EP0510009A1 - Machine a tiroir rotatif. - Google Patents

Machine a tiroir rotatif.

Info

Publication number
EP0510009A1
EP0510009A1 EP91900721A EP91900721A EP0510009A1 EP 0510009 A1 EP0510009 A1 EP 0510009A1 EP 91900721 A EP91900721 A EP 91900721A EP 91900721 A EP91900721 A EP 91900721A EP 0510009 A1 EP0510009 A1 EP 0510009A1
Authority
EP
European Patent Office
Prior art keywords
rotary
rotary vane
valve
circular cylinder
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP91900721A
Other languages
German (de)
English (en)
Other versions
EP0510009B1 (fr
Inventor
Georg Willi Eckhardt
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
Priority claimed from DE19904029345 external-priority patent/DE4029345C2/de
Application filed by Individual filed Critical Individual
Publication of EP0510009A1 publication Critical patent/EP0510009A1/fr
Application granted granted Critical
Publication of EP0510009B1 publication Critical patent/EP0510009B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the invention relates to a rotary valve machine on the geometric basis of the Pascal screw with one or more rotary valves per work area. It works as a rotary displacer based on the principle of the vane machine.
  • the circular cylinder 4 is rotatably mounted axially to the hollow cylinder 1 in the housing end plates with the bearings 15 and at the approach point 21 of the hollow cylinder inner surface except for a gap approximated.
  • the thickness of the housing end plate 2 can be reduced by installing a circular cylinder bearing 15 in the circular cylinder end wall 28.
  • the working space 12 with its crescent-shaped profile is delimited by the hollow cylinder 1, the housing end plates 2/3 and the circular cylinder 4.
  • the passage openings 7, consisting of the inlet opening 7e and the outlet opening 7a for the fluid, are located on the side of the approximation point 21 in the hollow cylinder 1.
  • the solid circular cylinder 4 is provided with one or more guide grooves 5 which extend longitudinally through the axis of rotation and in which plate-shaped rotary slides 6 of length 1 are guided.
  • the rotary slide valves 6 are at
  • the disadvantage mentioned can be avoided by mounting the rotary slide valve 6 on a control shaft 8 which leads through the hollow circular cylinder 4 and is rotatably mounted with the bearings 13 in the housing end plates 2/3. Construction examples are shown in the drawings 5-8.
  • the rotary valve 6 with the length 1 describe the base circle K with their centers P and can therefore with their bearings 14 seated in the bearing sleeves 61 on a control shaft 8 with the eccentricity r and the axis center M in the hollow circular cylinder 4 with the
  • the rotary slide valve 6 mounted on the control shaft 8 are guided in axial guide grooves 5 in the side wall of the circular cylinder 4 with an orientation to the axis of rotation of the circular cylinder and a point-symmetrical angular offset. They correspond functionally to each other by 180 ° offset pairs of wings 6f of a cell machine, which are connected here as a special constructional feature via a split bar or forked bars 6g with central bearing sleeves 61 supporting the rotary slide bearing 14 to form a rigid rotary slide.
  • the rotary slide valve is positively controlled with a contact-free run in the housing, because the rotary slide end points E with their rounded side edges 22 describe a path with the shape of the Pascal screw during the positive-controlled movement of the rotary slide valve and can therefore be carried out without contact along the inner surface of the hollow cylinder 1 same profile.
  • the ratio of the base circle diameter D to the rotary valve length 1 is an important variable. D and 1 are related to each other in the following relationship shown in drawing 3:
  • the desired high power density requires the selection of a factor f that is as small as possible, because the greatest displacement volume is achieved in this way.
  • the constructive design of the machine is technical
  • the circular cylinder 4 requires a certain wall thickness and the control shaft diameter must be matched to the circular cylinder cavity, which the control shaft 8 and the rotary valve 5 use as clearance.
  • control shaft As a crankshaft. Because the eccentricity is small in principle, the control shaft can also be built as an eccentric shaft with only a slight increase in f and thus has the following advantages:
  • Inner surface of the housing, and the control shaft can be designed for higher performance.
  • the usable eccentric surface for the rotary slide bearing 14 is larger. -The production as a split shaft is easier.
  • the individual eccentric segments 8s with the required angular offset are plugged onto a continuous central guide shaft 9, which is either fixed in the housing end plates 2/3 and is provided with rotating eccentric segments or is rotatably mounted with fixed eccentric segments in the housing end plates.
  • the central lubricant channel can, as shown in drawing 8, be designed as a straight central elongated hole 16. From it the radial bores 18 in the eccentrics go to the rotary slide bearings.
  • this construction requires the installation of at least two rotary slide valves per work area and, due to the torque acting on the control shaft, leads to additional bending stress in the rotary slide valves with an increased tendency to tilt in the guide groove 5.
  • the installation of more than one rotary valve per work area enables the balancing of the mass forces without counterweights if the rotary valves have a longitudinal and transverse axis symmetry and the bearing sleeves 61 with the webs 6g are arranged with a uniform overall width so that they do not overlap each other.
  • the interior of the circular cylinder can be sealed against the working space 12 using proven sealing elements.
  • the outer surface of the circular cylinder side wall can be sealed with radial sealing rings 20 against the housing end plates 2/3 and the guide groove 5 with straight spring-loaded sealing strips 19 against the rotary slide valve.
  • the lubrication expediently takes place via the central elongated hole 16 in the control shaft, through which the lubricant is guided via radial bores 18 in the eccentrics to the bearings 13, 14 and 15 and to the guide grooves 5.
  • the radial channels 26 in the end walls or the side wall of the circular cylinder discharge the lubricant pressed as a result of the centrifugal acceleration onto the inner surface of the circular cylinder side wall via the channels 27.
  • the inlet openings 26e of the radial channels 26, based on the axis of rotation of the circular cylinder, must not be more central than the inner surface of the circular cylinder side wall.
  • an internal gas cooling system can also be used in the rotary vane machine, as shown in drawing 8.
  • cooling gas is conducted into the circular cylinder cavity via the inlet opening 23 in the housing end plate 2 through the central opening 28e in the circular cylinder end wall 28 and is pressed into the outlet channel 25 of the opposite housing end plate 3 via the radial channels 24 in the opposite circular cylinder end wall as a result of the centrifugal acceleration.
  • the inlet openings 24e of the cooling gas channels 24, based on the axis of rotation of the circular cylinder 4, must be more central than the inlet openings 26e of the lubricant channels 26. Since both circuits are closed, the separation method described is sufficient.
  • the minimum vane stroke NE min depends on the number of rotary vane n per work area and results from the relationship:
  • V ⁇ lumenmaximum suckable rotary vane reduced.
  • the fluid would have to expand when passing through the volume maximum over the x-axis, with the consequence of a reduction in efficiency with gaseous fluids. Liquids could not be pumped with this arrangement of the inlet opening.
  • a reduction in the value (90 / n) would result in a symmetrical arrangement of the inlet and outlet opening that the input of the machine would not be separated from the outlet in every position by the rotary slide valve and no working pressure could be built up as a result.
  • the displacement volume would also be reduced in machines with internal compression.
  • the pulsation value is also a function of the number of rotary valves. According to the general relationship for the degree of non-uniformity
  • the minimum vane stroke NE min is a measure of the degree of non-uniformity of the rotary vane machine.
  • the pulsation also changes with the inner compression according to the relationship:
  • a max is the rotary valve angle position at the transition point Ea.
  • This function is the mathematical basis on which the proportions of the individual components can be coordinated and shifted to optimize performance.
  • f For a usable machine geometry of the Pascal screw, f must be ⁇ 1, because even in the simplest design of a rotary vane machine with only one rotary slide per working area, the circular cylinder diameter D K r ⁇ NE max ⁇ 1/2 must be.
  • the subject of this calculation method is the formulation of the above-mentioned function for machines with more than one rotary valve per work space in a notation, which can be used particularly advantageously as a design basis.
  • d 61 thickness of the rotary slide bearing sleeve 61
  • 1 is determined by the dimensions of the individual components. It is therefore a clear construction basis on which the individual dimensions can be coordinated and optimized.
  • the control shaft 8 can only be constructed as a crankshaft. With the value for D 8s > D and f> 2.5, the control shaft becomes an eccentric shaft. The choice of the eccentric diameter for the undivided control shaft depends on the desired bending and torsional strength. If, as already described, the control shaft is to be designed as a split eccentric shaft with a central guide shaft 9 and attached eccentrics 8s, the value for D 8s must be expanded by D 9 - D 16 .
  • the thickness d 61 of the rotary slide bearing sleeve 61 depends not only on the required strength, but also on the type of bearing selected.
  • the diameter of needle and ball bearings increases significantly compared to plain bearings and requires a higher value for d 61 .
  • the bearing sleeve 61 is here symmetrically divided into two halves in the rotary slide plane and provided on both sides of the dividing parts with a flange 6F1, which forms a groove with the flange of the other half.
  • the plate-shaped central web or a forked web 6g is inserted into this groove from the outside and fastened to the flange of each bearing sleeve half with a bolt or a fitting screw.
  • the value s indicates the minimum distance between the individual components.
  • the rotary valves are pushed out of the circular cylinder 4 to the maximum in the 0 ° position.
  • the bearing sleeve flange 6F1 approaches the shortest distance to the inner surface of the circular cylinder side wall.
  • the inner edge E 'of the rotary slide vane 6f approaches the bearing sleeve of the opposite rotary slide valve to its minimum distance.
  • this is somewhat larger with an odd number of rotary valves than with an even number of rotary valves. This results in a somewhat larger space for the bearing sleeves.
  • the height h 6F1 available for the bearing sleeve flange 6F1 and the maximum number of rotary valves n that can be used also depend on the value s.
  • h 6F1 a partial size for h 6F1 is derived . It is determined by the lateral minimum distance S'E 'of a rotary valve 6 from the inner edge E' of an adjacent rotary valve wing 6f and can be summarized in the following relationship, shown in drawing 12:
  • n the number of rotary valves
  • the conchoid of the circle can also be understood as a cardioid, a special form of epicycloid, with the center circle K 'rolling with its inside on the outside of the base circle K and the extension points E and E' Describe cardioids.
  • Circular cylinder radius r Kr extended and the extension of the points E 'is, as can be seen from the drawing 10, (r 8s + d 61 + s).
  • Drawing 9 shows an arc Kb with the radius passing through the points E'90 °, E'180 ° and E'270 °:
  • the individual parts of the bearing sleeve flange 6F1 describe corresponding cardioids with their rotation around the center M. If they lie within the circular arc with the radius r K b -s, they can undercut the inner edges E 'of the adjacent rotary slide vanes 6f. The degree of undercut increases with the height of the flange and the number of rotary valves.
  • the drawings 11-13 show the sequence of movements of a bearing sleeve flange with 2-7 rotary valves per work area.
  • the shape of the flange is chosen with a constant size so that it is also suitable for the highest number of rotary valves. In each case in the 90o position, the boundary lines of the maximum available installation space are projected onto the profile of the flange. It decreases significantly with increasing number of rotary valves n.
  • Drawing 11 also shows that the space with only two rotary valves per work space has no share with undercut. This can only happen if ß ⁇ 90o and this only occurs when n> 2.
  • V n / ⁇ rKr 2 / 4n - F Ds ) .4.nh
  • Pulsation or degree of non-uniformity ⁇ according to the general relationship for
  • a max is the rotary valve angle position at the transition point Ea.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Holding Or Fastening Of Disk On Rotational Shaft (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Crushing And Grinding (AREA)

Abstract

L'invention a pour objet une machine à tiroir rotatif basée sur le principe géométrique du limaçon avec l'équation de coordonnées cartésiennes: (x2 + y2 -Dx)2 = 12/4.(x2 + y2) et l'équation de coordonnées polaires E = D.cosa + 1/2. La constante (1) est représentée sous forme de fonction des constantes (D) dans la relation 1 = 2D.f + 2D. Le facteur de proportionnalité (f) est représenté par les dimensions des composants individuels de la machine dans la relation f = (2D + r8s + d6l + s + e) /D.
EP91900721A 1990-01-12 1990-12-18 Machine a tiroir rotatif Expired - Lifetime EP0510009B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4000762 1990-01-12
DE4000762 1990-01-12
DE19904029345 DE4029345C2 (de) 1990-09-15 1990-09-15 Drehschiebermaschine
DE4029345 1990-09-15
PCT/DE1990/000971 WO1991010812A1 (fr) 1990-01-12 1990-12-18 Machine a tiroir rotatif

Publications (2)

Publication Number Publication Date
EP0510009A1 true EP0510009A1 (fr) 1992-10-28
EP0510009B1 EP0510009B1 (fr) 1994-06-15

Family

ID=25889006

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91900721A Expired - Lifetime EP0510009B1 (fr) 1990-01-12 1990-12-18 Machine a tiroir rotatif

Country Status (6)

Country Link
US (1) US5316456A (fr)
EP (1) EP0510009B1 (fr)
AT (1) ATE107396T1 (fr)
DE (1) DE59006162D1 (fr)
ES (1) ES2057851T3 (fr)
WO (1) WO1991010812A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2287062C2 (ru) * 2004-12-20 2006-11-10 Руслан Казбекович Темираев Роторно-пластинчатое устройство
CZ301708B6 (cs) * 2005-03-29 2010-06-02 Frolík@Jirí Rotacní stroj s obežnými dvojkrídly zejména pro expanzní pohonné jednotky a kompresory
WO2007064866A2 (fr) * 2005-12-01 2007-06-07 Gray David D Appareil de combustion rotatif
US20110262291A1 (en) * 2008-04-28 2011-10-27 Randell Technologies Inc. Rotor Assembly for Rotary Compressor
US20110293457A1 (en) * 2010-05-28 2011-12-01 Atlas Copco Tools Ab Pneumatic vane motor
WO2012118456A1 (fr) * 2011-03-03 2012-09-07 Macsik Juraj Machine tournante à palettes comportant une chambre de travail de forme non cylindrique

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD46761A (fr) *
GB264819A (en) * 1926-01-20 1927-06-16 Pont A Mousson Fond Improvements relating to rotary compressors
US1994245A (en) * 1931-09-03 1935-03-12 Jr John O Gette Compressor and supercharger
US2071258A (en) * 1934-02-27 1937-02-16 Jr James Haydock Rotary blower and the like
FR826534A (fr) * 1936-12-15 1938-04-01 Appareil rotatif utilisable comme moteur, pompe ou compresseur
CH209718A (de) * 1938-04-21 1940-04-30 Cambron Gustave Maschine mit exzentrisch in einem Stator umlaufendem Rotor.
DE2235045A1 (de) * 1972-07-17 1974-01-31 Siemens Ag Drehschieberpumpe mit einem kreisrunden rotor
US3877851A (en) * 1973-02-16 1975-04-15 Sanpei Komiya Rotary compressor with integrally connected, diametrically aligned vanes
AU8101575A (en) * 1974-05-17 1976-11-11 Reynaud D A L M Vane type pump
US4385873A (en) * 1980-10-07 1983-05-31 Richter Hans H Rotary vane type pump or motor and the like with circular chamber portions
US4449899A (en) * 1982-04-29 1984-05-22 Ecton Corp. Rotary vane machine
JPS61268894A (ja) * 1985-05-22 1986-11-28 Diesel Kiki Co Ltd ベ−ン型圧縮機
EP0264778B1 (fr) * 1986-10-18 1991-01-02 B a r m a g AG Pompe à palettes

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9110812A1 *

Also Published As

Publication number Publication date
WO1991010812A1 (fr) 1991-07-25
EP0510009B1 (fr) 1994-06-15
US5316456A (en) 1994-05-31
ES2057851T3 (es) 1994-10-16
DE59006162D1 (de) 1994-07-21
ATE107396T1 (de) 1994-07-15

Similar Documents

Publication Publication Date Title
DE4241320C2 (de) Drehkolbenmaschine
DE2450418A1 (de) Drehkolbenmaschine
DE3220556A1 (de) Kompressor
DE3432915A1 (de) Innenachsige drehkolbenmaschine
EP0295480A2 (fr) Machine à déplacement positif
EP0367046B1 (fr) Machine hydrostatique à piston rotatif
EP0371305A1 (fr) Arbre excentré à contrepoids
DE2059158C3 (de) Hydraulischer Motor in Flügelzellenbauart
EP0899423B1 (fr) Machine de déplacement de fluide du type à spirale
EP0510009A1 (fr) Machine a tiroir rotatif.
DE19738132C2 (de) Mehrachsige Rotationskörper-Verdrängungsmaschine
EP1616079B1 (fr) Machine a piston rotatif
DE2603893A1 (de) Maschine mit gleichachsigen drehkolben
DE69931181T2 (de) Rotationspumpe
EP1005604A1 (fr) Machine a piston rotatif
DE19616880A1 (de) Verfahren und Vorrichtung zur Förderung eines Mediums
DE3913989A1 (de) Fluegelpumpe
DE2619474A1 (de) Leistungsgenerator
DE4029345C2 (de) Drehschiebermaschine
DE3614626C2 (fr)
DE2857227A1 (de) Fluessigkeitsringpumpe
DE1129962B (de) Drehkolbenmaschine mit Haupt- und Nebendrehkolben
DE3042493A1 (de) Maschine mit veraenderlichem volumen
DE102021133555A1 (de) Gerotor-Einheit und Pumpe bzw. Motor mit einer Gerotor-Einheit
DE4337427A1 (de) Statorgeometrie einer Rotations-Kolbenmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19920706

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT CH DE ES FR GB IT LI NL SE

17Q First examination report despatched

Effective date: 19930915

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT CH DE ES FR GB IT LI NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19940615

REF Corresponds to:

Ref document number: 107396

Country of ref document: AT

Date of ref document: 19940715

Kind code of ref document: T

REF Corresponds to:

Ref document number: 59006162

Country of ref document: DE

Date of ref document: 19940721

ITF It: translation for a ep patent filed

Owner name: STUDIO TORTA SOCIETA' SEMPLICE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19940915

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2057851

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19941021

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20011126

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20011221

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20011227

Year of fee payment: 12

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20020129

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20020311

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20021209

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021218

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021218

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021231

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021231

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20021218

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030901

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040701

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20021219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051218