EP0865566A2 - Systeme de distribution d'un moteur a combustion interne - Google Patents

Systeme de distribution d'un moteur a combustion interne

Info

Publication number
EP0865566A2
EP0865566A2 EP96946071A EP96946071A EP0865566A2 EP 0865566 A2 EP0865566 A2 EP 0865566A2 EP 96946071 A EP96946071 A EP 96946071A EP 96946071 A EP96946071 A EP 96946071A EP 0865566 A2 EP0865566 A2 EP 0865566A2
Authority
EP
European Patent Office
Prior art keywords
shaft
intermediate member
rotating body
groove
valve train
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
EP96946071A
Other languages
German (de)
English (en)
Other versions
EP0865566B1 (fr
Inventor
Erwin Korostenski
Armin Bertsch
Reiner Walter
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
Publication of EP0865566A2 publication Critical patent/EP0865566A2/fr
Application granted granted Critical
Publication of EP0865566B1 publication Critical patent/EP0865566B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive
    • 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
    • F01L1/34413—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 composite camshafts, e.g. with cams being able to move relative to the camshaft

Definitions

  • the invention relates to a valve train of an internal combustion engine and, in particular, to a valve train of an internal combustion engine, in which a rotating body, preferably an cam, on a shaft, preferably the camshaft, can be rotated cyclically during the rotation of the shaft, in order thereby to provide variable valve control
  • FIG. 23 An adjusting mechanism disclosed in this patent application is shown in FIG. 23 and comprises a camshaft 100 with an axis of rotation 500 on which a cam 200 is mounted. Also mounted on the camshaft 100 is an inner eccentric 300, on the outer surface 320 of which is eccentric to the axis of rotation 500, an outer eccentric 400 The inner eccentric 300 and the outer eccentric 400 can be rotated via an inner eccentric ring gear 340 or an outer eccentric ring gear 440, whereby an intermediate member 490 mounted on an eccentric outer surface of the outer eccentric 400 can be displaced in a plane perpendicular to the axis of rotation 500 relative to the camshaft 100.
  • the intermediate member 490 is also included the cam 200 and the camshaft 100 coupled in terms of drive for this purpose, an axial pin 800 rotatably mounted as the first transmission element 800 with the camshaft 100 engages with a sliding block flag 810 m, which is designed with the axial pin 800 as a sliding guide formed first groove 600 em, which is formed m the intermediate member 490 one of the first groove 600 diametrically Opposing second groove 700 of the intermediate member 490 is in engagement with a sliding star lug 910, which is made of the same material as a second axial pin 900, which is rotatably mounted in a bore 110 of the cam 200
  • the rotation of the camshaft 1 is transmitted via the first axial pin 100 through its flag 110 and the first groove 600 to the intermediate member 490 and from there via the second groove 700 and the flag 910 of the second axial pin 900 to cam 200.
  • the intermediate member 490 is located In a concentric position to the camshaft 100, the cam 200 rotates synchronously with the camshaft 100.
  • the camshaft 100 is cyclically increased and then lowered every revolution Rotational speed of the cam 200 relative to the camshaft 100 instead, which is used to influence the effective opening time of a gas inlet valve, not shown, of an internal combustion engine, which is actuated via a cup tappet 205.
  • the object of the invention is to further develop the prior art described above in such a way that the friction between the components moving towards one another and thus the wear of these components is reduced with a minimal overall volume.
  • the valve train according to the invention of an internal combustion engine has a shaft which has an axis of rotation, a rotating body which is rotatably mounted with respect to the shaft, and an intermediate element which surrounds the shaft and which is arranged in the axial direction next to the rotatable rotating body and can be rotated with respect to the shaft and with the shaft via a first sliding guide and a first transmission element and drivingly connected to the rotating body via a second sliding guide and a second transmission element.
  • a third sliding guide is provided between the rotating body and the intermediate member, which represents a support between the rotating body and the intermediate member and at the same time enables a relative movement between the rotating body and the intermediate member in a direction perpendicular to the axis of rotation.
  • This third sliding guide serves to transfer the tilting moment generated by the transmission of the rotary motion to the Taking up the intermediate link
  • the support provided thereby relieves the snow bearing bearing between the intermediate link and the external eccentric, instead the support against this tilting moment takes place between the rotating body and the intermediate link, which have only a low relative speed to one another Large bearing point between the rotating body and the shaft is supported, at which only low relative speeds also occur and which is therefore only slightly loaded. As a result, the overall friction losses of the system are considerably reduced. In addition, the holding torque of the external eccentric is significantly reduced
  • the third sliding guide can be designed such that a groove is provided in the rotating body, which engages a web formed on the intermediate member.
  • the groove extends in the circumferential direction of the rotating body, being interrupted by an opening through which the Intermediate link with the web can be inserted in the radial direction
  • an intermediate disk can be accommodated in the groove.
  • the intermediate member also abuts in the area in which the groove is interrupted
  • the rotating body can be widened in the area of the bearing surface in the direction of the axis of rotation and have dimensions, which are wider than at least a partial section of the outer contour of the rotating body
  • the first transmission element comprises a radial pin which is inserted essentially perpendicular to the axis of rotation into a corresponding bore in the shaft, the radial pin being slidably received in a recess of a sliding system which is pivotably mounted in a bearing seat of the intermediate link
  • Radial pin has the advantage that when the force is introduced from the shaft into the intermediate member, the tilting moment is reduced, thereby reducing the total tilting moment that occurs.
  • the radial pin can take over the axial fixation of the rotating body and the intermediate member on the shaft
  • the second transmission element can comprise an axial pin mounted parallel to the axis of rotation in a bore of the rotating body.
  • the intermediate disk can have an interruption which ensures free access to the axial pin hm, the intermediate disk on the side opposite the interruption Has flattening, which rests on the sliding block and acts as anti-rotation device for the washer
  • the side surfaces of the sliding flange can extend to one or both sides of the axial pin beyond the circumference of its cylindrical shaft, so that the axial pin together with the sliding stone flange has an L-shape or T-shape. This increases the contact surface of the sliding flange and thus reduces it Flumblepre ⁇ sung to the groove of the intermediate member hm and in the case of a T-shape achieved a symmetrical introduction of force.
  • the bore of the rotating body in which the axial pin is mounted can be closed on the side facing away from the intermediate member and the shaft can have a longitudinal bore as well as one or more shaft oil bores running from the longitudinal bore to the outer surface of the shaft.
  • a rotating body oil bore can be arranged so that oil from the longitudinal bore of the shaft via the shaft oil bore and the rotary body oil bore into the bore for mounting the axial pin between them and the closed end of this bore, whereby the axial pin passes through the oil pressure is firmly pressed against the end wall in the groove of the intermediate link. This improves the sliding behavior of the sliding stone flag in the groove.
  • a common inner eccentric can be provided for two adjacent rotating bodies.
  • the radial pin can have a shoulder which, when assembled, can be brought into engagement with part of the inner eccentric, so that the radial pin is fixed in position in the shaft and prevents the pin from moving out of the shaft by positive engagement.
  • the shaft is preferably a camshaft and the rotating body is a cam for actuating a gas exchange valve.
  • This provides an extremely compact device for variable valve control.
  • the intermediate link can be designed so that its outer contour does not project beyond the outer contour of the cam in any operating position. This enables the use of this embodiment in the case of tappet motors.
  • IA is an exploded perspective
  • FIG. 1B is an exploded perspective view corresponding to FIG. 1A from a different perspective
  • Fig. 2 is a radial section along the line E-E in Fig. 1,
  • FIG. 3 is a front view of a rotating body designed as a cam
  • FIG. 4 is a side view of the cam according to FIG. 3,
  • FIG. 5 is a sectional view of the cam along the line C-C in FIG. 3,
  • FIG. 6 is a perspective view of the cam of FIG. 3,
  • FIG. 7 is a front view of an embodiment of an intermediate member
  • FIG. 8 shows a side view of the intermediate member according to FIG.
  • Fig. 10 is a sectional view of the link along the line I-I in Fig. 8,
  • FIG. 12 is a first side view of an embodiment of a radial pin
  • FIG. 13 is a perspective view of the radial pin of FIG. 12,
  • FIG. 14 is a top view of the radial pin of FIG. 12;
  • 15 is a first side view of an embodiment of a sliding block
  • FIG. 17 is a top view of the sliding block according to FIG. 15 in the direction of arrow X in FIG. 15,
  • Fig. 22 is a radial section along the line L-L in Fig. 21 and
  • a first embodiment of a valve drive with an adjusting mechanism for providing a variable valve control for internal combustion engines is explained below with reference to FIGS. 1-17.
  • a rotary body 10 designed as a cam is rotatably mounted on a shaft 1 designed as a camshaft, which is rotated at half the crankshaft speed during operation of the internal combustion engine, preferably by the crankshaft of the internal combustion engine (not shown).
  • an inner eccentric 91 is provided, which is rotatably fixed by a bearing block 92 to a cylinder head 93, which is only indicated.
  • An outer eccentric 90 is rotatably mounted on an outer surface of the inner eccentric 91 that is eccentric to the axis of rotation D.
  • the inner eccentric 91 can be rotated via an inner eccentric ring gear 91A, while the outer eccentric 90 can be rotated by an outer eccentric ring gear 90A which is mounted coaxially to the inner eccentric and which engages with a lug 90B in a groove 90C of the outer eccentric.
  • an intermediate member 20 which is rotatably mounted on an eccentric outer surface of the outer eccentric 90.
  • the intermediate member 20 takes one to the axis of rotation D. coaxial position or a position in which its axis of rotation is offset from the axis of rotation D of the camshaft 1.
  • the intermediate member 20 is drivingly connected to the camshaft 1 and the cam 10, so that rotation of the camshaft 1 is transmitted to the cam 10 via the intermediate member 20. If, depending on the position of the outer eccentric 90 and the inner eccentric 91, the rotation of the intermediate member 20 is concentric with the rotation of the camshaft 1, the cam 10 rotates synchronously with the camshaft 1. This becomes by corresponding displacement of the outer eccentric 90 and / or the inner eccentric 91 Intermediate member 20 shifted radially from its concentric position to the camshaft 1, there is a cyclic increase in speed or decrease in the speed of rotation of the cam 10 relative to that of the camshaft 1 with each revolution.
  • the drive connection of the camshaft 1 to the intermediate member 20 takes place via a radial pin 40, which is inserted into a corresponding radial bore 4 of the camshaft 1.
  • the camshaft 1 has a longitudinal bore 2 and the radial bore 4 has a depth which is greater than the sum of the camshaft radius and the radius of the longitudinal bore 2.
  • the radial pin 40 has a cylindrical section 42 which is completely inserted into the camshaft 1, as well as an essentially rectangular section 43 which projects from the camshaft 1.
  • a shoulder 41 is formed between the cylindrical section 42 and the rectangular section 43.
  • the shoulder 41 is designed with a radius corresponding to the curvature of the surface of the camshaft 1 (see Fig. 12). This ensures surface contact and enables the formation of a lubricating film.
  • the rectangular section 43 is slidably encompassed by a recess 51 in a sliding block 50.
  • the sliding block 50 has the shape of a cylinder segment flattened on two sides, the two rounded side surfaces 52, 53 being jacket segments of a cylinder, which are connected to one another by an end face 54.
  • the recess 51 is open to the side opposite the end face 54 and has two sliding surfaces 55, 56 for sliding contact with two opposite faces of the rectangular section 43 of the radial pin 40 and two shoulders 57, 58 for contacting a third surface of the rectangular section 43 of the radial pin 40.
  • a recess 59 is formed between the shoulders 57, 58 in order to facilitate the assembly of the radial pin 40. Namely, if the diameter of the cylindrical section 42 of the radial pin 40 is smaller than at least the larger of the two cross-sectional edges 44, 45 of its essentially rectangular section 43, the radial pin 40 can be inserted into the shaft 1 due to the recess 59 through the m overlap with the radial bore 4
  • the rectangular section 43 of the radial pin 40 and the recess 51 of the slide stem 50 are so matched in terms of their dimensions that the slide stem 50 can slide over the rectangular section 43
  • the intermediate member 20 has a bearing seat 22 which is open on the side facing the cam 10.
  • the concave side walls 25, 26 of the intermediate member 20 has a bearing seat 22 which is open on the side facing the cam 10.
  • Bearing seats 22 are designed in accordance with the radius of the side surfaces 52, 53 of the slide stem 50, so that the slide stem 50 that can be inserted through the open side of the bearing seat 22 m against the intermediate member is the bearing stem 22
  • Bearing seat 22 serves to support the slide stem 50 mm in the end face 27 provided recess 27A enables the introduction of the radial pin 40 during assembly
  • a groove 23 is formed, which engages a sliding stem lug 71, which is made of material with an axial pin 70.
  • the axial pin 70 is rotatable in a bore 13 which is closed at one end and runs parallel to the axis of rotation D.
  • Camshaft 1 can be ensured that the rotating body oil bore 19 is located in connection with the shaft oil bore 3 over the entire rotational range of the cam 10 relative to the camshaft 1.
  • the diameter of the pin of the axial pin 70 is preferably smaller than the width of the sliding block lug 21 or the groove 23.
  • the length of the pin of the axial pin 70 is preferably greater than half the width of the cam 1.
  • the intermediate member 20 has on the end face which has the open side of the groove 23 and the open side of the bearing seat 22, a web 21 which extends substantially in the circumferential direction and is interrupted by the groove 23 and the open side of the bearing seat 22.
  • the web 21 can be inserted by radial insertion into a groove 11 which is formed on the side of the cam 10 facing the intermediate member 20.
  • the groove 11 runs essentially in the circumferential direction and is interrupted by an opening 12 which enables the web 21 to be pushed in radially.
  • the depth of the groove 11 and the thickness of the web 21 are matched to one another such that a tilting moment of the intermediate member 20 can be absorbed and at the same time a radial displacement and a rotation of the intermediate member 20 relative to the cam 10 is possible.
  • the groove 11 of the cam 10 is on the intermediate member
  • the bottom of the groove 28 formed on the intermediate member 20 by the web 21 is lowered in a corresponding central region 29 relative to the upper edge of the web 21, for example in that in this central region 29 the bottom portions of the groove 28 have a changed radius of curvature.
  • the axial pin 70 is inserted with its cylindrical shaft into the bore 13 of the cam 10.
  • the sliding block 50 is inserted into the bearing seat 22 from the open side thereof.
  • the intermediate member 20 is inserted with its web 21 into the groove 11 from the side of the cam 10 opposite the bore 13 and thus the cam tip.
  • the sliding stone flag 71 enters the groove 23.
  • the intermediate member 20 and the cam 10 are axially fixed to each other.
  • the unit thus produced from the intermediate link and cam is pushed onto the camshaft and the recess of the sliding block 50 is brought into overlap with the radial bore 4 in the camshaft 1.
  • the radial pin 40 is inserted through the recess 51 into the radial bore 4.
  • the Preassembled eccentric unit with the outer eccentric 90, the inner eccentric 91 and the eccentric toothed rings 90A, 91A is pushed onto the camshaft and the outer eccentric 90 m the bearing seat of the intermediate member 20 is inserted.
  • the inner eccentric 91 covers part of the radial bore 4 and thus secures the radial pin 40 against emigration
  • FIGS. 18-20 differs from the first embodiment described above only in that the groove 11 of the cam 10 receives an intermediate disk 60 next to the web 21 of the intermediate member 20, which serves for this purpose to increase the contact surface for the intermediate member 20, in particular in the region of the opening 12 on the cam 10.
  • the intermediate disk 60 is essentially ring-shaped and has a flattened portion 62 toward the cam tip, which provides free access for the axial pin 70 and acts as an anti-rotation device Interruption 61 on the opposite side of the intermediate disk 60, an interruption 61 is provided, which provides clearance for the sliding stem 50
  • FIG. 21 shows a third embodiment, in which a common inner eccentric 91 is provided for two cams 10A, 10B.
  • an adjustment unit is provided on both sides of the camshaft bearing, so that subsequent insertion of the eccentric is not possible.
  • localities are located on the eccentric Recesses (not shown) are provided in order to be able to insert the corresponding radial bores 4 of the camshaft 1 through the recesses 51 m into the respective sliding blocks 50 m in the case of a complete pre-assembly unit comprising cams 10A, 10B, the two intermediate members 20 and the eccentrics Reference list

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un système de distribution d'un moteur à combustion interne, qui comprend un mécanisme pour une commande de soupape variable, un arbre (1) comportant un axe de rotation (D), un élément rotatif (10) monté de manière à tourner par rapport à l'arbre (1) et un élément intermédiaire (20) entourant l'arbre (1), qui est monté à proximité de l'élément rotatif (10) dans le sens axial. A des fins d'entraînement, l'élément intermédiaire (10) est relié à l'arbre (1) par une première coulisse (15) et un premier élément de transmission (40, 50) et à l'élément rotatif (10) par une deuxième coulisse (16) et un deuxième élément de transmission (70). Entre l'élément rotatif (10) et l'élément intermédiaire (20), il est prévu une troisième coulisse (30) qui fait office de support entre l'élément rotatif (10) et l'élément intermédiaire (20) et permet simultanément un mouvement relatif entre l'élément rotatif (10) et l'élément intermédiaire (20) dans une direction perpendiculaire à l'axe de rotation (D).
EP96946071A 1995-12-12 1996-12-11 Systeme de distribution d'un moteur a combustion interne Expired - Lifetime EP0865566B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19546366A DE19546366C2 (de) 1995-12-12 1995-12-12 Ventiltrieb einer Brennkraftmaschine
DE19546366 1995-12-12
PCT/DE1996/002382 WO1997021909A2 (fr) 1995-12-12 1996-12-11 Systeme de distribution d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0865566A2 true EP0865566A2 (fr) 1998-09-23
EP0865566B1 EP0865566B1 (fr) 2000-04-05

Family

ID=7779901

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96946071A Expired - Lifetime EP0865566B1 (fr) 1995-12-12 1996-12-11 Systeme de distribution d'un moteur a combustion interne

Country Status (6)

Country Link
US (1) US5979381A (fr)
EP (1) EP0865566B1 (fr)
AT (1) ATE191540T1 (fr)
AU (1) AU1869597A (fr)
DE (2) DE19546366C2 (fr)
WO (1) WO1997021909A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1610014A1 (fr) * 2004-06-25 2005-12-28 Bayerische Motoren Werke Aktiengesellschaft Mécanisme de distribution de moteur à combustion interne

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2365508A (en) * 2000-08-08 2002-02-20 Mechadyne Internat Plc Variable valve timing mechanism
JP4078051B2 (ja) * 2001-08-29 2008-04-23 本田技研工業株式会社 動弁用被動回転部材及びカムの結合体
US20080017150A1 (en) * 2004-09-15 2008-01-24 Yamaha Hatsudoki Kabushiki Kaisha Variable Valve Drive Device, Engine, and Motorcycle
DE102004056191B4 (de) * 2004-11-20 2008-08-28 Mahle Ventiltrieb Gmbh Nockenwelle für insbesondere Kraftfahrzeugmotoren
GB2424257A (en) * 2005-03-18 2006-09-20 Mechadyne Plc Single cam phaser camshaft with adjustable connections between the inner shaft and associated cam lobes
DE102008062041A1 (de) * 2008-12-12 2010-06-17 Thyssenkrupp Presta Teccenter Ag Verstellbare Nockenwellenanordnung
US8109246B2 (en) * 2009-03-09 2012-02-07 GM Global Technology Operations LLC Camshaft damping mechanism and method of assembly
DE102009035120A1 (de) 2009-07-29 2011-02-03 Neumayer Tekfor Holding Gmbh Nockenwelle
DE102011051480B4 (de) 2011-06-30 2014-11-20 Thyssenkrupp Presta Teccenter Ag Nockenwelle mit axial verschiebbarem Nockenpaket

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2644408B2 (ja) * 1991-03-29 1997-08-25 アーウィン コロステンスキー 内燃機関の連続可変バルブタイミング機構
JP3177532B2 (ja) * 1992-01-27 2001-06-18 株式会社ユニシアジェックス 内燃機関の吸排気弁駆動制御装置
ES2119503T3 (es) * 1994-12-13 1998-10-01 Erwin Korostenski Accionamiento de valvula de un motor de combustion interna.
DE19502836C2 (de) * 1995-01-30 2000-02-24 Erwin Korostenski Brennkraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9721909A2 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1610014A1 (fr) * 2004-06-25 2005-12-28 Bayerische Motoren Werke Aktiengesellschaft Mécanisme de distribution de moteur à combustion interne

Also Published As

Publication number Publication date
DE59604914D1 (de) 2000-05-11
ATE191540T1 (de) 2000-04-15
US5979381A (en) 1999-11-09
EP0865566B1 (fr) 2000-04-05
DE19546366A1 (de) 1997-06-19
AU1869597A (en) 1997-07-03
WO1997021909A3 (fr) 1997-08-07
DE19546366C2 (de) 2002-01-17
WO1997021909A2 (fr) 1997-06-19

Similar Documents

Publication Publication Date Title
DE69105265T2 (de) Nockensteuerungen.
EP1608849B1 (fr) Commande de soupape d'un moteur a combustion interne presentant une culasse
DE4404708C2 (de) Ventilsteuer-Vorrichtung für einen Verbrennungskraftmotor
DE3617140C2 (fr)
DE10148177B4 (de) Ventiltrieb mit Ventilhubumschaltung für die Gaswechselventiele eines 4-Takt-Verbrennungsmotors
DE102009048621B4 (de) Ventiltrieb für Gaswechselventile mit Verspannung von Grundnockenwelle und Nockenträger in Umfangs- oder Drehrichtung
DE4210143C2 (de) Ventilantrieb für eine Brennkraftmaschine
DE69421686T2 (de) Ventilantriebssystem für eine interne brennkraftmaschine
DE3610639A1 (de) Ventilgestaenge fuer einen viertaktmotor
EP0521412B1 (fr) Moteur à combustion interne avec culbuteur pour la commande de soupape
EP0865566B1 (fr) Systeme de distribution d'un moteur a combustion interne
DE69421170T2 (de) Nockenspitze mit exzentrischer drehbewegung
EP0797726B1 (fr) Mecanisme de distribution pour moteur a combustion interne
WO1999056008A1 (fr) Element d'appui pour un basculeur d'un mecanisme de distribution d'un moteur a combustion interne
DE3687661T2 (de) Ventilantriebmechanismus fuer brennkraftmaschine.
DE19502836C2 (de) Brennkraftmaschine
EP0686756B1 (fr) Dispositif d'entraínement de soupape avec commande indépendante et variable de l'angle d'ouverture de soupape et de la levée de la soupape
DE10109234A1 (de) Variable Ventilvorrichtung eines Verbrennungsmotors
DE19807351C2 (de) Brennkraftmaschine mit innerer Verbrennung
DE3802528A1 (de) Drehzahlreduktionseinrichtung
DE10303601A1 (de) Ventilsteuerung
DE19544412C1 (de) Ventiltrieb einer Brennkraftmaschine
DE3645157C3 (de) Ventileinstellung für eine Brennkraftmaschine
WO2004085805A1 (fr) Dispositif permettant de faire fonctionner des soupapes d'echange des gaz dans des moteurs alternatifs a pistons
DE3320981C2 (fr)

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: 19980703

AK Designated contracting states

Kind code of ref document: A2

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

17Q First examination report despatched

Effective date: 19980924

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

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

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;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.SCRIBED TIME-LIMIT

Effective date: 20000405

Ref country code: GB

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000405

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000405

Ref country code: ES

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

Effective date: 20000405

REF Corresponds to:

Ref document number: 191540

Country of ref document: AT

Date of ref document: 20000415

Kind code of ref document: T

REF Corresponds to:

Ref document number: 59604914

Country of ref document: DE

Date of ref document: 20000511

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20000705

EN Fr: translation not filed
GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 20000405

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

Ref country code: DE

Payment date: 20060630

Year of fee payment: 10

Ref country code: AT

Payment date: 20060630

Year of fee payment: 10

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: 20070703

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

Ref country code: AT

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

Effective date: 20061211