EP0183093B1 - Hydraulische Schlagvorrichtung - Google Patents

Hydraulische Schlagvorrichtung Download PDF

Info

Publication number
EP0183093B1
EP0183093B1 EP85114037A EP85114037A EP0183093B1 EP 0183093 B1 EP0183093 B1 EP 0183093B1 EP 85114037 A EP85114037 A EP 85114037A EP 85114037 A EP85114037 A EP 85114037A EP 0183093 B1 EP0183093 B1 EP 0183093B1
Authority
EP
European Patent Office
Prior art keywords
control
line
valve
connection
pressure
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
Application number
EP85114037A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0183093A1 (de
Inventor
Friedrich-Karl Dr.-Ing. Arndt
Karlheinz Fritz
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.)
Fried Krupp AG
Original Assignee
Fried Krupp AG
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 Fried Krupp AG filed Critical Fried Krupp AG
Priority to AT85114037T priority Critical patent/ATE40067T1/de
Publication of EP0183093A1 publication Critical patent/EP0183093A1/de
Application granted granted Critical
Publication of EP0183093B1 publication Critical patent/EP0183093B1/de
Expired legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/145—Control devices for the reciprocating piston for hydraulically actuated hammers having an accumulator

Definitions

  • the invention relates to a device according to the preamble of claim 1.
  • Such devices are e.g. known from DE-B-2428236.
  • the percussion piston triggers a control pulse shortly before reaching its two end positions, which initiates the reversal of the control valve, which in turn causes the forces acting on the percussion piston to be reversed.
  • the control pulses dependent on the piston stroke of the percussion piston are selected such that the percussion piston comes to rest at the intended upper reversal point, taking into account the switching time of the control valve, and then begins its working stroke and, on the other hand, experiences the forces causing the return stroke after the piston hits the chisel.
  • the invention is based on the object of designing an impact device in such a way that in the event that the impact energy is reflected back from the chisel tip onto the impact piston, the number of impacts is not reduced and the smoothness is not impaired.
  • the pressure medium located above the large annular surface of the percussion piston arrives in a pressure accumulator.
  • the reflection energy absorbed by the pressure accumulator is available again for the next working stroke.
  • the device according to the invention thus enables the reflection energy to be recovered.
  • the striking device 1 has a working cylinder in which a striking piston 3 is movably guided. At its lower end, the striking device 1 is provided with a chisel which is slidable in a known manner by a certain amount. The end of the working cylinder 2 facing the chisel 4 is connected to the working pressure P o via a flow or pressure line 5 with a pressure source. An annular groove 6 is provided for the mouth of the supply or pressure line 5 in the working cylinder 2. The impact device 1 is also equipped with a pressure accumulator 8 which is connected to the pressure line 5.
  • the striking device 1 also contains a control valve 10 with a control cylinder 11 and a sleeve-like control slide 12 movable therein.
  • the control cylinder 11 has three cylindrical parts 11 a, 11 b, 11 c, the middle part 11 b having the largest diameter and the upper part 11 a has a diameter that lies between the other two diameters.
  • the front end of the lower cylindrical part 11 c of the control cylinder 11 is connected to the pressure line 5 via a branch line 13.
  • the upper end of the control cylinder 11 is connected via a groove 15 and a line 16 to the return line 17 (hereinafter also referred to as “return line” for short), which leads to the connection on the low-pressure side (symbol: P T ).
  • the lower part 11 c of the control cylinder 11 is also connected via a lateral line 18 to the upper part of the working cylinder 2, a groove 19 and a groove 20 being provided in the working cylinder 2 for opening the line 18.
  • the control cylinder 11 is connected directly to the return line 17 via a groove 22.
  • a further groove 23 is provided between the grooves 6 and 20 in the working cylinder 2 and is connected to the return line 17 via two lines 24, 25.
  • the working cylinder 2 has a control groove 26 through which the working cylinder 2 is connected to the control cylinder 11 via a control channel or a control line 27.
  • the control line 27 is formed by the two lines or line sections 27a and 27b. In the control cylinder, the control line 27 opens into a groove 29 which is located between the grooves 15 and 22.
  • the four grooves 15, 29, 22 and 19 of the control cylinder 11 define its three cylindrical parts as follows: the upper cylindrical part 11 a lies above the groove 15, the central cylindrical part 11 b is delimited by the two grooves 15 and 29 , and the lower cylindrical part 11 c extends from the lower edge of the groove 29 to below the groove 19.
  • the groove 22 lies within the lower cylindrical part 11 c.
  • the two line sections 27 and 27 b are connected to one another by a holding valve 30 provided with three connections, the third connection being connected to the return line 17 via a line section 31 and the line 25.
  • the percussion piston 3 each has a tapered front or lower and rear or upper section 32 or 33, the diameter of the front section 32 being larger than that of the rear section 33.
  • the tapered sections 32 and 33 each create one small or large annular surface 34 or 35 formed on the percussion piston 3.
  • a recess or circumferential groove 36 is arranged between the two ring surfaces 34, 35, through which two piston collars 37 and 38 are formed.
  • the small annular surface 34 is constantly acted upon by the oil or hydraulic medium through the pressure line 5 when it is ready for operation.
  • the piston collar 37 forms with its end adjoining the circumferential groove 36 an upper control edge 39 and with the end given by the small annular surface 34 a lower control edge 40.
  • the control slide 12 has at its lower end facing the branch line 13 a first tapered cylindrical section 41 with an end face 42 and at its opposite end a further cylindrical section 43 with an end face 44.
  • the diameter of the first section 41 is smaller than that of the second section 43, so that the first end surface 42 is also smaller than the second end surface 44.
  • Both end surfaces 42 and 44 are constantly pressurized in the case of readiness for operation, so that these surfaces constantly a downward force F acts on the control slide 12, which results from the area difference (A 44 - A 42 ) multiplied by the working pressure P o .
  • the space between the groove 15 of the control cylinder 11 and the second cylindrical section 43 of the control slide 12 is constantly connected to the return line 17.
  • the first section 41 of the spool 12 is guided in the lower and the second section 43 in the upper cylindrical part 11 c and 11 a of the control cylinder 11.
  • the piston collar 45 slides in the central cylindrical part 11 of the control cylinder 11.
  • the first cylindrical section 41 has a circumferential groove 49 and - between this and the control surface 47 - a small radial auxiliary bore 51.
  • the length of the circumferential groove 49 is greater than the distance between the two grooves 19 and 22 in the control cylinder 11.
  • the holding valve 30 is shown on an enlarged scale in FIG. 2. It consists of a hollow cylindrical part or a bore 53 and a valve body 54 formed as a ball.
  • the cylindrical part 53 has a valve seat 55 on its end face connected to the return line 17 via the line section 31 and a valve seat 55 on its other side, connected to the line section 27a a Front end of a valve seat 56.
  • the line section 27 b of the control line 27 opens radially into the hollow cylindrical part 53. Its central axis goes - when the ball 54 abuts the valve seat 55 - through the half of the ball 54 facing this valve seat.
  • the diameter of the ball 54 is smaller than the diameter of the cylindrical part 53, so that the pressure or hydraulic medium through the the ball 54 and the cylindrical part 53 formed gap 58 can flow.
  • FIG. 1 shows the striking device during the working stroke of the striking piston 3 indicated by an arrow.
  • the space of the cylinder 2 above the large annular surface 35 is connected to the pressure line 5 via the line 18 and the branch line 13.
  • the percussion piston 3 is thus accelerated with a force in the direction of the chisel 4 which results from the area difference (A35-A34) of the ring surfaces 35 and 34 multiplied by the working pressure P o .
  • the control slide 12 is in the upper position facing away from the high-pressure line 5 or the branch line 13.
  • the circumferential groove 36 connects the Line section 27 a - and thus the entire control line 27 - via the line 24 with the return line 17, whereby the space under the control surface 47 is depressurized. It acts exclusively on the force acting on the control spool 12 via the partial surface or surface difference (A44-- A 42 ) and presses it into its lower end position in the valve or control time tst specified by the design.
  • the auxiliary bore 51 is covered on the one hand by the part of the control cylinder 11 located between the grooves 29 and 22 and on the other hand by the circumferential groove 49 the annular surface 35 of the piston 3 via the grooves 22 and 19 and the Line 18 connected to the return line 17 (see FIG. 3).
  • the upper, large annular surface 35 is thus relieved and the percussion piston 3 is accelerated upward by the force acting on the lower small annular surface for the return stroke.
  • the lower control edge 40 given by the small annular surface 34 reaches the control groove 26 and thus (again) establishes a connection between the pressure line 5 and the line section 27 a of the control line 27: the ball 54 is pressed against the left valve seat 55 (See Fig. 4), and the entire control line 27 and the space under the control surface 47 is pressurized, so that the control slide 12 is moved back to its upper position, in which it over the line 18 to the cylinder 2 again Connecting line 13 connects to the pressure line 5 and a new working stroke is initiated.
  • the piston 3 is suddenly accelerated in the direction of the return stroke by the reflection pulse such that the time between the release or opening of the control groove 26 during the upward stroke of the piston 3 and the reclosing of the control groove 26 by the upper control edge 39 is too short to bring the control slide 12 into its lower position.
  • a possibly initiated small movement of the control slide 12 downward - with the control groove 26 closed - is reversed by feeding pressure medium through the auxiliary bore 51 into the space under the control surface 47.
  • valve time t st which also corresponds to the time that passes in order to separate the annular surface 35 from the pressure line 5 and to connect it to the return line 17, is chosen in such a way that the reflection energy by displacing the pressure oil in front of the annular surface 35 through the Lines 18 and 13 in the pressure accumulator 8 can be fully used.
  • the pressure oil that has flowed into the pressure accumulator 8 is available for the next stroke and has the effect of increasing the delivery quantity 0 0 . Since the number of strokes Z of the impact piston 3 is proportional to the delivery quantity Q o , the utilization of or recovery of the reflection energy also increases the number of strokes Z and thus the overall performance of the impact device 1.
  • control slide 12 can also be acted upon by a compression spring in the direction of its lower position, as is described, for example, in EP-A1-0070246.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP85114037A 1984-11-29 1985-11-05 Hydraulische Schlagvorrichtung Expired EP0183093B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85114037T ATE40067T1 (de) 1984-11-29 1985-11-05 Hydraulische schlagvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3443542 1984-11-29
DE19843443542 DE3443542A1 (de) 1984-11-29 1984-11-29 Hydraulische schlagvorrichtung

Publications (2)

Publication Number Publication Date
EP0183093A1 EP0183093A1 (de) 1986-06-04
EP0183093B1 true EP0183093B1 (de) 1989-01-18

Family

ID=6251484

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85114037A Expired EP0183093B1 (de) 1984-11-29 1985-11-05 Hydraulische Schlagvorrichtung

Country Status (5)

Country Link
US (1) US4646854A (enrdf_load_stackoverflow)
EP (1) EP0183093B1 (enrdf_load_stackoverflow)
JP (1) JPH0671714B2 (enrdf_load_stackoverflow)
AT (1) ATE40067T1 (enrdf_load_stackoverflow)
DE (1) DE3443542A1 (enrdf_load_stackoverflow)

Families Citing this family (44)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0236721A3 (en) * 1986-03-11 1989-10-25 NITTETSU JITSUGYO CO., Ltd. Hydraulic breaker
KR900003145B1 (ko) * 1986-08-12 1990-05-09 이교일 유 · 공압 브레이커
JPH0513509Y2 (enrdf_load_stackoverflow) * 1986-09-09 1993-04-09
US4828048A (en) * 1986-11-10 1989-05-09 Mayer James R Hydraulic Percussion tool
JPS63256378A (ja) * 1986-12-04 1988-10-24 日本ニユ−マチツク工業株式会社 油圧衝撃動工具
FR2618092B1 (fr) * 1987-07-17 1989-11-10 Montabert Ets Distributeur hydraulique pour appareil a percussions mu par un fluide incompressible sous pression
DE3913866A1 (de) * 1989-04-27 1990-10-31 Krupp Maschinentechnik Hydraulisches schlagwerk
US4930584A (en) * 1989-05-04 1990-06-05 Easy Industries Co., Ltd. Cracking device
EP0447552A4 (en) * 1989-07-11 1991-12-18 Petr Yakovlevich Fadeev Striking device
US5022309A (en) * 1989-08-17 1991-06-11 Ingersoll-Rand Company Variable frequency control for percussion actuator
DE3939785A1 (de) * 1989-12-01 1991-06-06 Krupp Maschinentechnik Automatische schmiereinrichtung fuer den meissel eines hydraulischen schlagwerks
JPH03208215A (ja) * 1990-01-10 1991-09-11 Izumi Seiki Seisakusho:Kk 油圧式ブレーカー
US5064005A (en) * 1990-04-30 1991-11-12 Caterpillar Inc. Impact hammer and control arrangement therefor
DK0543806T3 (da) * 1990-07-12 1996-05-06 G Drill Ab Bjergboremaskine med hydraulisk drev i borehullet
DE4036918A1 (de) * 1990-11-20 1992-05-21 Krupp Maschinentechnik Verfahren zur anpassung des arbeitsverhaltens eines schlagwerks an die haerte des zerkleinerungsmaterials und einrichtung zur durchfuehrung des verfahrens
ES2144125T3 (es) * 1994-02-28 2000-06-01 Berema Atlas Copco Ab Sistema de valvulas en motores de aire comprimido.
US5680904A (en) * 1995-11-30 1997-10-28 Patterson; William N. In-the-hole percussion rock drill
DE19545708A1 (de) * 1995-12-07 1997-06-12 Krupp Bautechnik Gmbh Verfahren zur Beeinflussung des Betriebsverhaltens eines fluidbetriebenen Schlagwerks und zur Durchführung des Verfahrens geeignetes Schlagwerk
EP0919339A1 (en) * 1996-07-25 1999-06-02 Komatsu Ltd. Hydraulically operated breaker with lost-motion prevention device
DE19636659C2 (de) * 1996-09-10 2000-11-23 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk mit automatischer Hubumschaltung
DE19652079C2 (de) * 1996-12-14 1999-02-25 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
US6058632A (en) * 1997-11-07 2000-05-09 Hawkins; Peter Arthur Taylor Tool holder with percussion member
DE19804078A1 (de) * 1998-02-03 1999-08-05 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
FI107891B (fi) * 1998-03-30 2001-10-31 Sandvik Tamrock Oy Painenestekäyttöinen iskulaite
US6464023B2 (en) 1999-01-27 2002-10-15 William N. Patterson Hydraulic in-the-hole percussion rock drill
US6155361A (en) * 1999-01-27 2000-12-05 Patterson; William N. Hydraulic in-the-hole percussion rock drill
CA2295463C (en) 1999-01-27 2008-04-29 William N. Patterson Hydraulic in-the-hole percussion rock drill
DE19923680B4 (de) 1999-05-22 2004-02-26 Atlas Copco Construction Tools Gmbh Verfahren zur Ermittlung der Betriebsdauer und des Einsatz-Zustands eines hydraulischen Schlagaggregats, insbesondere Hydraulikhammer, sowie Vorrichtung zur Durchführung des Verfahrens
US6631787B2 (en) 1999-12-27 2003-10-14 Lincoln Industrial Corporation Lubrication system
KR100400385B1 (ko) * 2001-07-11 2003-10-08 주식회사 코막 유압 브레이커의 유압 컨트롤밸브
FI114290B (fi) * 2003-02-21 2004-09-30 Sandvik Tamrock Oy Ohjausventtiili ja järjestely iskulaitteessa
SE528033C2 (sv) * 2004-03-12 2006-08-15 Atlas Copco Constr Tools Ab Hydraulslagverk
DE102004035306A1 (de) * 2004-07-21 2006-03-16 Atlas Copco Construction Tools Gmbh Druckmittelbetriebene Schlagvorrichtung insbesondere Hydraulikhammer
SE528745C2 (sv) * 2005-06-22 2007-02-06 Atlas Copco Rock Drills Ab Ventilanordning för slagverk och slagverk för bergborrmaskin
DE102006026274A1 (de) 2006-06-02 2007-12-06 Willy Vogel Ag Selbsttätige Schmierpumpe mit doppelt wirkendem Antriebskolben
US7681664B2 (en) 2008-03-06 2010-03-23 Patterson William N Internally dampened percussion rock drill
SE537608C2 (sv) * 2013-11-01 2015-07-28 Tools Pc Ab Const Pneumatisk slaganordning och förfarande vid pneumatisk slaganordning
EP3928927A1 (en) * 2014-01-30 2021-12-29 Furukawa Rock Drill Co., Ltd. Hydraulic hammering device
WO2018043175A1 (ja) * 2016-08-31 2018-03-08 古河ロックドリル株式会社 液圧式打撃装置
US20180133882A1 (en) * 2016-11-16 2018-05-17 Caterpillar Inc. Hydraulic hammer and sleeve therefor
DK3417951T3 (da) * 2017-06-19 2022-07-04 Eurodrill Gmbh Anordning og fremgangsmåde til generering af slagimpulser eller svingninger til en byggemaskine
WO2019022021A1 (ja) * 2017-07-24 2019-01-31 古河ロックドリル株式会社 液圧式打撃装置
KR102317232B1 (ko) * 2020-01-08 2021-10-22 주식회사 현대에버다임 유압 브레이커
EP4455444A1 (de) * 2023-04-24 2024-10-30 Eurodrill GmbH Vorrichtung zum erzeugen von schwingungen oder schlagimpulsen für eine baumaschine und verfahren zum betrieb

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2428236B1 (de) * 1974-06-11 1975-10-30 Klemm Bohrtech Schlagvorrichtung

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR404176A (fr) * 1908-10-12 1909-11-24 Ernst Flottmann Machine ou frappeur à air comprimé
US1832432A (en) * 1928-10-01 1931-11-17 Chicago Pneumatic Tool Co Pneumatic hammer
US2302018A (en) * 1940-12-30 1942-11-17 Independent Pneumatic Tool Co Distributing valve for pneumatic hammering tools
DE1281370B (de) * 1963-09-06 1968-10-24 Krupp Gmbh Schlaggeraet mit hydraulisch hin- und herbewegten Kolben
US4172411A (en) * 1976-06-09 1979-10-30 Mitsui Engineering & Shipbuilding Co., Ltd. Hydraulic hammer
DE2658455C3 (de) * 1976-12-23 1981-01-22 Fried. Krupp Gmbh, 4300 Essen Druckmittelbetriebenes Schlagwerk
SE420057B (sv) * 1980-02-20 1981-09-14 Atlas Copco Ab Hydrauliskt slagverk med mojlighet att reglera slagenergin
US4425835A (en) * 1981-01-26 1984-01-17 Ingersoll-Rand Company Fluid actuator
FR2509217A1 (fr) * 1981-07-10 1983-01-14 Montabert Ets Appareil a percussions mu par un fluide sous pression
SU1084435A1 (ru) * 1982-06-25 1984-04-07 Калининский Экскаваторный Завод Устройство ударного действи
SU1102935A1 (ru) * 1982-12-23 1984-07-15 Карагандинский Ордена Трудового Красного Знамени Политехнический Институт Гидропневматическое ударное устройство

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2428236B1 (de) * 1974-06-11 1975-10-30 Klemm Bohrtech Schlagvorrichtung

Also Published As

Publication number Publication date
DE3443542A1 (de) 1986-06-05
EP0183093A1 (de) 1986-06-04
ATE40067T1 (de) 1989-02-15
JPS61131877A (ja) 1986-06-19
JPH0671714B2 (ja) 1994-09-14
US4646854A (en) 1987-03-03
DE3443542C2 (enrdf_load_stackoverflow) 1990-07-26

Similar Documents

Publication Publication Date Title
EP0183093B1 (de) Hydraulische Schlagvorrichtung
DE3400302C2 (enrdf_load_stackoverflow)
DE2512731C2 (enrdf_load_stackoverflow)
DE19636659C2 (de) Fluidbetriebenes Schlagwerk mit automatischer Hubumschaltung
DE2737427A1 (de) Hydraulische schlagvorrichtung
CH636407A5 (de) Ventilsteuerung fuer rammbohrgeraete.
DE1242945B (de) Elektromagnetisch regelbarer hydraulischer Stossdaempfer
DE2062690C2 (de) Druckmittelbetriebener Versenkbohrhammer
DE2726165A1 (de) Vorrichtung zur erhoehung der ausfahrgeschwindigkeit der kolbenstange eines druckmitteldruck verwendenden hubzylinders
DE2643483B2 (de) Hydraulischer Schlagapparat
DE2754489A1 (de) Hydraulisch betaetigte schlagvorrichtung
DE2923229A1 (de) Hydraulisches schlagbohrgeraet
EP0067144B1 (de) Einrichtung zum Kühlen der Meissel einer Schrämmaschine
DE3922553A1 (de) Vorrichtung zur entlastung eines unter hohem druck stehenden mit hydraulikfluessigkeit gefuellten arbeitsraumes
DE2107510C3 (de) Hydraulisches Schlagwerkzeug
DE2550129A1 (de) Hydraulisch betaetigtes schlaggeraet
DE19652079C2 (de) Fluidbetriebenes Schlagwerk
DE69423511T2 (de) Hydraulischer schlagantrieb
EP0672506A1 (de) Hydraulischer Schlaghammer
EP0051728A1 (de) Steuervorrichtung für einen hydraulischen Arbeitszylinder
DE2349296A1 (de) Druckluft-schlagmaschine
DE3048229C2 (de) Rückschlagventil für Grubenausbaustempel
EP0933169A2 (de) Fluidbetriebenes Schlagwerk
DE2857176C1 (de) Hydraulischer Antrieb fuer den Schuetzen einer Webmaschine
DE19535795A1 (de) Prüfeinrichtung für die Funktion von Düsen einer meißelgesteuerten Schneidspurbedüsung

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 FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19861106

17Q First examination report despatched

Effective date: 19880222

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 FR GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 40067

Country of ref document: AT

Date of ref document: 19890215

Kind code of ref document: T

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

Payment date: 19911015

Year of fee payment: 7

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

Ref country code: LU

Payment date: 19911024

Year of fee payment: 7

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

Ref country code: AT

Payment date: 19911028

Year of fee payment: 7

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

Ref country code: NL

Payment date: 19911130

Year of fee payment: 7

EPTA Lu: last paid annual fee
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: 19921105

Ref country code: AT

Effective date: 19921105

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

Ref country code: BE

Effective date: 19921130

BERE Be: lapsed

Owner name: FRIED. KRUPP G.M.B.H.

Effective date: 19921130

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

Ref country code: NL

Effective date: 19930601

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
EAL Se: european patent in force in sweden

Ref document number: 85114037.6

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

Ref country code: CH

Payment date: 19961023

Year of fee payment: 12

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: 19971130

Ref country code: CH

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

Effective date: 19971130

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: SE

Payment date: 20021028

Year of fee payment: 18

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

Ref country code: GB

Payment date: 20021030

Year of fee payment: 18

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

Ref country code: FR

Payment date: 20021104

Year of fee payment: 18

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: 20031105

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: 20031106

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

Effective date: 20031105

EUG Se: european patent has lapsed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

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

Effective date: 20040730

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST