EP0446577A1 - Frein moteur pour moteur à compression d'air - Google Patents

Frein moteur pour moteur à compression d'air Download PDF

Info

Publication number
EP0446577A1
EP0446577A1 EP91100566A EP91100566A EP0446577A1 EP 0446577 A1 EP0446577 A1 EP 0446577A1 EP 91100566 A EP91100566 A EP 91100566A EP 91100566 A EP91100566 A EP 91100566A EP 0446577 A1 EP0446577 A1 EP 0446577A1
Authority
EP
European Patent Office
Prior art keywords
valve
engine
piston
solenoid valve
exhaust
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
EP91100566A
Other languages
German (de)
English (en)
Other versions
EP0446577B1 (fr
Inventor
Heribert Dipl.-Ing. Kubis
Dieter Wittmann
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.)
MAN Truck and Bus SE
Original Assignee
MAN Nutzfahrzeuge AG
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 MAN Nutzfahrzeuge AG filed Critical MAN Nutzfahrzeuge AG
Priority to AT91100566T priority Critical patent/ATE96500T1/de
Publication of EP0446577A1 publication Critical patent/EP0446577A1/fr
Application granted granted Critical
Publication of EP0446577B1 publication Critical patent/EP0446577B1/fr
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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to an engine brake according to the preamble of the claim.
  • Such an engine brake is known from DE-OS 30 26 529, in which a hydraulic linkage is provided between a cam and a push rod of an exhaust valve of an air-compressing internal combustion engine.
  • the hydraulic linkage consists of a valve lifter, which is also designed as a cylinder.
  • the cylinder receives a piston which interacts with the push rod.
  • the cylinder space between the piston and cylinder is connected to a control device which is designed as a piston pump and can be driven, for example, by a camshaft.
  • the path of the piston in the cylinder is limited so that when the valve tappet rests on the base circle of the cam by applying a pressure from the piston pump, the exhaust valve opens just enough to blow off air during engine braking during the compression phase.
  • the cylinder chamber is depressurized and the exhaust valve opens simply by the tappet striking the cam. Since the cylinder space is depressurized when it is pushed out, the force of the valve tappet is transmitted directly to the tappet rod by the piston striking the bottom of the cylinder. To compensate for leakage losses in the hydraulic linkage, the cylinder can be connected to a lubricating oil circuit via a check valve.
  • DE-OS 33 00 763 it is proposed to connect the cylinder space of the piston cooperating with the camshaft via a line to a controllable valve, so that the transmission of the movement of the piston to a valve piston can be interrupted as desired.
  • the hydraulic linkage can in turn be connected to the lubricating oil circuit via a check valve.
  • a hydraulic linkage of this type takes up a larger construction volume, since the cylinders and pistons do not form such a compact unit. In the absence of this unit, a connecting line, albeit a short one, is necessary between the cylinder spaces, which gives rise to greater inertia.
  • the application P 39 39 934 proposes to switch on a hydraulic linkage between a camshaft and an exhaust valve, the camshaft each having two elevations.
  • a first survey serves in the usual way to open the outlet valve in the push-out phase.
  • a second elevation can also raise the exhaust valve in the compression phase in order to perform braking work by throttling.
  • the switchover from normal operation to braking operation takes place by activating a solenoid valve, which branches off from a connecting line of the pistons of the hydraulic linkage.
  • the second elevation of the cam can transmit its movement to the outlet valve, so that the latter can also be raised somewhat during the compression phase and braking work is carried out by pushing out work.
  • the object of the invention is to save the complex and fault-prone pump and to make the control of the exhaust valves during braking operation more flexible by means of modern electronics.
  • a particular advantage of the engine brake according to the invention compared to the prior art is that the hydraulic pump unit required there, driven by the camshaft, to achieve the additional elevation of the exhaust valves in the compression cycle is dispensed with.
  • the additional survey in the engine brake according to the invention which is approximately the same in terms of survey characteristics and opening times, is represented by a modified exhaust cam shape and electronic control by means of "fast" solenoid valves, each of which is assigned to each exhaust tappet.
  • the electronic control according to the invention is therefore used advantageously over that by a hydraulic pump unit, since fast solenoid valves are now inexpensively manufactured and work reliably due to the widespread use of electronics in engine construction.
  • the control units and power current distributors which are anyway required for the fully electronic diesel control, which is planned as standard, can be adapted accordingly, so that for this purpose there are no significant additional costs.
  • further advantages include simplification through a smaller number of moving parts, the possibility of dispensing with external high-pressure lines, and greater flexibility with regard to the design of the outlet control times during the additional survey.
  • the hydraulic valve lash adjuster ensures that the exact exhaust valve control times are retained unchanged even when the exhaust valve is seated or the valve drive wears, so that the function is guaranteed in normal or engine braking mode, regardless of the state of wear.
  • the lack of valve clearance eliminates the need for the usual cam ramps at the beginning and end of the cam stroke to overcome the valve clearance area. This makes it possible to make the angles 2 and 6 correspondingly large in order to have sufficient time for emptying and filling the cylinder space 10.
  • a hydraulic linkage 4 is switched on according to FIG. 1 between a cam 2 and a push rod 3.
  • This hydraulic linkage 4 consists of the valve tappet 5, which at the same time takes over the function of a cylinder and a piston 6 which is movable in the axial direction, but its movement can be limited by first and second stops 7a and 7b.
  • a compensating piston 8 is arranged, which transmits the movement of the piston 6 to the push rod 3.
  • a compression spring 9 is switched on, which holds the piston 6 in the starting position.
  • the cylinder space 10 enclosed by the valve tappet 5 and the piston 6 is connected to a solenoid valve 12 via a short-held connecting line 11, the connecting line 11 again being in communication with an engine lubricating oil circuit 13 when the solenoid valve 12 is open.
  • the compensating piston 8 can be provided in the valve train as a hydraulic valve lash adjuster, which has a bore 14 which allows a cylinder space 15 between the piston 6 and the compensating piston 8 to be connected to the engine lubricating oil circuit 13 by means of a compensating line 16.
  • a spring 17 loaded valve 18 which can be designed as a ball, the bore 14 is closed, or oil can be sucked in via the compensating line 16.
  • the cam 2 is provided with a first and a second elevation 2a and 2b, the first elevation 2a bringing about the normal opening of the exhaust valve 1 during the push-out phase and the second elevation 2b opening the exhaust valve 1 in the compression phase with the engine - Brake operation is reserved.
  • the control of the solenoid valve 12 is carried out by a control device 19, which operates electronically and which receives its signals to be processed from at least one transmitter, which is designed as a sensor 20, and works on an inductive basis.
  • a control device 19 which operates electronically and which receives its signals to be processed from at least one transmitter, which is designed as a sensor 20, and works on an inductive basis.
  • two or more sensors 20 and 21 can also be provided, which are arranged offset by a certain angle on the periphery of a flywheel 23 provided with ring gear 22.
  • a camshaft gear can also be provided.
  • the voltage pulses coming from the sensors 20 and 21 are processed in the control unit 19 in such a way that the position of the cam 2 and its second elevation 2b are recognized and the angular ranges ⁇ 1 to ⁇ 6 described below in FIG. 2 are determined.
  • the pulses processed in the control unit 19 are fed to a solenoid 24 of the solenoid valve.
  • a fast solenoid valve 12 is assigned to each exhaust valve 1.
  • the control unit 19 is able to determine the position of all the cams via the sensors 20 or 21.
  • the control unit 19 is activated by a switch 25, which switch 25 can be one or two stages, so that the Motor brake is actuated in stages.
  • a throttle not shown here
  • the solenoid valve 12 is also actuated in order to open the exhaust valve 1 even during the compression phase to such an extent that push-out work is carried out in order to reduce the braking power to increase.
  • the order of the graduated engine brake can of course also be reversed in adaptation to the desired braking power.
  • the solenoid valve 12 When the engine is running, the solenoid valve 12 is permanently open and the electronic control is thus completely inactive. During the extension phase, the first elevation 2a of the cam 2 lifts the valve lifter 5. Since the solenoid valve 12 is open, no pressure can be built up in the cylinder space 10. Only when the first stop 7a in the valve tappet 5 hits the piston 6 is the movement of the valve tappet 5 transferred to the piston 6 and, via the second stop 7b, to the push rod 3, which opens the outlet valve 1. With further rotation of the cam 2, the exhaust valve 1 closes again.
  • the run-up of the valve tappet 5 on the second elevation 2b of the cam 2 has no effect, since no pressure can build up in the piston chamber 10 because of the open solenoid valve 12 and the stroke h of the tappet as a result of the second elevation 2b is equal to the free path length s between the is the first stop 7a of the valve lifter 5 and the piston 6.
  • the exhaust valve 1 thus opens only through the first elevation 2a to the exhaust stroke.
  • the switch 25 can also be designed in two stages, so that in a first stage only the normal exhaust brake is actuated and in a second stage additionally the hydropneumatic brake or vice versa. The braking power can thus be graded.
  • FIG. 2 shows a cam according to the invention with a second elevation.
  • Cam 2 is divided into sectors with angles ⁇ 1 to ⁇ 6.
  • a sector with angle ⁇ 1 serves to open the valve in the push-out phase.
  • a sector with angle ⁇ 2 fulfills the task.
  • a sector with angles .alpha.3 gives the solenoid valve 12 (FIG. 1) time to close in the motor braking mode.
  • the second elevation 2b begins in a sector with an angle ⁇ 4.
  • the solenoid valve 12 (FIG. 1) is closed and the outlet valve 1 opens in the compression phase, so that braking work can be performed in addition to the push-out phase.
  • a sector with angle ⁇ 5 gives the solenoid valve time to open.
  • a subsequent sector with angle ⁇ 6 serves to push the oil out of the cylinder space 10.
  • valve opening curve of the exhaust valve is labeled A.
  • the exhaust valve opens between bottom dead center UT and a gas exchange GOT.
  • GOT gas exchange
  • the exhaust valve 1 With additional activation of the solenoid valve 12 (FIG. 1), the exhaust valve 1 is also opened between the bottom dead center UT and an ignition ZOT by the second elevation 2b of the cam 2, so that in this phase the throttle effect of the exhaust valve 1, which is only slightly opened further push-out work is performed and compression work is destroyed, and the braking power is increased in addition to the braking power of the known exhaust brake.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
EP91100566A 1990-03-08 1991-01-18 Frein moteur pour moteur à compression d'air Expired - Lifetime EP0446577B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91100566T ATE96500T1 (de) 1990-03-08 1991-01-18 Motorbremse fuer luftverdichtende brennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4007287A DE4007287A1 (de) 1990-03-08 1990-03-08 Motorbremse fuer luftverdichtende brennkraftmaschine
DE4007287 1990-03-08

Publications (2)

Publication Number Publication Date
EP0446577A1 true EP0446577A1 (fr) 1991-09-18
EP0446577B1 EP0446577B1 (fr) 1993-10-27

Family

ID=6401676

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91100566A Expired - Lifetime EP0446577B1 (fr) 1990-03-08 1991-01-18 Frein moteur pour moteur à compression d'air

Country Status (6)

Country Link
US (1) US5086738A (fr)
EP (1) EP0446577B1 (fr)
JP (1) JPH04224215A (fr)
AT (1) ATE96500T1 (fr)
DE (2) DE4007287A1 (fr)
RU (1) RU2033548C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543210B1 (fr) * 1991-11-08 1997-05-02 IVECO FIAT S.p.A. Moteur comprenant un dispositif de freinage continu, en particulier pour un véhicule industriel
US8572964B2 (en) 2008-03-06 2013-11-05 Daimler Ag Method for recuperating energy from an exhaust gas flow and motor vehicle

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4209775A1 (de) * 1992-03-26 1993-09-30 Man Nutzfahrzeuge Ag Vorrichtung zur Steuerung eines Auslaßventils im Motor-Bremsbetrieb
US5255650A (en) * 1992-06-01 1993-10-26 Caterpillar Inc. Engine braking utilizing unit valve actuation
US5251590A (en) * 1992-06-01 1993-10-12 Caterpillar Inc. Method and apparatus for starting an engine utilizing unit valve actuation
GB9312389D0 (en) * 1993-06-16 1993-07-28 Hersham Valves Ltd Exhaust brake
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5540201A (en) 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
US5713331A (en) * 1994-12-21 1998-02-03 Mannesmann Rexroth Gmbh Injection and exhaust-brake system for an internal combustion engine having several cylinders
ES2116123T3 (es) * 1995-04-04 1998-07-01 Steyr Nutzfahrzeuge Procedimiento para el frenado por motor con un motor de combustion interna de cuatro tiempos.
EP1031706A1 (fr) * 1995-08-08 2000-08-30 Diesel Engine Retarders, Inc. Procédé de fonctionnement d'un moteur à combustion interne
DE19538729C2 (de) * 1995-10-18 1998-01-15 Daimler Benz Ag Motorbremsvorrichtung für eine Brennkraftmaschine
JP4004545B2 (ja) * 1996-09-19 2007-11-07 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング ピストンポンプ
US5787858A (en) * 1996-10-07 1998-08-04 Meneely; Vincent Allan Engine brake with controlled valve closing
RU2135785C1 (ru) * 1998-02-12 1999-08-27 Военный автомобильный институт Комбинированный моторный замедлитель грузовых автомобилей
US6085721A (en) * 1998-04-03 2000-07-11 Diesel Engine Retarders, Inc. Bar engine brake
US6092496A (en) * 1998-09-04 2000-07-25 Caterpillar Inc. Cold starting method for diesel engine with variable valve timing
DE60024838T2 (de) * 1999-08-23 2006-07-27 Toyota Jidosha K.K., Toyota Regelvorrichtung für die charakteristik von motorventilen
US6205975B1 (en) 1999-12-16 2001-03-27 Caterpillar Inc. Method and apparatus for controlling the actuation of a compression brake
RU2187660C2 (ru) * 2000-04-10 2002-08-20 Военный автомобильный институт Моторный замедлитель грузовых автомобилей
RU2186994C2 (ru) * 2000-08-15 2002-08-10 Военный автомобильный институт Моторный замедлитель для двигателя внутреннего сгорания
US6470851B1 (en) 2000-10-30 2002-10-29 Caterpillar Inc Method and apparatus of controlling the actuation of a compression brake
SE520346C2 (sv) * 2000-11-27 2003-07-01 Scania Cv Ab Förbränningsmotor som innefattar en motorbromsfunktion
RU2293864C2 (ru) * 2001-09-05 2007-02-20 Военный автомобильный институт Комбинированный моторный замедлитель грузовых автомобилей
RU2289710C2 (ru) * 2001-09-13 2006-12-20 Военный автомобильный институт Компрессионный тормоз для двигателей внутреннего сгорания грузовых автомобилей
EP1481152A2 (fr) * 2002-03-04 2004-12-01 Jenara Enterprises Ltd. Appareil et procede de ralentissement d'un moteur avec un frein d'echappement et un frein a commande de decompression
US6925976B2 (en) * 2003-03-06 2005-08-09 Jenara Enterprises Ltd. Modal variable valve actuation system for internal combustion engine and method for operating the same
DE102004048072A1 (de) * 2004-10-02 2006-04-13 Ina-Schaeffler Kg Variabler Ventiltrieb einer Brennkraftmaschine
AT500958B1 (de) * 2004-10-18 2006-10-15 Avl List Gmbh Brennkraftmaschine mit einer abgas-motorbremse
US9067489B2 (en) * 2007-10-09 2015-06-30 Toyota Motor Engineering & Manufacturing North America, Inc. System and method of preventing inadvertent check engine telltale
US7789065B2 (en) * 2008-07-09 2010-09-07 Zhou Yang Engine braking apparatus with mechanical linkage and lash adjustment
US20100037854A1 (en) * 2008-08-18 2010-02-18 Zhou Yang Apparatus and method for engine braking
CN103321759B (zh) * 2013-07-08 2016-01-13 潍柴动力股份有限公司 一种发动机、排气门制动模块及排气门制动液控系统
CN107060943B (zh) * 2017-06-07 2019-07-30 大连理工大学 一种低能耗制动开关

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2133288A5 (fr) * 1971-04-15 1972-11-24 Penhoet Loire Atlan Chan
US3786792A (en) * 1971-05-28 1974-01-22 Mack Trucks Variable valve timing system
FR2568629A1 (fr) * 1984-08-03 1986-02-07 Daimler Benz Ag Moteur a combustion interne a quatre temps

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2832542A1 (de) * 1978-07-25 1980-02-07 Maschf Augsburg Nuernberg Ag Brennkraftmaschine mit motorbremse
US4333430A (en) * 1979-06-15 1982-06-08 Rosquist Von D Engine brake
DE3026529A1 (de) * 1980-07-12 1982-02-11 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Motorbremse fuer eine verbrennungskraftmaschine
DE3300763A1 (de) * 1983-01-12 1984-07-12 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Hydraulische einrichtung zum betaetigen von gaswechselventilen
US4572114A (en) * 1984-06-01 1986-02-25 The Jacobs Manufacturing Company Process and apparatus for compression release engine retarding producing two compression release events per cylinder per engine cycle
US4592319A (en) * 1985-08-09 1986-06-03 The Jacobs Manufacturing Company Engine retarding method and apparatus
US4796573A (en) * 1987-10-02 1989-01-10 Allied-Signal Inc. Hydraulic engine valve lifter assembly
DE3923371C1 (en) * 1989-07-14 1990-06-13 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De IC engine valve control system - can adjust exhaust valve lift to give throttle effect during engine braking
DE3939934A1 (de) * 1989-12-02 1991-06-06 Man Nutzfahrzeuge Ag Ventilsteuerung fuer gaswechselventile von brennkraftmaschinen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2133288A5 (fr) * 1971-04-15 1972-11-24 Penhoet Loire Atlan Chan
US3786792A (en) * 1971-05-28 1974-01-22 Mack Trucks Variable valve timing system
FR2568629A1 (fr) * 1984-08-03 1986-02-07 Daimler Benz Ag Moteur a combustion interne a quatre temps

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543210B1 (fr) * 1991-11-08 1997-05-02 IVECO FIAT S.p.A. Moteur comprenant un dispositif de freinage continu, en particulier pour un véhicule industriel
US8572964B2 (en) 2008-03-06 2013-11-05 Daimler Ag Method for recuperating energy from an exhaust gas flow and motor vehicle

Also Published As

Publication number Publication date
JPH04224215A (ja) 1992-08-13
DE4007287A1 (de) 1991-09-12
DE4007287C2 (fr) 1992-02-20
EP0446577B1 (fr) 1993-10-27
DE59100515D1 (de) 1993-12-02
ATE96500T1 (de) 1993-11-15
US5086738A (en) 1992-02-11
RU2033548C1 (ru) 1995-04-20

Similar Documents

Publication Publication Date Title
EP0446577B1 (fr) Frein moteur pour moteur à compression d'air
EP0736672B1 (fr) Procédé de freinage moteur pour moteur à combustion interne à quatre temps
EP3033501B1 (fr) Dispositif d'actionnement de soupape permettant de modifier la course de soupape
EP2625395B1 (fr) Moteur à combustion interne à quatre temps présentant un frein moteur
EP0432404A2 (fr) Commande de soupape pour soupapes de distribution de moteurs à combustion interne
EP1596040A2 (fr) Déphaseur d'arbre à cames
DE68904693T2 (de) Vorrichtung zum umschalten der betriebsart der ventile in einer brennkraftmaschine.
DE3939065A1 (de) Hydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
EP0584575B1 (fr) Moteur à combustion interne ayant un mécanisme pour changer les modes opératoires.
DE69404799T2 (de) Bremsvorrichtung für eine Brennkraftmaschine
US5113811A (en) Hydraulic valve control device for internal combustion engines
DE4209775A1 (de) Vorrichtung zur Steuerung eines Auslaßventils im Motor-Bremsbetrieb
DE60200671T2 (de) Mechanische Dekompressions- und Vakuumsablasseinrichtung
DE10113079A1 (de) Vorrichtung und Verfahren zur Deaktivierung von Zylindern einer Brennkraftmaschine
EP0455763B1 (fr) Dispositif de commande hydraulique de soupapes pour un moteur a combustion interne multicylindre
DE4111610A1 (de) Vorrichtung zur veraenderung der steuerzeiten eines gaswechselventils
DE69432362T2 (de) Variables ventilverteilungssystem
DE60200525T2 (de) Brennkraftmaschine mit variabler hydraulischer Ventilsteuerung
DE102008015137A1 (de) Vorrichtung und Verfahen zum Betätigen mindestens eines Gaswechselventils einer Brennkraftmaschine
DE19807351C2 (de) Brennkraftmaschine mit innerer Verbrennung
EP1022444B1 (fr) Commande de soupape à régulation hydraulique pour culasse multisoupapes
DE102004048288A1 (de) Variabler Ventiltrieb einer Brennkraftmaschine
DE102006053703A1 (de) Vorrichtung zur Steuerung von Gaswechselventilen von Brennkraftmaschinen
DE4224988A1 (de) Hydrostatische ventilbetaetigung
DE102008049529B4 (de) Brennkraftmaschine mit hydraulischem Ventilspielausgleich und innerer Abgasrückführung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

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

17P Request for examination filed

Effective date: 19911029

17Q First examination report despatched

Effective date: 19921016

ITF It: translation for a ep patent filed
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 NL SE

REF Corresponds to:

Ref document number: 96500

Country of ref document: AT

Date of ref document: 19931115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 59100515

Country of ref document: DE

Date of ref document: 19931202

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

Effective date: 19931207

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: 91100566.8

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

Ref country code: SE

Payment date: 19961209

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: 19970109

Year of fee payment: 7

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

Ref country code: AT

Payment date: 19970128

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: 19970130

Year of fee payment: 7

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

Ref country code: FR

Payment date: 19970228

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: 19970311

Year of fee payment: 7

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: 19980118

Ref country code: AT

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

Effective date: 19980118

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: 19980119

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

Ref country code: FR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19980131

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

Ref country code: NL

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

Effective date: 19980801

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

Effective date: 19980118

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19980801

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: 19981001

EUG Se: european patent has lapsed

Ref document number: 91100566.8

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: IT

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

Effective date: 20050118