EP0276845A2 - Pfahlramme - Google Patents

Pfahlramme Download PDF

Info

Publication number
EP0276845A2
EP0276845A2 EP88101219A EP88101219A EP0276845A2 EP 0276845 A2 EP0276845 A2 EP 0276845A2 EP 88101219 A EP88101219 A EP 88101219A EP 88101219 A EP88101219 A EP 88101219A EP 0276845 A2 EP0276845 A2 EP 0276845A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
self
equilibration
vibration
pile
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
EP88101219A
Other languages
English (en)
French (fr)
Other versions
EP0276845A3 (en
EP0276845B1 (de
Inventor
Yasuo Tasaki
Seizo Kumai
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.)
TAKAHASHI ENGINEERING KK
Original Assignee
TAKAHASHI ENGINEERING KK
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=12018487&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0276845(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by TAKAHASHI ENGINEERING KK filed Critical TAKAHASHI ENGINEERING KK
Publication of EP0276845A2 publication Critical patent/EP0276845A2/de
Publication of EP0276845A3 publication Critical patent/EP0276845A3/en
Application granted granted Critical
Publication of EP0276845B1 publication Critical patent/EP0276845B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
    • E02D7/18—Placing by vibrating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D13/00—Accessories for placing or removing piles or bulkheads, e.g. noise attenuating chambers
    • E02D13/10—Follow-blocks of pile-drivers or like devices

Definitions

  • the present invention relates to a pile driver utilizing a vibration cylinder receiving a fluid pressure as energy source to generate a mechanical vibration under which a pile is driven into the ground.
  • Pile drivers using a vibration cylinder have been proposed as disclosed in, for example, the West Germany Patent No. 28 21 339.0.09 and the United States Patent No. 4,317,406, in which, as shown in Figure 1, the vibration cylinder itself has a function of self-equilibration and a pile P is coupled with a piston 101 of a vibration cylin­der 100 by means of a chunk 102, an internal weight 103 being coupled with the other end of the vibration cylinder 100 in line with the pile P, whereby a vibratory force of a periodic function is generated between the inertial weight 103 and the pile P which in turn will be driven into a ground E.
  • the vibratory force is damped when the inertial weight is applied with a pull-down force by any other construction machine such as crane truck, leader, etc.
  • the present invention has an object to overcome the above-mentioned drawbacks of the prior-art pile drivers by providing a pile driver of which the inertial weight can be pulled up and down by any other construction machine without damping the alternate vibratory force of the vibration cylinder.
  • a vibration cylinder of a vibration generating mechanism and a self-equilibration cylinder of a self-equilibration mechanism are so provided vertically in series with each other that the axes of their respective rods lie on the center line passing through the center of gravity of an inertial weight, the rods of the vibration and self-equi­libration cylinders are coupled to each other, the vibra­tion generating mechanism has a changeover valve to supply and discharge a pressurized fluid to and from the vibra­tion cylinder while the self-equilibration cylinder has a control valve responsive to the rod of either the self-­equilibration cylinder or vibration cylinder to supply and discharge the pressurized fluid to and from a control chamber in the self-equilibration cylinder, the piston of the self-equilibration cylinder is supported with a low rigidity to the inertial weight by means of accumulators provided as communicating with the control chamber in the self-
  • the vibration cylinder and self-equilibration cylinder are so provided in series with each other that the axes of the rods thereof lie on the center line passing through the center of gravity of the inertial weight, a control valve is pro­vided which operates in response to the rod of the vibra­tion cylinder to supply and discharge the pressurized fluid to and from the control chamber in the self-equili­bration cylinder, and the piston of the self-equilibration cylinder is supported with a low rigidity to the inertial weight by means of the accumulators provided as communi­cating with the control chamber or the spring provided inside the self-equilibration, whereby the piston of the self-equilibration cylinder is held in position within the inertial weight and also has a damping effect.
  • the vibration cylinder has its alternate vibratory force reduced due to the displacement of the piston of the self-equilibration cylinder. Also, owing to the damping effect of the self-equilibration cylinder, the weight of the inertial weight is conveyed to the pile without being damped so that the pile is effec­tively driven into the ground. Especially, when the inertial weight is applied with a pull-down or pull-up force by any other construction machine, no vibration is conveyed to the pull-down or pull-up equipment and the vibratory force is conveyed to the pile as a driving force or extraction force resulted from the superposition on the pull-up or pull-down force without being cancelled by the pull-up or pull-down force.
  • the pile driver according to the present invention comprises an intertial weight 1, a vibration generating mechanism 2 composed of a vibration cylinder 3 having rods 4 and 5, and a self-equalibration mechanism 6 composed of a self-equalibration cylinder 7 having rods 8 and 9, these cylinders 3 and 7 being so disposed vertically in series with each other that the axes of the rods 4 and 5 and those of the rods 8 and 9 lie on the center line passing through the center of gravity of the inertial weight 1.
  • the rods 5 and 8 are integrally formed into a one-piece structure.
  • the vibration cylinder 3 is provided with a changeover valve 10 to produce an alternate vibratory force.
  • the vibration cylinder 3 and the changeover valve 10 form together the vibration gene­rating mechanism 2.
  • the self-equilibration cylinder 7 is provided with a control valve 11 responsive to the rods 8 and 9 of the self-equilibration cylinder 7 to supply and discharge a pressurized fluid to and from the self-equili­bration cylinder. As shown in Figure 2, there are provided accumulators 14 communicating with oil chambers 12 and 13 in the self-equilibration cylinder 7.
  • the vertical vibration of the piston 15 of the self-equili­bration cylinder 7 is prevented from being conveyed to the inertial weight 1, or to prevent the alternate vibratory force from being reduced by the inertial weight 1, the piston 15 of the self equilibration cylinder 7 is flexibly (with a low rigidity) coupled to the inertial weight 1. This is intended to avoid that the vibration of the piston 15 due to the vibration cylinder 3 would be restricted (pile driving force would be reduced) if the inertial weight 1 is coupled to the piston 15 with a high rigidity by means of a pressurized fluid of a relatively small com­pressibility.
  • the rigidity of the spring effect due to the accumulators 14 should desirably be more than 20 mm when the vibratory force of the vibration cylinder 3 is maximum.
  • Such spring effect of the self-equilibration cylinder 7 can be attained by providing floating pistons 21 as fitted on the rods 8 and 9, respectively, on the opposite sides of the piston 15 and also providing springs 22 between the floating pistons 21 and the piston 15, respectively as shown in Figure 3.
  • the rod 4 of the vibration cylinder 3 has provided at the lower end thereof a chuck 17 which grasps a pile 16.
  • the vibration cylinder 3 has oil chambers 19 and 20 on the opposite sides, respectively, of the piston 18.
  • FIG. 4 A preferred embodiment of pile driver according to the present invention will be described with reference to Figure 4.
  • This embodiment is provided with a suspender 23 consisting of a hook 24 to be supported by a crane or the like, and a suspender body 25 having a C-shaped section and which is supported by the hook 24.
  • the inertial weight 1 is to be attached to the suspender body 25 with such a rubber cushion 26 placed betwen them that the vibration of the inertial weight 1 will not be conveyed directly to the suspender body 25.
  • the entire cylinders are made by relatively thick materials, and a sound-proof cover (skirt) 27 which also works as inertial weight is provided outside the cylinders. These are intended to reduce the manufacturing costs of the cylinders as a whole while isolating the sound and protecting the valves.
  • a servo-­controlled valve which operates with an electric signal is used as shown in Figures 5 and 6.
  • This changeover valve 10 is provided inside the valve body 28 therof with a four-­way valve 30 accomodating a spool 29 of which the shaft 29A is connected to a spool displacement detector 31 and which is driven by a electro-hydraulic servo valve 32.
  • the position of the spool 29 is converted into an electric signal which is fed back to a differential amplifier 33, and the spool 29 is moved following up with an instruction signal applied to the differential amplifier 33.
  • the reference numeral 34 indicates an oil port and 35 indicates a return port. Ports 36 and 37 communicate with the vibra­tion cylinder 3. The flow direction and flow rate of the oil under pressure to the vibration cylinder 3 can be controlled by the four ports 34 thru 37 bades on the position of th spool 29.
  • the self-equilibration mechanism 6 is constructed as shown in Figures 5 and 7.
  • the self-equilibration cylinder 7 has control oil chambers 12 and 13 on either side, respectively, of the piston 15 and accumulators 14 communicating with the control oil chambers 12 and 13, respectively.
  • the responsive control valve 11 is a four-way valve using a spool 42 and works to connect any of pressurized oil supply port P and discharge port T to the oil path 43 or 44 provided within the responsive control valve and which communicate with the oil paths 39 and 40, respecti­vely, according to the position of the spool 42.
  • the spool 42 of the responsive control valve 11 is forced upward by a spring 46 and the upper end of the shaft 42A of the spool 42 is projected outside of the valve body 45.
  • a member 48 pivotably installed to a fulcrum bracket 47 provided on the top of the self-equilibration cylinder body 38.
  • the other end of the member 48 is in contact with the rod 9 of the self-equilibration cylinder 7 (which serves in the same manner as the rods 4 and 5 of the vibration cylinder).
  • the fulcrum bracket 47 and member 48 form together a coupling means 41.
  • the spool 42 moves in response to the rods of the self-equilibration cylinder 7 and vibration cylinder 3.
  • the self-equilibration cylinder 7 has various functions; however, one of them will be described below:
  • the oil pressure in the oil chambers 12 and 13 of the self-equilibration cylinder 7 is controlled as in the following. Assume that the pistons 15 and 18 vibrate at a high frequency of more than 20 Hz and with an ampli­tude of less than ⁇ 2 to 3 mm.
  • the self-equilibration mechanism 6 is so arranged as not to respond to the vibration.
  • the four-way valve is designed to have an over­lap structure, or such an arrangement is made that even when the oil in the control oil chambers 12 and 13 is supplied and discharged at a high frequency owing to the compression of the accumulators 14, the pressure in the chambers will change little.
  • the spool 42 of the responsive control valve 11 is pressed down by the coupling means 41.
  • the oil chamber 13 in the self-equilibration cylinder is supplied with the oil from the oil supply port P through the oil paths 43 and 39, with the result that the oil pressure is raised, while the oil in the oil chamber 12 at the opposite side is discharged to the oil discharge port T through the oil paths 44 and 40 so that the oil pressure is lowered. Therefore, the piston 15 is pushed down and returned from the position upwardly displaced to the center.
  • Another function of the self-equilibration cylinder 7 is to provide a damping effect, namely, to prevent, owing to the compression of the accumulators 14 communicating with the oil chambers 12 and 13 of the self-equilibration cylinder 7, the vibration of the pistons 15 and 18 caused by the vibration cylinder 3 from being conveyed to the inertial weight 1 so that the vibration of the piston 18 is not restricted by the inertial weight 1.
  • the changeover valve 10 is not provided in the vibration cylinder 2 as in the West Germany Patent No. 28 21 339.0-09 but outside the vibration cylinder 3, which leads to a simplified con­struction of the piston 18 of the vibration cylinder 3.
  • the manufacturing costs of, especially, a large cylinder can be considerably reduced.
  • a pile driver in which, in addition to the frequency control element, an amplitude control element, namely, a servo-controlled valve is used as the changeover valve 10 according to the present inven­tion, it is possible to control the amplitude of the pile 16 from zero to the maximum independently of the frequency. Thereby, it is possible to eliminate the shock to the crane, etc. by reducing to zero the amplitude at start and stop of the pile driver. Also, by changing the amplitude of the pile vibration, the vibration of the ground can be minimized when piles are driven into a complicate ground. For example, when the pile cannot be easily driven into the ground, the amplitude of pile vibration is increased. In case the pile can be easily driven into the ground, the amplitude is limited to a minimum necessary one.
  • the changeover valve 10 can be closed and opened following up with the waveform of electric signal, a changeover like a simple sinusoidal waveform can be done, and a changeover like a rectangular waveform can be done as well.
  • the pile driving ability can be improved owing to the hammer effect by changing the pressure in the vibration cylinder abrubtly at time of driving a pile into the ground.
  • by controlling the opening and closing of the changeover valve so that the opening area follows up with a sinusoidal waveform it is possible to reduce the high frequency component in the vibration waveform, whereby it is possible to reduce the noise generated by the chuck 17 and pile 16 as well.
  • the cylinders 3 and 7 are disposed vertically in series with each other so that the axes of their respective rods 4 and 5, and 8 and 9 (the rods 5 and 8 are integrally formed into a one-piece structure) lie on the center line passing through the center of gravity of the inertial weight 1.
  • the responsive control valve 11 is provided which responds to the rods 4 and 5 of the vibration cylin­der 3 to supply and discharge the pressurized fluid to and from the oil chambers 12 and 13 of the self-equilibration cylinder 7.
  • the piston 15 of the self-equilibration cylin­der 7 is supported to with a low rigidity by means of the accumulators 14 communicating with the oil chambers 12 and 13 or by means of the spring 22 provided in the self-­equilibration cylinder 7.
  • the piston 15 of the self-­equilibration cylinder 7 is held in position and has a damping effect.
  • the alternate vibratory force of the vibration cylinder 3 is prevented from being reduced due to the displacement of the piston 15 of the self-­equilibration cylinder 7.
  • the weight of the inertial weight 1 is conveyed to the pile without being damped, whereby the pile can be effectively driven into the ground.
  • the vibration is not conveyed to the pull-down or pull-up equipment, and the vibratory force can be conveyed to the pile 16 as a driving force or extraction force re­sulted from superposition on the pull-down or pull-up force without being cancelled by the pull-down or pull-up force.
  • the pile driver according to the present invention is advantageous in that it is of a sound-proof structure, the alternate vibratory force of the vibration cylinder 3 can be conveyed to the pile 16 without being reduced and that the inertial weight 1 can be pulled down or up so that the pile driver itself may not be heavy.
  • Figure 8 shows a hydraulic circuit which supplies and discharges the pressurized fluid to and from the oil chambers 19 and 20, and 12 and 13 of the vibration cylinder 3 and self-equilibration cylinder 7, respectively.
  • the reference numeral 49 indicates a filter
  • 50 indicates a reducing valve.
  • the weight W of the inertial weight 1, pull-down force F1 and the alternate vibratory force of the vibration cylin­der 3 are superposed on each other and applied to the pile 16.
  • the pile head is applied with a compressive force and tractive force alternately and the pile is likely to be broken when the tensile force is applied since the concrete is weak against a tensile force while being strong against a compressive force.
  • the tensile force of the vibration cylinder 3 to the concrete pile is reduced by pulling down the inertial weight by means of the pull-down equipment 51, so that the concrete pile can be driven into the ground without being broken.
  • the pull-up force indicated with F2 in Figure 9 is applied to the inertial weight 1 by a pull-up equipment 52.
  • the pile can be easily extracted with a static component (F2-W) of the extraction force and the alternate vibratory force applied as superposed on each other to the pile.

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
EP19880101219 1987-01-30 1988-01-28 Pfahlramme Revoked EP0276845B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP20128/87 1987-01-30
JP2012887A JPS63189522A (ja) 1987-01-30 1987-01-30 杭打ち装置

Publications (3)

Publication Number Publication Date
EP0276845A2 true EP0276845A2 (de) 1988-08-03
EP0276845A3 EP0276845A3 (en) 1989-10-18
EP0276845B1 EP0276845B1 (de) 1992-07-22

Family

ID=12018487

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880101219 Revoked EP0276845B1 (de) 1987-01-30 1988-01-28 Pfahlramme

Country Status (3)

Country Link
EP (1) EP0276845B1 (de)
JP (1) JPS63189522A (de)
DE (1) DE3872889T2 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0449286A1 (de) * 1990-03-29 1991-10-02 Kabushiki Kaisha Takahashi Engineering Pfahlramme
KR100494072B1 (ko) * 1996-12-05 2005-08-31 가부시키가이샤 고마쓰 세이사쿠쇼 전환밸브장치

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2997739B1 (fr) 2012-11-07 2015-01-09 Thermodyn Compresseur comprenant un equilibrage de poussee

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1634303B (de) * Cordes, Hugo, Dipl.-Ing., 2000 Hamburg Rammhammer
DE2240385A1 (de) * 1971-08-23 1973-03-01 Bolt Associates Inc Verfahren zur steuerung der kraft beim eintreiben eines pfahls und geraet zur durchfuehrung des verfahrens
DE2250848A1 (de) * 1971-10-18 1973-04-26 Birger Ludvigson Verfahren und vorrichtung zum erzeugen einer druckwelle in einem langgestreckten koerper
DE2821339A1 (de) * 1977-05-18 1978-11-30 Takahashi Eng Kk Hydraulische kolbenzylindervorrichtung zur hervorrufung einer axialen kolbenvibration
US4317406A (en) * 1978-05-18 1982-03-02 Kabushiki Kaisha Takahashi Engineering Hydraulic cylinder for generating vibrations

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS572856A (en) * 1980-06-06 1982-01-08 Showa Alum Corp Cathodically protecting brazing sheet for vacuum brazing
JPS5846963A (ja) * 1981-09-16 1983-03-18 横河電機株式会社 血液透析用超音波検出装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1634303B (de) * Cordes, Hugo, Dipl.-Ing., 2000 Hamburg Rammhammer
DE2240385A1 (de) * 1971-08-23 1973-03-01 Bolt Associates Inc Verfahren zur steuerung der kraft beim eintreiben eines pfahls und geraet zur durchfuehrung des verfahrens
DE2250848A1 (de) * 1971-10-18 1973-04-26 Birger Ludvigson Verfahren und vorrichtung zum erzeugen einer druckwelle in einem langgestreckten koerper
DE2821339A1 (de) * 1977-05-18 1978-11-30 Takahashi Eng Kk Hydraulische kolbenzylindervorrichtung zur hervorrufung einer axialen kolbenvibration
US4317406A (en) * 1978-05-18 1982-03-02 Kabushiki Kaisha Takahashi Engineering Hydraulic cylinder for generating vibrations

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0449286A1 (de) * 1990-03-29 1991-10-02 Kabushiki Kaisha Takahashi Engineering Pfahlramme
KR100494072B1 (ko) * 1996-12-05 2005-08-31 가부시키가이샤 고마쓰 세이사쿠쇼 전환밸브장치

Also Published As

Publication number Publication date
EP0276845A3 (en) 1989-10-18
DE3872889T2 (de) 1993-03-04
JPS63189522A (ja) 1988-08-05
EP0276845B1 (de) 1992-07-22
DE3872889D1 (de) 1992-08-27

Similar Documents

Publication Publication Date Title
EP0401239B1 (de) Schwingungsdämpfendes maschinenlager
US6226989B1 (en) Wave energy converter
US5116188A (en) Vibration suppressing device for wheeled construction equipment
JPS62292517A (ja) 能動型サスペンシヨン
EP0381788A1 (de) Vorrichtung zur Unterdrückung von Vibrationen für Baumaschinen auf Rädern
CN100572255C (zh) 单索抓斗的启闭控制机构
JPS58218514A (ja) 杭打込装置
EP0276845B1 (de) Pfahlramme
WO1990013748A1 (en) Hydraulic driving device of construction equipment
US5331607A (en) Sweep frequency vibrator
US4964491A (en) System for limiting snap load intensity
WO2018084098A1 (ja) バルブブロック
US4023657A (en) Device for damping a perpendicularly oscillating mass
EP0539438A1 (de) Dämpfungseinheit.
JP2963935B2 (ja) 防振用支持装置
US4056123A (en) Hydraulic oscillator
JPH11287206A (ja) 流体圧式駆動装置及び建設機械の速度制御装置
KR102434572B1 (ko) 2단 압축 어큐뮬레이터 및 이를 사용한 선박 엔진의 횡방향 진동 감쇄를 위한 탑브레이싱
JPS59114323A (ja) 液圧式ハンマ
FI77079C (fi) Paolramm.
JP2909750B2 (ja) 車高調整装置付き緩衝器
JP2723984B2 (ja) 杭打ちハンマの油圧回路
SU1043261A1 (ru) Устройство дл гашени колебаний преимущественно вибромеханизма дл извлечени свай
JPH03286042A (ja) 車両のダイナミックダンパー
JPH07133805A (ja) 建設機械のシリンダ制御装置

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: A2

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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

17P Request for examination filed

Effective date: 19900329

17Q First examination report despatched

Effective date: 19910611

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 NL

REF Corresponds to:

Ref document number: 3872889

Country of ref document: DE

Date of ref document: 19920827

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: SIMSON INNOVATIONEN

Effective date: 19930421

NLR1 Nl: opposition has been filed with the epo

Opponent name: SIMSON INNOVATIONEN

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

Ref country code: FR

Payment date: 19931214

Year of fee payment: 7

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

Ref country code: CH

Payment date: 19940121

Year of fee payment: 7

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

Ref country code: GB

Payment date: 19940124

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: 19940131

Year of fee payment: 7

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

Ref country code: DE

Payment date: 19940324

Year of fee payment: 7

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

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

Free format text: STATUS: PATENT REVOKED

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

27W Patent revoked

Effective date: 19950204

GBPR Gb: patent revoked under art. 102 of the ep convention designating the uk as contracting state

Free format text: 950204

NLR2 Nl: decision of opposition