EP0384888B1 - Bohrvorrichtung - Google Patents

Bohrvorrichtung Download PDF

Info

Publication number
EP0384888B1
EP0384888B1 EP19900810078 EP90810078A EP0384888B1 EP 0384888 B1 EP0384888 B1 EP 0384888B1 EP 19900810078 EP19900810078 EP 19900810078 EP 90810078 A EP90810078 A EP 90810078A EP 0384888 B1 EP0384888 B1 EP 0384888B1
Authority
EP
European Patent Office
Prior art keywords
feed
valve
piston
percussion
throttle
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
EP19900810078
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0384888A1 (de
Inventor
Günter Straub
Pascher Arno
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 EP0384888A1 publication Critical patent/EP0384888A1/de
Application granted granted Critical
Publication of EP0384888B1 publication Critical patent/EP0384888B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B44/00—Automatic control systems specially adapted for drilling operations, i.e. self-operating systems which function to carry out or modify a drilling operation without intervention of a human operator, e.g. computer-controlled drilling systems; Systems specially adapted for monitoring a plurality of drilling variables or conditions
    • E21B44/02—Automatic control of the tool feed
    • E21B44/06—Automatic control of the tool feed in response to the flow or pressure of the motive fluid of the drive
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B6/00—Drives for drilling with combined rotary and percussive action
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/782—Concurrent control, e.g. synchronisation of two or more actuators

Definitions

  • the present invention relates to a rock drilling device for mining and tunnel construction in relatively soft rock, where rotary impact boring mills are advantageous and zones of different hardness have to be traversed.
  • Such devices have a rotating mechanism for rotating the boring bar, an impact mechanism for hitting the boring bar and a feed drive.
  • the speed of the rotating mechanism, the frequency and impact performance of the impact mechanism and the feed can usually be set. The setting depends on the type of rock to be drilled and is based on experience. However, it often happens that different types of rock are drilled during the advance. The set works are then selected for the hardest rock and are not optimal for softer layers, which leads to low propulsive power and increased tool wear.
  • a drilling device is known from CH-A 657 664.
  • This document describes a hammer drilling device with a rotating mechanism, a hammer mechanism and a feed drive.
  • the control pressure on a control valve is taken from the feed line of the feed drive.
  • a certain adaptation of the stroke frequency to the feed performance is indeed possible.
  • an optimal adaptation of the speed and impact frequency to different rock hardness cannot be achieved.
  • US-A-4 246 973 and US-A-4 356 871 describe further drilling devices in which the pressure to the striking mechanism, the pressure to the rotating mechanism and the pressure to the feed drive depend on one another.
  • the stroke frequency is made dependent either on the torque of the slewing gear or the feed force.
  • the present invention has for its object to provide a drilling device of the type mentioned in such a way that optimal drilling performance in different rocks species can be achieved. This object is achieved by the characterizing features of claim 1.
  • the working parts of the drilling device are only indicated schematically in FIG. 1. They consist of a rotating mechanism 1 for rotating a boring bar 2, a striking mechanism 3 for hitting the boring bar 2 and a feed drive 4 for advancing the drilling device 1, 2, 3.
  • the device also has a first control device 5 for adjusting the speed of the rotating mechanism 1 and the impact frequency and impact power of the impact mechanism 3, and a second control device 6 for adjusting the feed force and speed.
  • the slewing gear 1 consists of a hydraulic motor 10 with an output shaft 11 which is non-rotatably connected to the boring bar 2.
  • the striking mechanism 3 consists of a striking cylinder 12 in which a striking piston 13 is driven back and forth.
  • the Percussion piston 13 strikes against the rear end face of boring bar 2, preferably via an anvil, not shown.
  • Rotary mechanism 1 and percussion mechanism 3 are arranged in a common housing, not shown, which additionally contains a rotary slide valve 14 for controlling the percussion mechanism 3.
  • the rotary valve 14 is driven by the shaft 11 via a gear 15.
  • the impact frequency is exactly proportional to the speed of the slewing gear 1. This has proven to be extremely favorable for the optimal adaptation of the speed and impact frequency to different rock hardness.
  • the boring bar 2 makes a predetermined angle of rotation between two successive strokes, which is independent of the speed.
  • 14 pressure accumulators 18 are arranged in these lines adjacent to the rotary valve.
  • a four / three-way switching valve 23 is connected between the hydraulic motor 10 and the feed line 21 and the return line 22, so that the motor 10 can be operated clockwise or counterclockwise.
  • a parallel connection of an adjustable throttle 26 and a check valve 27 is arranged in each of the lines 24, 25 between the valve 23 and the motor 10.
  • the throttles 26 act as flow regulators and are used to adjust the basic speed of the motor 10 for RIGHT or left rotation.
  • motor 10 turns left with line 24 is connected to the feed line 21.
  • a proportional control valve 28 is connected in this line 24 in parallel to the valve 23 and the throttle 26. The valve 28 opens against the force of a spring 29 proportional to the pressure in its control line 30 and therefore acts on the motor 10 via the bypass line 31 with additional hydraulic oil, so that it rotates faster in proportion to the pressure in the line 30.
  • the feed drive 4 comprises a hydraulic cylinder 35 with a piston 36 and a piston rod 37 which is connected to the housing of the rotating and striking mechanism 1, 3 (not shown).
  • the two chambers 38, 39 of the cylinder 35 are connected via a further four / three-way valve 40 to a further feed line 41 and return line 42.
  • a double pilot-controlled pressure control valve 44 preloaded with an adjustable spring force, is connected in line 43 between valve 40 and feed chamber 39.
  • the two pilot pressures to the valve 44 are connected to the two chambers 38, 39. Through the valve 44, the pressure of the boring bar 2 can thus be limited to an adjustable value independently of the pressure in the chamber 38 during the advance.
  • the line 45 to the chamber 38 is connected to the valve 40 via a three / two-way valve 46 in its first switching position via an adjustable quantity regulator 47.
  • the quantity controller 47 limits the feed rate.
  • the line 45 is connected to a variable throttle 56 via a connecting line 55.
  • the drain 57 leads to the tank 58 via an adjustable pressure control valve 54.
  • This control valve 54 maintains the response pressure of the proportional control valve 28 even when the flow through the throttle 56 is low.
  • the control line 30 is connected to the line 55.
  • the throttle 56 is shown in section in FIG. 2.
  • a plunger 63 is slidably mounted in a cylindrical bore 61 of a housing 62.
  • the piston 63 penetrates a sharp-edged diaphragm 64 with sliding play.
  • the orifice 64 separates an input chamber 65 connected to the line 55 from an output chamber 66 connected to the line 57 in the housing 62.
  • a spring 67 presses against the end face of the piston 63.
  • the piston 63 bears against a cover 69 at the rear.
  • the piston 63 has centrally symmetrically arranged, increasingly deepening to the rear, axial grooves 70 on its circumferential surface.
  • the cross section of the grooves 70 increases with the axial distance from the spring-side end of the piston 63.
  • the throttle cross section thus increases steadily with the stroke of the piston 63, which in turn is proportional to the difference in pressure in the chambers 65, 66.
  • the increase in cross section of the grooves 70 with the stroke of the piston 63 is expediently designed such that the dynamic pressure which forms in the line 55 is proportional to the flow rate through the throttle 56. If the valve 28 opens linearly, then the speed increase of the hydraulic motor 10 is proportional to the feed rate.
  • a borehole is started with the valve 46 in the neutral position shown.
  • the pressure control valve 44 is used to set the optimum pressure for the hardest rock layer of the borehole to be expected.
  • the setting of the throttle 26 also depends on the hardest rock layer to be expected.
  • the quantity regulator 47 which is only decisive for the drilling, is set to the optimum feed rate for the rock to be drilled through first. As soon as the borehole has been drilled, the valve 46 is switched over. If the drill bit encounters softer rock during drilling, the feed rate increases due to the constant pressure.
  • the start of the connection of the bypass 31 can be set by the screw 68. If an adjustment of the speed dependence is desired, the spring constant of the spring 67 'can be made variable, as shown in Fig. 3.
  • the spring 67 ' is designed here as a spiral spring. With a shoe 73, the free length of the spring 67 'and thus the spring constant can be set here.
  • the shoe 73 is displaceable by an adjusting screw 74.

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Earth Drilling (AREA)
EP19900810078 1989-02-23 1990-02-05 Bohrvorrichtung Expired - Lifetime EP0384888B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH66089 1989-02-23
CH660/89 1989-02-23

Publications (2)

Publication Number Publication Date
EP0384888A1 EP0384888A1 (de) 1990-08-29
EP0384888B1 true EP0384888B1 (de) 1992-06-10

Family

ID=4192175

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900810078 Expired - Lifetime EP0384888B1 (de) 1989-02-23 1990-02-05 Bohrvorrichtung

Country Status (4)

Country Link
EP (1) EP0384888B1 (sv)
AU (1) AU630914B2 (sv)
DE (1) DE59000150D1 (sv)
FI (1) FI90277C (sv)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI115552B (sv) 2002-11-05 2005-05-31 Sandvik Tamrock Oy Arrangemang för styrning av bergborrning
SE532483C2 (sv) 2007-04-11 2010-02-02 Atlas Copco Rock Drills Ab Metod, anordning och bergborrningsrigg för styrning av åtminstone en borrparameter
CN102536141B (zh) * 2012-01-20 2013-11-06 中船重工中南装备有限责任公司 一种凿岩钻车的自动换钎控制***
CN103758802B (zh) * 2014-01-24 2016-01-13 长沙金阳机械设备科技开发有限公司 自动钻进液压控制***及作业车
DE102015107194A1 (de) * 2015-05-08 2016-11-10 TERRA AG für Tiefbautechnik Bohranlage zum Erzeugen oder Aufweiten einer Erdbohrung im Erdreich und Verfahren zur Steuerung eines Vorschubantriebs einer solchen Bohranlage
CN106351900B (zh) * 2016-09-27 2018-12-18 桂林航天工业学院 一种防偏斜凿岩控制***
CN111101859A (zh) * 2019-11-08 2020-05-05 四川诺克钻探机械有限公司 一种铁路工程勘探用取芯钻机钻压调节方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4064950A (en) * 1976-07-19 1977-12-27 Pekka Salmi Hydraulic drilling machine
US4271914A (en) * 1976-12-02 1981-06-09 The United States Of America As Represented By The Secretary Of The Interior Automatic feed and rotational speed control system of a hydraulic motor operated drill
US4246973A (en) * 1978-01-23 1981-01-27 Cooper Industries, Inc. Controls for hydraulic percussion drill
US4440236A (en) * 1979-09-20 1984-04-03 Toyo Kogyo Co. Ltd. Hydraulic control system for a rock drill
JPS5655684A (en) * 1979-10-06 1981-05-16 Toyo Kogyo Co Feed controller circuit for hydraulic rock driller
DE3115361A1 (de) * 1981-04-16 1982-10-28 Hydroc Gesteinsbohrtechnik GmbH, 5960 Olpe "hydraulische schlagvorrichtung"
FI67604C (fi) * 1983-06-14 1985-04-10 Tampella Oy Ab Foerfarande och anordning foer reglering av matningsroerelsen hos en borrstaong vid bergborrning
DE3518892C1 (de) * 1985-05-25 1987-02-26 Klemm Bohrtech Hydraulische Schlagbohrvorrichtung

Also Published As

Publication number Publication date
FI90277C (sv) 1994-01-10
FI900834A0 (sv) 1990-02-20
DE59000150D1 (de) 1992-07-16
AU4917490A (en) 1990-08-30
AU630914B2 (en) 1992-11-12
FI90277B (sv) 1993-09-30
EP0384888A1 (de) 1990-08-29

Similar Documents

Publication Publication Date Title
DE3023600C2 (de) Hydraulische Bohrvorrichtung mit einem gemeinsamen Betätigungselement für den Schlag- und den Drehkreis des Antriebs
DE2635191C3 (de) Hydraulische Gesteins-Schlagbohrmaschine
DE2658455C3 (de) Druckmittelbetriebenes Schlagwerk
CH597500A5 (en) Rotary percussive rock drill
DE2645213C3 (de) Schlagwerkzeug, insbesondere für Gesteinsbohrmaschinen
EP0863293B1 (de) Verfahren und Vorrichtung zur Steuerung des Vorschubantriebes einer Erdbohranlage
DE2443800A1 (de) Hydraulisch betriebene schlagvorrichtung
DE2557147C3 (de) Druckflüssigkeitsgetriebene Gesteinsbohrmaschine
DE4328278A1 (de) Bohrvorrichtung für einen Gesteinsbohrer
DE2511471B2 (de) Hydraulische bohrmaschine, insbesondere gesteinsbohrmaschine
EP0203282B1 (de) Regelung einer hydraulischen Schlagbohrvorrichtung
EP0384888B1 (de) Bohrvorrichtung
DE60207109T2 (de) Flüssigkeitsgetriebene bohrloch-bohrmaschine
DE3439268C2 (sv)
DE2657711C2 (de) Hydraulische Schlagvorrichtung, insbesondere für Gesteinsbohrhämmer
CH677813A5 (sv)
DE2208660B1 (de) Hydraulisch betriebene bohrhaemmer
CH657664A5 (de) Schlag-bohrvorrichtung.
EP0906811B1 (de) Bohrhammer
EP0300080A1 (de) Überlagerungsbohrvorrichtung
EP2514911B1 (de) Bohrgerät
EP0145701B1 (de) Regelung einer Schlagbohrmaschine
AT407280B (de) Einrichtung zum verstellen des hubes von fluidgesteuerten schlageinrichtungen
DE2738956B2 (de) Bohrgestänge-Vorspanneinrichtung für Drehschlagbohrmaschinen
DE2631307C2 (de) Hydraulische Bohrmaschine, insbesondere Gesteinsbohrmaschine

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 LI SE

17P Request for examination filed

Effective date: 19900917

17Q First examination report despatched

Effective date: 19910925

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 LI SE

REF Corresponds to:

Ref document number: 59000150

Country of ref document: DE

Date of ref document: 19920716

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
EAL Se: european patent in force in sweden

Ref document number: 90810078.7

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: 20030205

Year of fee payment: 14

Ref country code: GB

Payment date: 20030205

Year of fee payment: 14

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

Ref country code: FR

Payment date: 20030210

Year of fee payment: 14

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

Ref country code: DE

Payment date: 20030213

Year of fee payment: 14

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

Ref country code: CH

Payment date: 20030214

Year of fee payment: 14

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: 20040205

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: 20040206

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: 20040229

Ref country code: CH

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

Effective date: 20040229

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: 20040901

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

Effective date: 20040205

EUG Se: european patent has lapsed
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: FR

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

Effective date: 20041029

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST