EP0520286A2 - Pompe à pistons radiaux - Google Patents

Pompe à pistons radiaux Download PDF

Info

Publication number
EP0520286A2
EP0520286A2 EP92110092A EP92110092A EP0520286A2 EP 0520286 A2 EP0520286 A2 EP 0520286A2 EP 92110092 A EP92110092 A EP 92110092A EP 92110092 A EP92110092 A EP 92110092A EP 0520286 A2 EP0520286 A2 EP 0520286A2
Authority
EP
European Patent Office
Prior art keywords
bore
piston pump
pump according
radial piston
support body
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
EP92110092A
Other languages
German (de)
English (en)
Other versions
EP0520286A3 (en
EP0520286B1 (fr
Inventor
Siegfried Hertell
Ulrich Hiltemann
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.)
Comne Epo luk Automobilttechnik & Co KG GmbH
Original Assignee
Barmag Luk Automobiltechnik & Cokg GmbH
LuK Automobiltechnik GmbH and Co KG
Barmag Luk Automobiltechnik GmbH and Co KG
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 Barmag Luk Automobiltechnik & Cokg GmbH, LuK Automobiltechnik GmbH and Co KG, Barmag Luk Automobiltechnik GmbH and Co KG filed Critical Barmag Luk Automobiltechnik & Cokg GmbH
Publication of EP0520286A2 publication Critical patent/EP0520286A2/fr
Publication of EP0520286A3 publication Critical patent/EP0520286A3/de
Application granted granted Critical
Publication of EP0520286B1 publication Critical patent/EP0520286B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L33/00—Rotary or oscillatory slide valve-gear or valve arrangements, specially adapted for machines or engines with variable fluid distribution
    • F01L33/02—Rotary or oscillatory slide valve-gear or valve arrangements, specially adapted for machines or engines with variable fluid distribution rotary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0456—Cylindrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0535—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders the piston-driving cams being provided with inlets and outlets

Definitions

  • the invention relates to a radial piston pump according to the preamble of claim 1.
  • This radial piston pump is known from DE-C 19 03 256. With such a pump, pulsations are naturally noticeable.
  • the object of the invention is to reduce these pulsations and the noises caused thereby. Furthermore, the efficiency should be improved, in particular the output per piston stroke and the pressure build-up.
  • the radial piston pump according to FIG. 1 is housed in a cylindrical jacket 1.
  • a cylinder housing 10 is located concentrically in the casing 1.
  • the cylinder housing 10 is also cylindrical. It has four surfaces 12 on its outer circumference, which are successively offset from one another by 90 °. There is a radial in each of these surfaces Bore 14, which serves as a cylinder bore, introduced. If necessary, the cylinder bore can also be formed by a bushing (not shown here) which is inserted into the radial bore of the cylinder housing 10.
  • the bores 14 are preferably in the same cross-sectional plane, but they can also be expanded by further bores which are arranged on the circumference of the cylinder housing in the same cross-sectional plane or a further cross-sectional plane.
  • a top hat 2 On each of the surfaces 12, which are penetrated with a radial bore 14, a top hat 2 is attached and sealed.
  • the top hat On its cylindrical jacket, the top hat is surrounded by an elastic ring 4, which closes an outlet opening 5 and serves as a check valve.
  • each top hat 2 With its cover 6, each top hat 2 is supported on the inner surface M of the outer shell 1.
  • the housing 10 In its interior, the housing 10 forms a circular cylindrical chamber 16 which is connected via a schematically illustrated line I to a pressure medium source (not shown) in a manner known per se.
  • a shaft 20 In the chamber there is a shaft 20 which is rotatably mounted about an axis 18.
  • the bearings of the shaft 20 are located in the sealing caps or the end faces (not shown) at the two ends of a pump housing H which encloses the cylinder housing 10.
  • a crank disc 22 On the shaft 20, a crank disc 22, which is offset eccentrically by a dimension "e", is fastened in a rotationally fixed manner and, for reasons described below, lies in the same cross-sectional plane as the bores 14.
  • the crank disc 20 is surrounded by an octagonal ring or supporting body 24 on its outer circumference , whose eight equally wide surfaces 26 are parallel to the eight outer surfaces 12 of the housing 10.
  • the support body 24 is slidable on the crank disk 22 and is thus rotatable relative to the latter, its maximum diameter being at least twice the outer center "e" of the crank disk 20 less than the diameter of the chamber 16.
  • tangential grooves 28 which extend from the edge of the support body 24 formed between two adjoining surfaces to not quite in the middle of the respective surface 26.
  • pistons 30 slidably mounted in the bores 14 of the cylinder housing 10, which are hollow on the inside and resiliently supported by helical springs 32 supported on the cover 6 of the cylinder cap 2 against the surfaces 26 of the support body 24 provided with the grooves 28 be pressed.
  • Each piston 30 is provided on its end face 34 resting against the surface 26 with an axial bore 36, the axis of which intersects the axis 18 of the shaft 20. If necessary, the pistons 30 can be provided with piston rings.
  • crank disk 24 rotates with it, which leads to a wobbling or cranking movement of the support body 24.
  • the pistons 30 resting on the surfaces 26 thereof are set in radially inward and outward movements in accordance with the outer center of the disc 22 and under the load of the springs 32 with respect to the shaft 20.
  • the surfaces 26 slide radially to the end surfaces 34 of the pistons 30, the position of the grooves 28 with respect to the bores 36 changing between open and closed positions in the manner described in more detail below.
  • the grooves 28 extend from an edge of the surfaces 26 to not quite to the center thereof, namely they end by half the diameter of the piston bore 36 in front of the center of the surface.
  • the center of the surface 26 coincides with the axis of the piston 30, and the groove 28 ends immediately in front of the edge of the piston bore 36 so that it is closed.
  • the support body 24 begins in the crank disc 22 in the direction of the arrow shown in the opposite direction to slide along the end face of the piston 30, ie the groove 28 begins to slide under or in front of the bore 36 and to open it until it has reached its theoretically largest opening (see the piston in the "north position") after the disk 24 has been rotated 90 degrees.
  • the largest possible opening of the bore 36 is, however, reached at the moment when the front end of the groove 28 is aligned with the bore 36 at the rear edge in the direction of movement.
  • the closing process begins at the moment when the crank disk 24 has rotated by more than 90 ° and ends completely after a rotation of 180 degrees (see the piston in the "west position").
  • the opening of the bore 36 coincides with the suction of hydraulic fluid supplied via the line I to the chamber 16 into the interior of the piston 30, the amount of liquid conveyed by the pistons being a function the rotational speed of the crank disc 22, the force of the piston spring 32, the viscosity of the hydraulic fluid, the size of the piston bore 36, etc.
  • the pressure fluid is thus displaced from the interior of the piston and the cylinder space through outlet opening 5.
  • the outlet valve opens, which - as already stated - is designed as an elastic ring 4.
  • the elastic ring 4 widens accordingly due to the outlet pressure in the outlet opening 5.
  • the pressure oil enters the outlet space 7 and is supplied to the consumer (not shown) via outlet opening O.
  • the inlet opening 36 located on each piston head is opened as soon as the piston begins its radial inward movement. Similarly, the inlet bore 36 is closed again as soon as the piston has reached its radially innermost position and its radial outward movement begins. Therefore, the entire amount of liquid sucked in remains in the piston and is now expelled.
  • the radial piston pump shown in FIGS. 4 and 5 differs from that shown in FIG. 1 in that the pressure medium is supplied via an axial bore 38 provided in the drive shaft 20a.
  • the crank disk 22a is provided with a recess 40 of cross-sectional shape, into which a line 42 connected to the axial bore 38 opens.
  • the recess 40 is in turn connected over the area of its arc length to a bore 28 in the surface 26 of the support body 24 supporting the piston 30.
  • the bore 28 in turn communicates with the bore 36 of the end face 34 of the piston 30 during approximately half a revolution of the crankshaft 22. In the two dead center positions of the crank disc 22, the bore 28 lies next to the bore 36.
  • the bore 36 is therefore closed, and this closed position is maintained during the radial outward movement of the piston caused by the crank disc 22.
  • the bore 28 begins to lie in front of the bore 36 when the piston 30 begins its radial inward movement caused by the eccentric disc 22.
  • the radial inward movement of the piston 30 leads to a suction of pressure fluid, while the radial outward movement leads to a displacement of the suctioned pressure fluid from the interior of the piston 30 leads through an outlet, not shown.
  • FIGS. 6 and 7 The embodiment of the radial piston pump according to the invention shown in FIGS. 6 and 7 is similar to that shown in FIG. 4 in that the pressure medium is also supplied through a bore 38 provided in the rotary shaft 20.
  • a radial bore 42 leads from the bore to the outer circumference of the crank disc 22.
  • the radial bore 42 ends at a point on the crank disc circumference which corresponds to the bottom dead center of the crank disc 22.
  • a bore 28 is provided which produces the connection between the radial bore 42 and the bore 36 in the end face of the piston 30 in a certain rotation range of the crank disk 22 and thus a pressure medium flow into the interior of the piston 30.
  • connection between the radial bore 42 and the piston bore 36 begins shortly after the crank disc 22 has rotated out of its top dead center and the piston 30 begins to move radially inward. As the piston 30 begins to move radially outward under the influence of the rotating crank disk 22, the connection between the bore 42 and the piston bore 36 is interrupted, so that the outwardly moving piston 30 the pressure fluid in it via a not shown Can pump out the outlet.
  • the pump according to FIG. 8 consists of a cylinder housing 10, pistons 30 embedded in cylinder bores of the same, a shaft 20 rotatably mounted in the center of the cylinder housing 10 with a crank disk 22 non-rotatably connected to it and a support body 24 with support surfaces 26 for the crank disk 22 the pistons 30.
  • a support body 24 with support surfaces 26 for the crank disk 22 the pistons 30.
  • the bores 28 are centered in the support surfaces 26 of the support body 24, so that they are at both dead centers of the crank disk 22 with the Bores 36 of the pistons 30 are aligned. In the rotational area between the two dead centers, the bores 28 are, however, outside the region of the bores 36.
  • an axial bore 38 is provided which is aligned with the bore 28 in the support body 24 via a radial bore 42 corresponding to the rotational position of the crank disk 22 can be brought.
  • the axial bore 42 is aligned with the bore 28 of the support body 24, so that a connection is established between the pressure medium supply, which is connected to the axial bore 38 via a line 44, and the interior of the piston 30.
  • this connection occurs shortly before the crank disk 22 reaches its bottom dead center in front of the piston 30, ie while the piston 30 is immersed in the cylinder housing 10 under the pressure of its coil spring 32 and the receding support body 24.
  • hydraulic fluid is sucked in during the plunging movement of the piston 30 and continues until the connection between the pressure medium source and the piston 30 is interrupted by the rotation of the crankshaft 22 and the associated movement of the support body 24 becomes.
  • the pressure medium is pumped out of the piston 30, the bore 28 in the support body 24 being sealed by the crank disk 22 and thus no pressure medium liquid being able to flow back out of the piston 30.
  • FIG. 10 Another embodiment of the radial piston pump according to the invention is shown in FIG. 10.
  • the support body 24 shown here differs from those of the other embodiments by grooves 28 '' which lead in the axial direction of the support body 24 and which, according to the wobbling of the support body 24, lie in front of the piston bores 36 and thereby flow into the piston 30 or laterally through this pressure fluid of the bores 36 lie and are kept closed by the wings 26 of the ring 26.
  • the grooves 28 ′′ are offset such that there is a connection between the grooves 28 ′′ and the piston bores 36 only during the retracting movement of the piston 30. This embodiment is advantageous for a constant delivery rate.
  • the invention provides a radial piston pump, the inlet valve of which can be controlled as desired by the dimensioning of the grooves, bores and channels which serve for the liquid inlet. It is possible to control the inlet valve so that it is opened or closed in synchronism with the piston stroke. Likewise, the grooves, bores and channels can be dimensioned and matched to one another so that only a limited period of the intake stroke is available for opening the inlet valve. Such a dimensioning will be chosen above all if the delivery rate of the pump should not be speed-dependent in all speed ranges, but should be limited to a certain delivery rate at higher speeds.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP92110092A 1991-06-27 1992-06-16 Pompe à pistons radiaux Expired - Lifetime EP0520286B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE4121271 1991-06-27
DE4121271 1991-06-27
DE4139640 1991-12-02
DE4139640 1991-12-02
DE4213685 1992-04-25
DE4213685 1992-04-25

Publications (3)

Publication Number Publication Date
EP0520286A2 true EP0520286A2 (fr) 1992-12-30
EP0520286A3 EP0520286A3 (en) 1993-03-24
EP0520286B1 EP0520286B1 (fr) 1995-12-20

Family

ID=27202647

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92110092A Expired - Lifetime EP0520286B1 (fr) 1991-06-27 1992-06-16 Pompe à pistons radiaux

Country Status (3)

Country Link
EP (1) EP0520286B1 (fr)
JP (1) JPH05180153A (fr)
DE (1) DE59204725D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0743450A1 (fr) * 1995-05-18 1996-11-20 LuK Automobiltechnik GmbH & Co. KG Pompe à pistons radiaux
DE19640596A1 (de) * 1996-10-01 1998-04-02 Rexroth Mannesmann Gmbh Radialkolbenpumpe
FR2826063A1 (fr) * 2001-06-19 2002-12-20 Bosch Gmbh Robert Pompe a haute pression de carburant pour un moteur a combustion interne a charge partielle amelioree
EP1318302A2 (fr) * 2001-12-07 2003-06-11 Denso Corporation Pompe d'injection de carburant
EP1760312A2 (fr) * 2003-02-11 2007-03-07 Ganser-Hydromag Ag Pompe haute pression
CN107829897A (zh) * 2017-11-22 2018-03-23 浙江力俭新能源科技有限公司 一种液压泵

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4941262B2 (ja) * 2007-12-05 2012-05-30 株式会社デンソー ポンプ
DE102021204716A1 (de) * 2021-05-10 2022-11-10 Thyssenkrupp Ag Radialkolbenpumpe, insbesondere Radialkolbenverdichter
DE102021204713A1 (de) * 2021-05-10 2022-11-10 Thyssenkrupp Ag Radialkolbenpumpe, sowie Verfahren zur Herstellung einer Radialkolbenpumpe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB740784A (en) * 1953-08-17 1955-11-16 Lucas Industries Ltd Reciprocatory pumps
DE1101153B (de) * 1958-01-18 1961-03-02 Rech Etudes Prod Radialpumpe
US3125034A (en) * 1964-03-17 Pump with radial cylinders
DE2061962A1 (de) * 1970-12-16 1972-06-29 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe mit Gleitschuh zwischen Kolben und Exzenter
DE2848207A1 (de) * 1978-11-07 1980-05-14 Bosch Gmbh Robert Kolbenpumpe
US4673337A (en) * 1985-11-27 1987-06-16 General Motors Corporation Hydraulic radial piston pump intake porting arrangement
DE3921635C2 (de) * 1988-07-01 1994-04-14 Kayaba Industry Co Ltd Hydro-Radialkolbenpumpe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125034A (en) * 1964-03-17 Pump with radial cylinders
GB740784A (en) * 1953-08-17 1955-11-16 Lucas Industries Ltd Reciprocatory pumps
DE1101153B (de) * 1958-01-18 1961-03-02 Rech Etudes Prod Radialpumpe
DE2061962A1 (de) * 1970-12-16 1972-06-29 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe mit Gleitschuh zwischen Kolben und Exzenter
DE2848207A1 (de) * 1978-11-07 1980-05-14 Bosch Gmbh Robert Kolbenpumpe
US4673337A (en) * 1985-11-27 1987-06-16 General Motors Corporation Hydraulic radial piston pump intake porting arrangement
DE3921635C2 (de) * 1988-07-01 1994-04-14 Kayaba Industry Co Ltd Hydro-Radialkolbenpumpe

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0743450A1 (fr) * 1995-05-18 1996-11-20 LuK Automobiltechnik GmbH & Co. KG Pompe à pistons radiaux
DE19640596A1 (de) * 1996-10-01 1998-04-02 Rexroth Mannesmann Gmbh Radialkolbenpumpe
WO1998014704A1 (fr) 1996-10-01 1998-04-09 Mannesmann Rexroth Ag Pompe a piston radial
FR2826063A1 (fr) * 2001-06-19 2002-12-20 Bosch Gmbh Robert Pompe a haute pression de carburant pour un moteur a combustion interne a charge partielle amelioree
EP1318302A2 (fr) * 2001-12-07 2003-06-11 Denso Corporation Pompe d'injection de carburant
EP1318302A3 (fr) * 2001-12-07 2003-11-26 Denso Corporation Pompe d'injection de carburant
US6827000B2 (en) 2001-12-07 2004-12-07 Denso Corporation Fuel injection pump
EP1760312A2 (fr) * 2003-02-11 2007-03-07 Ganser-Hydromag Ag Pompe haute pression
EP1760312A3 (fr) * 2003-02-11 2007-09-05 Ganser-Hydromag Ag Pompe haute pression
CN107829897A (zh) * 2017-11-22 2018-03-23 浙江力俭新能源科技有限公司 一种液压泵

Also Published As

Publication number Publication date
EP0520286A3 (en) 1993-03-24
DE59204725D1 (de) 1996-02-01
JPH05180153A (ja) 1993-07-20
EP0520286B1 (fr) 1995-12-20

Similar Documents

Publication Publication Date Title
EP0808421B1 (fr) Pompe hydrostatique ajustable
EP0520286B1 (fr) Pompe à pistons radiaux
DE102005041579A1 (de) Innenzahnradpumpe mit Füllstück
DE69015795T2 (de) Flügelzellen-Verdrängungspumpe.
DE3030285A1 (de) Axialkolbenpumpe
DE3440850C2 (fr)
DE19703155C2 (de) Verstellbare Radialkolbenmaschine
DE1653921C3 (de) Rotationskolbenpumpe
DE102005017834B4 (de) Zellenpumpe
DE60129857T2 (de) Kugelförmige fluidmaschine mit durchflussregelungsvorrichtung
DE69931181T2 (de) Rotationspumpe
DE10156835C1 (de) Drehkolbenpumpe
DE3242983A1 (de) Regelbare fluegelzellenpumpe
DE3503437C2 (de) Axial-Kolbenmaschine
DE4428410C2 (de) Kompakte Regeleinheit für eine Flügelzellenpumpe
DE10334672B3 (de) Pendelschiebermaschine
DE102007039157B4 (de) Flügelzellenpumpe
EP0474001B1 (fr) Pompe à engrenages internes pour fluide hydraulique
DE60110314T2 (de) Axialkolbenpumpe
DE19810318B4 (de) Hydraulikmaschine
DE102007032102A1 (de) Pumpeneinheit mit Hauptpumpe und Hilfspumpe
DE19602770C2 (de) Kolbenrollen-Führung für Radialkolbenaggregat
DE4312498C2 (de) Förderpumpe
DE3624382A1 (de) Exzentrische sperrschieberpumpe, insbesondere zur foerderung von schmierstoffen fuer antriebe
DE1054300B (de) Hydrostatisches Getriebe

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): DE FR GB IT SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19930910

17Q First examination report despatched

Effective date: 19940622

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: LUK AUTOMOBILTECHNIK GMBH & CO. KG

REF Corresponds to:

Ref document number: 59204725

Country of ref document: DE

Date of ref document: 19960201

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)

Effective date: 19960321

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
ITPR It: changes in ownership of a european patent

Owner name: COM.NE EPO;LUK AUTOMOBILTTECHNIK GMBH & CO KG

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

Ref country code: FR

Payment date: 19980508

Year of fee payment: 7

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

Ref country code: SE

Payment date: 19980518

Year of fee payment: 7

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

Ref country code: GB

Payment date: 19980522

Year of fee payment: 7

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: 19990616

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

Ref country code: SE

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

Effective date: 19990629

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: 19990630

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

Effective date: 19990616

EUG Se: european patent has lapsed

Ref document number: 92110092.1

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

Ref country code: DE

Payment date: 20000615

Year of fee payment: 9

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: 20020403

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: 20050616