP 1355822B1 EP 02706725 A EP02706725 A EP 02706725A EP 02706725 A EP02706725 A EP 02706725A EP 1355822 B1 EP1355822 B1 EP 1355822B1
Authority
EP
European Patent Office
Prior art keywords
propulsion device
propulsion system
vessel
propulsion
covering
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
EP02706725A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1355822A1 (de
Inventor
Thomas SCHÜLLER
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.)
Schmitt Kugelantriebe GmbH
Original Assignee
Schmitt Kugelantriebe GmbH
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 Schmitt Kugelantriebe GmbH filed Critical Schmitt Kugelantriebe GmbH
Publication of EP1355822A1 publication Critical patent/EP1355822A1/de
Application granted granted Critical
Publication of EP1355822B1 publication Critical patent/EP1355822B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H1/00—Propulsive elements directly acting on water
    • B63H1/02—Propulsive elements directly acting on water of rotary type
    • B63H1/04—Propulsive elements directly acting on water of rotary type with rotation axis substantially at right angles to propulsive direction
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
    • B63H5/02—Arrangements on vessels of propulsion elements directly acting on water of paddle wheels, e.g. of stern wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H1/00—Propulsive elements directly acting on water
    • B63H1/38—Propulsive elements directly acting on water characterised solely by flotation properties, e.g. drums

Definitions

  • the present invention is in the field of propulsion of watercraft and relates to a ship drive, according to the preamble of claim 1, such as. known from US-A-4 004 544.
  • the present invention is based on the technical problem of a ship propulsion system to indicate with good efficiency, which also takes into account the above problems.
  • a marine propulsion system is used to solve the above problem of the above Kind formed with the features of the characterizing part of claim 1.
  • a propulsion device for example a rotatably driven wheel or a driven rotating belt is provided.
  • This peripheral jacking device is on its outer peripheral surface of surrounded by a cover.
  • the cover does not surround the jacking device fully extensive. Rather, the propulsion device comes below the waterline of the to be driven directly in contact with the surrounding water.
  • the distance between the cover and the propulsion device is in the invention
  • Vessel propulsion selected such that the vessel surrounding the propulsion device is in operation
  • Water from the jacking device in the gap between the face of the Propelled device and the cover promoted by displacing air from the gap is, at least in the event that - as explained in more detail below is - is to be regarded as the preferred embodiment and in which the cover is independent from the state of charge of a ship to below the waterline and the top edge coverage regardless of the state of charge of the ship above the waterline is arranged, in other words before the operation of the propulsion device between the circumferential surface of the propulsion device and the cover at least also Air is.
  • the device according to the invention was developed by the inventor with regard to its performance evaluated in a pile pull test. In such an attempt the ship or a model with the interposition of a load cell on one Pile attached and the tensile force per power unit is determined. With conventional Propellers, commonly referred to as propellers, can be found in Such a pile tensile test determined a yield of about 0.023 kg / W become. In contrast, one showed with the ship propulsion system according to the invention maximum power of 0.054 kg / W. The maximum performance was with the invention Ship propulsion is reached when the flow channel is filled with water was. The ship propulsion system according to the invention then offers compared to the previously known Ship drives have a much higher efficiency.
  • a band Circulating jacking device either on a circular path or according to Art an armored chain with two opposite linear sections and two opposite Semicircle sections can circulate, can be provided both outside as well as within a distance from a housing wall in a water-bearing Canal is arranged to simplify the design of the ship's drive proposed the drive device with a circumferentially closed peripheral surface train. In this case there is water circulating in the direction of advance in the radial direction of the propulsion device only between the outer one Peripheral surface and the cover.
  • the jacking device have a corresponding profile on its peripheral surface.
  • the peripheral surface of the propulsion device protruding laterally through the peripheral surface, almost to the cover bordering boundary elements.
  • These boundary elements can either according to a preferred development of the present invention such as the cover is stationary, for example directly on the hull or at least be arranged fixed relative to the hull. Alternatively, it is suggested that To connect boundary elements with the rotating jacking device.
  • teeth should be designed so that they carry off ambient water into the gap between the face of the jacking device and the cover promote.
  • the effectiveness of the ship's drive can be different Can influence the directions of rotation.
  • the invention Ship drive used as a transverse drive for maneuvering in a ship, and it is therefore important to move the jacking device in both directions
  • teeth with an identical design are preferred Front and rear flanks on the peripheral surface of the jacking device arranged.
  • the Teeth formed on the outer peripheral surface of the propulsion device are preferred sawtooth-like, i.e. the front and back flanks of the teeth have different inclinations. It has turned out to be advantageous to front flank directed radially outwards towards the tooth tip with a smaller one Inclination to form, as the adjoining this behind the tooth tip and from there radially inward flank.
  • the trailing edge can even one have a strictly radially inward course, i.e. not to the peripheral surface contribute. It is different with the leading edge.
  • the tooth tip has also proven to be advantageous of the teeth curved in the axial direction, as in a preferred Further development of the present invention is proposed.
  • the front flank and / or the rear flank form the teeth curved in the axial direction.
  • the front and / or rear flank of the teeth is convexly curved in the circumferential direction form, a combination of the two aforementioned preferred Measures, i.e. a spherical configuration of the front and / or the rear flank with regard to the efficiency of the ship's drive and also with regard to the Avoiding waves is considered advantageous.
  • the propulsion device With regard good efficiency, it has also proven to be advantageous between the propulsion device and the cover a minimum gap of 2 to 10%, preferably To provide 3 to 6% of the diameter of the rotating jacking device.
  • the minimal gap in the above sense is in the aforementioned preferred embodiment with teeth whose tooth tips are convexly curved in the axial direction, given where the distance between the tooth tip and the cover is the smallest is.
  • the cover for Achieving good efficiency preferably opposite the peripheral surface the propulsion device is relatively simple, preferably flat in the axial direction can be trained. With a wheel as a propulsion device, the cover thus has a cylindrical, but open in a peripheral portion configuration.
  • the propulsion device perpendicular to to arrange their axis of rotation rotatably mounted about a control axis and also a To provide rotation of the propulsion device about the control device controlling the control axis.
  • the direction of travel can be rotated of the propulsion device can be influenced about the control axis without the A rudder must also be arranged.
  • Rotation of the propulsion device both when reversing and when Forward driving the maximum efficiency of the jacking device can be used.
  • the hood encloses at least the propulsion device, but not a possible engine and lubricated bearings or similar. Located inside the hood and in the area of the jacking device water during operation of the ship's drive. However, here are no such parts that are lubricated with lubricant, so even inside no lubricant can be released into the surrounding water from the hood.
  • the bearing plate is rotatable in one Hull mounted, open at the bottom and penetrated by the jacking device Pot added, with a seal between the bearing plate and the pot is provided.
  • This seal can be formed, for example, by a bellows his.
  • surrounding water only comes to the bottom of the pot and the underside of the cover plate and in the sealed by the hood Area. Contamination of the water with lubricants through contact with Lubricated components can thus be avoided, for example if all bearing parts a drive shaft or axis of rotation from the hood to the water be sealed.
  • the hood forms the cover.
  • the radial serves Section of the hood surrounding the propulsion device simultaneously as a cover to limit the gap surrounding the jacking device.
  • the bearing plate pivotably on the pot, with the interposition of at least one tilt damper.
  • the gyro forces arising when the propulsion device is pivoted about the control axis can thus by a certain pivoting of the bearing plate against the Resistance of the tilt damper can be intercepted and are not transmitted immediately on the hull.
  • the behavior of the marine propulsion system according to the invention can be according to a preferred one Control training by providing a gap adjustment device which adjusts the distance between the propulsion device and the cover.
  • This gap adjustment device can be used in the ship propulsion system according to the invention the height of the flow channel can be changed, for example, the amount of in the flow channel of circulating water at constant engine speed (operating point of the drive motor). Therefore, the wave formation at the rear of the ship can be changed without changing the operating point of the drive motor is required.
  • the drive device together with the cover provide height-adjustable immersion depth adjustment.
  • This adjustment device can the immersion depth of the drive device in the surrounding water can be influenced without simultaneously forming the flow channel Gap is changed.
  • Such an immersion depth adjustment device is in particular to be preferred if the drive device is the underside of the ship's hull surmounted.
  • the drive device is the underside of the ship's hull surmounted.
  • the propulsion device With the usual arrangement of the propulsion device on the underside of the hull it is particularly important for the best possible buoyancy of the ship
  • a yourself such a tapering buoyancy body preferably closes directly on the end face the propulsion device and has an approximately the diameter in this area the diameter corresponding to the jacking device.
  • the Buoyancy body preferably conical with one adjacent to the propulsion device first convex and then straight or concave Outside surface is formed.
  • a buoyancy body designed in this way is preferably designed as a closed hollow body, but does not effect only one improved buoyancy of the ship, but lifts due to the against the buoyancy body effective back pressure during a trip to the ship.
  • the buoyancy body freely rotatable on the axis of rotation or drive shaft of the propulsion device to store.
  • the radially outer end of the propulsion device is connected to the propulsion device, the propulsion device covering the mushroom head and the buoyancy body to provide at least partially extensive thickening. Because it has shown that due to the high efficiency of the invention Ships propulsion ships designed as gliders supported by the buoyancy effect the buoyancy body so far out of the water at full speed can be that these essentially only over the mushroom-shaped thickenings be in contact with the water.
  • the invention Ship drives for this each have two drives at the front of the ship and two drives are arranged at the rear of the ship.
  • the drives as well as those parts from the for example, in a hydrofoil, apply the ship's load to the water.
  • the mushroom-shaped thickening it is preferable to use the mushroom-shaped thickening as much as possible aerodynamically, with its outer peripheral surface preferably the outer peripheral surface continuing to train the buoyancy body.
  • FIG 1 is a side view of a displacer with different depths trained ship 2 shown.
  • the different diving depths are based on the different water lines W for different charge states.
  • a ship propulsion 4 according to the first exemplary embodiment is located in the stern of the ship 2 of the present invention.
  • this ship propulsion 4 are essential Components of a driving device designed as a gear 6 and one of these Gear 6 provided at least partially circumferentially surrounding cover 8.
  • the axis of rotation 10 of the gear 6 extends in the embodiment shown in the horizontal direction and otherwise perpendicular to the direction of advance V, i.e. perpendicular to the longitudinal axis of the ship 2.
  • the cover 8 is cylindrical, i.e. has been parallel to the axis of rotation 10 extending side surfaces.
  • the cover 8 surrounds the gear 6 with a wrap angle of about 240 °.
  • the cover 8 has a front, i.e. bugracertiges End 12 and a rear, rear end 14 on.
  • the two ends 12, 14 end approximately at the same level and flush with the underside of the hull 16.
  • Between The gear hull 6 projects over the bottom of the ship's hull 16 at the two ends 12, 14.
  • the bottom view of the hull 16 according to FIG. 2 is that of the cover 8 circumferentially limited and laterally formed by stationary side walls 18, 20 receiving space clearly visible for the gear.
  • the side walls 18, 20 are with the ship's hull 16 and are connected by a drive shaft 22 which in the The axis of rotation of the gear lies through, as will be seen in the following with reference to FIG. 3 is described in more detail.
  • FIG. 3 shows an end view of the ship's drive according to the illustrations in Figures 1 and 2.
  • the drive shaft 22 is mounted on bearings 24, 26 on both sides.
  • the side walls 18, 20 surround the gear 6 in a U-shape and are on their underside welded to the hull 16.
  • the drive shaft is over suitable seals 22 sealed through the side walls 18, 20 passed.
  • One horizontal extending transverse web extending parallel to the axis of rotation 10 of the drive shaft 22 32 of the hood 34 thus formed forms the circumference partially surrounding the gear 6 Cover 8 off.
  • the hood 34 is formed in two parts, the lower part 36 the seal and bushing for the drive shaft 22 includes and fixed to the Hull is connected, whereas the upper part 38, which has a flange 40 is connected to the lower part 36 and sealed against it, for maintenance purposes can be lifted off.
  • the interface between the upper part 36 and the lower part 38 is preferably chosen so that the upper part is in each any load condition can be lifted without water in the Hull 16 runs.
  • the gear wheel 6 has a plurality of teeth 46 on its circumferential surface, which refer to FIG the axis of rotation 10 have a convex curve in the axial direction. In figure 3, the tooth tip 48 of the uppermost tooth 46 can be clearly seen.
  • FIG. 4 shows a sectional view along the line IV-IV as shown in FIG. 3 and serves in particular to illustrate the configuration of the teeth 46.
  • the direction of rotation D in the main direction of propulsion of the ship, i.e. the direction of rotation of the gear 6 when the ship is moving forward is indicated by a curved arrow at "D".
  • Each tooth 46 has a leading edge 50 and a trailing edge 52.
  • the leading edge 50 has a smaller pitch than the circumference of the gear 6 the rear flank 52.
  • Each tooth 46 of the gear 6 is identical.
  • the front flanks 50 and trailing edges 52 are based on the axial extent of the axis of rotation 10 convexly curved. Accordingly, the inner jagged contour shows in figure 4 the axially outer edge of the gear 46, whereas the outer serrated contour in Figure 4, the circumferential contour in the middle (based on the width direction of the tooth) reproduces.
  • the front and trailing flanks 50, 52 are also convexly curved in the circumferential direction. It turns out that the flanks 50, 52 of the respective teeth 46 are spherical. The curvature in the axial direction is shown schematically in Figure 2.
  • the exemplary embodiment shown in FIG. 4 has disk-shaped delimiting elements 42, 44, between which the front and rear flanks 50, 52 form welded sheets are.
  • the front and rear flanks 50, 52 of the teeth 46 one is circumferential closed peripheral surface formed on the gear 6.
  • the Water circulates continuously in the gap 54 with the direction of rotation D.
  • the flow in the flow channel takes place from the rear end 14 to the front end 12 of the channel, that is to say in the direction of advance V.
  • the water flows with a horizontal speed component, from which is assumed to propel the ship forward into the gap 54 through the
  • the leading edge 50 is conveyed in and also leaves the gap 54 with a horizontal one Speed component that is assumed to be the ship 2 also drives in the direction of advance V.
  • FIGS. 5 to 7 show a second exemplary embodiment of the invention Shown propulsion.
  • This embodiment is - like Figures 5 and 6 too remove is - installed in a ship 2 designed as a full glider. More specifically are four identical embodiments of the ship propulsion system according to the invention in the ship 2 installed. There are two ship drives 4a in the width direction side by side in the bow of the ship 2 and two ship drives 4b in the width direction next to each other in the stern of the ship 2.
  • a separate rudder can be dispensed with as the ship's propulsion systems are controllable.
  • FIG. 7 Details of this control can be seen in FIG. 7.
  • a circular recess 60 has been cut out on the underside of the ship's hull 16, which is bounded in each case by side walls 56 projecting over the water line W.
  • the Sidewall 60 extends parallel to sidewall 56 of fuselage 16.
  • the bottom the pot 58 is provided with a circular recess 62, which from the Gear 6 and buoyancy bodies 46, which are discussed in more detail below is to be surveyed.
  • the pot 58 is via bearing 66 opposite the hull rotatably supported about an axis of rotation S. This rotation of the pot 58 in the hull 16 is a control device, not shown, for controlling the controlled in each direction of rotation.
  • Each of the drives 4a, b can be independent are rotated from each other about the control axis S.
  • a bearing plate 68 is received in the pot 58, which is also circular and recess penetrated by the gear 6 and the buoyancy bodies 46 70 is provided.
  • the bearing plate 68 supports the bearings 24, 26 and also the motor 30.
  • a bellows 72 and the recesses 62, 70 provided seal that prevents water between the Bearing plate 68 and the bottom of the pot 58 reaches the same.
  • the hood 34 rises on the side of the bearing plate 68 facing away from the water. In this exemplary embodiment as well, the hood 34 is driven by the drive shaft 22 projects through.
  • the bearings 24, 26 are located outside the hood 34.
  • the gearwheel is also non-rotatable with the drive shaft 22 in this exemplary embodiment 6 connected.
  • the limiting elements 42, 44 are provided. Adjacent to the side of the limiting elements 42, 44 are the respective buoyancy bodies 64 which are rotatably supported on the drive shaft 22 via bearings 74.
  • the buoyancy bodies 64 are essentially identical and are adjacent to the gear 6 on a diameter that is approximately the same diameter equivalent.
  • the outer contour of the buoyancy body 64 is in the embodiment shown is configured as follows: a first circumferential section 76 extends parallel to the axis of rotation 10. There follows a second circumferential section 78, which essentially a plane that has a contour tapering to the axis of rotation 10. This second peripheral section 78 can with a view to the greatest possible buoyancy in the water immersing buoyancy body 64 also extending convexly outward be trained.
  • the first peripheral section 76 is circumferentially covered by a thickening 80 surrounded, which is fixedly connected to the gear 6.
  • the inside of the thickening 80 is cylindrical.
  • the thickening 80 extends on both sides of the gear 6 and the associated delimiting elements 42, 44 and appears in the figure 7 shown sectional view mushroom-like.
  • the thickening 80 is centered in the area of the gear 6 continued through the surface contour of the teeth 46.
  • the tooth tip 48 of the teeth leads the outer contour of the thickening 80 continuously and without a step continued.
  • the bearing plate 68 is held in the pot 58 and can be pivoted relative to the latter stored, with the interposition of at least one inclination damper 82, the is designed as a conventional telescopic damper.
  • One end of the damper 82 is connected to the upper end of side wall 60, whereas the other End is hinged near the bearing plate 68.
  • the inclination damper 82 serves to dampen a pivoting movement by one Pivot axis, which in the embodiment shown in the longitudinal direction of the Ship extends.
  • the bearing plate 68 is at its in the direction of advance front and rear end pivoted about bearings.
  • the swivel axis formed thereby is perpendicular to the axis of rotation of the Motor 30 and the control axis S and intersects the two axes in their common Intersection. This intersection is in the embodiment shown Center of gear 6.
  • the hood 34 is a larger one Covering area and also includes the buoyancy body 64.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Farming Of Fish And Shellfish (AREA)
  • Control Of Multiple Motors (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Feed For Specific Animals (AREA)
  • Paper (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Prevention Of Electric Corrosion (AREA)
  • Seal Device For Vehicle (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Vehicle Body Suspensions (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Toys (AREA)
EP02706725A 2001-02-02 2002-01-21 Schiffsantrieb Expired - Lifetime EP1355822B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10104680 2001-02-02
DE10104680A DE10104680A1 (de) 2001-02-02 2001-02-02 Kugelantrieb
PCT/EP2002/000562 WO2002062658A1 (de) 2001-02-02 2002-01-21 Schiffsantrieb

Publications (2)

Publication Number Publication Date
EP1355822A1 EP1355822A1 (de) 2003-10-29
EP1355822B1 true EP1355822B1 (de) 2004-08-04

Family

ID=7672600

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02706725A Expired - Lifetime EP1355822B1 (de) 2001-02-02 2002-01-21 Schiffsantrieb

Country Status (17)

Country Link
US (1) US7040941B2 (pl)
EP (1) EP1355822B1 (pl)
JP (1) JP2004532151A (pl)
KR (1) KR100521519B1 (pl)
CN (1) CN1289350C (pl)
AT (1) ATE272529T1 (pl)
AU (1) AU2002240916B2 (pl)
DE (2) DE10104680A1 (pl)
DK (1) DK1355822T3 (pl)
EE (1) EE200300358A (pl)
ES (1) ES2225759T3 (pl)
HK (1) HK1060337A1 (pl)
NO (1) NO336075B1 (pl)
PL (1) PL201796B1 (pl)
PT (1) PT1355822E (pl)
WO (1) WO2002062658A1 (pl)
ZA (1) ZA200305937B (pl)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005005142A1 (de) * 2005-02-04 2006-08-24 Thomas Hauck Zentrifugalarbeitsmaschine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR200491672Y1 (ko) * 2016-04-29 2020-05-18 대우조선해양 주식회사 체인 타입 웨더타이트 댐퍼 구조물 및 이를 가지는 선박 또는 해양플랜트
CN107097909B (zh) * 2017-05-03 2023-02-28 太仓市农业技术推广中心 一种水面清洁船的明轮驱动装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US100820A (en) * 1870-03-15 tucker
US175405A (en) * 1876-03-28 Improvement in paddle-wheels
GB251869A (en) * 1925-11-02 1926-05-13 Andrew Young Vaned wheel propeller for light naval craft
US1701925A (en) * 1928-01-24 1929-02-12 George G Kisevalter Boat
FR755483A (fr) * 1932-12-28 1933-11-25 Procédé de propulsion d'un véhicule aquatique et dispositif de propulsion travaillant suivant ce procédé
US3166039A (en) * 1963-02-28 1965-01-19 Ralph W Weymouth Water craft
US3628493A (en) * 1969-06-12 1971-12-21 Edward E Headrick Impeller wheel for amphibious vehicle
GB1408486A (en) * 1973-06-25 1975-10-01 British Hovercraft Corp Ltd Propulsive force generating means for marine vehicles
US4004544A (en) * 1975-12-24 1977-01-25 Moore John J Twin turbine-wheel driven boat
CA1225288A (en) * 1985-12-17 1987-08-11 Christopher Ives Linear propeller
FR2619546B1 (fr) * 1987-08-17 1992-05-07 Auguste Legoy Engin de navigation modulaire equipe de flotteurs rotatifs
NO306247B1 (no) * 1997-12-05 1999-10-11 Tore Hystad FristrÕlepropell

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005005142A1 (de) * 2005-02-04 2006-08-24 Thomas Hauck Zentrifugalarbeitsmaschine
DE102005005142B4 (de) * 2005-02-04 2013-07-18 Thomas Hauck Zentrifugalarbeitsmaschine

Also Published As

Publication number Publication date
NO20033420D0 (no) 2003-07-30
AU2002240916B2 (en) 2005-06-16
ZA200305937B (en) 2004-09-01
DE50200751D1 (de) 2004-09-09
NO20033420L (no) 2003-10-02
CN1496317A (zh) 2004-05-12
NO336075B1 (no) 2015-05-04
DK1355822T3 (da) 2004-10-11
US7040941B2 (en) 2006-05-09
ES2225759T3 (es) 2005-03-16
PT1355822E (pt) 2004-11-30
WO2002062658A1 (de) 2002-08-15
CN1289350C (zh) 2006-12-13
US20060046587A1 (en) 2006-03-02
PL201796B1 (pl) 2009-05-29
KR100521519B1 (ko) 2005-10-12
JP2004532151A (ja) 2004-10-21
DE10104680A1 (de) 2002-04-04
KR20030096253A (ko) 2003-12-24
HK1060337A1 (en) 2004-08-06
EP1355822A1 (de) 2003-10-29
EE200300358A (et) 2004-04-15
PL367784A1 (pl) 2005-03-07
ATE272529T1 (de) 2004-08-15

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