EP0035757B1 - Dampfturbine - Google Patents

Dampfturbine Download PDF

Info

Publication number
EP0035757B1
EP0035757B1 EP81101580A EP81101580A EP0035757B1 EP 0035757 B1 EP0035757 B1 EP 0035757B1 EP 81101580 A EP81101580 A EP 81101580A EP 81101580 A EP81101580 A EP 81101580A EP 0035757 B1 EP0035757 B1 EP 0035757B1
Authority
EP
European Patent Office
Prior art keywords
steam
rotor
laval nozzles
steam turbine
stage
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
EP81101580A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0035757A1 (de
Inventor
Paul Dipl.-Ing. Morcov
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 AT81101580T priority Critical patent/ATE17774T1/de
Publication of EP0035757A1 publication Critical patent/EP0035757A1/de
Application granted granted Critical
Publication of EP0035757B1 publication Critical patent/EP0035757B1/de
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/32—Non-positive-displacement machines or engines, e.g. steam turbines with pressure velocity transformation exclusively in rotor, e.g. the rotor rotating under the influence of jets issuing from the rotor, e.g. Heron turbines

Definitions

  • the invention relates to a multi-stage steam turbine with a closed circuit, with at least one impeller arranged in a closed turbine housing, which has a plurality of internal Laval nozzles which are connected to a plurality of Laval nozzles arranged on the circumference of the impeller.
  • the steam turbine has been the most important engine in thermal power plants for about a century; it has gained considerable importance as a marine propulsion system, for driving pumps, compressors, power generators etc. While the steam turbine developed rapidly in the first 50 years of this period, the technical literature shows that in the past 50 years the development of the steam turbine has ceased is characterized by drastic further developments.
  • the steam turbine according to the invention can be classified as a counter-pressure reaction turbine, but differs in essential features from the conventional turbines in this group.
  • a known multi-stage steam turbine of the type mentioned at the beginning (US-A-3 032 988) has a drum as an impeller with an inner and an outer shell, in each of which a plurality of Laval nozzles are arranged, the Laval nozzles of the inner shell having a first turbine stage and the Laval nozzles of the outer jacket form a second turbine stage. All Laval nozzles are connected to a common cavity between the two drum jackets.
  • the steam therefore does not flow continuously from a Laval nozzle of the first stage to a Laval nozzle of the second stage in this known turbine, but part of the steam emerging from a Laval nozzle of the first stage flows through the Laval nozzle of the second stage, but another part of the flows Steam into the space between the two drum coats and only causes flow losses there.
  • the steam emerging from the Laval nozzles of the first stage hits the jacket of the next stage, with the vast majority of its kinetic energy being lost. Only then does the steam flow partly through the outer Laval nozzles and partly into the space between the two drum coats. The efficiency due to the unfavorable flow conditions and gap losses shown is very low.
  • the object of the invention is to design a multi-stage steam turbine of the type outlined in the preamble of claim 1 in such a way that the efficiency is significantly improved, gap losses between the individual stages of an impeller in particular being avoided.
  • the steam is conducted continuously through the curved tubes without any gap loss from an internal Laval nozzle to an external Laval nozzle. Possibly. further Laval nozzles can be provided in the course of the tube. Any gap losses between the Laval nozzles connected in series are excluded, as are flow losses due to sharp deflections of the steam flow.
  • thermal efficiency of this steam turbine is significantly higher than that of conventional designs because gap losses and sealing losses are largely avoided or at least greatly reduced, so that only friction, insulation and flow losses have to be taken into account, which together do not exceed 4 to 5% in one Steam turbine of medium power. Compared to an average efficiency of 78% of a conventional back pressure turbine and 80% of a conventional condensation turbine, this means an efficiency improvement of 12 to 15%.
  • the design of the steam turbine according to the invention is simpler and more robust than conventional designs due to the omission of the stator and the blades of the impeller, so that not only is the manufacture easier and cheaper, but also the operational safety is increased because damage due to mechanical overloading of the blades is excluded are.
  • the steam turbine according to the invention is also suitable for driving ships, locomotives and other vehicles.
  • Laval nozzles designed for supercritical gradients
  • the steam turbine is designed with a plurality of impellers mounted on a common rotor shaft, and that the steam outlet of one stage is connected to a cavity in the impeller of the following stage.
  • this multi-stage design which is required to utilize the entire available heat gradient, can be implemented in a structurally very simple manner, namely without guide wheels.
  • the successive Laval nozzles on the circumference of the impeller are alternately angled axially to both sides out of the impeller plane. It is thereby achieved that the steam jet emerging from a nozzle does not impinge on the subsequent nozzle, but rather flows freely past it. Despite this axial angling of the individual nozzles, there is no resulting axial force that would require an axial force compensation, because the axial forces generated by the alternately angled nozzles on the impeller cancel each other out.
  • At least two impellers are arranged with mutually opposite exit directions of the Laval nozzles arranged on the circumference, and that the two impellers can optionally be connected to the cavity for supplying steam. This allows the direction of rotation to be reversed in a very simple manner without the need for a manual transmission.
  • an axially movable slide is arranged centrally in the impellers or in a rotor shaft carrying the impellers, which selectively shuts off one of the two impellers from the cavity for the supply of steam.
  • the steam leaving the steam outlet of the possibly last stage is conducted in a closed circuit via a pressure regenerator and back to the impeller of the possibly first stage.
  • a pressure regenerator as is known for example from DE-A-2 613 418, a particularly high efficiency is achieved because the steam in the closed circuit does not condense and the water would have to be evaporated again. Instead, the steam remains in a vapor phase; by applying heat, its pressure is increased to the value desired at the turbine inlet.
  • a rotor shaft 2 ' is mounted in bearings 3' in a two-part turbine housing 1 ', which are designed, for example, as plain bearings made of white metal.
  • Two disk-shaped impellers 6 'and 6 are arranged next to one another on the rotor shaft 2', each carrying a plurality of tangentially directed nozzles 9 'and 9" on their circumference, which are designed as so-called Laval nozzles with a cross section that extends from the nozzle inlet to reduced to the narrowest cross section and expanded again towards the nozzle outlet.
  • the exit direction of the nozzles 9 'of one impeller 6' and the nozzles 9 "of the other impeller 6" are tangentially opposite.
  • the impellers 6 'and 6 are freely rotatable in a housing chamber 10' of the turbine housing 1 ', which has a steam outlet 11'.
  • a cover 24 is attached, through which a steam supply line 15' leads centrally into a central cavity 5 'of the rotor shaft 2'. From there, the steam passes through tangentially arranged nozzles 25, which are also designed as Laval nozzles for supercritical gradients, into curved tubes 7 ', which run outwards to the nozzles 9' or 9 ".
  • the heat gradient of the steam is reduced in a first stage in the nozzles 25 on the inside of the impeller.
  • the external nozzles 9 'and 9 "form the second stage.
  • the steam flows from the steam outlet 11' to a pressure regenerator (not shown in FIG. 1) and from there in a closed circuit back into the steam supply line 15 '.
  • nozzles 9' of the impeller 6 'and the nozzles 9 "of the impeller 6" are tangentially opposite, the direction of rotation of the rotor shaft 2 'can be changed by either impinging the impeller 6' or the impeller 6 "with steam.
  • a slide 26 is arranged axially displaceably in the cavity 5 'of the rotor shaft 2' and has a bushing 27 at its end facing the steam supply line 15 ', which is connected to a piston-shaped slide part 29 via webs 28.
  • the steam enters the interior of one of the impellers 6 ′ or 6 ′′ between the webs 28.
  • the slide 26 is connected to a piston 31 via a piston rod 30.
  • a ring 32 surrounds the piston rod 30 in a sealing manner and can be on both of them Hydraulic pressure is alternately applied to the sides via hydraulic lines 33.
  • the slide 26 is optionally moved into one of its two axial end positions, so that steam is optionally applied to the impeller 6 'or the impeller 6 ".
  • the direction of rotation of the rotor shaft 2 ' is reversed accordingly.
  • the rotor shaft 2 ' consists of two hollow shafts 34 and 35, which receive the impellers 6' and 6 "between them, a shaft intermediate piece 36 being arranged between these two impellers.
  • One hollow shaft 35 is included a shaft journal 37 connected.
  • FIGS. 1 and 2 The embodiment shown in FIGS. 1 and 2 is particularly suitable for heavy vehicles, such as locomotives, ships, etc.
  • the machine does not require a controller.
  • the steam turbine with nozzles 25 and 6 'connected in series according to FIGS. 1 and 2 can also be designed without a device for reversing the direction of rotation, for example with a plurality of adjacent impellers 6' which are connected to the common cavity 5 '.
  • a rotor shaft 2 is rotatably supported at its ends in bearings 3, which are preferably designed as roller bearings.
  • a bushing 4 is fastened on the shaft 2 and, between itself and the shaft 2, axially next to one another includes a plurality of divided cavities 5 designed as annular spaces.
  • a plurality of disk-shaped impellers 6 are attached to the sleeve 4, each of which has a plurality of radial tubes 7, which are connected to the annular spaces 5 via bores 8 and angled in the circumferential direction at their outer end and there each with a nozzle 9 (FIG. 4 ) are connected, which are designed as Laval nozzles.
  • the impellers 6 are each freely rotatable in a housing chamber 10 of the turbine housing 1.
  • Each housing chamber 10 has a steam outlet 11, which is connected to one of the annular cavities 5 via an intermediate chamber 12, a plurality of radial housing bores 13 and a plurality of radial bores 14 of the bush 4.
  • These openings through which the steam flows can also be designed in the manner of Laval nozzles, as shown in the drawing, in order to keep the flow losses low.
  • FIG. 3 shows a multi-stage steam turbine.
  • the steam passes through a steam supply line 15 through a housing bore 16 and a radial bore 17 of the sleeve 4 into the annular space 5 of the first stage.
  • the steam passes through the steam outlet 11 into the annular space 5 of the second stage, etc., until the steam through the steam outlet 11 of the last stage via a line 18 to only one in FIG. 1 schematically indicated pressure regenerator 19 and from there via a line 20 and a regulator 21 in the closed circuit again in the steam supply line 15.
  • the individual nozzles 9 are each arranged at a flat angle to the impeller plane, so that the steam jets emerging from the nozzles 9 do not strike the respectively neighboring nozzle 9.
  • the nozzles 9 are screwed to web plates 22 or welded to them.
  • the tubes 7 are also welded to these web plates 22, so that the individual impellers 6 each form a disk-shaped component.
  • the individual turbine stages are sealed off from one another and from the atmosphere by means of stuffing boxes 23 or similar seals, which are only schematically indicated in FIG. 3.
EP81101580A 1980-03-08 1981-03-05 Dampfturbine Expired EP0035757B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81101580T ATE17774T1 (de) 1980-03-08 1981-03-05 Dampfturbine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803008973 DE3008973A1 (de) 1980-03-08 1980-03-08 Dampfturbine
DE3008973 1980-03-08

Publications (2)

Publication Number Publication Date
EP0035757A1 EP0035757A1 (de) 1981-09-16
EP0035757B1 true EP0035757B1 (de) 1986-01-29

Family

ID=6096637

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81101580A Expired EP0035757B1 (de) 1980-03-08 1981-03-05 Dampfturbine

Country Status (3)

Country Link
EP (1) EP0035757B1 (ja)
AT (1) ATE17774T1 (ja)
DE (2) DE3008973A1 (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101229575B1 (ko) 2011-10-05 2013-02-05 주식회사 에이치케이터빈 반작용식 터빈장치 및 이의 제조방법
KR101392496B1 (ko) * 2011-09-30 2014-05-12 주식회사 에이치케이터빈 반작용식 터빈장치

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3827450A1 (de) * 1988-08-12 1990-02-15 Weh Herbert Schwingungsarme ausfuehrung von transversalflussmaschinen
GB2240817A (en) * 1990-02-09 1991-08-14 Vni I Kt I Kompressornogo Mash Reaction-jet turbine
AUPM896094A0 (en) * 1994-10-24 1994-11-17 Ward, Charles Water turbine
DE10008721A1 (de) * 2000-02-24 2001-08-30 Siemens Ag Gas- und Dampfturbinenantrieb für ein Schiff
DE10045379A1 (de) * 2000-09-12 2002-03-28 Juergen Balck Turbine, für die Energieumwandlung von physikalischer Energie in mechanischer Energie für den Antrieb technischer Geräte
US7786192B2 (en) 2006-07-14 2010-08-31 University Of Florida Research Foundation, Inc. Nanomodified concrete additive and high performance cement past and concrete therefrom
KR100905963B1 (ko) 2007-03-27 2009-07-06 김기태 반작용식 스팀 터빈
KR101052253B1 (ko) * 2007-10-11 2011-07-27 주식회사 에이치케이터빈 반작용식 터빈
WO2010107146A1 (ko) * 2009-03-18 2010-09-23 Kim Ki-Tae 반작용식 터빈
JP5625117B2 (ja) * 2010-08-31 2014-11-12 エイチケー タービン カンパニー リミテッドＨｋ Ｔｕｒｂｉｎｅ Ｃｏ．，Ｌｔｄ． 反作用式タービン
ES2424171B1 (es) * 2010-12-22 2014-07-25 Francisco BARBA TRIGUEROS Dispositivo (turbina) para la conversión de la energía térmica de un fluido, en energía cinética (mecánica) mediante un proceso de expansión, sin la utilización de álabes, ni rotóricos ni estatóricos
KR101092783B1 (ko) * 2011-03-02 2011-12-09 김기태 가스터빈
KR101388216B1 (ko) * 2011-03-28 2014-04-23 주식회사 에이치케이터빈 반작용식 터빈
KR101303343B1 (ko) * 2011-09-30 2013-09-03 주식회사 에이치케이터빈 반작용식 터빈장치
KR101368408B1 (ko) * 2012-05-08 2014-03-03 주식회사 에이치케이터빈 반작용식 터빈
KR101589260B1 (ko) * 2012-05-10 2016-01-28 주식회사 에이치케이터빈 반작용식 터빈
ES2479166B1 (es) * 2013-01-23 2015-05-11 Cristobal Lozano Fernandez Turbina de toberas a doble reacción
ITRN20130006A1 (it) * 2013-02-04 2014-08-05 Giancarlo Fabbri Turbina idraulica a immissione centrale e flusso centrifugo
KR20150038770A (ko) * 2013-09-30 2015-04-09 포스코에너지 주식회사 반작용식 스팀 터빈용 노즐 회전체
CN105041385A (zh) * 2015-06-01 2015-11-11 王瀚诚 一字水滴型转子喷射式旋转马达
DE102017005615A1 (de) 2017-06-14 2018-12-20 Erol Kisikli Turbine
CN109339867A (zh) * 2018-11-15 2019-02-15 翁志远 反动喷嘴式叶轮、转子、汽轮机、汽轮设备及原动机

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE181146C (ja) *
FR345573A (fr) * 1904-08-13 1904-12-05 Louis Dubois Turbine à vapeur à admission centrale
DE446413C (de) * 1924-11-18 1927-06-30 Rudolf Wagner Dr Laeufer fuer Rueckdruck-Dampf- oder -Gasturbinen
FR633236A (fr) * 1927-04-23 1928-01-25 Turbine
DE504502C (de) * 1925-06-18 1930-08-05 Rudolf Wagner Dr Laeufer fuer Rueckdruckdampf- oder Gasturbinen
CH161928A (de) * 1931-09-14 1933-05-31 Oerlikon Maschf Gasturbine.
DE1109452B (de) * 1955-05-17 1961-06-22 Henri Moulin Rueckdruck-Brennkraftturbine
US3032988A (en) * 1959-06-10 1962-05-08 Loyal W Kleckner Jet reaction turbine
DE2607600A1 (de) * 1976-02-25 1977-09-01 Georg Sontheimer Antriebsrad fuer stroemungsmaschinen, insbesondere fuer gas- und dampfturbinen
US4124993A (en) * 1975-07-14 1978-11-14 Michael Eskeli Refrigeration machine
DE2739055A1 (de) * 1977-08-30 1979-03-08 Siemens Ag Fluidmotor nach dem reaktionsprinzip
US4178125A (en) * 1977-10-19 1979-12-11 Dauvergne Hector A Bucket-less turbine wheel

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2613418C3 (de) * 1976-03-30 1981-05-27 Dipl.-Ing. Paul 6050 Offenbach Morcov Verfahren und Vorrichtung zur Erzeugung von Hochdruckdampf

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE181146C (ja) *
FR345573A (fr) * 1904-08-13 1904-12-05 Louis Dubois Turbine à vapeur à admission centrale
DE446413C (de) * 1924-11-18 1927-06-30 Rudolf Wagner Dr Laeufer fuer Rueckdruck-Dampf- oder -Gasturbinen
DE504502C (de) * 1925-06-18 1930-08-05 Rudolf Wagner Dr Laeufer fuer Rueckdruckdampf- oder Gasturbinen
FR633236A (fr) * 1927-04-23 1928-01-25 Turbine
CH161928A (de) * 1931-09-14 1933-05-31 Oerlikon Maschf Gasturbine.
DE1109452B (de) * 1955-05-17 1961-06-22 Henri Moulin Rueckdruck-Brennkraftturbine
US3032988A (en) * 1959-06-10 1962-05-08 Loyal W Kleckner Jet reaction turbine
US4124993A (en) * 1975-07-14 1978-11-14 Michael Eskeli Refrigeration machine
DE2607600A1 (de) * 1976-02-25 1977-09-01 Georg Sontheimer Antriebsrad fuer stroemungsmaschinen, insbesondere fuer gas- und dampfturbinen
DE2739055A1 (de) * 1977-08-30 1979-03-08 Siemens Ag Fluidmotor nach dem reaktionsprinzip
US4178125A (en) * 1977-10-19 1979-12-11 Dauvergne Hector A Bucket-less turbine wheel

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101392496B1 (ko) * 2011-09-30 2014-05-12 주식회사 에이치케이터빈 반작용식 터빈장치
KR101229575B1 (ko) 2011-10-05 2013-02-05 주식회사 에이치케이터빈 반작용식 터빈장치 및 이의 제조방법

Also Published As

Publication number Publication date
EP0035757A1 (de) 1981-09-16
ATE17774T1 (de) 1986-02-15
DE3008973A1 (de) 1981-09-24
DE3173593D1 (en) 1986-03-13

Similar Documents

Publication Publication Date Title
EP0035757B1 (de) Dampfturbine
EP0953100B1 (de) Dampfturbine
DE2518919A1 (de) Kreiselverdichter-gasturbinenanlage
DE2356721B2 (de) Kühleinrichtung für hohle Laufschaufeln einer axial durchströmten Turbine
DE1130646B (de) Diagonalgasturbinen-Energieanlage
DE2907748A1 (de) Einrichtung zur minimierung und konstanthaltung der bei axialturbinen vorhandenen schaufelspitzenspiele, insbesondere fuer gasturbinentriebwerke
DD237533A5 (de) Seitenkanalpumpe mit kraefteausgleich
DE3801914A1 (de) Zugdampfkolben-ausgleichseinrichtung
DE2821233A1 (de) Stroemungsmaschine mit zwei aufeinanderfolgenden radial-axialen umlenkungen der stroemungswege im laufrad
EP0992656B1 (de) Strömungsmaschine zum Verdichten oder Entspannen eines komprimierbaren Mediums
DE1601664A1 (de) Anordnung fuer den Durchtritt von Gas durch den Mantel eines Rotors
WO2004094087A1 (de) Strangführungsrolle
DE2907749A1 (de) Einrichtung zur minimierung und konstanthaltung der bei axialturbinen vorhandenen schaufelspitzenspiele, insbesondere fuer gasturbinentriebwerke
CH663251A5 (de) Einrichtung zur kuehlung der rotoren von dampfturbinen.
DE1481565A1 (de) Schubumkehrvorrichtung
DE2503493C2 (de) Thermische Turbomaschine, insbesondere Niederdruck-Dampfturbine
DE2412242C2 (de) Mantelstromtriebwerk
DE2128233B2 (de) Radialverdichter
DE112019001682T5 (de) Dampfturbinenanlage und Kombikraftwerk
DE3424141A1 (de) Luftspeicher-gasturbine
DE915217C (de) Dampf- oder Gasturbine mit mehrfach vom gleichen Dampf- bzw. Gasstrom beaufschlagtem Laufkranz
DE112019002207T5 (de) Dampfturbinenanlage und Kombikraftwerk
DE818277C (de) Brennkraftturbine fuer Strahlantrieb
DE102020103384A1 (de) Schraubenverdichter mit einseitig gelagerten Rotoren
DE696872C (de) Kreiselmaschine, insbesondere Dampf- oder Gasturbine, mit einem fliegend angeordneten mehrstufigen, vorzugsweise radial beaufschlagten Vorschaltteil und einem nachgeschalteten Niederdruckteil am gleichen Wellenstrang

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

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

17P Request for examination filed

Effective date: 19820225

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

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

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

Ref country code: NL

Effective date: 19860129

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 19860129

REF Corresponds to:

Ref document number: 17774

Country of ref document: AT

Date of ref document: 19860215

Kind code of ref document: T

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

Ref country code: SE

Effective date: 19860131

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

Ref country code: AT

Effective date: 19860305

REF Corresponds to:

Ref document number: 3173593

Country of ref document: DE

Date of ref document: 19860313

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

Ref country code: LI

Effective date: 19860331

Ref country code: CH

Effective date: 19860331

ET Fr: translation filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
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

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed
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: 19871130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19881118

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

Ref country code: DE

Payment date: 19901017

Year of fee payment: 10

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

Ref country code: DE

Effective date: 19920101