WO2003056186A1 - Pompe a gaz - Google Patents

Pompe a gaz Download PDF

Info

Publication number
WO2003056186A1
WO2003056186A1 PCT/GB2002/005651 GB0205651W WO03056186A1 WO 2003056186 A1 WO2003056186 A1 WO 2003056186A1 GB 0205651 W GB0205651 W GB 0205651W WO 03056186 A1 WO03056186 A1 WO 03056186A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
vane
accordance
rotor
axis
Prior art date
Application number
PCT/GB2002/005651
Other languages
English (en)
Inventor
Geoffrey Lover
Original Assignee
Power Jets Ltd.
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 Power Jets Ltd. filed Critical Power Jets Ltd.
Priority to AU2002352379A priority Critical patent/AU2002352379A1/en
Publication of WO2003056186A1 publication Critical patent/WO2003056186A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F04D3/02—Axial-flow pumps of screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps

Definitions

  • the present invention relates to gas pumps, i.e. devices for moving and/or com- pressing gases.
  • the present invention relates to pumps for moving and/or compressing air.
  • blowers for air ranging from domestic fans to the sophisticated turbines in gas jet engines. These all comprise essentially two or more blades radiating out from an axis. When turned they collect an amount of air determined by their physical dimensions and shape, plus the pitch or twist in the blade that presents more or less of the width of the blade to the air. This air is then moved axially in a direction determined by the pitch and rotation of the blades. In the case of aircraft propellers the pitch can sometimes be altered to vary the volume of air being moved, so altering the thrust and direction of air movement.
  • Embodiments of the present invention aim to overcome at least some of these shortcomings, resulting in safer, quieter and more effective movement of air or other gases.
  • compressors which of course are forms of pumps, there are basically two main versions, a reciprocating pump or a rotary pump.
  • centrifugal pumps and so-called screw pumps or compressors where male and female lobes mesh to compress the air.
  • Centrifugal pumps need to operate at very high speeds and the compression ratio increases according to the square of the rate of rota- tion, i.e. to double the compression it is necessary to quadruple the rotational speed. Operating at extremely high speeds results in centrifugal and heat generation problems. All these compressors are relatively nosy and require careful manufacturing, becoming quite expensive to produce.
  • embodiments of the invention aim to provide simple gas compressing pumps which will be quieter to operate and less costly to manufacture.
  • a gas pump comprising, a rotor, arranged to rotate about a longitudinal axis; and a housing arranged to enclose the rotor and having a gas inlet and a gas outlet, wherein the rotor comprises at least one substantially helical vane extending along and around said longitudinal axis, whereby, as the rotor rotates, the vane drives gas inside the housing along the longitudinal axis in a direction from the inlet towards the outlet.
  • the rotor comprises a plurality of helical vanes.
  • the rotor comprises two such vanes which are diametrically opposed about the axis.
  • the vanes are preferably evenly spaced about the axis with a phase difference of 360°/n between adjacent vanes.
  • the or each vane extends at least 180° around the axis. More preferably, the or each vane extends at least 360° around the longitudinal axis. Even more pref- erably, the or each vane forms a number of complete turns around the axis so that air or other gas can be continuously driven along an extended length inside the housing.
  • the housing may also be referred to as a stator.
  • the vane or vanes have a length along the axis which exceeds their maximum radial extent. More preferably, the vane length exceeds the vane's maximum radial extent from the axis by at least a factor of two.
  • the or each vane is continuous or essentially continuous along the axis so that the air or gases inside the housing are continuously driven along the axis between the rotor and the housing.
  • the vane or vanes may thus extend in essentially a continuous line along the length of the axis.
  • the rotating vane or vanes of the rotor extend radially from the axis so as to form a clearance fit with the inner surface of the housing.
  • "Clearance fit” is a well known engineering term, and will be understood as meaning that there is a small gap between the rotor extremities and the adjacent housing wall to permit free rotation, whilst at the same time reducing the amount of gas which can leak through the space between the rotor and stator, which would reduce the efficiency of the pump.
  • the vane or vanes may have a substantially constant radial extent from the axis along their lengths, such that as the rotor rotates its extremities sweep out a cylindrical surface.
  • the housing comprises a correspondingly shaped cylindrical inner surface to accommodate the rotor.
  • the radial extent of the vane from the axis may vary along the axis, preferably in a progressive manner, such that as the rotor rotates it has a tapering profile, i.e. it may be bounded by a conical or trumpet-shaped surface.
  • the inner surface of the housing accommodating the rotating vanes is correspondingly shaped, i.e. it may be conical, trumpet-shaped, or tapered in some other fashion.
  • the or each vane may spiral around the axis with substantially constant pitch.
  • the or each vane may have a pitch which varies along the axis.
  • the or each vane may have a substantially constant thickness along the axis, or al- ternatively its thickness may vary.
  • the rotor may comprise a shaft, with the vane or vanes being attached to the shaft such that they extend along its length and also extend out radially from it.
  • the shaft may have a substantially constant diameter along its length, or alternatively its diameter may vary.
  • the shaft and vanes may be fabricated from separate components, or alternatively may be formed as an integral unit.
  • the pump further comprises a deflector arranged at the inlet so as to deflect any gas leaking back along the axis, between the rotor and housing, forwards into the inlet.
  • the deflector may take the form of an annular plate.
  • the pump further comprises means for rotating the rotor, such as an electric motor driving the rotor via a suitably arranged shaft, or gearbox assembly for example.
  • embodiments of the invention may provide an axial flow machine for air or other gases where the air or gases are continuously driven along the axis between a rotor and a stator housing by means of one or more helical vanes positioned and extending along the axis of the rotor of the machine in essentially a continuous line along the length of the axis.
  • the rotor and/or stator may be designed such that the gases are compressed as they are moved along the axis.
  • the diameter of both the rotor and stator housing interior of the machine may be arranged to alter progressively along the length of the machine, so altering the spatial volume along the axis.
  • the rotor and housing may be tapered such that compression of the gas caused by the rotation is enhanced. It will be appreciated, however, that even where the rotor has substantially constant diameter along its length, some gas compression will be achieved, and this may be enhanced by arranging a tapered receiving chamber at the outlet of the housing, the chamber having another outlet of reduced diameter.
  • Another way of achieving enhanced compression is to vary the pitch of the rotor vane or vanes along the axis. Yet another way is to vary the thickness of the vane or vanes along the axis. Yet another way is to utilise a rotor with a shaft having a diameter which varies along the axis. As the diameter of the shaft increases towards one end, the volume available to gases between the rotor and stator housing is thus progressively decreased.
  • the design of the rotor and stator assembly may be altered to adjust the speed and pressure of the gas exiting the machine from the gas outlet.
  • a deflector plate is positioned at the inlet to deflect gases that may leak between the rotor and the stator back into the stator.
  • the rotor and stator are designed to achieve enhanced compression, it will be appreciated that the rotor may be rotated in the reverse direction for use as a form of vacuum machine, i.e. the design features which enhanced compression of gases in the forward direction similarly enhance suction in the reverse direction.
  • Fig 1 is a schematic representation of a gas pumping machine embodying the invention
  • Fig 2 is a schematic representation of a further embodiment with tapered rotor and housing for increasing the pressure and outlet flow speed;
  • Fig 3 is a schematic representation of a rotor suitable for use in embodiments of the invention, to give increased outlet pressure and flow speed, or alternatively increased suction in the reverse direction;
  • Fig 4 is a schematic diagram of a further rotor for use in embodiments of the invention;
  • Fig 5 is a schematic diagram of yet another rotor with a tapered shaft, and suitable for use in embodiments of the invention.
  • Fig 6 is an exploded side view of a pump embodying the invention
  • Fig 7 is an exploded perspective view of the pump of Fig 6;
  • Fig 8 is a perspective view of the front of the pump of Figs 6 and 7;
  • Fig 9 is a side view of the rotor of the pump form Figs 6 to 8;
  • Fig 10 is a front view of the rotor from Fig 9;
  • Fig 1 1 is a front view of an annular deflector plate suitable for use in embodiments of the invention
  • Fig 12 is a cross section of the deflector plate from Fig 11 ;
  • Fig 13 is a schematic representation of a further embodiment.
  • the Archimedes screw is well known for applications such as moving water, chemicals, metals and even meat. In all these applications the screw is moved relatively slowly. Except in water applications, the screw is open, i.e. not enclosed within a stator. However, by rotating the screw rapidly and enclosing it within a tube, similar to a ducted fan where the air movement is concentrated rather like focusing a torch beam, air would be moved axially and continuously along the tube. Now, instead of a blade blowing air in a direction and at a speed determined by the pitch of the blade, it would be driven continuously, so resulting in greater efficiency. The volume moved per revolution is determined by the pitch of the vane or lobe in one revolution along the axis and its height from the axis.
  • the inlet diameter can be significantly reduced. Not only is the tip of the blade travelling at slower speeds than a conventional propeller but it forms one long edge, so reducing the tip noise generated. At the same time, because the blades are shrouded in a tube, it results in a safer design. Also, at the same time, because the blades are now of smaller radius, the centrifugal forces are reduced, so reducing distortion and increasing its strength.
  • FIG. 1 A basic embodiment of the invention is shown in Fig 1.
  • a rotor 2 is rotated about a longitudinal axis A inside a stator housing 3 by a motor 5 and cou- pling shaft 51.
  • the rotor 2 comprises a shaft portion 22 of substantially constant diameter, to which are attached two generally helical vanes 21 a, 21 b which extend radially outwards from the shaft 22 and along the axis A.
  • Each helical vane thus spirals around the shaft 22, and hence the axis A.
  • the helical vanes are diametrically spaced about the rotational axis A (i.e. they are always opposite each other). Another way of describing this feature is that the two vanes are 180° out of phase.
  • the vanes have substantially uniform thickness along their lengths and have substantially constant radial extent from the axis A such that as the rotor rotates its extremities (i.e. the edges of the vanes) sweep out a cylindrical surface.
  • This cylindrical surface is just inside a cylindrical inner surface 33 of the housing 3.
  • the rotor is a clearance fit inside the housing 3 to mini- mise back leakage and so improve efficiency.
  • the housing 3 has a gas inlet 31 and a gas outlet 32, spaced apart along the longitudinal axis, and the confinement of the rotor within the housing means that as the rotor rotates gas is moved through the machine from the inlet 31 to the outlet 32 generally in the direction shown by the arrows in the figure.
  • the pump shown in Fig 1 may also be referred to as an axial flow machine.
  • the helical vane 21 a may also be referred to as a blade, comprising a virtually continual helix formed on a shaft.
  • the shaft is rotated by means of the mechanical drive 5.
  • two or more blades or vanes can be formed around the shaft to improve balance and effectiveness.
  • Fig 1 shows two such blades mounted on the shaft. The blades are rotated within the housing 3, which in this case is in the form of a tube, and as the shaft is rotated air is drawn into the tube inlet 31 , moved positively along the axis in the direction shown by the arrows and exhausted at the outlet 32.
  • each vane 21 a, 21 b makes two full turns around the axis A, i.e. each vane extends 720° around the shaft 22.
  • the pitch of each helix is con- stant, as is the outer radius.
  • the length of each vane is just over 4 times greater than its radial extent from the axis A. The continuous vanes thus drive gas continuously along their entire lengths through the housing 3.
  • Fig 1 The form of invention shown in Fig 1 will work quite effectively. Input and output air speeds will be similar and the air moves further and therefore faster per revolution of the shaft than would be the case with a conventional fan or propeller blade at the same rotational speed.
  • the volume of air moved per revolution is a function of the pitch of the helix and its height above the shaft, that is, the diameter of the rotating blade(s).
  • both the rotating blades 21 a, 21 b and the housing 3 are tapered to form a cone-like shape.
  • the radial extent of each blade varies progressively along the length of the rotor. Taking the first blade 21 a its initial radius is r1 , after 1 revolution the radius is r2, and after two turns its radius is r3 where r1>r2>r3.
  • the spatial volume i.e. the volume available for the gas between the rotor and stator at a particular axial position
  • the air is being progressively reduced, so compressing the air.
  • the pressure produced is then a factor of the ratio between the inlet volume and speed to the outlet volume and speed. Where the outlet area is significantly smaller than the inlet area, the outlet pressure will be significantly higher. If insufficient pressure is produced, it would be possible to provide several stages, and certain preferred embodiments of the invention comprise several stages, each including a gas pump in accordance with the invention.
  • the helical blades or vanes 21 a, 21 b although reducing in diameter, have substantially constant thickness and constant pitch along the rotor. It is possible that the air or gas compressed by the pump shown in Fig 2 can leak out backwards between the rotating blades and the housing 3.
  • a deflecting plate 4 is fitted at the inlet end of the housing 3.
  • FIGs 3, 4 and 5 show alternative rotors which may be housed in a close-fitting cylindrical stator chamber, and which are each adapted to enhance gas compression.
  • the rotor of Fig 3 comprises two generally helical vanes, each of which has substantially uniform thickness and radial extent from the shaft. However, the pitch of each helix is arranged to progressively reduce towards the left hand end of the shaft in the figure. Thus the pitch between each vane is progressively altered along the axis, so again altering the spatial volume for the air as it is moved along the axis.
  • the pitch of each vane is substantially constant, but the vanes become progressively thicker in one direction along the axis. Again, this results in spatial volume being a function of axial position.
  • the extreme radial edges of the vanes are at sub- stantially constant radius r with respect to the axis A.
  • the rotor shaft includes generally cylindrical end portions 221 and a tapering, cone-like central portion 222, from which the vanes extend outwards.
  • the radial extent, pitch and thickness of the vanes is constant, the spatial volume available for gases as they move along the axis is reduced in the direction towards the left in the figure.
  • the diameter of the shaft is progressively altered along its length.
  • Figs 2 to 5 for increasing output pressure etc may be used in any combination in order to alter the pressure as the air is moved along towards the outlet by altering the spatial volume progressively along the axis.
  • Figs 6,7 and 8 show different views of a nebuliser embodying the invention.
  • This nebuliser is a pump which comprises a stator housing 3 which has a generally conical chamber 34 for receiving a tapered rotor 2.
  • the rotor rotates such that there is a clearance between the rotor vanes and the inner conical surface 33 of the housing 3.
  • the rotor 2 is driven by a mechanical drive 5 via a shaft 51 to draw air in to an inlet 31 of the housing, and expel air out of the outlet 32.
  • the housing and mechanical drive are mounted to a base 80.
  • a cover 81 incorporating air intake vents 82 encloses the me- chanical drive 5.
  • the drive shaft 51 is received within a bushing 83 which is itself supported on 3 radial struts 84 inside a circular aperture in the sidewall of the base 80.
  • the rotor 2 comprises two helical vanes 21 a, 21 b which are arranged so as to be 180° out of phase with each other. Each vane makes substantially two complete turns around the rotor axis. Each vane has reducing radius/diameter in the forward direction along the axis, so that the rotor defines a cone shape. A forward end of the shaft portion of the rotor 223 is pointed to enhance gas flow out of the outlet 32.
  • Fig 10 shows a view of the rotor along the rotational axis, from the front. The spiralling of each vane around the central axis can be clearly seen.
  • Figs 1 1 and 12 show a front view and a cross section respec- tively of a deflector plate suitable for use with embodiments of the invention.
  • This deflector plate is generally annular and comprises a forward facing channel 41 which is arranged to deflect back-flowing gas (escaping between the rotor and stator) forwards in the direction shown generally by the arrow in figure 12.
  • Fig 13 shows a further embodiment.
  • the rotor 2 is mounted in-line inside a gas pipe G.
  • the rotor is generally cylindrical and the walls of the gas pipe itself G form the stator housing 3.
  • the gas inlet and gas outlet are thus not precisely defined, but are shown generally by reference numerals 31 and 32 in the figure.
  • the rotor 2 comprises a plurality of helical vanes, each of which extends along the rotational axis A and forms four complete turns around the axis.
  • the rotor 2 thus forms an extended impeller.
  • the means for rotating the rotor 2 is not shown in the figure, but various configurations will be apparent to those skilled in the art.
  • gas pumps embodying the invention including nebulisers, air pumps, other gas pumps, air blowers, gas blowers, compressors, super chargers, turbo chargers, and spraying equipment. These are, of course, merely examples, and the present invention can be utilised in any application where movement and/or compression of a gas or gases is required.
  • the rotor may be rotated at any speed suitable for a particular application. It is envisaged that typical rotational speeds will be in the region of 2000 - 50 000 rpm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention se rapporte à une pompe à gaz, comprenant un rotor (2) disposé de manière à effectuer un mouvement de rotation autour d'un axe longitudinal (A), et un logement (3) disposé de manière à entourer le rotor (2) et comportant un orifice d'entrée de gaz et un orifice de sortie de gaz. Le rotor (2) possède au moins une aube hélicoïdale qui s'étend le long de l'axe et autour de ce dernier, afin de déplacer le gaz axialement de l'orifice d'entrée à l'orifice de sortie, lors de la rotation du rotor. Les modes de réalisation préférés de l'invention font appel à des rotors coniques (2) possédant au moins deux aubes hélicoïdales, ce qui permet d'améliorer la compression du gaz à l'intérieur du logement (3).
PCT/GB2002/005651 2002-01-03 2002-12-13 Pompe a gaz WO2003056186A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2002352379A AU2002352379A1 (en) 2002-01-03 2002-12-13 Gas pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0200058A GB0200058D0 (en) 2002-01-03 2002-01-03 Screw jet or compressor
GB0200058.6 2002-01-03

Publications (1)

Publication Number Publication Date
WO2003056186A1 true WO2003056186A1 (fr) 2003-07-10

Family

ID=9928566

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2002/005651 WO2003056186A1 (fr) 2002-01-03 2002-12-13 Pompe a gaz

Country Status (3)

Country Link
AU (1) AU2002352379A1 (fr)
GB (1) GB0200058D0 (fr)
WO (1) WO2003056186A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004055600A1 (de) * 2004-11-18 2006-05-24 Robert Wild Turbolüfter für vorzugsweise Computer u.a.
WO2011070589A3 (fr) * 2009-11-27 2011-08-11 Pravin Kashiramji Katare Compresseur à rotor unique en forme de cône
FR2984969A1 (fr) * 2011-12-26 2013-06-28 Eltrova Dispositif d'entrainement de fluide
US9090829B1 (en) 2014-09-03 2015-07-28 Strategy Licensing, Llc Apparatus for controlled blowing of asphalt
CN110219810A (zh) * 2019-07-23 2019-09-10 中国民用航空飞行学院 一种螺旋压缩机及组合压缩系统

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE249099C (fr) *
US1701103A (en) * 1927-02-14 1929-02-05 George C Egy Rotary pump
US2449531A (en) * 1942-06-02 1948-09-14 Lee Nixon Impeller
DE870499C (de) * 1951-06-24 1953-03-16 Adolf Roth Spiral-Rotor-Pumpe
US5209608A (en) * 1991-10-18 1993-05-11 Kevin Edwards Air grain conveyor system
DE19808311A1 (de) * 1998-02-27 1999-09-30 Armin Stelzig Einrichtung zur Aufladung von Verbrennungsmotoren mit einem Verdichtergebläse

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE249099C (fr) *
US1701103A (en) * 1927-02-14 1929-02-05 George C Egy Rotary pump
US2449531A (en) * 1942-06-02 1948-09-14 Lee Nixon Impeller
DE870499C (de) * 1951-06-24 1953-03-16 Adolf Roth Spiral-Rotor-Pumpe
US5209608A (en) * 1991-10-18 1993-05-11 Kevin Edwards Air grain conveyor system
DE19808311A1 (de) * 1998-02-27 1999-09-30 Armin Stelzig Einrichtung zur Aufladung von Verbrennungsmotoren mit einem Verdichtergebläse

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004055600A1 (de) * 2004-11-18 2006-05-24 Robert Wild Turbolüfter für vorzugsweise Computer u.a.
WO2011070589A3 (fr) * 2009-11-27 2011-08-11 Pravin Kashiramji Katare Compresseur à rotor unique en forme de cône
FR2984969A1 (fr) * 2011-12-26 2013-06-28 Eltrova Dispositif d'entrainement de fluide
WO2013098515A1 (fr) * 2011-12-26 2013-07-04 Eltrova Dispositif de propulsion de fluide
US9090829B1 (en) 2014-09-03 2015-07-28 Strategy Licensing, Llc Apparatus for controlled blowing of asphalt
CN110219810A (zh) * 2019-07-23 2019-09-10 中国民用航空飞行学院 一种螺旋压缩机及组合压缩系统

Also Published As

Publication number Publication date
AU2002352379A1 (en) 2003-07-15
GB0200058D0 (en) 2002-02-20

Similar Documents

Publication Publication Date Title
US5562405A (en) Multistage axial flow pumps and compressors
AU636292B2 (en) Rotary machine with non-positive displacement, for use as a pump, compressor, propulsion unit, generator or drive turbine
JP5249778B2 (ja) スクリューポンプ
US10240613B2 (en) Supersonic compressor with structural arrangement to increase pressure energy in a discharge process fluid received from a centrifugal impeller
EP0770781A1 (fr) Pompes à vide turbomoléculaires
US5810557A (en) Fan wheel for an inline centrifugal fan
US3444817A (en) Fluid pump
US20070248454A1 (en) Device for changing the pressure of a fluid
JP2009519405A5 (fr)
JP2003515037A5 (fr)
WO2003056186A1 (fr) Pompe a gaz
EA012818B1 (ru) Ротор лопастной машины и лопастная машина
TW200419074A (en) Vacuum pumping arrangement
US7090460B2 (en) Pump embodied as a side channel pump
KR101776883B1 (ko) 압력발생날개가 부가된 임펠러를 포함하는 원심펌프
JP2010236401A (ja) 遠心形流体機械
JPH0553955B2 (fr)
US20050175450A1 (en) Axial-flow pump
JPS61226596A (ja) タ−ボ分子ポンプ
KR100790305B1 (ko) 원심형 터보 임펠라 구동방식의 축류형 송풍장치
CN211599030U (zh) 无叶片超强高效高压风机
CN111237210B (zh) 一种分子泵
EP3036441A1 (fr) Diffuseur pour compresseur à écoulement tangentiel en flèche négative
JP3233364U (ja) 真空システム
CN217107517U (zh) 一种电磁驱动模式的压气机组

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ OM PH PL PT RO RU SD SE SG SK SL TJ TM TN TR TT TZ UA UG US UZ VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LU MC NL PT SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 69 (1) EPC (EPO FORM 1205A DATED 20/10/04)

122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP

WWW Wipo information: withdrawn in national office

Country of ref document: JP