EP0676547A1 - Régulateur de débit pour un système hydraulique à haute pression et soupape pour frein de descente - Google Patents

Régulateur de débit pour un système hydraulique à haute pression et soupape pour frein de descente Download PDF

Info

Publication number
EP0676547A1
EP0676547A1 EP95105308A EP95105308A EP0676547A1 EP 0676547 A1 EP0676547 A1 EP 0676547A1 EP 95105308 A EP95105308 A EP 95105308A EP 95105308 A EP95105308 A EP 95105308A EP 0676547 A1 EP0676547 A1 EP 0676547A1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
piston
orifice
brake valve
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
EP95105308A
Other languages
German (de)
English (en)
Other versions
EP0676547B1 (fr
Inventor
Martin Dipl. Ing. Heusser
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik 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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP0676547A1 publication Critical patent/EP0676547A1/fr
Application granted granted Critical
Publication of EP0676547B1 publication Critical patent/EP0676547B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves

Definitions

  • the invention relates to a flow control device according to the preamble of claim 1 and a lowering brake valve of the type specified in the preamble of claim 7.
  • two-way flow controllers which contain a metering orifice and a regulating pressure compensator orifice and keep the pressure medium quantity constant regardless of pressure changes from a predetermined response pressure.
  • a two-way flow regulator is arranged in the working pressure line.
  • 3, 5, 6, 7, the two-way flow regulator is arranged in a bypass line to the tank.
  • Two-way flow regulators arranged in the working pressure line are often used as so-called lowering brake valves in order to limit the maximum movement speed of a hydraulic consumer, either in one or the other flow direction, the flow regulator being part of a quantity control device for the high pressure hydraulics.
  • a quantity control device known from DE-A-39 38 560 limits the speed of a hydraulic consumer which can only be acted upon from one side in two directions of movement in different ways.
  • the flow control device namely forms a two-way flow controller for lowering movements and a three-way flow controller for lifting movements.
  • a common orifice plate, through which the same flow direction flows when lifting and lowering, is assigned to two parallel pressure compensator orifice plates.
  • This quantity control device has a complicated structure and is only useful for a single hydraulic consumer supplied by the pump, the pressure medium flowing out of which plays no role in the control thereof when lifting to the tank. In the case of several consumers supplied by a common pressure source, this is unsuitable because the pressure medium flowing to the tank impairs the supply to other consumers. In a lifting device such as a forklift, in particular an electrically powered forklift, this quantity control device would be unsuitable because electrical energy is wasted due to the pressure medium pumped to the tank when lifting, or pressure medium is missing when supplying other parallel consumers.
  • the subordinate hydraulic consumer With the speed-controlled pump, the subordinate hydraulic consumer can be moved up to its limit speed in the respective direction of movement selected by the directional control valve start up.
  • the limit speed is maintained by a lowering brake in each direction.
  • Two lowering brake valves are provided for the two directions of movement, each of which limits the amount of pressure medium flowing out in its working pressure line, while it opens unthrottled in the inflow direction.
  • the construction effort of two lowering brakes in the working pressure lines is high because a measuring orifice and a pressure compensator orifice and a bypass for the unthrottled flow are required for each flow direction.
  • the working line connected to the piston-side working chamber of the hydraulic consumer contains a single control orifice which interacts with one orifice plate each of two orifice plates provided in the direction of the control valve, in order to to regulate the flow dependence of the deflection of the directional control valve in each flow direction, namely either the quantity flowing in to the piston-side working chamber or the quantity flowing out of the piston-side working chamber.
  • a multi-position directional control valve is also required to swap the pressure compensator control pressures in order to control the pressure compensator accordingly in each flow direction.
  • the pressure compensator is expressly structurally separated from the directional control valve containing the measuring orifices and the multi-position directional control valve. This requires a considerable amount of construction work and considerable circuit and space requirements.
  • the invention has for its object to provide a flow control device and a lowering brake valve of the type known from DE-A-39 38 560, in which the speed limitation of the hydraulic consumer in both directions of movement is possible with little structural effort and reduced circuitry and space requirements.
  • the object is achieved according to the invention with the quantity control device according to claim 1 or the lowering brake valve according to claim 7.
  • the quantity control device does not allow unnecessary pressure medium to flow unused in both directions of movement.
  • the safety valve normally provided in the pressure supply can be used to discharge excess pressure medium.
  • the flow control device is particularly suitable for cooperation with a speed-controlled pump, which enables speed control until the flow control device intervenes and also provides the required delivery rate for several consumers.
  • the speed-controlled pump can only deliver the required delivery rate, so that no pump drive energy is wasted. This is particularly advantageous in the case of lifting devices whose hydraulic pump is supplied by a battery.
  • both two-way flow controllers are combined with a common measuring orifice in one and the same working pressure line. This reduces the construction effort and the space required. There is no need to intervene in the other working pressure line. In spite of the quantity control or speed limitation, no excess pressure medium is wasted for both directions of movement of the hydraulic consumer because no pressure medium is released to the tank in the two-way flow regulator function.
  • the flow control device uses excess pressure medium to supply at least one other hydraulic consumer. Excess pressure medium could be released via the safety pressure relief valve.
  • the subordinate hydraulic consumer processes only as much pressure medium as the pressure compensator orifice plate allows. This benefits primary, other hydro consumers, the operation of which is not impaired by the subordinate hydraulic consumer, which is limited in both directions to maximum speeds.
  • the pump provides only as much pressure medium as that Pressure compensator orifice plate at the speed limit needs. Up to this delivery rate, the speed of the hydraulic consumer can be adjusted by means of the pump speed. The pump only pumps more pressure medium if additional hydraulic consumers have to be supplied.
  • the respective direction of movement of the hydraulic consumer is selected by means of the directional control valve.
  • the quantity control device is effective in every direction of movement of the hydraulic consumer.
  • the quantity control device is accommodated in a single working pressure line. Nevertheless, the speed of movement of the hydro consumer is limited in both directions of movement.
  • a structurally simple, compact and functionally reliable embodiment of the lowering brake valve emerges from claim 8.
  • the two pressure compensator control orifices are designed so that they are open together in the normal position and regulate in the flow direction they monitor from the open position towards their shut-off position. This avoids unnecessary flow losses at low speed of the hydro consumer.
  • the union nut has a double function, since on the one hand it secures the measuring orifice and on the other hand it forms the stop for the control spring.
  • the passages are housed in a space-saving manner. Nevertheless, the control behavior is clean.
  • the embodiment according to claim 15 is particularly space-saving.
  • the lowering brake valve integrated into the screw-in housing represents a structural unit that can be screwed into the working pressure line or a channel of the hydraulic consumer.
  • a hydraulic control device S according to Fig. 1 e.g. of a lifting device, such as a forklift truck or forklift truck, has a pump P which sucks from a tank T and feeds a pump line 1.
  • a tank line 2 leads to the tank.
  • a safety pressure relief valve 3 is provided between the pump line and the tank line 1, 2.
  • the pump P can be a speed-controlled pump, the delivery rate of which is proportional to the pump speed.
  • a hydro consumer V e.g. a double-acting hydraulic cylinder 5, with a piston-side and a piston rod-side working chamber 6, 7 is connected via working pressure lines 3, 4 to a directional control valve W (4/3-way control valve with blocked zero position), with which the direction of movement of the hydraulic consumer 5 can be adjusted.
  • a quantity control device M In the working pressure line 3 is a quantity control device M, additionally in the form of a Two-way lowering brake valve Z, provided.
  • a further hydraulic consumer V1 is connected to the pump line 1 or the tank line 2 via a working pressure line 8 and a further directional control valve W1.
  • the hydraulic consumer V can be used for swivel adjustment, e.g. a lifting fork, be provided in both directions, while the hydraulic consumer V1 is used for another function of the lifting device.
  • the bidirectional lowering brake valve Z has a (in the present case fixed) orifice 9 and a pressure compensator orifice arrangement 10, which via a pilot line 11 with the pressure prevailing in the working pressure line 3 between the chamber 7 and the orifice 9 and in the opposite direction a pilot line 12 can be acted upon by the pressure prevailing between the measuring orifice 9 and the pressure compensator orifice arrangement 10.
  • a control spring 13 (or two) serves to center the pressure compensator orifice arrangement 10 in an open normal position.
  • FIG. 2 shows the construction of the quantity control device M or the bidirectional lowering brake valve Z. It is a screw-in valve, the screw-in housing G of which is screwed with an external thread section 15 into an internal thread section 14 of the working pressure line 3. It is conceivable to design the valve with a conventional block-shaped housing and to provide connections for the working pressure line 3.
  • an axial bore forms a housing chamber 16, in which a control piston 17 designed as a hollow cup piston is guided in a sealed, displaceable manner with a guide section 18.
  • a control piston 17 designed as a hollow cup piston
  • the orifice 9 is fixed in the form of an aperture ring 36 with an aperture bore 37.
  • the piston crown designated 20 contains at least one throttle passage 21 to a control chamber part 22 of the housing chamber 16.
  • a screw-in tool engagement point 23 is provided at the lower end of the screw-in housing G.
  • Radial bores 24 distributed in the circumferential direction are provided in the wall of the control piston 17 and form a pair of first and second control edges 25, 26 spaced apart in the direction of displacement of the control piston 17.
  • a circumferential groove 27 open to the control piston 17 is formed in the wall of the housing chamber 16, the groove flanks of which also form a pair of first and second control edges 29, 28.
  • a control spring 13 surrounds the control piston end 19 and is fixed with prestress via abutment parts 35 between stops 33 and 34 on the control piston 17 and between abutments 32 and 31 of the screw-in housing.
  • the abutment 32 is formed by a screw-in ring 40 with which the control piston 17 and the control spring 13 are secured in the screw-in housing G.
  • the stop 33 is formed by a union nut 38, with which the orifice plate 9 is fixed interchangeably with another orifice plate with a differently sized orifice hole 37.
  • the union nut 38 has a passage 39 which is also shaped as a turning aid.
  • pressure medium can pass in the working pressure line 3 in any direction of flow, as long as the amount of pressure medium only generates a pressure difference across the measuring orifice 9 which is less than the force of the control spring 13.
  • the speed of the hydraulic consumer V in FIG. 1 is increased or decreased by means of the speed of the pump P.
  • the respective direction of movement is set with the directional control valve W.
  • the control spring 13 serves to maintain the normal position of the control piston 17 shown in FIG. 2.
  • the pressure difference occurring via the measuring orifice acts on the action area of the control piston 17 defined by the guide section 18, which acts downward on the pressure acting in FIG. 2 above the measuring orifice 9 , while the pressure below the orifice 9 acts through the passage 21 in the control chamber part 22 in the direction of displacement upwards.
  • control piston 17 If the pressure rises upstream of the orifice plate, then the control piston 17 is shifted further downward and the quantity passing between the control edges 25 and 29 is further regulated until the pressure difference across the orifice plate 9 is again at its predetermined value. The speed of the hydraulic cylinder 5 still does not change.
  • the stop 34 of the control piston 17 is released from the lower spring end of the control spring 13 supported on the spring abutment 31, while the upper stop 33 compresses the control spring, the upper end of which springs from the spring abutment 32.
  • the lowering brake valve Z is flowed through in the opposite flow direction 42.
  • the then higher pressure upstream of the orifice 9 acts through the passage 21 in the control chamber part 22 on the pressure surface of the control piston 17, while the lower pressure downstream of the orifice 9 acts in the opposite direction on the control piston 17.
  • the control piston 17 is adjusted upwards in FIG. 4.
  • the cross-cooperating control edges 26, 28 regulate the amount of pressure medium until the pressure difference across the measuring orifice 9 again corresponds to the predetermined value, the speed of movement of the hydraulic consumer V being limited in the new adjustment direction.
  • control spring 13 instead of a control spring 13 common to both flow directions 41, 42, it is possible to have two separate control springs 13 act on the control piston 17. These can be biased differently or have different spring stiffnesses in order to bring about different control behavior for the two flow directions to be monitored. Both with a common control spring 13 and with two separate control springs, structural measures can be taken in order to be able to change the preload as desired.
  • the installation position of the bidirectional lowering brake valve Z in relation to the hydraulic consumer is irrelevant.
  • the orifice 9 could also be arranged separately from the control piston 17.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Braking Systems And Boosters (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Fluid-Driven Valves (AREA)
EP95105308A 1994-04-08 1995-04-07 Régulateur de débit pour un système hydraulique à haute pression et soupape pour frein de descente Expired - Lifetime EP0676547B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9405872U DE9405872U1 (de) 1994-04-08 1994-04-08 Senkbremsventil und Mengenregel-Vorrichtung für die Hochdruck-Hydraulik
DE9405872U 1994-04-08

Publications (2)

Publication Number Publication Date
EP0676547A1 true EP0676547A1 (fr) 1995-10-11
EP0676547B1 EP0676547B1 (fr) 1999-07-07

Family

ID=6907088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95105308A Expired - Lifetime EP0676547B1 (fr) 1994-04-08 1995-04-07 Régulateur de débit pour un système hydraulique à haute pression et soupape pour frein de descente

Country Status (3)

Country Link
EP (1) EP0676547B1 (fr)
AT (1) ATE181991T1 (fr)
DE (2) DE9405872U1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0823559A3 (fr) * 1996-08-09 1998-07-15 Robert Bosch Gmbh Dispositif de commande hydraulique
EP0987444A3 (fr) * 1998-09-18 2002-07-31 HydraForce, Inc. Régulateur de flux proportional et prioritaire avec régulation de contreflux
FR2846718A1 (fr) * 2002-10-31 2004-05-07 Linde Ag Vanne installee sur un verin
WO2008151732A1 (fr) * 2007-06-12 2008-12-18 Voith Patent Gmbh Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique
CN111692154A (zh) * 2020-06-23 2020-09-22 三一海洋重工有限公司 限速阀

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111734352B (zh) * 2020-07-17 2024-07-23 西南石油大学 一种布酸效果好的均匀布酸装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3139944A1 (de) * 1981-10-08 1983-04-28 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische steuereinrichtung zur lastunabhaengigen steuerung eines doppeltwirkenden servomotors
FR2551171A1 (fr) * 1983-08-22 1985-03-01 Cessna Aircraft Co Valve de commande perfectionnee de limitation de debit et d'equilibrage de pression
DE3422978A1 (de) * 1984-06-22 1986-01-02 Robert Bosch Gmbh, 7000 Stuttgart Vorrichtung zur steuerung einer hydraulischen stelleinrichtung
DE3605980A1 (de) * 1985-03-05 1986-10-16 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Proportionalventil mit druckdifferenzwaage
DE3938560A1 (de) * 1989-11-21 1991-05-23 Bosch Gmbh Robert Hydraulische steuereinrichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3139944A1 (de) * 1981-10-08 1983-04-28 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische steuereinrichtung zur lastunabhaengigen steuerung eines doppeltwirkenden servomotors
FR2551171A1 (fr) * 1983-08-22 1985-03-01 Cessna Aircraft Co Valve de commande perfectionnee de limitation de debit et d'equilibrage de pression
DE3422978A1 (de) * 1984-06-22 1986-01-02 Robert Bosch Gmbh, 7000 Stuttgart Vorrichtung zur steuerung einer hydraulischen stelleinrichtung
DE3605980A1 (de) * 1985-03-05 1986-10-16 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Proportionalventil mit druckdifferenzwaage
DE3938560A1 (de) * 1989-11-21 1991-05-23 Bosch Gmbh Robert Hydraulische steuereinrichtung

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
BARTOLO: "How to select flow control valves", MACHINE DESIGN, 18 July 1963 (1963-07-18), CLEVELAND, US, pages 168 - 184 *
BREITSPRECHER: "Understanding pressure-compensated flow controls.", HYDRAULICS AND PNEUMATICS, vol. 17, no. 6, CLEVELAND US, pages 72 - 75 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0823559A3 (fr) * 1996-08-09 1998-07-15 Robert Bosch Gmbh Dispositif de commande hydraulique
EP0987444A3 (fr) * 1998-09-18 2002-07-31 HydraForce, Inc. Régulateur de flux proportional et prioritaire avec régulation de contreflux
FR2846718A1 (fr) * 2002-10-31 2004-05-07 Linde Ag Vanne installee sur un verin
WO2008151732A1 (fr) * 2007-06-12 2008-12-18 Voith Patent Gmbh Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique
DE102007027603A1 (de) * 2007-06-12 2008-12-18 Voith Patent Gmbh Hydraulischer Antrieb, insbesondere für Werkzeugmaschinen, und Verfahren zum Steuern des hydraulischen Antriebs
US8549983B2 (en) 2007-06-12 2013-10-08 Voith Patent Gmbh Hydraulic drive, in particular for machine tools, and method for controlling the hydraulic drive
CN111692154A (zh) * 2020-06-23 2020-09-22 三一海洋重工有限公司 限速阀

Also Published As

Publication number Publication date
EP0676547B1 (fr) 1999-07-07
ATE181991T1 (de) 1999-07-15
DE9405872U1 (de) 1994-05-26
DE59506326D1 (de) 1999-08-12

Similar Documents

Publication Publication Date Title
DE2343611C2 (de) Vorrichtung zum lastabhängigen Steuern einer hydrostatischen Verstellpumpe
DE3532816A1 (de) Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
EP0105473B1 (fr) Circuit hydraulique comprenant deux pompes à débit variable commandées par l'excédent du débit
DE1916224B2 (de) Hydrostatisches Getriebe
DE1601729B2 (de) Mit Vorsteuerung arbeitende hydraulische SteuerventUeinrichtung
DE3513582A1 (de) Proportional arbeitendes hydroventil mit informationserfassung betreffend die staerksten druecke in den verbraucherkreisen
DE3710699C1 (de) Hydraulische Steuervorrichtung fuer eine Verbrauchergruppe
DE69206170T2 (de) Proportionales Wegeventil und Steuersystem für mehrere hydraulische Verbrauchen, wobei jeder solch ein Ventil beinhaltet.
DE3232695C2 (de) Leistungsregel-Vorrichtung für eine Hydropumpe
EP0676547B1 (fr) Régulateur de débit pour un système hydraulique à haute pression et soupape pour frein de descente
DE9115265U1 (de) Vorrichtung zum Schmieren von Zylindern
DE4025638C1 (fr)
DE4230183C2 (de) Steuervorrichtung für Hydromotoren
DE2523937A1 (de) Hydraulische steuervorrichtung
DE3919175C2 (fr)
EP0331958B1 (fr) Dispositif de commande hydraulique
DE3823892A1 (de) Hydraulikanlage mit mehreren pumpen
DE69305708T2 (de) Steuervorrichtung für mehrere hydraulische Verbraucher
DE2744792A1 (de) Hydraulisches steuersystem mit einem druckregulierungsventil und stellelementen fuer ein getriebe
DE19613393C2 (de) Zweiseitig druckerfassendes Wechselentlastungsventil
DE3200126C2 (fr)
DE2800814A1 (de) Hydraulische steuereinrichtung
DE2611088C3 (de) Steuereinrichtung für einen hydraulischen Arbeitzylinder mit einem Differentialkolben
DE3711050C2 (fr)
DE3844399A1 (de) Verstellpumpe fuer mehrere unabhaengig voneinander betaetigbare verbraucher

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): AT CH DE FR GB IT LI SE

RBV Designated contracting states (corrected)

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

17P Request for examination filed

Effective date: 19960410

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 19980730

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

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 FR GB IT LI SE

REF Corresponds to:

Ref document number: 181991

Country of ref document: AT

Date of ref document: 19990715

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PATENTANWALTSBUERO JEAN HUNZIKER

Ref country code: CH

Ref legal event code: EP

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

Effective date: 19990708

REF Corresponds to:

Ref document number: 59506326

Country of ref document: DE

Date of ref document: 19990812

ITF It: translation for a ep patent filed
ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000327

Year of fee payment: 6

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

Ref country code: FR

Payment date: 20000417

Year of fee payment: 6

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

Ref country code: AT

Payment date: 20000420

Year of fee payment: 6

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
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: 20010407

Ref country code: AT

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

Effective date: 20010407

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

Ref country code: SE

Payment date: 20010413

Year of fee payment: 7

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: 20010430

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

Effective date: 20010407

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: SE

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

Effective date: 20020408

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

Ref country code: CH

Payment date: 20020430

Year of fee payment: 8

EUG Se: european patent has lapsed

Ref document number: 95105308.1

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: 20030430

Ref country code: CH

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

Effective date: 20030430

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: 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: 20050407

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

Ref country code: DE

Payment date: 20120426

Year of fee payment: 18

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: 20131101

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59506326

Country of ref document: DE

Effective date: 20131101