EP0178428B1 - Elektrisch gesteuerte Pumpedüse für die Kraftstoffeinspritzung bei Dieselbrennkraftmaschinen - Google Patents

Elektrisch gesteuerte Pumpedüse für die Kraftstoffeinspritzung bei Dieselbrennkraftmaschinen Download PDF

Info

Publication number
EP0178428B1
EP0178428B1 EP85110504A EP85110504A EP0178428B1 EP 0178428 B1 EP0178428 B1 EP 0178428B1 EP 85110504 A EP85110504 A EP 85110504A EP 85110504 A EP85110504 A EP 85110504A EP 0178428 B1 EP0178428 B1 EP 0178428B1
Authority
EP
European Patent Office
Prior art keywords
pump
overflow
duct
overflow valve
housing part
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
EP85110504A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0178428A3 (en
EP0178428A2 (de
Inventor
Jean Leblanc
Jean Pigeroulet
François Rossignol
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to AT85110504T priority Critical patent/ATE42612T1/de
Publication of EP0178428A2 publication Critical patent/EP0178428A2/de
Publication of EP0178428A3 publication Critical patent/EP0178428A3/de
Application granted granted Critical
Publication of EP0178428B1 publication Critical patent/EP0178428B1/de
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically

Definitions

  • the invention relates to an electrically controlled pump nozzle according to the preamble of the main claim.
  • a pump nozzle for diesel engines known from US Pat. No. 4,392,612
  • the pump stroke during the delivery stroke Fuel injection quantity displaced from the pump work chamber to the injection nozzle is determined by the duty cycle of a normally open, electromagnetically operated overflow valve which is inserted into an overflow channel connecting the pump work chamber with a low pressure chamber.
  • the first section of the overflow channel which is permanently connected to the pump working chamber, is then under the full injection pressure when the overflow valve for controlling the fuel injection blocks the connection between the two sections of the overflow channel and thus blocks the fuel from the low pressure chamber.
  • the overflow valve is fastened to a housing part projecting laterally at the level of the cylinder bore at the pump housing, and the first section of the overflow channel that can be set under injection pressure cannot be carried out directly from the pump work chamber to the overflow valve in such an arrangement, but instead has a kinked course.
  • This first section of the overflow channel therefore consists of a branch bore arranged laterally offset from the cylinder bore and a cross channel connecting this branch bore with a control channel controlled by the overflow valve.
  • this transverse channel has been designed to lead from the outside, from an inlet bore through the laterally projecting housing part into the branch bore.
  • the transverse channel traverses the control channel forming a control pressure chamber of the overflow valve in this pump nozzle and must be closed to the outside by a sealing plug towards the inlet.
  • Such sealing plugs form a constant risk of leakage due to the very high injection pressures of around 1,000 bar, or they are destroyed by the high pressures or driven out of the bore.
  • the aim of the invention is now, in pump nozzles of the type mentioned, in which a direct connection between the pump work chamber and the overflow valve is not possible for structural reasons, to design the first section of the overflow channel which can be set under injection pressure in such a way that an easy to produce even without sealing plug and an externally sealed connection between the pump work space and the overflow valve is guaranteed.
  • the pump piston with a lateral surface which is fitted into the cylinder bore with a play in the range of a few thousandths of a millimeter forms the necessary seal for the tap bore emanating from the pump work space with the transverse channel connecting the control valve controlled by the overflow valve.
  • No special sealing means are therefore required for the section of the transverse channel which is separated by means of the pump piston, and the transverse channel can be designed as a simple transverse bore crossing the cylinder bore.
  • a pump nozzle according to the invention which according to claim 2, as is known from the patent mentioned at the beginning, is provided with a flange surface located on the laterally projecting housing part and serving to fasten an actuator of the overflow valve, against which an end face on the overflow valve can be clamped in a pressure-tight manner Control channel to avoid inadmissibly large dead spaces as a blind hole from the flange surface in the laterally projecting housing part up to a connection point with the cross channel.
  • the overflow valve which is designed as a structural unit comprising all valve components, can thus be manufactured and tested on its own and then flanged to the projecting housing part of the pump nozzle.
  • the two sections of the overflow channel which have a very high pressure difference, are perfectly sealed against one another by the surfaces which can be easily ground flat and form a sealing gap, the flange surface on the projecting housing part and the end face of the overflow valve.
  • pressure compensation grooves can be formed in the lateral surface of the pump piston or in that according to the characteristic features of claims 4 or 5 Wall of the Zylin be introduced.
  • FIG. 1 shows a longitudinal section through the first embodiment
  • FIG. 2 shows a partial cross section along the line II-II in FIG. 1, but through the second embodiment having pressure compensation grooves in the cylinder bore.
  • the first exemplary embodiment of an electrically controlled pump nozzle 10 according to the invention shown in FIG. 1 consists of a piston injection pump 9, which is mechanically driven by a camshaft in a manner which is not shown, but is known, the pump housing, designated 11, having a pump piston driven with a constant stroke and guided in a cylinder bore 12 13 receives and at the end carries an injection nozzle 16, which is fastened by means of a screw sleeve 14 with the interposition of a pressure valve 15, of a known and therefore not shown type.
  • the pump piston 13 is driven by known drive means, which are therefore only indicated by an arrow A, via a pump tappet 17 against the restoring force of a tappet spring 18. With its end face 19, it delimits a pump working chamber 21 located in the cylinder bore 12, which is closed on the injection nozzle side by the pressure valve 15 and can be connected to the injection nozzle 16 via a pressure channel 53.
  • the pump work space 21 is in the drawn outer dead center position of the pump piston 13 by a feed pump 22 under a low inlet pressure of z. B. 4 bar of fuel supplied.
  • This fuel passes from the feed pump 22 via a feed line 23 and at least one opening 24 in the wall of the screw sleeve 14 into a low pressure chamber 25 surrounding the pressure valve 15 within the screw sleeve 14 and from there via an inlet channel 26 into the pump work chamber 21.
  • the low pressure chamber 25 and the pump working space 21 are also connected to one another via an overflow channel 28 which can be controlled by an overflow valve 27 in the drawn open position of this valve.
  • the inlet pressure of the fuel supplied to the low pressure chamber 25 from the feed pump 22 via the feed line 23 is determined by a pressure relief valve 29 which is inserted into a return line 31.
  • This return line 31 is shown interrupted as part of a ring line leading to the further pump nozzles of the same internal combustion engine and ultimately leads the excess fuel back to a tank 32.
  • the overflow valve 27 which operates as a 2/2-way valve, is a solenoid valve which is shown only partially in section in FIG. 1 to show its control function and is the subject of a parallel application with regard to its special configuration.
  • the overflow valve 27 is designed as a needle valve, the valve member 33 of which is actuated by an electric actuator 34 formed by an electromagnet and is surrounded by a pressure chamber 35 in the region of its end section facing away from the actuator 34.
  • This pressure chamber 35 is on the one hand permanently connected to the pump working chamber 21 via a first section 28a of the overflow duct 28 and on the other hand can be connected to the low-pressure chamber 25 via a second section 28b of the overflow duct 28 shown in dashed lines in FIG.
  • the open connection in FIG. 1 from the pressure chamber 35 to the low-pressure chamber 25 carries at the transition from the pressure chamber 35 to the second section 28b of the overflow channel 28 a conical valve seat 36 which can be closed by a conical closing surface 33a on the valve member 33.
  • the overflow valve 27 is fastened to a housing part 11a which projects laterally on the pump housing 11 at the level of the cylinder bore 12.
  • the first section 28a of the overflow channel which extends from the pump work chamber 21 and which, in order to achieve the compact design important according to the invention, consists of a branch bore 37, one of the overflow valve, which is connected to the pump work chamber 21 and is offset laterally to the cylinder bore 12 to the overflow valve 27 27 controlled control channel 38 and a transverse channel 39 connecting this tap hole 37 with the control channel 38.
  • the transverse channel 39 extends in the form of an oblique branch hole from the side of the housing designated 11, facing away from the lateral projecting housing part 11a, through the cylinder bore 12 to the control channel 38, thereby cutting the branch hole 37 and forming an orifice 37a at this point the branch bore 37.
  • the transverse channel 39 is placed in such a way that it crosses the cylinder bore 12 in an area which is covered by the outer surface 13a of the pump piston 13 in each stroke position.
  • the first one which is under injection pressure when the overflow valve 27 is blocked, becomes the control channel from the tap hole 37. 38 and the transverse channel 39, existing section 28a of the overflow channel 28 is sealed by means of the outer surface 13a of the pump piston 13.
  • a flange surface 11 On the laterally projecting housing part 11a there is a flange surface 11, which is arranged at right angles to the longitudinal axis of the pump piston 13 and serves to fasten the overflow valve 27, and against which an end face 27a of the overflow valve 27 is clamped in a pressure-tight manner.
  • the overflow valve 27 is both one Actuator 34 as well as all valve components, e.g. B. valve member 33, pressure chamber 35 and valve seat 36, comprehensive unit and also has in its end face 27a opening connecting channels 41a and 41b for the two sections 28a and 28b of the overflow channel 28. Due to the sealing gap which ensures a metallic seal between the flange surface 11b on the projecting housing part 11a and the end surface 27a of the overflow valve, the control channel 38 in the first section 28a of the overflow channel 28 is opposite a section of the housing section 11a which is also drilled from the flange surface 11b second section 28b of the overflow channel 28 sealed properly. This results in easy-to-produce sealing surfaces and bores on all components, which ensure proper functioning of the control of the start of injection and the delivery rate effected by the overflow valve 27.
  • all valve components e.g. B. valve member 33, pressure chamber 35 and valve seat 36, comprehensive unit and also has in its end face 27a opening connecting channels 41a and 41b for
  • the lateral surface 13a of the pump piston 13 is provided with two pressure compensation grooves 42 which are permanently connected to the pump working chamber 21 and are designed as longitudinal grooves. These pressure compensation grooves 42 are incorporated symmetrically into the lateral surface 13a of the pump piston 13 symmetrically to the longitudinal axis of the transverse channel 39 at a lateral distance from one another and to the housing side 11c facing away from the projecting housing part 11a. This distance corresponds to the distance a shown in Figure 2 to the second embodiment.
  • the second exemplary embodiment shown in FIG. 2 in a partial cross section along the line 11-11 in FIG. 1, differs from the first exemplary embodiment shown in FIG. 1 only in the modified arrangement of two pressure compensation grooves made in the wall of the cylinder bore. Since only the pump housing and the pump piston are designed differently, these and their modified components are given a reference number increased by 100, the other unchanged components are designated as in FIG. 1.
  • the two pressure equalization grooves 42 in FIG. 1 correspond in FIG. 2 to the pressure equalization grooves 142 which are incorporated into the wall of the cylinder bore 112 and which are machined symmetrically to the longitudinal axis of the transverse channel 39 and at a lateral distance a from one another into the wall of the cylinder bore 112 in the form of longitudinal grooves. They are opposite the part of the transverse channel 39 that can be set under injection pressure, i. H. they point to the housing side 11c facing away from the laterally projecting housing part 11. So that these pressure compensation grooves 142 always remain connected to the pump work space 21, they have to be carried out down to the lowest point of the pump work space 21.
  • the power supply to the actuator 34 of the overflow valve 27 is switched off in accordance with the operating data determined in an electronic control device.
  • the overflow valve 27 is switched to its open position shown in FIG. 1. As a result, the pressure in the pump work chamber 21 drops suddenly, and the injection nozzle 16 and the pressure valve 15 close, so that the injection is ended.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
EP85110504A 1984-09-14 1985-08-21 Elektrisch gesteuerte Pumpedüse für die Kraftstoffeinspritzung bei Dieselbrennkraftmaschinen Expired EP0178428B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85110504T ATE42612T1 (de) 1984-09-14 1985-08-21 Elektrisch gesteuerte pumpeduese fuer die kraftstoffeinspritzung bei dieselbrennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843433710 DE3433710A1 (de) 1984-09-14 1984-09-14 Elektrisch gesteuerte pumpeduese fuer die kraftstoffeinspritzung bei dieselbrennkraftmaschinen
DE3433710 1984-09-14

Publications (3)

Publication Number Publication Date
EP0178428A2 EP0178428A2 (de) 1986-04-23
EP0178428A3 EP0178428A3 (en) 1987-12-16
EP0178428B1 true EP0178428B1 (de) 1989-04-26

Family

ID=6245358

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85110504A Expired EP0178428B1 (de) 1984-09-14 1985-08-21 Elektrisch gesteuerte Pumpedüse für die Kraftstoffeinspritzung bei Dieselbrennkraftmaschinen

Country Status (5)

Country Link
US (1) US4669659A (enrdf_load_stackoverflow)
EP (1) EP0178428B1 (enrdf_load_stackoverflow)
JP (1) JPS6172869A (enrdf_load_stackoverflow)
AT (1) ATE42612T1 (enrdf_load_stackoverflow)
DE (2) DE3433710A1 (enrdf_load_stackoverflow)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629754C2 (de) * 1986-09-01 1994-07-14 Bosch Gmbh Robert Vorrichtung zur Erzeugung von Voreinspritzungen bei Pumpedüsen
DE3629751C2 (de) * 1986-09-01 1998-07-02 Bosch Gmbh Robert Voreinspritzvorrichtung für Brennkraftmaschinen
FR2605055B1 (fr) * 1986-10-08 1991-09-27 Daimler Benz Ag Procede d'injection directe de carburant pour un moteur diesel
GB8828157D0 (en) * 1988-12-02 1989-01-05 Lucas Ind Plc Fuel injection nozzles
US5011079A (en) * 1989-02-27 1991-04-30 Cummins Engine Company, Inc. Unit injector and drive train with improved push rod-plunger connection
DE3924127A1 (de) * 1989-07-20 1991-01-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JP2734132B2 (ja) * 1989-11-06 1998-03-30 トヨタ自動車株式会社 ユニットインジェクタ
US5072709A (en) * 1990-03-29 1991-12-17 Cummins Engine Co., Inc. Fuel injection for an internal combustion engine
GB9026838D0 (en) * 1990-12-11 1991-01-30 Lucas Ind Plc Fuel pump
GB9026840D0 (en) * 1990-12-11 1991-01-30 Lucas Ind Plc Fuel pump
US5485823A (en) * 1990-12-11 1996-01-23 Lucas Industries Public Limited Company Fuel pump having a leaked fuel conveying structure
DE4127003A1 (de) * 1991-08-16 1993-02-18 Bosch Gmbh Robert Elektrisch gesteuerte pumpeduese fuer kraftstoffeinspritzvorrichtungen in brennkraftmaschinen
BR9107316A (pt) * 1991-10-11 1994-04-19 Caterpillar Inc Conjunto de atuador e valvula para um injetor controlado eletronicamente
US5385301A (en) * 1992-10-28 1995-01-31 Zexel Corporation Fuel injector with spill off for terminating injection
DE4237726C2 (de) * 1992-11-09 1993-12-23 Hermann Dr Ing Golle Pumpedüse zur Kraftstoffeinspritzung für Brennkraftmaschinen
US5651501A (en) * 1993-12-23 1997-07-29 Caterpillar Inc. Fluid damping of a valve assembly
US5862995A (en) * 1996-04-01 1999-01-26 Diesel Technology Company High pressure fluid passage sealing for internal combustion engine fuel injectors and method of making same
US5918630A (en) * 1998-01-22 1999-07-06 Cummins Engine Company, Inc. Pin-within-a-sleeve three-way solenoid valve with side load reduction
US6109536A (en) * 1998-05-14 2000-08-29 Caterpillar Inc. Fuel injection system with cyclic intermittent spray from nozzle
DE19918984A1 (de) * 1999-04-27 2000-11-02 Deutz Ag Kraftstoffversorgungssystem einer Brennkraftmaschine
DE10055271A1 (de) * 2000-11-08 2002-05-23 Bosch Gmbh Robert Druck/Hubgesteuerter Injektor mit hydraulischem Übersetzer
DE10102234A1 (de) 2001-01-19 2002-07-25 Bosch Gmbh Robert Vorrichtung zur Kraftstoff-Hochdruckversorgung einer Brennkraftmaschine
DE10305187A1 (de) * 2003-02-08 2004-08-19 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für Brennkraftmaschinen mit Kraftstoff-Direkteinspritzung
DE102017222171A1 (de) * 2017-12-07 2019-06-13 Robert Bosch Gmbh Kraftstofffördereinrichtung für kryogene Kraftstoffe

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392612A (en) * 1982-02-19 1983-07-12 General Motors Corporation Electromagnetic unit fuel injector
US4463900A (en) * 1983-01-12 1984-08-07 General Motors Corporation Electromagnetic unit fuel injector
US4540122A (en) * 1983-10-26 1985-09-10 General Motors Corporation Electromagnetic unit fuel injector with pivotable armature
US4568021A (en) * 1984-04-02 1986-02-04 General Motors Corporation Electromagnetic unit fuel injector

Also Published As

Publication number Publication date
DE3569784D1 (en) 1989-06-01
EP0178428A3 (en) 1987-12-16
EP0178428A2 (de) 1986-04-23
JPH0551064B2 (enrdf_load_stackoverflow) 1993-07-30
ATE42612T1 (de) 1989-05-15
US4669659A (en) 1987-06-02
JPS6172869A (ja) 1986-04-14
DE3433710A1 (de) 1986-03-27

Similar Documents

Publication Publication Date Title
EP0178428B1 (de) Elektrisch gesteuerte Pumpedüse für die Kraftstoffeinspritzung bei Dieselbrennkraftmaschinen
EP0178427B1 (de) Elektrisch gesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3888468T2 (de) Elektronisch gesteuertes Brennstoffeinspritzventil.
DE3243176C2 (enrdf_load_stackoverflow)
DE2836225C2 (enrdf_load_stackoverflow)
DE3102642A1 (de) Elektromagnetisches kraftstoffeinspritzventil
DE19519191A1 (de) Einspritzventil
DE69124228T2 (de) Elektronische Hochdruckeinspritzkraftstoffleitung für Dieselmotoren
EP0657643B1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
WO1998040623A1 (de) Ventil zum steuern von flüssigkeiten
EP1131552B1 (de) Brennstoffeinspritzventil für verbrennungskraftmaschinen
EP1342005B1 (de) Kraftstoffeinspritzsystem für brennkraftmaschinen
DE19545162B4 (de) Brennstoffeinspritzvorrichtung mit federvorgespanntem Steuerventil
DE19603435A1 (de) Von Einspritzratenform- bzw. -gestaltungssteuerung geöffnetes Rückschlagventil für eine Brennstoffeinspritzdüse
DE3523536A1 (de) Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE69107405T2 (de) Hochdruck-Dichtungssystem für das Steuerventil eines elektromagnetischen Brennstoffeinspritzventils für Verbrennungsmotoren.
EP0348786A2 (de) Elektromagnetisches Kraftstoffeinspritzventil
DE4341739C1 (de) Einspritzsystem
EP1045975B1 (de) Steuereinheit zur steuerung des druckaufbaus in einer pumpeneinheit
EP1278952B1 (de) Brennstoffeinspritzventil
DE19732070C2 (de) Direkteinspritzendes Kraftstoffeinspritzventil mit Magnetventilsteuerung für eine mehrzylindrige Brennkraftmaschine
DE69117206T2 (de) Verbessertes Einspritzventil für Brennkraftmaschinen
DE3841462C2 (de) Brennstoffeinspritzvorrichtung
DE19941709A1 (de) Gebautes Steuerventil für einen Injektor eines Kraftstoffeinspritzsystems für Brennkraftmaschinen
DE4404050C1 (de) Injektor mit Magnetventilsteuerung für eine Brennkraftmaschine

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): AT DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT DE FR GB IT

17P Request for examination filed

Effective date: 19880505

17Q First examination report despatched

Effective date: 19880912

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE FR GB IT

REF Corresponds to:

Ref document number: 42612

Country of ref document: AT

Date of ref document: 19890515

Kind code of ref document: T

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

Ref document number: 3569784

Country of ref document: DE

Date of ref document: 19890601

ET Fr: translation filed
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
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19920730

Year of fee payment: 8

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

Ref country code: GB

Payment date: 19920807

Year of fee payment: 8

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

Ref country code: FR

Payment date: 19920827

Year of fee payment: 8

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

Ref country code: DE

Payment date: 19921029

Year of fee payment: 8

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

Ref country code: GB

Effective date: 19930821

Ref country code: AT

Effective date: 19930821

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

Effective date: 19930821

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

Ref country code: FR

Effective date: 19940429

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

Ref country code: DE

Effective date: 19940503

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST