EP0392975B1 - Rotierender Spirallader für kompressible Medien - Google Patents

Rotierender Spirallader für kompressible Medien Download PDF

Info

Publication number
EP0392975B1
EP0392975B1 EP19900810243 EP90810243A EP0392975B1 EP 0392975 B1 EP0392975 B1 EP 0392975B1 EP 19900810243 EP19900810243 EP 19900810243 EP 90810243 A EP90810243 A EP 90810243A EP 0392975 B1 EP0392975 B1 EP 0392975B1
Authority
EP
European Patent Office
Prior art keywords
displacement
scroll compressor
ribs
reinforcement
compressor 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.)
Expired - Lifetime
Application number
EP19900810243
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0392975A1 (de
Inventor
Heinrich Güttinger
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.)
Aginfor AG
Original Assignee
Aginfor AG fuer industrielle Forschung
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 Aginfor AG fuer industrielle Forschung filed Critical Aginfor AG fuer industrielle Forschung
Publication of EP0392975A1 publication Critical patent/EP0392975A1/de
Application granted granted Critical
Publication of EP0392975B1 publication Critical patent/EP0392975B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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
    • F01C21/08—Rotary pistons
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps

Definitions

  • the invention relates to a rotating spiral loader for compressible media according to the preamble of patent claim 1.
  • Such a spiral charger with rotating displacement disks is characterized by an almost pulsation-free conveyance of the gaseous working medium, for example consisting of air or an air / fuel mixture, and can therefore be used with advantage for charging purposes of internal combustion engines.
  • the gaseous working medium for example consisting of air or an air / fuel mixture
  • several, approximately sickle-shaped work spaces are enclosed along the conveying space between the spirally shaped ribs. These move from an inlet to an outlet, their volume constantly decreasing and the pressure of the working fluid being increased accordingly.
  • a spiral machine of the type mentioned at the outset is known from CH-A-501 838.
  • the variant shown in FIGS. 8 and 9 is a two-speed, single-stage machine in which the two movable displacement disks are loosely mounted on fixed eccentric axes are arranged.
  • One of the Axes are hollow to allow the work equipment to be conveyed out of the machine.
  • the displacement disks are provided with toothed rings on their circumference, in which a common gearwheel arranged on a drive shaft engages.
  • the ribs are therefore generally formed by spiral strips, which are held essentially vertically on the displacement disks and have a relatively large axial length in relation to their thickness.
  • the vertical end edges of these strips are at least in the area of the fiber furthest away from the displacement disk, i.e. Relatively unstable in the head area, so that they could tarnish on the foot parts of the cooperating last during operation. In the foot area of these ledge end edges there are also considerable stresses that could even lead to breakage under certain circumstances.
  • the invention has for its object to provide a spiral charger of the type mentioned, in which centrifugal deformations of the ribs are largely avoided.
  • the advantage of the invention is to be seen in particular in the fact that those spiral parts through which the working medium flows only have to be made with the smallest possible wall thickness.
  • Thickenings at the spiral ends are already known from FR-A-2 232 674, which shows an orbiting machine. But not to be misunderstood is the fact that both the orbiting spiral and the fixed spiral are provided with thickenings at their respective ends. Since the fixed spiral ends are also thickened, these thickenings are not reinforcements. If one also looks at FIG. 17 belonging to FIG. 22 of FR-A-2 232 674 and lets the spiral orbit "mentally", one finds the cause of the thickening. This is because they form those end faces that are absolutely necessary so that an axial seal can be made against the respective cooperating part during operation. With regard to the thickening on the fixed spiral, FIG. 21 in FR-A-2 232 674 and the associated description explains an additional function. The thickening is used to supply lubricating oil, which is fed to the front end of the spiral ribs.
  • 1 denotes the housing composed of two halves.
  • the two halves are connected to one another via fastening eyes, not shown, for receiving screw connections.
  • Axle stub 2 or 2 are in the housing halves on both sides. 3 arranged, which protrude into the interior of the housing.
  • the longitudinal axes 4 respectively. 5 of the 2 stub axles are offset from each other by the eccentricity e.
  • the rotatable displacement disks 6 and 7 are placed loosely on this axle stub.
  • the hub 9 of the right displacement disk 7 is mounted on the axle stub 3 by means of two ball bearings 11 and is axially secured.
  • the left displacement disk 6 is designed to be axially displaceable.
  • the displacement discs 6 and 7 are constructed symmetrically. They essentially consist of a flat plate 13, which run parallel to one another in the assembled state, and of ribs 14, which are held vertically on the respective plate 13. These ribs 14 are spiral (Fig. 2), i.e. they can either be classic spirals or they can be composed of several circular arcs connected to each other.
  • the ribs 14 have an arc length of one and a half turns, which the machine enters the name "one stage".
  • Each plate 13 is equipped with two such ribs 14, the ribs being offset from one another by 180 °. This leads to the designation "two-course”.
  • four parallel working spaces 15 are formed, which represent the actual conveying space.
  • these workrooms open at a 1/4 turn against the outlet 16.
  • At the outer diameter open the spirals against the inlet 17, from which they draw in fresh air.
  • a pressure chamber 26 is therefore formed between the axially displaceable displacement disk 6 and the housing wall, which is acted upon by the pressure of the working medium in the outlet 16.
  • the hollow stub shaft 2 is connected to the pressure chamber 26 via a removal tube 27.
  • the pressure in the chamber acts on an annular disc 28 which is attached to the housing 1 by means of bellows 29 in an airtight manner using suitable means.
  • the annular disk 28 slides with its hub 30 on the stub axle 2. In doing so, it displaces the inner cage of the axial bearing 12 the plates opposite each other.
  • those parts of the ribs which are subjected to the highest stresses in terms of centrifugal force, but on the other hand are not used to form conveying spaces, are provided with a reinforcement 32.
  • these reinforcements are actual thickenings of the entry parts. They can be produced in a simple manner if the displacement disks with the ribs are cast or sintered together from metal. Even in the event that the conveying spaces 15 are milled, these reinforcements do not require any rework, since they are located outside the flow-through channels on the outside of the fin ends. The reinforcements extend over the entire axial length of the ribs.
  • the respective reinforcement begins at the outermost periphery of the rib, i.e. at their leading edge. It extends to the area of the leading edge of the neighboring rib.
  • the reinforcement is flush with the outer edge of the displacement disc at the foot area, that is to say the point at which the rib is connected to the displacement disc. This means - after the displacement disks are circular, but the ribs are designed with a decreasing radius - that the reinforcement becomes increasingly thicker in the circumferential direction from the rib end.
  • the reinforcement runs obliquely from the outer edge of the displacement disk to the outer wall of the rib.
  • This slope is advantageously chosen from a fluidic point of view, care being taken that the free and unimpeded suction of the working medium in the conveying space formed by the two ribs is not impaired.
  • the equipped displacement unit 6, 7 consists of an aluminum alloy or magnesium
  • the free surface of the reinforcement 32 facing the interior of the housing can be provided with a hardening treatment in order to further increase the dimensional stability.
  • Anodization, anodizing or the application of an enamel layer may be mentioned as an example.
  • the reinforcement can also terminate radially in the circumferential direction if it does not extend into the area of the next rib. This can be the case for example with catchy spirals, the entrances of which are offset by 180 °. A reinforcement over such a large angular range is certainly not necessary, since with such a spiral the affected rib areas are so far inward due to the increasing curvature that the centrifugal forces have less effect.
  • a reinforcement 32 'in the sandwich design is shown in FIGS. It can be used, for example, if the rotating elements are produced in a casting or injection process.
  • a cover ring 34 which tapers conically from the outer edge of the displacement disk 6.7 to the head end of the rib 14, can be connected to the rib and, if necessary, the displacement disk via a plurality of webs 37.
  • the cavity between the rib, The displacement disk and cover ring are then preferably filled with an intermediate body 36, for example foam.
  • the displacement disks are also reinforced on their rear side facing the housing.
  • these webs 33 can, according to FIG. 3, be equipped with a cover plate 35 on their side facing away from the displacement disk.
  • the displacer disks are rotated via a drive shaft 18, which is mounted outside of the displacer disks by means of ball bearings 19 in the housing 1.
  • a drive shaft 18 which is mounted outside of the displacer disks by means of ball bearings 19 in the housing 1.
  • pulleys 20 which drive the pulleys 22 and 23 via toothed belts 21, which in turn with the hubs 8 and. 9 of the displacement disks are connected in a rotationally fixed manner.
  • the spirals open against the inlet 17, from which they draw in fresh air.
  • the crescent-shaped working spaces 15 result, which are displaced through the spirals from the inlet 17 towards the outlet 16.
  • the work equipment conveyed in this way is then led out of the loader through the hollow stub shaft 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Supercharger (AREA)
EP19900810243 1989-04-08 1990-03-27 Rotierender Spirallader für kompressible Medien Expired - Lifetime EP0392975B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1294/89A CH678969A5 (enrdf_load_stackoverflow) 1989-04-08 1989-04-08
CH1294/89 1989-04-08

Publications (2)

Publication Number Publication Date
EP0392975A1 EP0392975A1 (de) 1990-10-17
EP0392975B1 true EP0392975B1 (de) 1993-07-21

Family

ID=4207068

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900810243 Expired - Lifetime EP0392975B1 (de) 1989-04-08 1990-03-27 Rotierender Spirallader für kompressible Medien

Country Status (5)

Country Link
US (1) US5082430A (enrdf_load_stackoverflow)
EP (1) EP0392975B1 (enrdf_load_stackoverflow)
JP (1) JP2823650B2 (enrdf_load_stackoverflow)
CH (1) CH678969A5 (enrdf_load_stackoverflow)
DE (1) DE59002000D1 (enrdf_load_stackoverflow)

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4207984A1 (de) * 1992-03-13 1993-09-16 Asea Brown Boveri Verdraengermaschine nach dem spiralprinzip
US5466134A (en) * 1994-04-05 1995-11-14 Puritan Bennett Corporation Scroll compressor having idler cranks and strengthening and heat dissipating ribs
US6017204A (en) * 1995-07-31 2000-01-25 Knorr-Bremse Systeme Fur Schienenfahrzeuge Gmbh Spiral compressor, useful in particular to generate compressed air for rail vehicles
US5944500A (en) * 1996-06-20 1999-08-31 Sanden Corporation Scroll-type fluid displacement apparatus having a strengthened inner terminal end portion of the spiral element
JPH10205468A (ja) * 1997-01-22 1998-08-04 Sanden Corp スクロール型コンプレッサ
US6106247A (en) * 1998-03-18 2000-08-22 Haldex Brake Corporation Scroll-type fluid displacement apparatus including an eccentric crank mechanism having an elongated shaft
US6439864B1 (en) 1999-01-11 2002-08-27 Air Squared, Inc. Two stage scroll vacuum pump with improved pressure ratio and performance
US6511308B2 (en) 1998-09-28 2003-01-28 Air Squared, Inc. Scroll vacuum pump with improved performance
US10683865B2 (en) * 2006-02-14 2020-06-16 Air Squared, Inc. Scroll type device incorporating spinning or co-rotating scrolls
JP5280315B2 (ja) * 2009-08-18 2013-09-04 本田技研工業株式会社 内燃機関の過給機潤滑構造
US11047389B2 (en) 2010-04-16 2021-06-29 Air Squared, Inc. Multi-stage scroll vacuum pumps and related scroll devices
US20130232975A1 (en) 2011-08-09 2013-09-12 Robert W. Saffer Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle
JP6161407B2 (ja) * 2013-05-28 2017-07-12 有限会社スクロール技研 スクロール流体機械
US10508543B2 (en) 2015-05-07 2019-12-17 Air Squared, Inc. Scroll device having a pressure plate
JP6636304B2 (ja) * 2015-11-10 2020-01-29 三菱重工業株式会社 スクロール圧縮機
US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
WO2018110147A1 (ja) * 2016-12-12 2018-06-21 三菱重工業株式会社 両回転スクロール圧縮機
US11454241B2 (en) 2018-05-04 2022-09-27 Air Squared, Inc. Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump
US20200025199A1 (en) 2018-07-17 2020-01-23 Air Squared, Inc. Dual drive co-rotating spinning scroll compressor or expander
US11067080B2 (en) 2018-07-17 2021-07-20 Air Squared, Inc. Low cost scroll compressor or vacuum pump
US11530703B2 (en) 2018-07-18 2022-12-20 Air Squared, Inc. Orbiting scroll device lubrication
US11473572B2 (en) 2019-06-25 2022-10-18 Air Squared, Inc. Aftercooler for cooling compressed working fluid
US11898557B2 (en) 2020-11-30 2024-02-13 Air Squared, Inc. Liquid cooling of a scroll type compressor with liquid supply through the crankshaft
US11885328B2 (en) 2021-07-19 2024-01-30 Air Squared, Inc. Scroll device with an integrated cooling loop
CN114893398B (zh) * 2022-05-20 2023-08-15 重庆超力高科技股份有限公司 涡旋压缩机和克服倾覆力矩方法

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR48616E (fr) * 1936-12-23 1938-04-19 Perfectionnements au capsulisme à excentrique
US2324168A (en) * 1940-01-26 1943-07-13 Montelius Carl Oscar Josef Rotary compressor or motor
DE1935621A1 (de) * 1968-07-22 1970-01-29 Leybold Heraeus Gmbh & Co Kg Verdraengerpumpe
US3924977A (en) * 1973-06-11 1975-12-09 Little Inc A Positive fluid displacement apparatus
JPS589278B2 (ja) * 1979-02-17 1983-02-19 サンデン株式会社 容積式流体圧縮装置
JPS5799202A (en) * 1980-12-10 1982-06-19 Hitachi Ltd Scroll fluid machine
JPS57195801A (en) * 1981-05-27 1982-12-01 Sanden Corp Fluidic device of volute type
US4472120A (en) * 1982-07-15 1984-09-18 Arthur D. Little, Inc. Scroll type fluid displacement apparatus
DE3402548A1 (de) * 1984-01-26 1985-08-01 Leybold-Heraeus GmbH, 5000 Köln Verdraengermaschine
CH672351A5 (enrdf_load_stackoverflow) * 1986-12-24 1989-11-15 Bbc Brown Boveri & Cie
JPS63189680A (ja) * 1987-01-24 1988-08-05 フオルクスウアーゲン・アクチエンゲゼルシヤフト 圧縮媒体用容積形機械

Also Published As

Publication number Publication date
CH678969A5 (enrdf_load_stackoverflow) 1991-11-29
JPH0367082A (ja) 1991-03-22
DE59002000D1 (de) 1993-08-26
EP0392975A1 (de) 1990-10-17
US5082430A (en) 1992-01-21
JP2823650B2 (ja) 1998-11-11

Similar Documents

Publication Publication Date Title
EP0392975B1 (de) Rotierender Spirallader für kompressible Medien
EP0167846B1 (de) Innenachsige Drehkolbenmaschine
DE3442621A1 (de) Spiralfluidverdraengervorrichtung
DE3312280C2 (enrdf_load_stackoverflow)
DE69709199T2 (de) Innenzahnradmotor
DE3400594A1 (de) Stroemungsmaschine
EP0899423B1 (de) Spiralverdrängermaschine für kompressible Medien
DE2246901A1 (de) Von fluid durchstroemte fluegelzellenmaschine
EP1934479A1 (de) Flügelzellenpumpe
DE19622833A1 (de) Schneckenkompressor mit einer verstärkten Dreh-Verhinderungseinrichtung
EP0337950B1 (de) Innenachsige Rotationskolbenmaschine
DE1653921C3 (de) Rotationskolbenpumpe
DE2158518B2 (de) Horizontale mehrstufige Zentrifugalpumpe
EP3827170B1 (de) Fluidfördereinrichtung
EP0137421B1 (de) Aussenachsige Rotationskolbenmaschine
EP1828609A1 (de) Flügelzellenpumpe
DE20210003U1 (de) Flüssigkeitsringpumpe
DE4403649C2 (de) Lagerung und Antrieb der Rotoren eines Schraubenverdichters
EP0381682B1 (de) Drehkolbenverdichter
DE69501214T2 (de) Spiralverdichter und Verfahren zur Fertigung einer stationären Spirale des Spiralverdichters.
DE2541861C2 (de) Rotationskolbenmaschine mit Schraubenrotor
DE9207087U1 (de) Rotationskolbenmaschine
DE3727281A1 (de) Rotationskolbenkompressor
DE19537674C1 (de) Drehkolbenmaschine
EP0088288A1 (de) Innenachsige Rotationskolbenmaschine

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

AK Designated contracting states

Kind code of ref document: A1

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

17P Request for examination filed

Effective date: 19901130

17Q First examination report despatched

Effective date: 19920319

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

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

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59002000

Country of ref document: DE

Date of ref document: 19930826

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19930927

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
EAL Se: european patent in force in sweden

Ref document number: 90810243.7

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

Ref country code: GB

Payment date: 20010214

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: 20010219

Year of fee payment: 12

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

Ref country code: SE

Payment date: 20010305

Year of fee payment: 12

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

Ref country code: FR

Payment date: 20010313

Year of fee payment: 12

Ref country code: DE

Payment date: 20010313

Year of fee payment: 12

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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: 20020327

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

Ref country code: SE

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

Effective date: 20020328

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: 20020331

Ref country code: CH

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

Effective date: 20020331

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: 20021001

EUG Se: european patent has lapsed

Ref document number: 90810243.7

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20020327

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: 20021129

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: 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: 20050327