EP0287434B1 - Differentialhydraulischer Kraftzylinder, mit Dämpfungsvorrichtung,zur Steuerung von Leistungsschaltern - Google Patents

Differentialhydraulischer Kraftzylinder, mit Dämpfungsvorrichtung,zur Steuerung von Leistungsschaltern Download PDF

Info

Publication number
EP0287434B1
EP0287434B1 EP88400826A EP88400826A EP0287434B1 EP 0287434 B1 EP0287434 B1 EP 0287434B1 EP 88400826 A EP88400826 A EP 88400826A EP 88400826 A EP88400826 A EP 88400826A EP 0287434 B1 EP0287434 B1 EP 0287434B1
Authority
EP
European Patent Office
Prior art keywords
piston
jack
ring
damping
cylinder
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
EP88400826A
Other languages
English (en)
French (fr)
Other versions
EP0287434A1 (de
Inventor
Claude Alain Gratzmuller
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 AT88400826T priority Critical patent/ATE85459T1/de
Publication of EP0287434A1 publication Critical patent/EP0287434A1/de
Application granted granted Critical
Publication of EP0287434B1 publication Critical patent/EP0287434B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F3/00—Devices, e.g. jacks, adapted for uninterrupted lifting of loads
    • B66F3/24—Devices, e.g. jacks, adapted for uninterrupted lifting of loads fluid-pressure operated
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/222—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which throttles the main fluid outlet as the piston approaches its end position
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34—Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic

Definitions

  • the present invention relates to a differential hydraulic cylinder for controlling electric circuit breakers, of the type in which the annular chamber of the cylinder, defined by the interior surface of the cylinder of the cylinder and by the exterior surface of the outgoing rod of the piston, is permanently connected. to a high pressure hydraulic source.
  • the outgoing rod of the jack is coupled to the movable contact of the circuit breaker and a supply / bleed orifice, formed in the bottom of the main chamber of the jack, can be selectively connected to said high pressure source (position “Supply”) to push the piston, or to a low pressure tank (“Purge” position) to let the piston return to its initial position under the effect of the high pressure P prevailing in the annular chamber.
  • the first maneuver brings out the piston rod and brings the circuit breaker into the latched or closed position, while the second maneuver brings the rod back into the cylinder and brings the circuit breaker into the tripped or open position.
  • differential cylinders for this application, presents constructive difficulties, in particular because they must guarantee a permanent and absolute tightness, for very long periods, despite the very high hydraulic operating pressures P, of the order of 300 to 400 bar.
  • These jacks must therefore include at least, as shown in the aforementioned prior patent, a first seal at the passage of the outgoing rod through the bottom of the cylinder and a second seal on the piston.
  • This second packing preferably of the "spring packing” type, if one wishes to obtain a perfect seal, must withstand severe operating conditions and is therefore of delicate construction.
  • Damping systems are already known for hydraulic cylinders comprising a ring mounted floating in the bottom of the cylinder of the cylinder which is engaged in an extension, or damping stud, substantially frustoconical, carried by the piston.
  • an extension, or damping stud substantially frustoconical, carried by the piston.
  • the section of the annular passage located between the inner surface of the damping ring and the aforementioned extension of the piston decreases, which produces a gradual rolling of the oil contained in the chamber. of the cylinder, between the piston and the bottom of the cylinder carrying the damping ring. This oil rolling dampens the end of the piston stroke.
  • the object of the present invention is to remedy these drawbacks and to allow the production of a differential cylinder, with a ring damping system, of simple construction and of more reliable operation than in the past, the invention applying to a cylinder.
  • a cylinder of the type described in the abovementioned French patent application No. 87.04.134, that is to say, wherein the piston is combined with a valve-closing valve of the supply / drain orifice of the chamber main actuator, the piston positively actuating the valve of said valve to close said orifice at the end of the triggering stroke of the piston, and in which the piston is devoid of any seal.
  • the shut-off valve is constituted by a damping ring mounted floating in the bottom of the cylinder of the jack and surrounding the supply / bleed orifice, said ring having a substantially cylindrical inner surface with which comes cooperate an extension or damping stud, substantially conical, carried by the underside of the piston, to perform an oil rolling between said surface of the ring and said extension.
  • Said floating ring carries, on its upper annular surface, a first protruding circular lip against which the seal faces the lower face of the piston, at the end of the trigger stroke, and carries, on its lower annular surface, a second protruding circular lip which comes to bear in leaktight manner against the bottom of the cylinder of the jack, around the feed / bleed orifice, when the ring is pushed back by the piston, at the end of the triggering stroke.
  • the floating ring thus forms a double sealing valve, on the one hand between the piston and the ring and, on the other hand, between the ring and the cylinder bottom.
  • the differential actuator shown in FIG 1 is of the type described in the abovementioned French patent application No. 87.04.134.
  • a cylinder 2 preferably from the foundry in a foundry part 4, in which a piston 6 slides, devoid of a gasket.
  • the piston rod 6 is coupled to the movable contact of an electric circuit breaker not shown.
  • the piston 6 divides the interior volume of the cylinder 2 into an annular chamber 10 (above the piston) and a main chamber 12 (below the piston).
  • the bottom of the main chamber, or bottom of the cylinder, is constituted by a screwed stopper 14 in the center of which is formed a supply / bleed orifice 16.
  • the annular chamber 10 is placed in permanent communication with an oleopneumatic accumulator 20 connected to an orifice 21 of the cylinder.
  • the feed / purge orifice 16 can be selectively placed in communication, via a 3-way valve 26, or with the accumulator 20 ("feed" position) through pipes 18-28-24 , or with a low pressure tank 32 ("purge” position) through pipes 24-30.
  • the pipe 18 is a pipe of large section, preferably from the foundry in the cylinder block 4, which ensures a high-speed oil transfer between the two chambers 10 and 12 of the jack.
  • the outgoing rod 8 passes through the upper plug 34 through a seal 36.
  • the piston 6 carries first and second male damping members, of substantially or partially frustoconical shape or with sections storied.
  • the first damping member 38, above the piston 6, cooperates with a damping ring 40, similar to that described in the patent cited above, to damp the high end of stroke of the piston 6.
  • the second damping member 42 which constitutes an extension of the piston 6, below the latter, cooperates with the ring 44 forming both a damper and a double sealing valve, according to the damping system of the present invention.
  • the damping system follow the invention comprises the ring 44 which is mounted floating in a housing 46 where it is retained by the annular face upper part of the plug 14 and by a shoulder 48 cut in the cylinder 2.
  • a clearance is provided in the housing so that the ring can move radially in order to center freely on the damping extension 42 of the piston 6.
  • Such a floating mounting of a damping ring is well known and it allows an annular oil rolling passage to be obtained between the inner surface 50 of the ring 44 (see figure 3) and the extension 42 of the piston 6, producing an always reproducible damping.
  • the ring has, on its upper annular surface 52 a first projecting circular lip 53 and on its lower surface 56 a second identical lip 58.
  • the upper lip 54 forms, in cooperation with the lower annular face 60 of the piston 6, a tight seal in the end-of-travel position of the piston, while the lower lip 58 forms, in cooperation with the upper annular face 62 of the plug 14, a second waterproof seal.
  • the damping ring 44 plays the role of a double valve ensuring the tight closure of the feed / bleed orifice 16 when the piston is in its end-of-travel position, this same ring constituting the end-of-travel stop of the piston after damping.
  • the ring 44 is made of a harder metal than the piston 6 and that the plug 14 against which the lips 54, 58 bear. Thanks to the fact that, in the low position of the piston, the guides of the piston itself and of the piston rod 8 are the furthest apart, good parallelism is always obtained between the lower annular surface 60 of the piston 6 and the top of the circular lip 54, which ensures a good seal.
  • FIG. 2 shows the surfaces (or sections) S1 S2, and s respectively of the piston 6, the lips 54, 58 and the outgoing rod 8.
  • This figure shows the end-of-travel position for triggering the piston 6, the latter being in abutment against the ring 44.
  • the feed / purge orifice is in the purge, that is to say a low pressure P0 substantially equal to atmospheric pressure, while in the annular chamber 10 of the cylinder reigns the permanent high pressure P1 supplied by the accumulator 20 ( Figure 1).
  • the oil at pressure P1 contained in the chamber 10 above the cylinder leaks between the cylindrical outer surface 64 of the piston 6 and cylinder 2.
  • the pressure P1 is therefore established above and below the ring 44 in its outer zone limited by the lips 54, 58, said lips forming, with the facing surfaces 60-62, a pressure tight barrier P1.
  • the support force F1 is of the order of 0.3 (S2xP1)
  • the service pressure P1 in the hydraulic circuit breaker controls being of the order of 300 to 400 bar and the section S2 of the valve being able to be of the order of 10 to 20 cm2 in the most common applications, we see that the permanent closing force exerted on the valve can be very high, several tons, and ensures an absolute permanent seal, especially since the hard metal lips 54-58 imprint their imprint in the less hard metal of the piston 6 and of the plug 14.
  • the orifice 16 is supplied under the high pressure P1 (supply position - see figure 1, valve 24).
  • P1 supply position - see figure 1, valve 24.
  • the pressure therefore rapidly passes from the pressure P0 to the pressure P1: in the orifice 16; in the annular gap between the facing surfaces 50 and 68 of the ring 44 and the damping stud 42; then in space 70, below the piston 6, to the lip 54.
  • P2 P1 (1 -s / S2) that is, in the preferred case where S2 is of the order of 1.5 times s , P2 is of the order of 0.33 P1
  • these recharging means essentially comprise a non-return valve constituted by a ball 72 and a seat 74, this seat being cut from a socket 76 screwed into a bore 78 hollowed out in the stud of 'Damping 42.
  • One or more diametric holes 80 communicate the space located above the ball 72 with the outer surface 68 of the damping stud and, therefore, with the space 70 to be replenished.
  • the high damping pressure produced below the piston keeps the non-return valve 72-74 closed by pressing the ball 72 on its seat 74, so well that the oil can escape only by rolling between the stud 42 and the ring 44.
  • the non-return valve 72-74 need not be sealed since the same low pressure P0 prevails in the interval 70 and in the feed / drain hole (which is then in the drain). The non-return valve therefore has no severe production conditions.
  • External chamfers 84-84 ⁇ can also be provided to avoid any risk of the floating ring catching in its housing.
  • the section S3 of the damping pin 42 is smaller than the section S2 of the lips 54, 58 of the valve, but it is greater than the section s of the outgoing rod, by an amount such that the difference in section S3 - s is sufficient for the piston 6 to surely go to the bottom of the stroke (stroke of trigger), despite the leaks between the piston and the cylinder, when tests of slow operation are performed at low flow.
  • a valve surface S2 of the order of 50% greater than the section s of the outgoing rod is chosen
  • a section S3 is chosen for the damping stud of the order of 30% greater than the section s of the outgoing rod.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Structural Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Vehicle Body Suspensions (AREA)
  • Sealing Devices (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Servomotors (AREA)
  • Braking Arrangements (AREA)
  • Braking Systems And Boosters (AREA)
  • Regulating Braking Force (AREA)
  • Retarders (AREA)

Claims (10)

  1. Differentialhydraulische Zylindereinrichtung zur Öl-Luft-Druck-Steuerung eines elektrischen Schaltschützes, mit einem Zylinder (2), einem Kolben (6) und einer nach außen führenden Stange (8) des Kolbens (6), die im Zylinder eine Ringkammer (10) auf der einen Seite des Kolbens und eine Hauptkammer (12) auf der anderen Seite des Kolbens bilden, wobei die genannte, nach außen führende Stange (8) an dem beweglichen Kontakt des Schaltschützes angekoppelt ist, die genannte Ringkammer (10) ständig mit einer Quelle (20) für hydraulisches Strömungsmittel unter hohem Druck verbunden ist, und die genannte Hauptkammer (12) am entsprechenden Boden (14) des Zylinders eine Einspeise-/Ablauföffnung (16) der genannten Kammer (12) aufweist und der genannte Kolben auf seiner der Hauptkammer (12) zugewandten Fläche (60) einen Dämpfungsansatz (42) aufweist, der dazu eingerichtet ist, mit einem Dämpfungsring (44) zusammenzuwirken, der schwimmend rund um die Einspeise-/Ablauföffnung (16) angebracht ist, und wobei die genannte Zylindereinrichtung dadurch gekennzeichnet ist,
    - daß sein Kolben (6) der Innenfläche des Zylinders (2) gegenüberliegend keine Dichtungsanordnung aufweist;
    - daß der genannte Ring (44) einen Endanschlag für den Bewegungsweg des Kolbens (6) bildet; und
    - daß der genannte Ring auf seiner radialen, der Hauptkammer (12) zugewandten, kreisringförmigen Fläche eine erste ringförmige Dichtungszone (54) und auf seiner radialen, gegenüberliegenden, kreisringförmigen Fläche eine zweite ringförmige Dichtungszone (58) aufweist, wobei die genannte erste und zweite Zone (54, 58) dazu eingerichtet sind, eine erste und zweite Ventilklappe zu bilden, die mit der oben genannten Fläche (60) des Kolbens bzw. dem Boden (14) des Zylinders abdichtet, wenn sich der Kolben am Ende seines Bewegungsweges befindet.
  2. Zylindereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die erste und zweite, ringförmige Dichtungszone von einer ersten (54) und einer zweiten (58), kreisförmigen Dichtungslippe gebildet sind, die jeweils auf den beiden kreisringförmigen Radialflächen des Rings (44) übersteht und mit dem genannten Ring ein einziges Bauteil bildet.
  3. Zylindereinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Ring (44) und mithin die Lippen (54, 58) aus einem Metall hergestellt ist bzw. sind, das härter ist als das des Kolbens (6) und das des Bodens des Zylinders (14).
  4. Zylindereinrichtung nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, daß die Oberfläche S₂, die von den Lippen (54, 58) begrenzt ist, größer ist als der Querschnitt s der nach außen führenden Stange (8), und zwar bevorzugt in der Größenordnung von 50% größer.
  5. Zylindereinrichtung nach Anspruch 4, dadurch gekennzeichnet, daß die erste Lippe (54) und die zweite Lippe (58) eine identische Fläche S₂ begrenzen.
  6. Zylindereinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß er mit Mitteln zur Wiederbeaufschlagung mit Hochdruck-Strömungsmittel in den Ringräumen (70) versehen ist, die zwischen der Fläche (60) des Kolbens und der gegenüberliegenden Fläche (52) des Ringes (44) gelegen sind.
  7. Zylindereinrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die Mittel zur Wiederbeaufschlagung ein Rückschlagventil (72-74) aufweisen, das im Dämpfungsansatz (42) des Kolbens (6) sitzt, und radiale Kanäle (80), die den genannten Ansatz (42) durchsetzen.
  8. Zylindereinrichtung nach Anspruch 7, dadurch gekennzeichnet, daß die Mittel zur Wiederbeaufschlagung eine Fase (82) aufweisen, die am Innenumfang (50) des Ringes (44) im wesentlichen den Kanälen (80) gegenüberliegen, eingebracht ist.
  9. Zylindereinrichtung nach Anspruch 8, dadurch gekennzeichnet, daß eine zweite Fase (82') in den Ring (44) symmetrisch zur Fase (82) eingebracht ist, dank deren der genannte Ring umdreh-symmetrisch ist.
  10. Zylindereinrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß der Querschnitt S₃ des Dämpfungsansatzes (42) größer ist als der Querschnitt s der nach außen führenden Stange (8).
EP88400826A 1987-04-13 1988-04-06 Differentialhydraulischer Kraftzylinder, mit Dämpfungsvorrichtung,zur Steuerung von Leistungsschaltern Expired - Lifetime EP0287434B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88400826T ATE85459T1 (de) 1987-04-13 1988-04-06 Differentialhydraulischer kraftzylinder, mit daempfungsvorrichtung,zur steuerung von leistungsschaltern.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8705198A FR2613785B1 (fr) 1987-04-13 1987-04-13 Verin hydraulique differentiel, avec systeme d'amortissement, pour la commande de disjoncteurs electriques
FR8705198 1987-04-13

Publications (2)

Publication Number Publication Date
EP0287434A1 EP0287434A1 (de) 1988-10-19
EP0287434B1 true EP0287434B1 (de) 1993-02-03

Family

ID=9350052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88400826A Expired - Lifetime EP0287434B1 (de) 1987-04-13 1988-04-06 Differentialhydraulischer Kraftzylinder, mit Dämpfungsvorrichtung,zur Steuerung von Leistungsschaltern

Country Status (20)

Country Link
US (1) US4807514A (de)
EP (1) EP0287434B1 (de)
JP (1) JPS63262396A (de)
KR (1) KR920004481B1 (de)
CN (1) CN1010243B (de)
AT (1) ATE85459T1 (de)
AU (1) AU594292B2 (de)
BR (1) BR8801717A (de)
CA (1) CA1287040C (de)
CZ (1) CZ281194B6 (de)
DE (1) DE3878010T2 (de)
ES (1) ES2037853T3 (de)
FI (1) FI91314C (de)
FR (1) FR2613785B1 (de)
HU (1) HU212745B (de)
IN (1) IN170818B (de)
SU (1) SU1600640A3 (de)
UA (1) UA5568A1 (de)
YU (1) YU47412B (de)
ZA (1) ZA882602B (de)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3909424C2 (de) * 1989-03-22 1997-06-05 Walterscheid Gmbh Gkn Schwenkverschraubung
US6286836B1 (en) * 1999-02-02 2001-09-11 American Roller Company Sealed charging port and method of charging for a heat pipe roller
DE29905322U1 (de) * 1999-03-23 1999-06-24 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Hydraulisch entsperrbares Füllventil
IT1312235B1 (it) * 1999-03-29 2002-04-09 Luciano Migliori Dispositivo ammortizzatore per cilindri pneumatici.
US6409180B1 (en) * 2000-04-21 2002-06-25 Perkinelmer, Inc. Metallic seal
US6536327B2 (en) * 2001-06-08 2003-03-25 Festo Corporation Double acting cylinder with integral end position volume chambers
DE102008050674A1 (de) * 2008-10-07 2010-04-08 Abb Technology Ag Hydromechanischer Federspeicherantrieb
DE102011109227B3 (de) 2011-08-03 2012-11-29 Abb Technology Ag Differentialzylinder für einen hydromechanischen Antrieb für elektrische Leistungsschalter
DE102011109210B3 (de) * 2011-08-03 2012-10-11 Abb Technology Ag Differentialzylinder für einen hydromechanischen Antrieb für elektrische Leistungsschalter
CN102936917B (zh) * 2012-11-30 2014-03-12 时寿斌 自动冲水座便器
DE102014202794A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE680031C (de) * 1937-04-14 1939-08-19 Aeg Steuerventil fuer stroemende Medien bei elektrischen Schaltern
NL103618C (de) * 1957-08-26
GB998753A (en) * 1962-12-13 1965-07-21 Parker Hannifin Corp Piston cushion for fluid operated cylinder
DE2027395A1 (de) * 1970-06-04 1971-12-09 Hennecke E Doppelt wirkender druckmittelbeaufschlagter Arbeitszylinder mit Endlagendämpfung
FR2181529B2 (de) * 1972-04-27 1974-07-26 Snecma
FR2181525B1 (de) * 1972-04-27 1976-10-29 Gratzmuller Jean Louis
FR2317532A1 (fr) * 1975-07-07 1977-02-04 Gratzmuller Jean Louis Verin hydraulique a amortisseur incorpore avec realimentation de la chambre d'amortissement
US4065112A (en) * 1976-08-23 1977-12-27 Towmotor Corporation Hydraulic jack cushioning apparatus
DE2712669A1 (de) * 1977-03-23 1978-09-28 Volkswagenwerk Ag Anordnung mit einem pneumatik- zylinder
FR2422848A1 (fr) * 1978-04-14 1979-11-09 Outillage Air Comprime Dispositif d'amortissement et de demarrage de verins
DE2835063A1 (de) * 1978-08-08 1980-02-14 Siemens Ag Hydraulischer antrieb
US4289264A (en) * 1979-03-23 1981-09-15 The United States Of America As Represented By The Secretary Of The Air Force Uniform load piston ring
US4296675A (en) * 1979-07-16 1981-10-27 Aeroquip Corporation Cylinder cushion with contractable ring
JPS5783705A (en) * 1980-11-13 1982-05-25 Hitachi Constr Mach Co Ltd Cushion device for cylinder
SE8101054L (sv) * 1981-02-17 1982-08-18 Vaggeryds Mek Verk Anordning vid endlegesdempning for rorelsen hos kolven med tillhorande kolvstang m fl komponenter i en hydraulcylinder
JPS57195964A (en) * 1981-05-28 1982-12-01 Seiko Epson Corp Gasket
DE3269801D1 (en) * 1981-06-30 1986-04-17 Hitachi Construction Machinery Shock absorbing device for hydraulic cylinder
US4785712A (en) * 1986-05-27 1988-11-22 Mitsubishi Denki Kabushiki Kaisha Hydraulic operating apparatus for electric circuit breaker

Also Published As

Publication number Publication date
YU72188A (en) 1990-04-30
FR2613785A1 (fr) 1988-10-14
CN1010243B (zh) 1990-10-31
KR920004481B1 (ko) 1992-06-05
AU1407988A (en) 1988-10-13
US4807514A (en) 1989-02-28
CN88102072A (zh) 1988-10-26
CS249288A3 (en) 1992-04-15
FI91314C (fi) 1994-06-10
CZ281194B6 (cs) 1996-07-17
ES2037853T3 (es) 1993-07-01
FI881668A (fi) 1988-10-14
HUT52217A (en) 1990-06-28
JPS63262396A (ja) 1988-10-28
IN170818B (de) 1992-05-23
ATE85459T1 (de) 1993-02-15
DE3878010D1 (de) 1993-03-18
BR8801717A (pt) 1988-11-16
FI91314B (fi) 1994-02-28
SU1600640A3 (ru) 1990-10-15
DE3878010T2 (de) 1993-06-03
YU47412B (sh) 1995-03-27
CA1287040C (en) 1991-07-30
EP0287434A1 (de) 1988-10-19
FI881668A0 (fi) 1988-04-11
AU594292B2 (en) 1990-03-01
UA5568A1 (uk) 1994-12-28
ZA882602B (de) 1988-10-03
FR2613785B1 (fr) 1990-11-23
KR880012475A (ko) 1988-11-26
HU212745B (en) 1996-10-28
JPH0536356B2 (de) 1993-05-28

Similar Documents

Publication Publication Date Title
EP0287434B1 (de) Differentialhydraulischer Kraftzylinder, mit Dämpfungsvorrichtung,zur Steuerung von Leistungsschaltern
EP0935715B1 (de) Haltevorrichtung einer hydraulischen arbeitszylinderstange
EP2440806B1 (de) Stossdämpfer und mit solch einem stossdämpfer versehenes fahrwerk
FR3014163A1 (fr) Robinet d'isolement a chambre morte
EP0296936A1 (de) Antriebsvorrichtung zum schnellen und geregelten Trennen von zwei miteinander verbundenen Teilen
EP0493155B1 (de) Ventil und Verfahren zur Hydraulikkreislaufentlüftung
FR2481214A1 (fr) Unite de commande de la pression de freinage pour un systeme de freinage hydraulique
FR3016007A1 (fr) Dispositif d'actionnement d'urgence notamment destine a un ouvrant d'aeronef
EP0070778B1 (de) Steuervorrichtung eines Sicherheitsventils
FR2676414A1 (fr) Servomoteur pneumatique.
FR2676415A1 (fr) Servomoteur pneumatique.
EP0284482B1 (de) Differentialhydraulischer Kraftzylinder zur Steuerung von Leistungsschaltern
FR2573709A1 (fr) Maitre-cylindre de frein pour installations de freinage a double circuit
FR2667908A1 (fr) Verin pneumatique a plusieurs positions d'arret.
EP0004948A1 (de) Arbeitszylinder mit Endlagendämpfung
EP0054469B1 (de) Trommelbremse mit Bremskraftregelung
FR2602819A1 (fr) Vanne de securite commandee par un fluide de surface pour puits petrolier et outil de montage de ladite vanne
EP0321609B1 (de) Erdölbohrungssicherheitsventil und Werkzeug zum Einbau eines derartigen Ventils
FR2465605A1 (fr) Valve hydraulique de regulation de niveau pour suspensions de vehicules automobiles destinee a compenser les variations statiques, du niveau de la carrosserie par rapport a l'essieu du vehicule
FR3102814A1 (fr) Bielle à longueur variable pour moteur à rapport volumétrique piloté
FR2522084A1 (fr) Verin avec distributeur auxiliaire incorpore de fluide
WO1986000966A1 (fr) Ressort pneumatique basculant a etancheite amelioree
FR2475484A1 (fr) Regulateur de pression jumele pour deux circuits, pour systemes de freinage hydraulique
FR2617927A1 (fr) Dispositif hydraulique d'actionnement de frein, notamment pour cylindre de roue de frein arriere de vehicule
FR2670859A1 (fr) Soupape de purge pour circuit hydraulique et procede de purge d'un circuit hydraulique muni d'une telle soupape.

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 BE CH DE ES FR GB GR IT LI LU NL SE

17P Request for examination filed

Effective date: 19890203

17Q First examination report despatched

Effective date: 19910822

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 GR IT LI LU NL SE

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19930203

REF Corresponds to:

Ref document number: 85459

Country of ref document: AT

Date of ref document: 19930215

Kind code of ref document: T

ITF It: translation for a ep patent filed

Owner name: BARZANO' E ZANARDO MILANO S.P.A.

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

Effective date: 19930215

REF Corresponds to:

Ref document number: 3878010

Country of ref document: DE

Date of ref document: 19930318

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2037853

Country of ref document: ES

Kind code of ref document: T3

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
EPTA Lu: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 88400826.9

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: LU

Payment date: 20060303

Year of fee payment: 19

Ref country code: BE

Payment date: 20060303

Year of fee payment: 19

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

Ref country code: AT

Payment date: 20060307

Year of fee payment: 19

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

Ref country code: ES

Payment date: 20060314

Year of fee payment: 19

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

Ref country code: CH

Payment date: 20060331

Year of fee payment: 19

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

Ref country code: GB

Payment date: 20060403

Year of fee payment: 19

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

Ref country code: SE

Payment date: 20060406

Year of fee payment: 19

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

Ref country code: NL

Payment date: 20060427

Year of fee payment: 19

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

Ref country code: DE

Payment date: 20060428

Year of fee payment: 19

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

Ref country code: IT

Payment date: 20060430

Year of fee payment: 19

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20070406

BERE Be: lapsed

Owner name: *GRATZMULLER CLAUDE ALAIN

Effective date: 20070430

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

Effective date: 20071101

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: 20071101

Ref country code: DE

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

Effective date: 20071101

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

Ref country code: CH

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

Effective date: 20070430

Ref country code: AT

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

Effective date: 20070406

Ref country code: LI

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

Effective date: 20070430

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

Ref country code: BE

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

Effective date: 20070430

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: 20070406

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

Ref country code: FR

Payment date: 20070402

Year of fee payment: 20

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: 20070407

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20070407

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: 20070407

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

Ref country code: LU

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

Effective date: 20070406

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: 20070406