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WO2003056137A1 - Convertisseur energetique coaxial - Google Patents

Convertisseur energetique coaxial Download PDF

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Publication number
WO2003056137A1
WO2003056137A1 PCT/NO2002/000410 NO0200410W WO03056137A1 WO 2003056137 A1 WO2003056137 A1 WO 2003056137A1 NO 0200410 W NO0200410 W NO 0200410W WO 03056137 A1 WO03056137 A1 WO 03056137A1
Authority
WO
WIPO (PCT)
Prior art keywords
ofthe
rotor
energy converter
groove
stator
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.)
Ceased
Application number
PCT/NO2002/000410
Other languages
English (en)
Other versions
WO2003056137A8 (fr
Inventor
Odd J. Edvardsen
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AU2002339765A priority Critical patent/AU2002339765A1/en
Priority to EP02778114A priority patent/EP1458954B1/fr
Priority to DE60226490T priority patent/DE60226490D1/de
Publication of WO2003056137A1 publication Critical patent/WO2003056137A1/fr
Publication of WO2003056137A8 publication Critical patent/WO2003056137A8/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/107—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape

Definitions

  • the present invention regards an energy converter, particularly for use as a hydrodynamic pump, compressor, motor or turbine, comprising a first part with a bore, where at least one helical groove is formed in the wall ofthe bore, and a second part with an external surface in which there is formed at least one helical groove, the first and second parts being designed to rotate relative to each other, and where at least one ofthe first and second parts is designed to be coupled to a shaft for transmission of torque.
  • a number of pumps for pumping fluid, and also motors, are known, which pumps and motors are based wholly or in part on utilisation ofthe energy in fluids. Often, one and the same unit will be able, with certain adaptations, to act as both pump, compressor, motor and turbine. This is also the case for the energy converter according to the present invention.
  • GB 2234557 describes a hydroelectric generator in which two rotatable cylinders are arranged one inside the other.
  • the cylinders each have helical flow paths directed in opposite directions.
  • the rotation is transmitted via a system of cogwheels to en electric generator.
  • the cross section ofthe cylinders is constant along their entire length.
  • GB 1573334 describes a cylindrical water wheel with wings that are twisted helically around the shaft. It is located inside a chamber with smooth walls. The cross sections of the water wheel and the chamber are constant along the entire active length.
  • US 4378195 describes a cylindrical rotor with a rough surface placed inside a chamber with smooth walls.
  • the chamber and the rotor also have the same cross section along the entire length.
  • US 4412417 describes a wave power station where a rotor is equipped with at least two helical wings slightly offset relative to each other. The rotor is not located in a housing, and has a constant cross section along its entire length.
  • US 5313103 describes a type of windmill with a rotor having a helical vane. This is not located in a housing either.
  • the rotor has a constant cross section along its entire length.
  • GB 1157273 describes a screw-type motor in which two oppositely twisted helical wings have been placed after each other on the same shaft inside a chamber with smooth walls.
  • the cross section of both the rotor and the chamber is the same along the entire length.
  • WO 94/13957 describes an impeller.
  • the rotor is constructed from helical wings attached to a central conical body.
  • the walls ofthe rotor chamber are smooth.
  • GB 98714 describes a mixer especially designed for mixing plastic materials.
  • the mixer comprises a rotor and a stator, both of which are provided with helical grooves.
  • the helical grooves on the rotor and the stator may be laid/twisted in opposite directions.
  • the grooves have an approximately rectangular cross section.
  • the present invention aims to provide an energy converter, particularly for use as a hydraulic pump, compressor, motor or turbine, for co-operation with one or more fluids, which is flexible in use, has low internal friction, is simple to manufacture, with low tolerance requirements, and which is highly applicable in several areas of use. This is achieved by the characteristics stated in the characterising part ofthe appended Claim 1.
  • the bore in the first part and the external surface ofthe second part are conical and exhibit complementary taper.
  • conical and cone denote all shapes where the diameter of one end is smaller than that ofthe other. This does not necessarily imply that the increase in diameter is constant.
  • a machine according to the invention having "bottle shaped" parts may also be utilised.
  • Figure la is a schematic diagram of an energy converter according to the present invention.
  • Figure lb shows the energy converter according to Figure la seen in the direction of arrow A;
  • Figure lc shows the energy converter according to Figure la seen in the direction of arrow B
  • Figure Id shows an alternative design ofthe stator
  • Figure le shows an alternative design ofthe rotor
  • Figure 1 f shows an assembly of the rotor and the stator
  • FIG. 2 illustrates the operating principles ofthe present invention
  • FIG 3 shows the stator according to Figure la
  • Figure 4 shows the rotor according to Figure la.
  • FIG. 5 schematically illustrates a practical use ofthe energy converter according to the invention.
  • Figure la shows an example of an embodiment of an energy converter according to the present invention.
  • the energy converter consists of a stator 1 and a rotor 2.
  • a shaft 3 is attached to the rotor.
  • FIG 3 schematically illustrates the stator 1.
  • the rotor and the stator to be shown as partially transparent. It defines an internal, conical bore 4 with its smallest diameter Dl to the left in Figure 3 and the largest diameter D2 to the right in the figure. It is expedient for a small section 5 by the smaller diameter Dl to be constructed with a uniform diameter, while the rest ofthe stator has an internal surface 6 that forms an angle with the external cylindrical surface 7 ofthe stator.
  • the angle a lies between 1° and 3°.
  • Helical grooves 8 are formed in the internal surface 6. Preferably, several helical grooves are formed and offset slightly relative to each other. In the embodiment shown, 12 helical grooves are laid/twisted at an angle of 45° to the longitudinal axis ofthe stator. The number of grooves may be higher or lower than this, and the angle may also be greater or smaller than 45°.
  • the section 5 having a uniform diameter constitutes between 5% and 20% of the length ofthe stator. It is also expedient for the diameters Dl and D2 to measure approximately 1/3 to 1/5 ofthe overall length ofthe stator.
  • the grooves 8 are very shallow at the largest diameter D2 ofthe stator 1 (to the right in Figure 3), having a depth of approximately zero at this end ofthe stator 1. The depth of the grooves then increases gradually towards the opposite end ofthe stator at diameter Dl (to the left in Figure 3). Here, the grooves 8 reach a depth approximately equal to the diameter D2, leaving the bottom ofthe grooves 8 lying along the surface of an imaginary cylinder corresponding to the diameter D2. This simplifies the production of the stator 1 considerably, as will be explained below. However, this is not critical to the operation, and for stators cast into a ready-made shape, the bottom ofthe grooves may also lie along an imaginary cone. The pitch ofthe grooves 8 may be uniform along the entire length ofthe stator, or it may vary.
  • Figure 4 shows the rotor 2.
  • the rotor 2 has a conical outer surface 10 that forms an angle with an imaginary cylinder circumscribing the rotor 2. The angle is the same as for the stator 1.
  • the largest diameter D3 ofthe rotor 2 is at the end where the shaft 3 is attached. Here is also a section 15 of uniform diameter.
  • the diameter D3 may be approximately equal to the largest diameter ofthe stator, D2.
  • the smallest diameter D4 ofthe rotor is equal to or smaller than the smallest diameter Dl ofthe stator 1.
  • Grooves 18 corresponding to the grooves 8 in the stator are formed in the surface 10 of the rotor.
  • the number of grooves and their pitch angle may be the same as for the grooves 8 in the stator 1, but they may also deviate from this.
  • the grooves 18 are laid/twisted in the opposite direction ofthe grooves 8 in the stator 1. In order to achieve the best possible efficiency, the grooves in the stator 1 and the rotor 2 must intersect at 90 °.
  • the section 15 of uniform diameter prefferably constitute between 5% and 20% ofthe length ofthe rotor.
  • the diameters D3 and D4 measure approximately 1/3 to 1/5 ofthe overall length ofthe rotor.
  • the grooves 18 are very shallow at the smallest diameter D4 ofthe rotor 2 (to the left in Figure 4) and have a depth of approximately zero at this end ofthe rotor 2.
  • the depth of the grooves increases gradually towards the opposite end ofthe rotor at diameter D3 (to the right in Figure 4).
  • the grooves 18 reach a depth approximately equal to the diameter D4, so as to leave the bottom ofthe grooves 18 lying along the surface of an imaginary cylinder equivalent to diameter D4.
  • the bottom ofthe grooves may also lie along an imaginary cone.
  • the pitch ofthe grooves 18 may be the same along the entire length ofthe rotor, or it may vary.
  • the stator 1 and the rotor 2 have approximately the same length.
  • a section ofthe rotor 2 protrudes from the stator 1, and correspondingly, a section ofthe stator 1 is not overlapped by the rotor 2. The significance of this will be explained below.
  • the energy converter will function perfectly also when the rotor can be inserted fully into the stator.
  • Figure lb shows the energy converter of Figure la seen in the direction of arrow A in Figure la.
  • the entrance to the 12 grooves 8 in the stator can be seen at the point of their greatest depth.
  • the rotor 2 here appears with a smooth surface, as the grooves in the rotor have a depth of approximately zero at this end ofthe energy converter.
  • Figure lc shows the energy converter of Figure la seen in the direction of arrow B in Figure la.
  • the entrance to the 12 grooves 18 in the rotor 2 can be seen at the point of their greatest depth.
  • the stator 1 here appears with a smooth surface, as the grooves in the stator have a depth of approximately zero at this end ofthe energy converter.
  • Figure Id shows an alternative embodiment ofthe stator.
  • the drawing shows a section through the energy converter at the end where the grooves 8' in the stator 1 ' have their greatest depth.
  • the rotor 2' here appears with a smooth surface, as the grooves in the rotor have a depth of approximately zero at this end ofthe energy converter.
  • the width ofthe grooves 8' increases in the direction of depth, so as to allow optimal utilisation ofthe cross sectional area ofthe stator 1' as a flow area.
  • a relatively thin wall la remains outside the grooves 8', in addition to a thin wall lb between the individual grooves 8' in the stator 1 '.
  • the purpose of this wall is to keep fluids in and provide the stator with sufficient strength and rigidity, but apart from this, it should be as thin as possible.
  • Figure le shows an alternative embodiment ofthe rotor 2'.
  • the drawing shows a section through the energy converter at the end where the grooves 18' in the rotor 2' have their greatest depth.
  • the stator 1 ' here appears with a smooth surface, as the grooves in the stator have a depth of approximately zero at this end ofthe energy converter.
  • the width ofthe grooves 18 ? decreases in the direction of depth, so as to allow optimal utilisation ofthe cross sectional area ofthe rotor 2' as a flow area.
  • the cross section ofthe grooves assumes an approximate wedge-shape. This leaves only a small core area 2a in the rotor and a thin wall 2b between the individual grooves 18'.
  • the function of this core area is primarily to provide the stator with sufficient rigidity and strength, and it should be as small as possible.
  • Figure 1 f shows an assembly of the rotor 2 ' in Figure 1 e and the stator 1 ' in Figure 1 d, which gives a better impression ofthe area ofthe grooves 8' and 18' in the stator 1' and the rotor 2' respectively, in relation to each other.
  • the areas ofthe grooves 8' and the grooves 18' at the largest flow area for the two parts is the same, but may also be made dissimilar by increasing or decreasing the diameter ofthe two parts (external diameter for the rotor and internal diameter for the stator).
  • the location of the largest flow area for the rotor and the same for the stator will not coincide, but will preferably be at opposite ends ofthe energy converter. Consequently, Figure If is a section through the stator at one end and the rotor at the other end ofthe energy converter.
  • the energy converter will be used as a hydraulic motor. Fluid flows in at the end ofthe stator 1 having the smallest diameterDl (see arrow A in Fig. 1) but the greatest groove depth. As the grooves in the rotor 2 at this end ofthe energy converter have a depth of zero, the fluid will flow along the grooves 8 in the stator 1. However, the grooves 8 in the stator 1 become shallower as the fluid flows along groove 8. Coincident with this, the grooves 18 in the rotor 2 become deeper.
  • Figure 2 shows a picture ofthe situation at a given moment in time for two grooves, one groove 8 in the stator 1 and one groove 18 in the rotor 2.
  • groove 8 and groove 18 can be seen to intersect at approximately right angles at point X at this given point in time. Therefore, some ofthe fluid will here flow across from groove 8, the cross section of which is steadily decreasing, to groove 18, the cross section of which is steadily increasing.
  • the fluid has to go through a 90° change in direction (here from flowing down to the right to flowing up to the right). This change in direction causes a force to be applied to the rotor 2, which is then forced to rotate.
  • the energy converter When used as a pump, the energy converter will work in the opposite way, with rotation ofthe rotor 2 creating a negative pressure in the grooves 8 in the stator 1 which sucks fluid into the grooves 8, while creating an overpressure in the grooves 18 which forces the fluid out at the opposite end ofthe pump.
  • the principles that apply when using the energy converter as a compressor will basically be the same as when using it as a pump. It is also possible to use the energy converter as a fuel turbine, with combustion of a fuel being initiated at the entrance to the turbine, and fuel and any expansion gas expanding through the turbine. However, this will require the energy converter to be constructed with a relatively small inlet area and a relatively large outlet area, due to the volumetric expansion.
  • the net orifice area (flow area) through the converter will typically be in the range 30 - 40% ofthe axial cross sectional area ofthe stator.
  • the flow area is substantially larger.
  • the angle of taper may be approximately the same for the bore ofthe stator and the external surface ofthe rotor, in order to avoid leakage and back flow which may reduce the efficiency and lead to overheating.
  • the rotor or the stator may have a slightly convex or concave shape (e.g. a barrel shape) but still have a largest diameter at one end and a smallest diameter at the other end.
  • One part (the rotor or the stator) may be made from a softer material than the other, allowing the running surface of this to adapt to the harder part after a period of operation. This may enhance the sealing effect between the parts.
  • Figure 5 schematically shows a practical example of a use ofthe energy converter. Here it is pumping oil, and this oil is also used to drive the device.
  • a hydraulic motor 20 and a hydraulic pump 21 are placed in a common housing 22.
  • the motor 20 has a stator 20a that is fixed relative to the housing 22 through being attached to a partition 24, and a rotor 20b.
  • the pump 21 has a stator 21a that is fixed relative to the housing 22 through being attached to a partition 25, and a rotor 21b.
  • the rotors 20b and 21b are coupled to a common shaft 23.
  • the displacement volume ofthe pump 21 is greater than that ofthe motor 20.
  • the pump 21 and the motor 20 are arranged in a manner such that the outlet end ofthe motor 20 faces the inlet end ofthe pump 21.
  • An inlet 26 for propellant fluid is disposed at the inlet end ofthe motor 20 to the left of the partition 24.
  • An inlet 27 for pumping medium is disposed between the partitions 24 and 25, and an outlet 28 for both the propellant fluid and the pumping medium is disposed at the outlet end ofthe pump 21 to the right ofthe partition 25.
  • a propellant medium such as e.g. oil is supplied through inlet 26 under pressure and forced through the motor 20. This rotates the rotor 20b ofthe motor 20, in turn driving the rotor 21b ofthe pump 21 via the shaft 23. As the displacement volume ofthe pump 21 is greater than that ofthe motor 20, a negative pressure will be created in the chamber between the partitions 24 and 25. This causes pumping medium to be sucked in through the inlet 27, to be mixed with the propellant medium flowing out through the outlet ofthe motor 20, and to be pulled through the pump 21. The unified fluid flow is then forced out through outlet 28.
  • the object of this solution is to convert the energy in high pressure fluid into mechanical rotational energy for driving a larger piece of low pressure equipment, which converts mechanical energy into fluid energy with a lower pressure but a significantly larger volume.
  • the energy converter according to the invention is particularly well suited to drawing off energy at high pressure. As such it will be highly appropriate to use the energy converter as a turbine when exploiting small hydroelectric resources, i.e. hydroelectric resources with a relatively low water regime but a steep hydraulic gradient (pressure head).
  • the energy converter in accordance with the invention is also suited for wave power stations. In this case, the pressure is relatively low, while the water regime is high. However, this will involve a change in the length/diameter ratio of the energy converter, through the diameter being increased in order to increase the flow area.
  • the energy converter may also be used as an expansion engine, e.g. as an internal combustion engine.
  • the flow area then increases in the direction ofthe flow ofthe combustion medium. This may be done e.g. by increasing the width ofthe grooves in the direction of flow.
  • the energy converter is particularly favourable in terms of manufacture, as it makes few demands w.r.t. tolerances.
  • Both the rotor and the stator can be cast to the finished shape without requiring any significant finishing treatment. Generally, it is only necessary to remove burrs and polish those surfaces that come into contact with each other.
  • the bore ofthe stator may be milled out, and the grooves may be turned.
  • the grooves ofthe rotor may also be turned through simple operations.
  • the rotor does not need to be supported at both ends.
  • This embodiment may be relevant to special applications.
  • the rotor should normally be supported at both ends, so as to achieve minimum - approximately zero - clearance between the stator and the rotor, which avoids cavitation and recirculation.
  • one ofthe parts should be made from a softer material, so that upon wearing down, the rotor may be pushed further into the stator.
  • the energy converter according to the invention is highly insensitive to particles and contamination in the medium flowing through it. Even with a highly abrasive medium such as drilling mud, the length ofthe service life ofthe energy converter will still be adequate.
  • the rotor and the stator may be made from different materials, depending on the area of use. Relevant materials may be steel, aluminium and various types of thermoset plastic or thermoplastic.
  • the cross-sectional shape ofthe grooves 8 and 18 is quadrangular. However, it may also be rounded or triangular, or have another shape that is appropriate in terms ofthe manufacturing process or provides optimum efficiency for the application in question.
  • stator 1 does not necessarily have to be stationary, but may rotate in the opposite direction ofthe rotor, which in fact gives the energy converter two rotors.
  • the inner part may be stationary and act as a stator while the outer part rotates and functions as a rotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Rotary Pumps (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Detergent Compositions (AREA)
  • Table Equipment (AREA)

Abstract

L'invention concerne un convertisseur énergétique, utilisé en particulier comme pompe hydrodynamique, compresseur, moteur ou turbine, qui comprend un stator (1) présentant un alésage (4), dans la paroi duquel est formée au moins une cannelure hélicoïdale (8), et un rotor présentant une surface externe (10), dans laquelle est formée au moins une cannelure hélicoïdale (18). Le stator (1) et le rotor (2) sont conçus pour tourner l'un par rapport à l'autre, au moins le rotor (1) étant conçu pour se coupler à un arbre (3) aux fins de la transmission de couple. L'alésage (4) dans le stator (1) et la surface externe (10) du rotor (2) sont coniques présentant un cône complémentaire.
PCT/NO2002/000410 2001-11-08 2002-11-08 Convertisseur energetique coaxial Ceased WO2003056137A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU2002339765A AU2002339765A1 (en) 2001-11-08 2002-11-08 Coaxial energy converter
EP02778114A EP1458954B1 (fr) 2001-11-08 2002-11-08 Convertisseur energetique coaxial
DE60226490T DE60226490D1 (de) 2001-11-08 2002-11-08 Koaxialenergiewandler

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20015468 2001-11-08
NO20015468A NO320961B1 (no) 2001-11-08 2001-11-08 Energiomvandler

Publications (2)

Publication Number Publication Date
WO2003056137A1 true WO2003056137A1 (fr) 2003-07-10
WO2003056137A8 WO2003056137A8 (fr) 2003-09-18

Family

ID=19913001

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO2002/000410 Ceased WO2003056137A1 (fr) 2001-11-08 2002-11-08 Convertisseur energetique coaxial

Country Status (6)

Country Link
EP (1) EP1458954B1 (fr)
AT (1) ATE394582T1 (fr)
AU (1) AU2002339765A1 (fr)
DE (1) DE60226490D1 (fr)
NO (1) NO320961B1 (fr)
WO (1) WO2003056137A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2482861A (en) * 2010-07-30 2012-02-22 Hivis Pumps As Assembly for use as a pump or motor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1157273A (en) * 1965-07-17 1969-07-02 Philips Electronic Associated Improvements in and relating to Screw-type Hydraulic Motors
GB1573334A (en) * 1976-05-06 1980-08-20 Watts J Submersible power coverter
US4378195A (en) * 1976-12-10 1983-03-29 Joseph Gamell Industries, Inc. Pressure fluid motor
GB2234557A (en) * 1989-07-10 1991-02-06 William Charles Pearson Keen Hydro electric generator
WO1994013957A1 (fr) * 1992-12-07 1994-06-23 Kittles, Pamela Appareil de pompage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1157273A (en) * 1965-07-17 1969-07-02 Philips Electronic Associated Improvements in and relating to Screw-type Hydraulic Motors
GB1573334A (en) * 1976-05-06 1980-08-20 Watts J Submersible power coverter
US4378195A (en) * 1976-12-10 1983-03-29 Joseph Gamell Industries, Inc. Pressure fluid motor
GB2234557A (en) * 1989-07-10 1991-02-06 William Charles Pearson Keen Hydro electric generator
WO1994013957A1 (fr) * 1992-12-07 1994-06-23 Kittles, Pamela Appareil de pompage

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2482861A (en) * 2010-07-30 2012-02-22 Hivis Pumps As Assembly for use as a pump or motor
GB2482861B (en) * 2010-07-30 2014-12-17 Hivis Pumps As Pump/motor assembly
US9382800B2 (en) 2010-07-30 2016-07-05 Hivis Pumps As Screw type pump or motor
USRE48011E1 (en) 2010-07-30 2020-05-26 Hivis Pumps As Screw type pump or motor

Also Published As

Publication number Publication date
NO20015468D0 (no) 2001-11-08
NO20015468L (no) 2003-05-09
DE60226490D1 (de) 2008-06-19
WO2003056137A8 (fr) 2003-09-18
AU2002339765A1 (en) 2003-07-15
EP1458954B1 (fr) 2008-05-07
NO320961B1 (no) 2006-02-20
ATE394582T1 (de) 2008-05-15
EP1458954A1 (fr) 2004-09-22

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