EP0237868B1 - Radial- oder Axialkreiselpumpe - Google Patents

Radial- oder Axialkreiselpumpe Download PDF

Info

Publication number
EP0237868B1
EP0237868B1 EP87103057A EP87103057A EP0237868B1 EP 0237868 B1 EP0237868 B1 EP 0237868B1 EP 87103057 A EP87103057 A EP 87103057A EP 87103057 A EP87103057 A EP 87103057A EP 0237868 B1 EP0237868 B1 EP 0237868B1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump
auxiliary
pressure
centrifugal pump
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
EP87103057A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0237868A2 (de
EP0237868A3 (en
Inventor
Ernst Hauenstein
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 AT87103057T priority Critical patent/ATE60411T1/de
Publication of EP0237868A2 publication Critical patent/EP0237868A2/de
Publication of EP0237868A3 publication Critical patent/EP0237868A3/de
Application granted granted Critical
Publication of EP0237868B1 publication Critical patent/EP0237868B1/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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/404—Transmission of power through magnetic drive coupling
    • F05B2260/4041—Transmission of power through magnetic drive coupling the driven magnets encircling the driver magnets

Definitions

  • the present invention relates to a centrifugal centrifugal pump, the working side of which is completely sealed off by a canned pot, in which pump the pump impeller mounted on a shaft is driven by a magnetic coupling acting through the wall of the canned pot and acting on the impeller during operation, caused by axial thrust forces Different pressure ratios on the impeller front and impeller rear, whereby to compensate for these thrust forces the auxiliary pump impeller, which is provided directly on the front of the pump channels, is assigned to the rear of the auxiliary impeller, which is used to reduce pressure in the room or the rooms on the impeller rear with control slots the pressure chamber boundary edge interacts.
  • Centrifugal pumps of this type are generally known. Their field of application is very wide, but due to the lack of seals, it is mainly in the chemical field, where particularly toxic or otherwise aggressive liquids have to be pumped.
  • centrifugal pumps in the form of so-called canned motor pumps or magnetic coupling pumps was the collection and balancing of the hydraulic forces inside the pump, in particular the thrust forces acting on the pump wheel.
  • the previously known solutions were unsatisfactory in the sense that complex constructions were required, which were also associated with relatively high energy losses (friction losses, efficiency reductions). This is all the more regrettable, since today's materials have made it possible to build the actual drive system more compactly and thus to keep the external dimensions small.
  • EP-A-O 163 126 shows a canned pump with an auxiliary rotor on the rear, which serves to reduce the axial forces acting on the bearings, but without changing the effective cross section of the control slots.
  • the purpose of the present invention was to find a structurally simple solution for the compensation of the axial thrust acting on the impeller in radial or axial centrifugal pumps of the type described at the outset, which further simplifies the actual pump construction and helps to reduce the internal forces that occurred earlier that in particular the canned tube can be made with a further reduced wall thickness, which in turn can improve the overall efficiency.
  • the solution to this problem is characterized according to the invention in that the actual pump impeller, on its front side, i.e. on the side facing the suction, the delivery channels are provided, an auxiliary delivery wheel is assigned, which serves to reduce the pressure in the room or the rooms on the rear of the impeller.
  • the spaces on the rear of the impeller usually consist of a so-called hub space and an inner and outer drive space.
  • the latter two spaces are separated from one another by the flange of the carrier of the one magnetic coupling part, which flange-like protrudes from the rear of the impeller.
  • control means preferably in the form of control slots or channels, are preferably provided on the pump housing, specifically in relation to the periphery of the delivery channels of the auxiliary delivery wheel, so that the medium delivered by the auxiliary delivery wheel from the space behind the impeller as a function of the to promote the pressure conditions prevailing on the front or rear of the impeller into the pressure chamber of the pump.
  • the auxiliary conveyor wheel is preferably arranged or formed on the rear side of the actual pump impeller, for example directly on the rear wall of the pump impeller.
  • the conveying channels of the auxiliary conveying wheel are preferably designed such that they communicate with one or more of the spaces on the rear of the impeller. For example, a number of separate conveying channels of the auxiliary conveying wheel can be assigned to each of the spaces to be relieved. Depending on the magnitude of the thrust forces that arise in each case, the output of the delivery channels of the auxiliary feed wheel is more or less covered by the control means, caused by an oscillating axial displacement of the pump impeller, which ensures permanent automatic thrust compensation.
  • thrust compensation enables impellers with open or closed blading to be used as desired.
  • the bearing journal or the support shaft for the impeller can e.g. be integrated into the end face of the containment shell, or, in the case of larger embodiments, be supported in a suitable manner in the intake manifold.
  • Pumps of any desired design can be built without complex control channels.
  • the rooms on the rear of the impeller can also be rinsed with cleaning fluid with little effort.
  • only a supply line for cleaning fluid into the rear hub space is required, from which certain delivery channels of the auxiliary feed wheel lead the rinsing fluid into the outer drive space.
  • the flushing liquid could also be supplied directly to the outer drive compartment.
  • the construction according to the invention is particularly suitable for pumps in which the driven part is designed as an external rotor, since on the one hand modern materials allow the construction of rotors with a low mass and on the other hand practically no friction losses occur. Nevertheless, the inevitable gaps can be made very narrow, since the risk of clogging is greatly reduced in the construction according to the invention.
  • Fig. 1 of the drawing shows purely schematically a radial centrifugal pump with magnetic coupling in section, with a variant of the upper half of the picture both with respect to the canned pot and the impeller being shown in the lower half of the figure.
  • the variants have no influence on the basic structure of the pump.
  • the pump essentially consists of a housing 1 with an intake port 2, a bearing journal 3 arranged in the example shown in the intake port 2 (which in the lower variant is also formed in one piece with the canned pot bottom) for a pump impeller 4 and a completely sealed working side (pump side) from the drive side (motor side) separating canned pot 5. Also shown is the internal magnet rotor 6 of a drive motor, not shown, the housing of which is flanged to the pump housing 1.
  • the bearing journal 3 for the pump impeller 4 is seated in a hub cover 3 ', which is supported and fastened in the intake flange 2 via supports 7, 8.
  • the medium to be delivered reaches the pressure chamber 8 via the suction nozzle 2 and the pump impeller 4 (in the example shown a closed impeller) and from there into the pressure line (not shown).
  • the impeller 4 with closed blading 4 ' is overhung on the bearing journal 3, it being able to move freely between the stops 9 and 10 under the axial thrust forces which occur. As will be shown, the impeller does not come to rest against the stops 9, 10, which essentially serve to position the wheel.
  • This ring flange 12 divides the pump-side drive space 13, which is located on the rear side of the impeller 4, into an outer and an inner space A or B. Also on the impeller rear side is a so-called hub space C.
  • the pressure acting on the impeller from spaces A, B and C is greater than the pressure on the suction or front side of the impeller 4, so that the impeller would be pressed in the suction direction without special precautions. However, this should be avoided.
  • auxiliary conveying wheel 4 ′′ which usually consists of one piece with the actual pump impeller 4, and the axial movement of the impeller 4 in the direction of the suction is thereby stopped. ie a shift in the direction of the drive side, the delivery rate of the auxiliary conveyor wheel 4 "is controlled:
  • one or more bores 17 are preferably provided between the pressure space 8 of the pump and the drive space A.
  • the auxiliary feed wheel 4 can be designed such that inlet openings 18, 19 and 20 to the individual feed channels 16 of the auxiliary feed wheel 4" are provided from the different rooms A, B and C, respectively, with a different design that for each room A , B and C a number of separate delivery channels (eg 21 for room C in the lower variant) can be provided.
  • a mixed construction is also conceivable.
  • the hub space C has its own delivery channels 21, e.g. a rinsing liquid via a line 22 and a bore 23 in the journal 3 in the room C to be conveyed from there via the delivery channels 21 of the auxiliary feed wheel 4 "not into the pressure chamber 8 of the pump, but into the room A (and from here in the Room B) can thus be easily cleaned, but a flushing or cleaning liquid could also be introduced directly into room A, for example via an inlet 24.
  • a flushing or cleaning liquid could also be introduced directly into room A, for example via an inlet 24.
  • FIG. 2 and 3 show purely schematically how the control of the delivery rate of the auxiliary conveyor wheel 4 "takes place via control slots on the housing, relative to the delivery channels of the auxiliary delivery wheel.
  • the delivery channels are covered and the pressure in space A will increase, while Fig 3 shows the situation with delivery channels open via the control slots, in which the pressure in space A drops.
  • Fig. 4 finally shows a purely schematic plan view of the rear of the impeller, i.e. on the auxiliary feed wheel, with different inlet openings in the feed channels.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Cyclones (AREA)
  • Non-Positive Displacement Air Blowers (AREA)
EP87103057A 1986-03-21 1987-03-04 Radial- oder Axialkreiselpumpe Expired - Lifetime EP0237868B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87103057T ATE60411T1 (de) 1986-03-21 1987-03-04 Radial- oder axialkreiselpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1160/86 1986-03-21
CH1160/86A CH672820A5 (enrdf_load_stackoverflow) 1986-03-21 1986-03-21

Publications (3)

Publication Number Publication Date
EP0237868A2 EP0237868A2 (de) 1987-09-23
EP0237868A3 EP0237868A3 (en) 1988-01-20
EP0237868B1 true EP0237868B1 (de) 1991-01-23

Family

ID=4203879

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87103057A Expired - Lifetime EP0237868B1 (de) 1986-03-21 1987-03-04 Radial- oder Axialkreiselpumpe

Country Status (7)

Country Link
US (1) US4793777A (enrdf_load_stackoverflow)
EP (1) EP0237868B1 (enrdf_load_stackoverflow)
JP (1) JP2535004B2 (enrdf_load_stackoverflow)
AT (1) ATE60411T1 (enrdf_load_stackoverflow)
CH (1) CH672820A5 (enrdf_load_stackoverflow)
DE (1) DE3767517D1 (enrdf_load_stackoverflow)
ES (1) ES2020520B3 (enrdf_load_stackoverflow)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6352992U (enrdf_load_stackoverflow) * 1986-09-25 1988-04-09
JP2519466Y2 (ja) * 1990-10-12 1996-12-04 株式会社帝国電機製作所 ガスシール型モータポンプ
FR2698667B1 (fr) * 1992-11-30 1995-02-17 Europ Propulsion Pompe centrifuge à rouet ouvert.
FR2715442B1 (fr) * 1994-01-26 1996-03-01 Lorraine Carbone Pompe centrifuge à entraînement magnétique.
FR2733010B1 (fr) * 1995-04-14 1997-07-04 Ceramiques Et Composites Sa Pompe centrifuge a entrainement magnetique
DE59911579D1 (de) * 1998-08-21 2005-03-17 Cp Pumpen Ag Zofingen Magnetgekuppelte Kreiselpumpe
US6135728A (en) * 1998-10-29 2000-10-24 Innovative Mag-Drive, L.L.C. Centrifugal pump having an axial thrust balancing system
US6234748B1 (en) 1998-10-29 2001-05-22 Innovative Mag-Drive, L.L.C. Wear ring assembly for a centrifugal pump
US6293772B1 (en) 1998-10-29 2001-09-25 Innovative Mag-Drive, Llc Containment member for a magnetic-drive centrifugal pump
US6123507A (en) * 1998-11-30 2000-09-26 Smith & Loveless, Inc. Single port impeller
EP1340917B2 (en) * 2001-06-05 2011-08-31 Iwaki Co., Ltd. Magnet pump
US7101158B2 (en) 2003-12-30 2006-09-05 Wanner Engineering, Inc. Hydraulic balancing magnetically driven centrifugal pump
JP4959424B2 (ja) * 2007-05-31 2012-06-20 勇 青谷 ポンプ装置
US8506259B2 (en) 2009-12-23 2013-08-13 Solar Turbines Inc. Fluid compression system
US8905729B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with electro-magnet coupling inside the impeller
US8905728B2 (en) 2011-12-30 2014-12-09 Peopleflo Manufacturing, Inc. Rotodynamic pump with permanent magnet coupling inside the impeller
US9488184B2 (en) 2012-05-02 2016-11-08 King Abdulaziz City For Science And Technology Method and system of increasing wear resistance of a part of a rotating mechanism exposed to fluid flow therethrough
DE102013007849A1 (de) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pumpenanordnung
DE102014006568A1 (de) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pumpenanordnung und Verfahren zum Herstellen eines Spalttopfes der Pumpenanordnung
US9771938B2 (en) * 2014-03-11 2017-09-26 Peopleflo Manufacturing, Inc. Rotary device having a radial magnetic coupling
JP6671048B2 (ja) * 2015-11-12 2020-03-25 パナソニックＩｐマネジメント株式会社 ポンプ
EP3387262A4 (en) * 2015-12-07 2019-07-24 Fluid Handling LLC. CLEARANCE OF WEAR RING OF OPERATED TURBINES FOR OFFSETTING AXIAL THRUST GENERATED IN A MULTI-STAGE PUMP
DE202016105312U1 (de) * 2016-09-23 2018-01-09 Speck Pumpen Verkaufsgesellschaft Gmbh Förderpumpe
US10746196B2 (en) * 2017-04-09 2020-08-18 Technology Commercialization Corp. Methods and devices for reducing circumferential pressure imbalances in an impeller side cavity of rotary machines

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0163126A1 (en) * 1984-05-02 1985-12-04 Pompe Ing. Calella S.p.A. Electric pumping device

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2209109A (en) * 1935-11-30 1940-07-23 Firm A W Mackensen Centrifugal pump with axial movement of the shaft
US2361521A (en) * 1943-11-01 1944-10-31 W S Darley & Company Centrifugal pump
US2942555A (en) * 1957-04-15 1960-06-28 Rinaldo F Pezzillo Combination pump and motor
AT242520B (de) * 1963-04-09 1965-09-27 Philip Pensabene Elektrisch angetriebene Pumpe
AT262774B (de) * 1963-12-14 1968-06-25 Richard Halm Flüssigkeitspumpe
US3589827A (en) * 1969-08-12 1971-06-29 Sergei Stepanovich Gerasimenko Centrifugal leakproof fluid pump
US3881840A (en) * 1973-09-05 1975-05-06 Neratoom Centrifugal pump for processing liquids containing abrasive constituents, more particularly, a sand pump or a waste-water pumper
JPS5055902A (enrdf_load_stackoverflow) * 1973-09-20 1975-05-16
FR2311201A1 (fr) * 1975-05-12 1976-12-10 Siebec Filtres Perfectionnement apporte aux pompes a entrainement magnetique
JPS527002A (en) * 1975-07-07 1977-01-19 Mitsubishi Heavy Ind Ltd Method of removing thrust of impeller in high pressure multistage pump
DE3490285T1 (de) * 1983-06-08 1985-08-22 Sundstrand Corp., Rockford, Ill. Zentrifugalpumpe
ATE29275T1 (de) * 1984-07-16 1987-09-15 Cp Pumpen Ag Kreiselpumpe mit spaltrohrtopf.
EP0171514B1 (de) * 1984-07-16 1988-03-09 CP Pumpen AG Kreiselpumpe mit einem Spaltrohrtopf

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0163126A1 (en) * 1984-05-02 1985-12-04 Pompe Ing. Calella S.p.A. Electric pumping device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
KSB-Kreiselpumpenlexikon, 02/1980 *

Also Published As

Publication number Publication date
JP2535004B2 (ja) 1996-09-18
US4793777A (en) 1988-12-27
CH672820A5 (enrdf_load_stackoverflow) 1989-12-29
JPS62233493A (ja) 1987-10-13
DE3767517D1 (de) 1991-02-28
ES2020520B3 (es) 1991-08-16
EP0237868A2 (de) 1987-09-23
ATE60411T1 (de) 1991-02-15
EP0237868A3 (en) 1988-01-20

Similar Documents

Publication Publication Date Title
EP0237868B1 (de) Radial- oder Axialkreiselpumpe
DE69005510T2 (de) Pumpe um Gas von einer zu pumpenden Flüssigkeit abzutrennen.
DE69023699T2 (de) Selbstansaugende Kreiselpumpe.
EP0536159A1 (de) Aggregat zum fördern von kraftstoff vom vorratstank zur brennkraftmaschine eines kraftfahrzeuges.
DE2223087A1 (de) Fluegelzellenverdichter
EP1719914B1 (de) Kreiselpumpe mit Magnetkupplung
AT412065B (de) Rotationspumpe mit hydraulisch gelagertem rotor
DE102020100602A1 (de) Motorisch angetriebene rotationstranslatorische Pumpe und Verfahren zum Betreiben einer Pumpe
DE69119183T3 (de) Kreiselpumpe mit Abdichtungsmitteln
EP4376270A1 (de) Pumpe-motor-einheit mit integrierter kühlung einer elektronikkomponente
DE2342605C3 (de) Pumpe, insbesondere Umwälzpumpe für Heizungsanlagen
DE2249510C2 (de) Flüssigkeitspumpenaggregat
DE3722530C2 (de) Turbinentriebwerk
DE4011671C2 (de) Regelbare Flügelzellenpumpe
DE4122487C2 (de) Förderaggregat aus einer Strömungsarbeitsmaschine und aus einem Antriebsmotor
DE4039712C2 (de) Peripheralpumpe
DE69106779T2 (de) Einstufige Kreiselpumpe mit einem peripherisch-axialen Diffusor.
DE69415269T2 (de) Zusammenbau einer Brennstoffpumpe
EP3978760B1 (de) Tauchkreiselpumpe
EP0601220B1 (de) Flüssigkeitspumpenaggregat, insbesondere Laugenpumpe
EP0644317B1 (de) Flüssigkeitsringgaspumpe
DE2857227C2 (de) Mehrflutige Flüssigkeitsringgaspumpe
DE19825521C2 (de) Flüssigkeitsringpumpe
DE4205542A1 (de) Selbstansaugende seitenkanalpumpe
DE102023118148B3 (de) Kreiselpumpe

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: A2

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

RHK1 Main classification (correction)

Ipc: F04D 13/06

AK Designated contracting states

Kind code of ref document: A3

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

17P Request for examination filed

Effective date: 19880713

17Q First examination report despatched

Effective date: 19890529

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

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

REF Corresponds to:

Ref document number: 60411

Country of ref document: AT

Date of ref document: 19910215

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3767517

Country of ref document: DE

Date of ref document: 19910228

ITF It: translation for a ep patent filed
ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
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: 87103057.3

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

Ref country code: ES

Payment date: 19950316

Year of fee payment: 9

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

Ref country code: BE

Payment date: 19950419

Year of fee payment: 9

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

Ref country code: CH

Payment date: 19950523

Year of fee payment: 9

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: 19960305

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

Ref country code: LI

Effective date: 19960331

Ref country code: CH

Effective date: 19960331

Ref country code: BE

Effective date: 19960331

BERE Be: lapsed

Owner name: HAUENSTEIN ERNST

Effective date: 19960331

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: SE

Payment date: 19970324

Year of fee payment: 11

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

Ref country code: FR

Payment date: 19970327

Year of fee payment: 11

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

Ref country code: AT

Payment date: 19970328

Year of fee payment: 11

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

Ref country code: AT

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

Effective date: 19980304

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: 19980305

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

Ref country code: FR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19980331

EUG Se: european patent has lapsed

Ref document number: 87103057.3

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: GB

Payment date: 19990222

Year of fee payment: 13

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

Ref country code: NL

Payment date: 19990331

Year of fee payment: 13

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990201

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: 20000304

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

Ref country code: NL

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

Effective date: 20001001

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

Effective date: 20000304

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20001001

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

Effective date: 20050304

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

Ref country code: DE

Payment date: 20060302

Year of fee payment: 20