EP0455763B1 - Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine - Google Patents

Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine Download PDF

Info

Publication number
EP0455763B1
EP0455763B1 EP90915300A EP90915300A EP0455763B1 EP 0455763 B1 EP0455763 B1 EP 0455763B1 EP 90915300 A EP90915300 A EP 90915300A EP 90915300 A EP90915300 A EP 90915300A EP 0455763 B1 EP0455763 B1 EP 0455763B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
piston
accumulator
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90915300A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0455763A1 (de
Inventor
Helmut Rembold
Ernst Linder
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
Publication of EP0455763A1 publication Critical patent/EP0455763A1/de
Application granted granted Critical
Publication of EP0455763B1 publication Critical patent/EP0455763B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a hydraulic valve control device for an internal combustion engine according to the preamble of the main claim.
  • the pressure line is controlled via a 2/2-way valve by, according to a special exemplary embodiment (FIGS. 8 and 9), the directional valve in one switching position, the pressure line with the Pressure chamber of a valve lifter and in the other switching position with the pressure chamber of another valve lifter connects and this using only a single liquid reservoir for both print rooms.
  • One control position of the solenoid valve is used for two engine intake valves and only one accumulator is used for both intake valves.
  • the precision of the control i.e.
  • valve control device with the characterizing features of claim 1 has the advantage that to switch on the liquid reservoir, ie to open the connection between the pressure line and the storage space, the storage piston only has to be shifted slightly from its rest position. All possible control devices are conceivable for such a slight displacement. In any case, however, the accumulator piston is only moved further if a corresponding hydraulic pressure is present in the pressure chamber of the valve tappet, which hydraulic pressure can only be present if the drive cam acts on this valve tappet. Accordingly, in all those valve control units in which the drive cam is not currently effective, the displacement of the storage piston from its rest position has no further effect.
  • the bottom edge of the accumulator piston which cooperates with a fixed seat, is preferably used for this control, so that, in the rest or initial position of the accumulator piston, the pressure channel is delimited radially by the circumferential surface of the accumulator piston, while the accumulator space is delimited by the end face.
  • an annular groove in the area of the seat be formed around the lateral surface, so that the pressure channel opens into this annular groove, as in the valve control device previously proposed above.
  • this "accumulator solenoid valve” is open when de-energized, so that when the magnet is not energized, the pressure that expands from the pressure chamber via the pressure channel during the opening action of the drive cam shifts the accumulator piston from the accumulator chamber, as well as when the power supply fails. This is to ensure that if the plug on the solenoid valve fails, the motor cannot go through, but at the expense of a considerable reduction in function, apart from a rather complicated structure of this "storage solenoid valve".
  • the valve control device according to the invention enables the actual control device to be uncoupled from the high-pressure valve store.
  • a slide control of the storage piston can of course also be provided, according to which the pressure channel is connected to the storage space only after a certain minimum path of the storage piston has been covered.
  • the accumulator piston can be displaced from its rest position by means of a control piston, the control piston for its adjustment, which results in the displacement of the accumulator piston, being acted upon by control fluid of low pressure in its working space, which can be supplied to the work area from a liquid source (engine oil circuit) via a control line and the control line can be controlled by the solenoid valve.
  • control fluid of low pressure in its working space which can be supplied to the work area from a liquid source (engine oil circuit) via a control line and the control line can be controlled by the solenoid valve.
  • control piston is additionally loaded in the direction of the storage piston by a spring.
  • this is a relatively weak spring, it nevertheless ensures that there is a positive connection between the accumulator piston and the control piston, in order to avoid any advance causing a control error.
  • a radially sealingly guided pressure pin is used for the transmission of movement and force between the control piston and the storage piston.
  • a pressure pin enables a largely free choice of cross-section of the control piston, so that, despite the low pressure of the control fluid, a sufficient actuating force is ensured for safely lifting the storage piston out of its rest position.
  • the frictional forces of a radial seal on such a pressure pin are lower than in the case of a control piston of relatively large diameter.
  • valve control unit is assigned to each engine cylinder, several of them become simultaneous Pressure lines controlled by only one solenoid valve, in which only such valve control units are controlled by the solenoid valve, in which the drive caused by the engine camshaft with drive cams does not overlap in time.
  • several pressure lines connecting the pressure chamber of the valve tappet with the respective storage chamber can be controlled with only one solenoid valve, so that costs for unnecessary solenoid valves are saved and, in addition, the susceptibility to faults is reduced.
  • the accumulators can be arranged very close to the valve lifters in order to keep the control volume and the construction volume as small as possible. The assignment of a valve tappet to a storage piston, which is important for good control precision, is advantageously retained.
  • engine oil which is under delivery pressure serves as the liquid source and can be removed from the engine oil circuit which is usually present in every engine without an additional pump.
  • an extra control oil circuit for the engine valve control can be present in multi-cylinder internal combustion engines.
  • the working space of the control piston is on the control line is connected upstream of the solenoid valve, a throttle being present in the control line upstream of this connection.
  • This throttle decouples the area between the throttle and the solenoid valve, so that when the solenoid valve is open, the pressure in this intermediate section drops to such an extent that the control piston or accumulator piston remains loaded in the initial or rest position by the accumulator spring. It is a kind of passive control, in which an adjustment is only carried out when the solenoid valve is closed and this creates a dynamic pressure in the control line.
  • the solenoid valve is designed as a 2/2-way valve.
  • such a valve can be designed to be extremely simple, since absolute tightness is not required and leaks do not have a disruptive effect as long as the amount of oil flowing in via the throttle maintains the dynamic pressure.
  • the control fluid which flows continuously when the solenoid valve is open, ensures that all rooms are filled evenly and that the fluid in the control line is renewed evenly.
  • the working space of the control piston is downstream of the solenoid valve on the control line connected. This ensures that the pump for the control liquid is less stressed, since only small amounts of liquid have to be replaced for the control process, namely what the control piston swallows during its stroke. In addition, due to the relatively large possible cross sections, a quick reaction when actuating the control piston can be achieved.
  • the solenoid valve is designed as a 3/2-way valve.
  • the storage space is connected via a compensating line to the low pressure fluid source (engine oil circuit), a non-return valve opening in the direction of the storage space being arranged in the compensating line.
  • a first embodiment of a hydraulic valve control device is shown in longitudinal section and as a hydraulic circuit diagram, which between a valve stem carrying a valve stem 2 and one with a Camshaft 3 rotating drive cam 4 is arranged.
  • the valve stem 2 is guided in an axially displaceable manner in a valve housing 5 and is loaded in the closing direction of the valve by valve closing springs 6 and 7, as a result of which the valve plate 1 is pressed onto a valve seat 8 in the valve housing 5.
  • the valve disk 1 controls a valve inlet opening 9 formed between it and the valve seat 8 when the valve is open.
  • the hydraulic valve control device has a control housing 11 inserted into the valve housing 5, in which a housing chamber and a spring chamber 12 are arranged coaxially therewith, the valve closing springs 6 and 7 being accommodated coaxially to one another in the spring chamber 12.
  • a cup-shaped spring plate 13 which is anchored to the valve stem 2 and axially displaceable and loaded by the valve closing springs 6 and 7, is inserted from below.
  • a valve piston 15 cooperating with the valve stem 2 of the inlet valve and, above this, a working piston 16 of a cam piston 17 are arranged so as to be axially displaceable.
  • the working piston 16 is loaded by a return spring 18 which is supported on the one hand on the control housing 11 and on the other hand engages a flange of the working piston 16 and thereby presses the cam piston 17 against the valve control cam 4.
  • An oil-filled pressure chamber 19 is enclosed in the housing bore 14 between the mutually facing end faces of the valve piston 15 and the working piston 16, the effective length of the entire valve tappet being determined by the amount of oil that is present in the pressure chamber 19.
  • the effective opening stroke of the inlet valve is smaller when the amount of oil enclosed is reduced, and the stroke is maximal when the maximum filling is maintained.
  • the pressure chamber 19 is connected via a pressure channel 21 to a storage valve 22, which has a radially sealing cup-shaped storage piston 23 which is loaded by a storage spring 24 and rests on a valve seat in its rest position shown in broken lines.
  • the lower end face of the storage piston 23 delimits a storage space 26, while part of the outer surface of the storage piston 23 delimits an annular channel 27 surrounding the latter, into which the pressure channel 21 opens.
  • the valve control device works with a hydraulic circuit, with a feed pump 28, which draws in the control oil from an oil tank 29 and supplies it to the control device via a feed line 31.
  • a pressure control valve 33 is arranged in a line 32 branching off from the delivery line 31 and returning to the oil container 29.
  • the delivery line 31 leads on the one hand to the ring channel 27 or pressure channel 21 and pressure chamber 19 and on the other hand to the storage space 26.
  • Check valves 34 and 35 opening towards the ring channel 27 and the storage space 26 are arranged in both line sections.
  • the core of the control system is a 2/2-way solenoid valve 36, with which a control line 37 is controlled, which branches off from the delivery line 31 and leads to a working space 38, in which a control piston 39 is radially sealed and axially displaceable by the one in the control line 37 hydraulic pressure is applied.
  • the control piston 39 is relieved of pressure on the side facing away from the working space 38 via a relief channel 41 to a return line 42 of the hydraulic circuit leading to the oil tank 29 without pressure.
  • the control piston 39 is arranged coaxially with the storage piston 23, a pressure pin 43 being provided between the two mutually facing end faces of the pistons and being guided in the housing in a radially sealing and axially displaceable manner.
  • control piston 39 is loaded by a spring 44 in the direction of the storage piston 23.
  • This spring has only a small force and is not in itself able to overcome the force of the storage spring 24.
  • a control line 45 branches off from the control line 37 and leads to a further valve control unit.
  • a throttle 46 is arranged in the control line 37 upstream of the working space 38 downstream of the branch point of the delivery line 31.
  • the control line 37 opens into the unpressurized return line 42 downstream of the solenoid valve 36.
  • further delivery lines 47 branch off from the delivery line 31, which on the one hand lead to the valve control devices controlled by the same solenoid valve 36 and on the other hand supply the remaining valve control devices of the internal combustion engine with hydraulic oil .
  • the control line 48 branches off from the delivery line 31 upstream of the solenoid valve 49.
  • the solenoid valve is designed as a 3/2 solenoid valve (3 connections / 2 positions).
  • the control line 48 designed here as a sack line ends in the working space 38 of the control piston 39, the control piston 39 being arranged between the pressure pin 43 and the spring 44, as in the first exemplary embodiment.
  • the second control line 51 branches off from the control line 48 and leads to the pressure chamber of another one Valve control device leads and which is also designed as a bag line.
  • FIG. 3 the opening stroke h of four intake valves I, II, III and IV of a four-cylinder internal combustion engine is shown via the crankshaft rotation angle ° KW.
  • the ignition sequence of this internal combustion engine is one, three, four, two of the side-by-side engine cylinders with the intake valves I to IV.
  • a crank angle 0 is assumed when the cam of motor valve III is just beginning to drive its valve, which then extends to over 200 ° until the valve closes KW can go.
  • the control cam of the engine valve IV already begins to act on the cam piston 17 assigned to it, so that here the inlet valve of the cylinder IV opens before the inlet valve of the cylinder III is closed.
  • the control cam 4 of the engine valve II which becomes effective from 360 ° KW and from 540 ° KW the start of opening of the engine valve I.
  • any interventions in the stroke of an intake valve can therefore only take place if a valve control cam for actuation of the valve acts on the cam piston 17 assigned to it.
  • the respective stroke control per inlet valve is indicated in the valve control curves in FIG. 3 by the various groups of curves indicated for each engine valve I to IV for 4 different desired control values.
  • the control surface of the valve control cam 4 runs on the cam piston 17, which presses the working piston 16 downward against the force of the return spring 18 and thereby the valve piston 15 via the oil volume enclosed in the pressure chamber 19 including valve stem 2 and inlet valve plate 1 presses against the force of the valve closing springs 6 and 7 downward, the valve plate 1 lifting off the valve seat 8.
  • this control process namely a reduction in the opening time cross section, is achieved by opening the solenoid valve 49. It is only because of the dynamic pressure in the control line 48 that the control piston 39 is displaced after the solenoid valve 49 is closed and causes the storage piston 23 to be lifted from the valve seat 25 accordingly.
  • valve control units can be controlled via only one solenoid valve.
  • branching control lines 45 and 51 then go from the control lines 37 and 48 to these control units which are not simultaneously effective.
  • the branching control line 45 which leads to the valve control unit of the engine valve II as described above, transmits this dynamic pressure from the control line 37 to the control piston 39 provided on the engine valve II, which likewise causes the storage piston 23 to be displaced from its rest position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP90915300A 1989-11-25 1990-10-26 Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine Expired - Lifetime EP0455763B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3939002A DE3939002A1 (de) 1989-11-25 1989-11-25 Hydraulische ventilsteuervorrichtung fuer eine mehrzylinder-brennkraftmaschine
DE3939002 1989-11-25

Publications (2)

Publication Number Publication Date
EP0455763A1 EP0455763A1 (de) 1991-11-13
EP0455763B1 true EP0455763B1 (de) 1993-12-29

Family

ID=6394155

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90915300A Expired - Lifetime EP0455763B1 (de) 1989-11-25 1990-10-26 Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine

Country Status (6)

Country Link
US (1) US5165369A (es)
EP (1) EP0455763B1 (es)
JP (1) JPH04502950A (es)
DE (2) DE3939002A1 (es)
ES (1) ES2048509T3 (es)
WO (1) WO1991008380A1 (es)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5451029A (en) * 1992-06-05 1995-09-19 Volkswagen Ag Variable valve control arrangement
DE4228517A1 (de) * 1992-08-27 1994-03-03 Man Nutzfahrzeuge Ag Dieselbrennkraftmaschine
US5327858A (en) * 1992-09-25 1994-07-12 Hausknecht Louis A Flow restriction controlled variable engine valve system
US5233951A (en) * 1992-09-25 1993-08-10 Hausknecht Louis A Flow restriction controlled variable engine valve system
DE10158873A1 (de) * 2001-11-30 2003-06-12 Daimler Chrysler Ag Hydraulische Auslassventilbetätigung
DE10224038A1 (de) * 2002-05-31 2003-12-11 Ina Schaeffler Kg Hydraulisch betätigter, variabler Ventiltrieb einer Brennkraftmaschine
FI117348B (fi) * 2004-02-24 2006-09-15 Taimo Tapio Stenman Hydraulinen laitejärjestely polttomoottorin venttiilien toiminnan ohjaamiseksi
US20080178149A1 (en) * 2007-01-24 2008-07-24 Peterson James G Inferencing types of variables in a dynamically typed language
CL2008000317A1 (es) * 2008-02-01 2008-03-28 Servicios Asoc A M Limitada Piloto para valvula reguladora de presion que tiene una tuberia de comunicacion, entre la camara de la valvula y una fuente de presion alta, que esta interrumpida por un elemento de cierre con accionamiento electrico.
KR101145631B1 (ko) * 2009-12-04 2012-05-15 기아자동차주식회사 전기-유압 가변 밸브 리프트 장치
DE102015004868A1 (de) 2015-04-13 2016-10-13 Bernd Niethammer Pumpe für ein SCR-System in Fahrzeugen
US10233795B2 (en) * 2017-02-15 2019-03-19 Schaeffler Technologies AG & Co. KG Bypass valve for pressure oscillation control
DE102017005069A1 (de) * 2017-05-22 2018-11-22 Bernd Niethammer Einrichtung zur Verstellung des Hubes eines Ventils von Verbrennungsmotoren

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2825316A1 (de) * 1978-06-09 1979-12-20 Maschf Augsburg Nuernberg Ag Regelbare hydraulische ventilsteuerung fuer hubkolbenkraft- oder arbeitsmaschinen
DE3135650A1 (de) * 1981-09-09 1983-03-17 Robert Bosch Gmbh, 7000 Stuttgart "ventilsteuerung fuer hubkolben-brennkraftmaschinen mit mechanisch-hydraulischen bewegungsuebertragungsmitteln"
JPH0612058B2 (ja) * 1984-12-27 1994-02-16 トヨタ自動車株式会社 可変バルブタイミング・リフト装置
DE3511820A1 (de) * 1985-03-30 1986-10-02 Robert Bosch Gmbh, 7000 Stuttgart Ventilsteuervorrichtung fuer eine hubkolben-brennkraftmaschine
DE3511819A1 (de) * 1985-03-30 1986-10-09 Robert Bosch Gmbh, 7000 Stuttgart Ventilsteuervorrichtung
DE3532549A1 (de) * 1985-09-12 1987-03-19 Bosch Gmbh Robert Ventilsteuervorrichtung
US4716863A (en) * 1985-11-15 1988-01-05 Pruzan Daniel A Internal combustion engine valve actuation system
JPH01134018A (ja) * 1987-11-19 1989-05-26 Honda Motor Co Ltd 内燃機関の動弁装置
DE3807699A1 (de) * 1988-03-09 1989-09-21 Audi Ag Regelbare hydraulische ventilsteuerung
DE3815668A1 (de) * 1988-05-07 1989-11-16 Bosch Gmbh Robert Ventilsteuervorrichtung mit magnetventil fuer brennkraftmaschinen

Also Published As

Publication number Publication date
EP0455763A1 (de) 1991-11-13
JPH04502950A (ja) 1992-05-28
WO1991008380A1 (de) 1991-06-13
ES2048509T3 (es) 1994-03-16
DE3939002A1 (de) 1991-05-29
DE59004046D1 (de) 1994-02-10
US5165369A (en) 1992-11-24

Similar Documents

Publication Publication Date Title
EP0736672B1 (de) Verfahren zur Motorbremsung mit einem 4-Takt-Verbrennungsmotor
DE69014894T2 (de) Brennkraftmaschine mit solenoidkontrolle der ventile und akkumulator zur druckrückgewinnung.
EP0455762B1 (de) Elektrohydraulische ventilsteuervorrichtung für brennkraftmaschinen
EP0455761B1 (de) Hydraulische ventilsteuervorrichtung für brennkraftmaschinen
EP0909883B1 (de) Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine
DE3511820A1 (de) Ventilsteuervorrichtung fuer eine hubkolben-brennkraftmaschine
EP1001143A2 (de) Ventilsteuerung für Ein- und Auslassventile von Verbrennungsmotoren
EP0455763B1 (de) Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine
DE4023853C2 (es)
EP0455760B1 (de) Hydraulische ventilsteuervorrichtung für brennkraftmaschinen
WO2003027450A1 (de) Hydraulisch gesteuerter aktuator zur betätigung eines ventils
DE4118555A1 (de) Foerderbeginnverstelleinrichtung einer kraftstoffeinspritzpumpe
EP0539320B1 (de) Vorrichtung zum hydraulischen Betätigen eines Auslassventils einer Hubkolbenbrennkraftmaschine
EP0282508B1 (de) Brennstoffeinspritzvorrichtung für eine dieselbrennkraftmaschine mit voreinspritzung
DE19939452C2 (de) Vorrichtung zur Einspritzung von Kraftstoff
EP0032168B1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen, insbesondere für Dieselmotoren
DE4202506A1 (de) Variabler ventiltrieb fuer ein hubventil
EP1415070B1 (de) Vorrichtung zur steuerung von gaswechselventilen
EP1521902B1 (de) Vorrichtung zur steuerung von gaswechselventilen
EP0346607A2 (de) Hydraulische Steuereinrichtung insbesondere für Kraftstoffeinspritzanlagen von Brennkraftmaschinen
DE4244374C2 (de) Ventilsteuervorrichtung
DE4324987A1 (de) Einrichtung zur hydraulischen Verstellung einer Nockenwelle
DE69432362T2 (de) Variables ventilverteilungssystem
DE2918867A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE19523578C2 (de) Rotationsverteiler-Kraftstoffeinspritzpumpe

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

17P Request for examination filed

Effective date: 19910622

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT SE

RAP3 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ROBERT BOSCH GMBH

17Q First examination report despatched

Effective date: 19920928

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT SE

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

Effective date: 19940111

REF Corresponds to:

Ref document number: 59004046

Country of ref document: DE

Date of ref document: 19940210

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2048509

Country of ref document: ES

Kind code of ref document: T3

ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

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: 90915300.9

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

Ref country code: GB

Payment date: 19971010

Year of fee payment: 8

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

Ref country code: SE

Payment date: 19971027

Year of fee payment: 8

Ref country code: FR

Payment date: 19971027

Year of fee payment: 8

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

Ref country code: ES

Payment date: 19971031

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: 19971229

Year of fee payment: 8

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: 19981026

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: 19981027

Ref country code: ES

Free format text: LAPSE BECAUSE OF THE APPLICANT RENOUNCES

Effective date: 19981027

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

Effective date: 19981026

EUG Se: european patent has lapsed

Ref document number: 90915300.9

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: 19990630

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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: 19990803

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20001009

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;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: 20051026