EP0296104A1 - Servo-amplificateur linéaire hydraulique - Google Patents

Servo-amplificateur linéaire hydraulique Download PDF

Info

Publication number
EP0296104A1
EP0296104A1 EP88810364A EP88810364A EP0296104A1 EP 0296104 A1 EP0296104 A1 EP 0296104A1 EP 88810364 A EP88810364 A EP 88810364A EP 88810364 A EP88810364 A EP 88810364A EP 0296104 A1 EP0296104 A1 EP 0296104A1
Authority
EP
European Patent Office
Prior art keywords
piston
servo amplifier
rod
amplifier according
piston rod
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
EP88810364A
Other languages
German (de)
English (en)
Other versions
EP0296104B1 (fr
Inventor
Karel Hampejs
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.)
Schweizerische Industrie Gesellschaft
Original Assignee
Schweizerische Industrie Gesellschaft
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 Schweizerische Industrie Gesellschaft filed Critical Schweizerische Industrie Gesellschaft
Publication of EP0296104A1 publication Critical patent/EP0296104A1/fr
Application granted granted Critical
Publication of EP0296104B1 publication Critical patent/EP0296104B1/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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage

Definitions

  • a hydraulic servo amplifier according to the preamble of claim 1 is known from EP-A-88'017. This servo amplifier is particularly suitable for small strokes and relatively low output powers.
  • a piston In a housing with a cylindrical first bore, a piston is supported with a piston rod that projects beyond the housing on one side.
  • a control slide with an actuating rod is guided in a second, coaxial bore in the piston rod. This projects beyond the housing on the other side and is actuated by an electric motor, for example a stepper motor.
  • a pressure connection is connected to the first cylinder chamber on the piston rod side.
  • the control slide controls the flow of hydraulic fluid from the first cylinder chamber into the piston-side cylinder chamber and from there to a return connection via control edges.
  • the piston follows the movement of the control spool.
  • the ratio of the maximum flow cross is cut limited over the control edges to the piston surface.
  • the hydraulic fluid flows to and from the control edges via relatively narrow channels. This limits the adjustment speed of the known device.
  • the object of the present invention is to design a hydraulic servo amplifier in such a way that it achieves very high adjustment speeds. This object is achieved by the characterizing features of claim 1.
  • This design makes it possible to avoid all channels restricting the inflow or outflow of the hydraulic fluid via the control edges. This enables extremely high adjustment speeds to be achieved.
  • the two effective piston surfaces can be chosen arbitrarily in relation to the maximum opening cross section of the control edges, so that the adjustment speed can be increased further.
  • small and therefore responsive pilot motors can be used because the mass to be accelerated directly by the pilot motor can be kept to a minimum.
  • FIGS. 1 to 4 has a housing 1 with an axial bore 2.
  • a piston 3 is displaceably guided.
  • the piston 3 is connected in one piece to a coaxial piston rod 4.
  • a section 5 of the piston rod 4 is guided in a bore 6 of a housing cover 7 and sealed by a sealing ring 8.
  • the section 5 carries a threaded pin 9 for attachment to a member to be actuated.
  • a first cylinder space 14 is formed between the cover 7, the section 5, the piston 3 and the bore 2. This opens into an enlarged housing bore 15 adjacent to the cover 7.
  • the bore 15 communicates with a pressure connection 16 for connecting a pressure oil source P.
  • a return space 22 is formed between the piston 3, a second housing cover 20, a second section 21 of the piston rod 4 and the bore 2.
  • the space 22 opens into a likewise enlarged housing bore 23 adjacent to the cover 20.
  • the bore 23 communicates with a return connection 24 for connection to a return line R.
  • the piston rod 4 has a coaxial bore 28 in which a control slide 29 is longitudinally displaceable.
  • the control slide 29 is designed as a hollow cylinder with a wall 30 and an end wall 32 located in section 5 and broken through by bores 31.
  • the hollow cylinder is open against the section 21 of the piston rod 4.
  • the slide 29 is firmly seated on an actuating rod 33.
  • the rod 33 is guided through a bore 34 through the cover 20 and sealed with a sealing ring 35.
  • the rod 33 penetrates an auxiliary piston 39 which is displaceably guided in an enlarged, coaxial bore 38.
  • the auxiliary piston 39 closes the end of the second cylinder space 40 formed by the bores 28, 38 and lies loosely on the cover 20.
  • it has an enlarged bore 41 on the side facing away from the space 40, which communicates with the return space 22 via radial grooves 42.
  • the slide 29 there are four radially directed, evenly distributed windows 46 in the wall 30 which are rectangular in outline recessed.
  • the control edges 50, 51 each lie in a radial plane.
  • three radial openings 52, 53, each with a rectangular outline, are also provided in both sections 5, 21 adjacent to the piston 3.
  • the control edges 56, 57 are also each in a radial plane and have approximately the same distance from one another as that Control edges 50, 51.
  • the control edges 50, 51, 56, 57 extend over most of the circumference of the outer surface 49 or the bore 28.
  • a toothed rack 68 is screwed onto the end of the actuating rod 33 which projects beyond the cover 20. This supports descends on a roller 69 and is in engagement with a pinion 70, which is seated on the output shaft 71 of an electric stepping motor 72.
  • the servo amplifier described operates as follows: In the idle state shown in FIG. 1, the control slide 29 is held in one position by the rod 33. The piston 3 moves until its control edges 56, 57 with the control edges 50, 51 of the control slide 29 are such that the product of the piston ring surface F 1, formed by the bores 2, 6, times the pressure P is in equilibrium with the product of the piston ring surface F2, formed by bore 38 and the rod 33 times the pressure P1 in space 40 (plus any effect of the return pressure R, plus an external force acting on the piston rod 4). If the actuating rod 33 and thus the control slide 29 is now shifted to the right (FIG.
  • the gap between the control edges 50 and 56 opens and pressure oil flows from the space 14 through the windows 45 into the second cylinder space 40 and thus pushes the Piston 3 with the piston rod 4 also to the right.
  • the piston 3 follows the control slide 29 until the rest state described above has been restored. If the control slide 29 is moved to the left, the control opening formed by the control edges 51, 57 opens and the hydraulic fluid flows from the cylinder space 40 to the return connection 24.
  • the opening cross section is formed from the distance between the control edges 50, 56 or 51, 57 and the circumference of the outer surface 49 in relation to the surface of the auxiliary piston 39 and the oil flow through the control edges is not hindered and limited by any narrow channels, so that the achievable piston speed is high.
  • the effective piston surfaces F1 and F2 can be chosen arbitrarily small in relation to the cross section of the control slide 29. Since there are no oil columns of small cross-section to be accelerated, the inertia effects of the accelerated oil quantities are negligible compared to the mass of the piston rod 4. Because the windows 46 and the openings 52, 53 are evenly distributed over the circumference, no radial forces arise on the control slide 29 during operation.
  • the rotary position of the control slide 29 relative to the piston rod 4 is irrelevant.
  • the sealing of the actuating rod 33 is only necessary against the return pressure and can therefore be carried out with low friction.
  • the actuating rod 33 is thin and the control slide 29 designed as a hollow cylinder is thin-walled, so that only small masses can be accelerated by the drive. Therefore, a small stepper motor with high dynamics can be used.
  • the servo amplifier described is particularly suitable for applications in which very high adjustment speeds are necessary and / or changeable strokes, with moderate power transmission.
  • Typical areas of application are, for example, in textile machines for the adjustment of the needle bars or needle bars, in embroidery machines for the needle or embroidery frame movement, in assembly or packaging machines, for example for the Equipping (of printed circuit boards) Plug (from brushes) Labeling, marking Dosing Pushing, pulling, bending, folding Shaking, vibrating, stuffing Pliers or lever actuation in machine tools and devices, for example for Embossing, pressing, shaping, punching, drawing Hammering, riveting, fine forging Nibbling, latching, quick punching Cut impact damper and hold-down device on punch presses Control or drive of the injection valves in injection molding machines Spring manufacturing (feed and deformation) Materials testing machine (vibration test, endurance test) as a control or drive element, for example Injection pumps in internal combustion engines Dosing pumps in mixing plants Mixing valves Quick couplings Hydraulic proportional valves Hydraulic pump
  • the drive of the actuating rod 33 is a screw gear, in contrast to the embodiment according to FIG. 1.
  • a threaded sleeve 77 is fastened, which is screwed onto a threaded pin 78 screwed onto the actuating rod 33.
  • the pin 78 carries a flange 79 which is secured against rotation by a pin 80 fixed to the housing.
  • a spring 81 loads the flange 79 so that the screw gear is free of play.
  • the auxiliary piston is formed by the second section 21 of the piston rod 4, which slides in a bore 84 of the housing 1.
  • the first cylinder space 14, which is connected to the pressure connection 16, is passed through here the bore 84 formed.
  • the annular surface F2 formed between the bores 2 and 6 of the second cylinder chamber 40 is larger than the effective surface F1 of the first cylinder chamber 14.
  • the control slide 29, which in turn is designed as a hollow cylinder, has windows 46 which open into a circumferential groove 85 of the control slide 29.
  • the end wall 47 of this groove 85 facing the piston 3 forms, together with the outer surface 49, the one control edge 50 assigned to the control slide 29.
  • the other control edge 51 of the control slide 29 is formed by the end wall 48 facing the piston 3 of a further groove 86 of the control slide 29.
  • the two control edges 56, 57 assigned to the piston rod 4 are formed by the two end faces 54, 55 of a circumferential groove 87 of the piston rod 4 and the bore 28.
  • the groove 86 is connected to the return chamber 22 via radial openings 53 in section 21 of the piston rod 4.
  • the groove 87 communicates with the cylinder chamber 40 via openings 52 in the piston rod 4. Otherwise, the structure and the mode of operation of the embodiment according to FIG. 6 are analogous to each according to FIG. 1.
  • FIG. 7 is analogous to that according to FIG. 6, but here the pressure connection 16 and the return connection 24 are interchanged. Accordingly, the first cylinder chamber 14, which is acted upon by feed pressure, is arranged with the effective area F 1, here on the left of the piston 3. The openings 52, 53 cross each other and therefore each extend over less than half the circumference. Since the entire actuating rod 33 is acted upon by return pressure, the relief by a chamber 61 acted upon by return pressure is superfluous.
  • FIG. 8 is constructed analogously to that according to FIG. 1, except that here the auxiliary piston is formed by a second flange 90 on section 21 of the piston rod 4.
  • the flange 90 slides in the same bore 2 of the housing 1 as the piston 3.
  • the effective area F2 of the second cylinder space 40 corresponds to the cross section of the bore 2, minus the cross section of the actuating rod 33.
  • the diameter of the flange 90 to be chosen smaller than the diameter of the piston 3, that is to say the bore 2 as in the exemplary embodiment according to FIG. 7.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP88810364A 1987-06-16 1988-06-03 Servo-amplificateur linéaire hydraulique Expired - Lifetime EP0296104B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH226587 1987-06-16
CH2265/87 1987-06-16

Publications (2)

Publication Number Publication Date
EP0296104A1 true EP0296104A1 (fr) 1988-12-21
EP0296104B1 EP0296104B1 (fr) 1990-10-03

Family

ID=4229726

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88810364A Expired - Lifetime EP0296104B1 (fr) 1987-06-16 1988-06-03 Servo-amplificateur linéaire hydraulique

Country Status (3)

Country Link
US (1) US4907492A (fr)
EP (1) EP0296104B1 (fr)
DE (1) DE3860735D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991014103A1 (fr) * 1990-03-10 1991-09-19 Schnuerle Friedhelm Ensemble cylindre-piston pneumatique ou hydraulique a servocommande
DE19757157C2 (de) * 1997-12-20 2003-06-12 Ipm Ingenieur Und Projektman G Hydraulischer Linearantrieb
DE102007054774B3 (de) * 2007-11-16 2008-09-25 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulischer Verstärker
WO2009062650A2 (fr) 2007-11-15 2009-05-22 Hoerbiger Automatisierungstechnik Holding Gmbh Machine à estamper à commande numérique par ordinateur
WO2009062649A2 (fr) * 2007-11-15 2009-05-22 Hoerbiger Automatisierungstechnik Holding Gmbh Amplificateur électro-hydraulique
EP2116715A1 (fr) * 2006-12-28 2009-11-11 Komatsu Ltd Dispositif de soupape de recyclage des gaz d'échappement
WO2010084043A1 (fr) * 2009-01-23 2010-07-29 Voith Patent Gmbh Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6182925B1 (en) * 1999-03-30 2001-02-06 The Boeing Company Semi-levered landing gear and auxiliary strut therefor
US8639666B2 (en) * 2008-09-05 2014-01-28 Cast Group Of Companies Inc. System and method for real-time environment tracking and coordination
DE102009011441B4 (de) 2009-02-25 2012-11-29 Voith Patent Gmbh Hydraulikantrieb
CN105020190A (zh) * 2014-04-30 2015-11-04 张凯 阀芯内直动导控机构及流体控制阀

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB654416A (en) * 1948-02-23 1951-06-20 British Messier Ltd Improvements in or relating to fluid-operated servo-motors and jacks
US3757640A (en) * 1971-12-01 1973-09-11 Avco Corp Simplified follower servomechanism
DE2211994A1 (de) * 1972-03-09 1973-09-13 Ronald Arthur Foley Hydraulische schaltvorrichtung
EP0088017A2 (fr) * 1982-02-26 1983-09-07 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Dispositif de distribution hydraulique à tiroir

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR562326A (fr) * 1922-03-13 1923-11-08 Dispositif de servo-moteur
US1533767A (en) * 1924-09-12 1925-04-14 Westinghouse Electric & Mfg Co Governor
US1732813A (en) * 1926-12-16 1929-10-22 Westinghouse Electric & Mfg Co Fluid-pressure governor
US2738770A (en) * 1952-11-14 1956-03-20 Int Harvester Co Hydraulically lockable ram and control therefor
FR1117743A (fr) * 1954-12-20 1956-05-25 Mécanisme de servo-commande hydraulique pour direction de véhicule automobile et autres applications
FR1163246A (fr) * 1956-12-11 1958-09-23 Creusot Forges Ateliers Télécommande hydraulique asservie
US3015310A (en) * 1957-07-12 1962-01-02 Faisandier Jacques Hollow piston jack and control valve
US3076442A (en) * 1959-11-10 1963-02-05 Vevey Atel Const Mec Hydraulic relay
US3053052A (en) * 1961-03-24 1962-09-11 Garrison Fluid operated booster valve
US3228305A (en) * 1964-03-19 1966-01-11 Chandler Evans Inc Electro-pneumatic digital positioner
US3961561A (en) * 1971-11-08 1976-06-08 Applied Power Inc. Proportional force amplifier
US3768369A (en) * 1971-12-01 1973-10-30 Applied Power Inc Force release device
US3892164A (en) * 1973-12-19 1975-07-01 Mimik Limited Servo control for machine tools
US4085920A (en) * 1976-11-15 1978-04-25 Caterpillar Tractor Co. Pilot control valve with servo means

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB654416A (en) * 1948-02-23 1951-06-20 British Messier Ltd Improvements in or relating to fluid-operated servo-motors and jacks
US3757640A (en) * 1971-12-01 1973-09-11 Avco Corp Simplified follower servomechanism
DE2211994A1 (de) * 1972-03-09 1973-09-13 Ronald Arthur Foley Hydraulische schaltvorrichtung
EP0088017A2 (fr) * 1982-02-26 1983-09-07 COMPAGNIE PARISIENNE D'OUTILLAGE A AIR COMPRIME Société anonyme dite: Dispositif de distribution hydraulique à tiroir

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991014103A1 (fr) * 1990-03-10 1991-09-19 Schnuerle Friedhelm Ensemble cylindre-piston pneumatique ou hydraulique a servocommande
DE19757157C2 (de) * 1997-12-20 2003-06-12 Ipm Ingenieur Und Projektman G Hydraulischer Linearantrieb
EP2116715A1 (fr) * 2006-12-28 2009-11-11 Komatsu Ltd Dispositif de soupape de recyclage des gaz d'échappement
US8113184B2 (en) 2006-12-28 2012-02-14 Komatsu Ltd. EGR valve device
EP2116715A4 (fr) * 2006-12-28 2011-08-17 Komatsu Mfg Co Ltd Dispositif de soupape de recyclage des gaz d'échappement
WO2009062650A3 (fr) * 2007-11-15 2010-06-24 Hoerbiger Automatisierungstechnik Holding Gmbh Machine à estamper à commande numérique par ordinateur
DE202008017285U1 (de) 2007-11-15 2009-06-18 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulischer Verstärker
WO2009062649A3 (fr) * 2007-11-15 2009-11-12 Hoerbiger Automatisierungstechnik Holding Gmbh Amplificateur électro-hydraulique
WO2009062649A2 (fr) * 2007-11-15 2009-05-22 Hoerbiger Automatisierungstechnik Holding Gmbh Amplificateur électro-hydraulique
CN102016329A (zh) * 2007-11-15 2011-04-13 贺尔碧格自动化技术控股股份有限公司 Cnc冲压机
WO2009062650A2 (fr) 2007-11-15 2009-05-22 Hoerbiger Automatisierungstechnik Holding Gmbh Machine à estamper à commande numérique par ordinateur
US8074557B2 (en) 2007-11-15 2011-12-13 Hoerbiger Automatisierungstechnik Holding Gmbh Electrohydraulic booster
CN102016329B (zh) * 2007-11-15 2014-07-09 贺尔碧格自动化技术控股股份有限公司 Cnc冲压机
DE102007054774B3 (de) * 2007-11-16 2008-09-25 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulischer Verstärker
WO2010084043A1 (fr) * 2009-01-23 2010-07-29 Voith Patent Gmbh Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression
US9121419B2 (en) 2009-01-23 2015-09-01 Voith Patent Gmbh Hydraulic drive device having two pressure chambers and method for operating a hydraulic drive device having two pressure chambers

Also Published As

Publication number Publication date
DE3860735D1 (de) 1990-11-08
EP0296104B1 (fr) 1990-10-03
US4907492A (en) 1990-03-13

Similar Documents

Publication Publication Date Title
DE2808810C2 (de) Stufenlos einstellbares Kegelscheibenumschlingungsgetriebe
DD147269A5 (de) Verteilereinspritzpumpe fuer verbrennungsmotoren
EP0296104B1 (fr) Servo-amplificateur linéaire hydraulique
CH656965A5 (de) Druckregelventil.
EP1217209B1 (fr) Dispositif de commande pour une machine hydrostatique à débit variable
DE2914334A1 (de) Stroemungsmittel-betaetigter stelltrieb
DE2322818A1 (de) Vorrichtung zur erzeugung eines lastund drehzahlabhaengigen schaltdruckes in fahrzeuggetrieben
EP1219831A2 (fr) Dispositif de réglage de la course pour une machine hydrostatique à débit variable
DE2625909A1 (de) Fluidischer verstaerker
DE2265348C3 (de) Druckmittelbetriebener Servomotor
DE2236589B2 (de) Stufenlos einstellbares Reibungsgetriebe
DE19506184A1 (de) Reziprozierender Kolbenmotor, funktionierend mit Druckmedium
DE3226809C2 (fr)
DE2625063A1 (de) Steuervorrichtung zur geschwindigkeitsregelung von pneumatischen und/oder hydraulischen arbeitskolben
DE1037793B (de) Verteiler fuer eine unter Druck gehaltene Fluessigkeit
DE19757157C2 (de) Hydraulischer Linearantrieb
DE1929483B2 (de) Fliehkraftregler
DE2223964B2 (de) Servoverstelleinrichtung
DE2825790C2 (de) Stellmotor mit Nachlaufsteuerung
DE2848108C2 (de) Papierschneidemaschine oder ähnliche Schneidemaschine mit einem Preßbalken zum Andeuten
DE2538203C2 (de) Mechanismus zur Hublängenveränderung bei einem Getriebe zur Umwandlung einer Drehbewegung in eine hin- und hergehende Bewegung
DE2841083C2 (fr)
EP1045965B1 (fr) Pompe d'injection de carburant
DE19806980C2 (de) Zweistufiger hydraulischer Kurzhublinearantrieb
DE19858758C1 (de) Vorrichtung und Verfahren zur Hubübertragung

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

17P Request for examination filed

Effective date: 19881125

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): CH DE FR GB IT LI

REF Corresponds to:

Ref document number: 3860735

Country of ref document: DE

Date of ref document: 19901108

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

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

Ref country code: FR

Payment date: 19930512

Year of fee payment: 6

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

Ref country code: CH

Payment date: 19930514

Year of fee payment: 6

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

Ref country code: GB

Payment date: 19930519

Year of fee payment: 6

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

Ref country code: DE

Payment date: 19930524

Year of fee payment: 6

ITTA It: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19940603

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

Ref country code: LI

Effective date: 19940630

Ref country code: CH

Effective date: 19940630

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

Effective date: 19940603

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

Ref country code: FR

Effective date: 19950228

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: DE

Effective date: 19950301

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

ET Fr: translation filed
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: 20050603