EP0498682A1 - Deactivating valve operating device for an internal combustion engine - Google Patents

Deactivating valve operating device for an internal combustion engine Download PDF

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Publication number
EP0498682A1
EP0498682A1 EP92400025A EP92400025A EP0498682A1 EP 0498682 A1 EP0498682 A1 EP 0498682A1 EP 92400025 A EP92400025 A EP 92400025A EP 92400025 A EP92400025 A EP 92400025A EP 0498682 A1 EP0498682 A1 EP 0498682A1
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EP
European Patent Office
Prior art keywords
liquid
volume
pistons
control device
hydraulic
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.)
Withdrawn
Application number
EP92400025A
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German (de)
French (fr)
Inventor
Patrick Gastaldi
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.)
Renault SAS
Regie Nationale des Usines Renault
Original Assignee
Renault SAS
Regie Nationale des Usines Renault
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Publication date
Application filed by Renault SAS, Regie Nationale des Usines Renault filed Critical Renault SAS
Publication of EP0498682A1 publication Critical patent/EP0498682A1/en
Withdrawn legal-status Critical Current

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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
    • F01L1/02—Valve drive
    • F01L1/024—Belt 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • 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
    • 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 present invention relates to a valve control device with a shutdown function, in particular for a multi-valve internal combustion engine.
  • a first solution is to have a variable valve lift depending on the speed and the engine load.
  • Many devices have been developed, mention may be made of variable profile rotary cams carried by a shaft sliding along its axis as a function of an engine operating parameter; or alternatively two cams carried respectively by two parallel camshafts, the selective use of one of the cams being effected by engagement of one of the shafts or by tilting of a support of the two shafts.
  • the disadvantage of these devices is their great complexity and their significant additional cost.
  • 2,546,968 relating to a mechanism for operating valves with a shutdown function for an internal combustion engine, describes a device in which first and second rocker arms, having respective arms abutting against the upper ends of the intake or exhaust valve fitted , are articulated on a common carrier axis fixed on the body of the engine and whose geometric axis is perpendicular to the directions of movement of the valves;
  • the first rocker has a bore forming a cylinder which opens towards the second rocker to carry a plunger in its interior while the second rocker has a guide bore opening towards the first rocker so that the plunger fits there;
  • a hydraulic operating chamber defined between the bottom of the cylinder bore and the rear end of the plunger is connected to a source of pressurized oil through a hydraulic permutation valve intended to permute the sending and non-sending of 'oil under pressure in the operating chamber; and one or the other of the first and second rocker arms has a cam feeler intended to slide against a cam arranged to rotate according to
  • the object of the present invention is to overcome these drawbacks by providing a valve control device of limited size, which can be stopped in an extremely short time, of the order of ten milliseconds, does not interfere with the controls of the other valves, which can be used with direct drive distribution such as rocker distributions: rockers, latches, etc. and allowing more to catch the operating clearances; such an extremely flexible use device makes it possible to pass from a four-valve operation to a two-valve operation or else to pass from a four-cylinder operation to a three-cylinder operation by equipping all the valves with a cylinder.
  • the present invention relates to a valve control device with a shutdown function, for internal combustion engines, comprising a hydraulic tappet capable of transmitting or not the thrust of a cam, carried by a camshaft, to a valve stem against elastic return means, this hydraulic tappet comprising two pistons separated by a volume of liquid, in particular oil.
  • the valve control device comprises distribution means suitable for communicating the volume, comprised between the two pistons, either with means for connection to a source of pressurized liquid, or with means for connection with a liquid discharge tank, these distribution means being controlled by a high liquid source pressure depending on engine speed and / or load.
  • the distribution means comprise a first hydraulic distributor, comprising in particular a movable drawer in its housing, having at least one fluid passage duct, this drawer being able to occupy two limit positions, a first limit position wherein the drawer connects the volume between the two pistons and the means of connection to a source of pressurized liquid while all communication between said volume and the means of connection to a liquid discharge tank is cut and a second limit position in which the slide valve connects said volume and the means of connection to a liquid discharge tank while all communication between said volume and the means of connection to a source of pressurized liquid is cut off and a second hydraulic distributor allowing to operate said first distributor from a source of liquid high pressure depending on engine speed and / or load.
  • a first hydraulic distributor comprising in particular a movable drawer in its housing, having at least one fluid passage duct, this drawer being able to occupy two limit positions, a first limit position wherein the drawer connects the volume between the two pistons and the means of connection to a source of pressurized liquid while all communication between
  • the drawer of the first hydraulic distributor defines in its housing two chambers, a first chamber, in which are arranged elastic pressure means which act on the drawer, and a second chamber forming part of said means of connections to a liquid discharge tank; these chambers are connected, one to a high liquid source pressure, the other to a liquid discharge tank and vice versa, via the second hydraulic distributor of the type: piloted with four ways and two positions.
  • the volume between the two pistons is limited axially by the two pistons and transversely by a bore, slidingly receiving the two pistons, in which open at least one recess which also communicates with the housing of the first hydraulic distributor, the axial length of the recess being sufficient to ensure permanent communication between said volume and said recess.
  • the means for connecting to a source of pressurized liquid notably comprise a cavity forming a hydraulic shock absorber, this cavity opening into the housing of said first distributor, means forming a valve and a pressure reducing valve ensuring regulation of the pressure of the liquid supplying said cavity.
  • said movable drawer consists of a substantially cylindrical sheath, coaxial with the hydraulic plunger, comprising an enlarged end forming an operating piston, this sheath having at least one lumen forming a conduit for the passage of fluid.
  • the bore in which the two pistons form stop means intended to cooperate with shoulders carried by the two pistons so as to limit the relative movement of these pistons and in particular to confine said volume inside said bore.
  • the piston of the hydraulic pusher intended to come into contact with the operating cam is subjected to the action of elastic pressure means capable of moving this piston away from the cam.
  • the source of high pressure liquid comprises in particular a supply pump, an accumulator and a discharge device of the contactor-circuit breaker type.
  • control of the distribution means is integrated into the ignition control of the engine according to a predetermined map as a function of the speed and of the load, the response time of said means being taken into account by the calculator.
  • the invention also relates to a hydraulic tappet comprising two pistons separated by a volume of liquid, in particular oil, arranged for a valve control device with a shutdown function according to the invention.
  • FIG. 1 one can see a device for controlling an intake or exhaust valve of an internal combustion engine, presented in the particular case of a mode of distribution. direct attack.
  • the control device comprises a hydraulic pusher 1 intended to transmit the thrust from a cam 52 carried by a camshaft 5 to an intake or exhaust valve 4, of an internal combustion engine of which only the parts of interest the invention have been shown, against elastic return means formed by a helical spring 31.
  • the spring 31 works in compression and tends to return the valve 4 to its closed position, which corresponds, in the representation of FIG. 1, to an upward movement of the valve stem 42.
  • the hydraulic pusher 1 comprises two pistons 2, 3 separated by a volume or cavity 6 filled with liquid, in particular oil.
  • One of the pistons, namely the piston 2 is intended to come into contact with the cam 52 while the other piston 3 is in permanent abutment against the stem of the valve 42 due to the thrust of the spring 31.
  • the pistons 2 and 3 have their ends, respectively lower and upper, slidably mounted in a housing 64 of the cylinder head 99.
  • the volume 6 is thus limited axially by the two pistons and transversely by this bore 64.
  • the piston 2 which is substantially cylindrical, carries an upper pad 26 intended to rub on the cam 52; it has a circumferential shoulder 25 on which elastic pressure means bear, formed by a helical spring 21. These means 21, also bearing on the cylinder head 99 by means of a crimped barye 22, tend to spread the piston apart 2 of the cam 52 as well as forcing the piston 2 towards the piston 3.
  • the substantially cylindrical piston 3 is blind; it has a shoulder 35 intended to cooperate with a recess of the bore 64, on its lower end support elastic pressure means, formed by a helical spring 31. These means also bearing on the cylinder head tend to force the piston 3 towards piston 2.
  • a hydraulic distributor 70 intended to control the volume of liquid 6 comprised between the two pistons 2 and 3.
  • This hydraulic distributor comprises a housing 75 of revolution extending around the pusher 1 and in which slides axially at pusher 1 a cylindrical sheath 7.
  • the sleeve 7 has an enlarged end which forms an operating piston 76 of the sleeve 7.
  • the piston 76 defines in the housing 75 two pressure chambers, a first chamber 9 extending under the piston 76 and a second chamber 8 disposed above of the piston 76.
  • the underside of the piston 76 is subjected to the action of elastic pushing means in the form of a helical spring 71 also bearing in the bottom of the housing 75.
  • the sheath has two slots 72,73 arranged at different levels which allow the communication of the volume 6 with respectively means of connection to a source of pressurized liquid and means of connection to a discharge tank.
  • the volume 6 is placed in communication with the housing 75 of the distributor 70 by two recesses 62, 63 formed in the body of the cylinder head 99 and opening both into the bore 64 and into the housing 75; the axial length of these two recesses is sufficient to ensure permanent communication between these recesses 62, 63 and the volume 6.
  • the housing 75 communicates with a cavity of pressurized liquid 10 supplied by a pressure source which can be for example the oil pump of the lubrication circuit, a reduction gear pressure 11 is interposed on the hydraulic circuit in order to regulate the pressure of the liquid to a predetermined value of approximately 10 bars.
  • a non-return ball valve 61 is also disposed between the reduction gear 11 and the cavity 10.
  • the displacement of the sheath 7 of the distributor 70 is operated by a second distributor 12 which controls the pressure of the chambers 8 and 9.
  • This distributor 12 is a hydraulic distributor controlled with four channels and two positions. It makes it possible to put the chambers 8 and 9 into communication with a source of liquid under high pressure 20, around 100 bars, or with a liquid discharge tank 13 and vice versa.
  • the source of high pressure liquid 20 can be constituted, as shown diagrammatically, by a hydraulic pump 14, a contactor-circuit breaker 15 and a pressure accumulator 16.
  • the valve control device 4 is in operation or in clutched mode, as shown in FIG. 1.
  • the distributor 12 is positioned so as to send the high pressure into the cavity 8 while the cavity 9 is placed in communication with the liquid reservoir. 13.
  • the distributor 70 thus supplied, the drawer or sleeve 7 is kept locked in the lower limit position, its end forming a piston 76 bearing against the shoulder 77, the spring 71 being compressed in the chamber 9.
  • the volume 6 is filled with and is in communication with the auxiliary cavity 10 through the orifice 72 formed in the sleeve 7 which places the recess 62 in communication with the cavity 10.
  • This cavity 10 supplied with pressurized oil via the oil reducer serves to dampen the oscillations of the pressure due to the compressibility of the oil during movement of the pusher 1.
  • valve control device 4 conventionally operates with a hydraulic pusher 1 with backlash adjustment.
  • the pusher 1 When the pusher 1 is at rest, valve 4 closed, the oil of the lubrication system under pressure, coming from of the pressure reducer 11 fills the device, namely the cavity 10, the chamber 6 and the adjacent recesses 62, 63.
  • the cam 52 acts on the pusher 1, a ball valve 61 traps this volume of oil whose incompressibility secures the complete device: the pusher 1 can then transmit the thrust from the cam 52 to the valve stem 42.
  • the distributor 12 is operated so as to send the high pressure into the chamber 9 of the distributor 70 while simultaneously the chamber 8 is placed in communication with the discharge tank 13.
  • the imbalance of the pressures exerted on the faces of the piston 76 causes the sleeve 7 to rise up until it comes into abutment and stops in the upper limit position.
  • the spring 71 locks the drawer or sleeve 7 in the high position and prevents the latter does not vibrate because of the play existing between the pusher and its stop.
  • the volume 6 is placed in communication with the chamber 8 through the lumen 73 while all communication with the cavity 10 is cut off.
  • the piston 2 is pushed back towards the piston 3, the oil contained in the volume 6 is then driven into the chamber towards the discharge tank until the piston 2 comes in contact with the piston 3 and remains there under the action of the spring 21.
  • the cam 52 can no longer reach the piston 2, the piston 3 remains stationary, its shoulder 35 bearing against the bore 64 under the action of the spring 31.
  • the valve 4 therefore also remains stationary in abutment on its seat.
  • the high pressure pump 14 charges the accumulator 16 at a pressure of approximately 100 bars, necessary for operating distributors 12 and 70, and therefore a disengagement and a clutch of the control device, extremely fast.
  • the hydraulic circuit breaker 15 allows the pump 14 to deliver without pressure, therefore consuming very little during the rest periods.
  • the control of the distributor 12 which controls the operation of the valve control device can be carried out mechanically and / or electrically as a function of one or more engine operating parameters.
  • a particularly interesting solution is the integration into the already existing ignition computer of the engine according to a specific map, three dimensions for example depending on the speed and the load, the computer having to take into account the response times of distributors 12 and 70 .
  • a valve control device has therefore been produced according to the invention for an internal combustion engine with a shutdown function which allows extremely fast clutch and disengage speeds and this in a relatively simple manner.
  • the invention includes all the technical equivalents of the means described and their combinations if these are carried out according to the spirit. So it is possible to use as a drawer for the dispenser 70 a folder rotating having a light and being able to rotate by means of a stepping motor by means of a belt.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

[1] Deactivating valve operating device, for internal combustion engines, comprising a hydraulic tappet (1) suitable for transmitting or otherwise the thrust of a cam (52), carried by a camshaft (5), to a valve stem (42) against elastic return means (41), this hydraulic tappet (1) comprising two pistons (2,3) separated by a volume of liquid (6), especially oil, characterised in that it comprises distribution means (70,12) suitable for causing the volume (6), included between the two pistons (2,3), to communicate either via linkage means (10,11) with a source of pressurised liquid, or via linkage means (8) with a liquid discharge tank (13), these distribution means (70,12) being controlled by a high-pressure liquid source (20) as a function of the speed and/or the load of the engine. <IMAGE>

Description

La présente invention concerne un dispositif de commande de soupape à fonction de mise à l'arrêt, notamment pour moteur à combustion interne multisoupapes.The present invention relates to a valve control device with a shutdown function, in particular for a multi-valve internal combustion engine.

le développement actuel des moteurs à plusieurs soupapes d'admission est principalement dû à la recherche d'une puissance élevée, c'est à dire d'un bon rendement à haut régime et à forte charge. Malheureusement, ce choix s'avère pénalisant aux bas régimes de rotation et aux faibles couples demandés.The current development of engines with several intake valves is mainly due to the search for high power, that is to say a good performance at high speed and at high load. Unfortunately, this choice is penalizing at low revs and at the low torques required.

En effet pour obtenir une puissance élevée à haut régime, il est nécessaire d'avoir un fort remplissage en mélange air-essence des chambres de combustion, ce qui nécessite une section de passage à l'admission importante pour chaque cylindre. Cette augmentation de la section de passage à l'admission, ne pouvant être réalisée par l'augmentation en diamètre des soupapes à cause d'un trop grand poids des équipages mobiles, est réalisée par l'augmentation en nombre des soupapes d'admission.Indeed, to obtain high power at high speed, it is necessary to have a high filling of the air-fuel mixture of the combustion chambers, which requires a large intake passage section for each cylinder. This increase in the intake passage section, which cannot be achieved by increasing the diameter of the valves due to the excessive weight of the moving parts, is achieved by increasing the number of intake valves.

A bas régime de rotation et à faible charge, c'est à dire à des débits d'admission du mélange air-essence faibles, ces sections de passage à l'admission importantes constituent des freins à la pénétration et au conditionnement du mélange dans les cylindres en faisant chuter les vitesses d'arrivée. Ce qui à pour effet de diminuer les performances et de supprimer de la souplesse au moteur et d'augmenter la production de polluants.At low speed and at low load, i.e. at low air-fuel mixture intake rates, these sections of Passage to the large intake constitute brakes on the penetration and conditioning of the mixture in the cylinders by reducing the arrival speeds. This has the effect of reducing performance and removing flexibility from the engine and increasing the production of pollutants.

Diverses solutions ont été développées pour pallier ces inconvénients.Various solutions have been developed to overcome these drawbacks.

Une première solution est de disposer d'une levée de soupape variable en fonction du régime et de la charge du moteur. De nombreux dispositifs ont été développés, on peut citer les cames rotatives à profil variable portées par un arbre coulissant le long de son axe en fonction d'un paramètre de fonctionnement du moteur ; ou bien encore deux cames portées respectivement par deux arbres à cames parallèles, l'utilisation sélective de l'une des cames s'effectuant par embrayage d'un des arbres ou par basculement d'un support des deux arbres. L'inconvénient de ces dispositifs est leur grande complexité et leur surcoût important .A first solution is to have a variable valve lift depending on the speed and the engine load. Many devices have been developed, mention may be made of variable profile rotary cams carried by a shaft sliding along its axis as a function of an engine operating parameter; or alternatively two cams carried respectively by two parallel camshafts, the selective use of one of the cams being effected by engagement of one of the shafts or by tilting of a support of the two shafts. The disadvantage of these devices is their great complexity and their significant additional cost.

Une autre solution est de débrayer certaines soupapes à bas régime et faible charge. Cette approche permet, par exemple, d'utiliser quatre soupapes par cylindre à haut régime et deux seulement à bas régime. Cette solution a le mérite de la simplicité et offre un excellent rapport prix - performances. Plusieurs dispositifs ont été développés, on peut citer notamment les brevets d'invention français n°2 535 390 et n° 2 546 968. Le brevet n° 2 546 968, relatif à un mécanisme de manoeuvre de soupapes à fonction de mise à l'arrêt pour moteur à combustion interne, décrit un dispositif dans lequel un premier et un second culbuteurs, présentant des bras respectifs en butée contre les extrémités superieures des soupapes d'admission ou d'échappement appareillées, sont articulés sur un axe porteur commun fixé sur le corps du moteur et dont l'axe géométrique est perpendiculaire aux directions de mouvement des soupapes ; le premier culbuteur présente un alésage formant cylindre qui débouche vers le second culbuteur pour porter un plongeur dans son intérieur tandis que le second culbuteur présente un alésage de guidage débouchant vers le premier culbuteur pour que le plongeur s'y emboîte ; une chambre de manoeuvre hydraulique définie entre le fond de l'alésage formant cylindre et l' extrémité arrière du plongeur est reliée à une source d'huile sous pression à travers une vanne de permutation hydraulique destinée à permuter l' envoi et le non envoi d'huile sous pression à la chambre de manoeuvre ; et l'un ou l'autre des premier et second culbuteurs présente un palpeur de came destiné à porter à coulissement contre une came agencée pour tourner selon la marche du moteur.Another solution is to disengage certain valves at low speed and low load. This approach allows, for example, to use four valves per cylinder at high speed and only two at low speed. This solution has the merit of simplicity and offers an excellent price-performance ratio. Several devices have been developed, one can cite in particular the French invention patents No. 2,535,390 and No. 2,546,968. Patent No. 2,546,968, relating to a mechanism for operating valves with a shutdown function for an internal combustion engine, describes a device in which first and second rocker arms, having respective arms abutting against the upper ends of the intake or exhaust valve fitted , are articulated on a common carrier axis fixed on the body of the engine and whose geometric axis is perpendicular to the directions of movement of the valves; the first rocker has a bore forming a cylinder which opens towards the second rocker to carry a plunger in its interior while the second rocker has a guide bore opening towards the first rocker so that the plunger fits there; a hydraulic operating chamber defined between the bottom of the cylinder bore and the rear end of the plunger is connected to a source of pressurized oil through a hydraulic permutation valve intended to permute the sending and non-sending of 'oil under pressure in the operating chamber; and one or the other of the first and second rocker arms has a cam feeler intended to slide against a cam arranged to rotate according to the speed of the engine.

Toutefois un tel système présente l'inconvénient d'être complexe, d'interférer avec les commandes des autres soupapes, de ne pas pouvoir être utilisé avec une distribution à attaque directe et de plus d'avoir des temps de réponse assez longs .However, such a system has the drawback of being complex, of interfering with the controls of the other valves, of not being able to be used with a direct drive distribution and moreover of having fairly long response times.

Le but de la présente invention est de pallier à ces inconvénients en offrant un dispositif de commande de soupape d'encombrement restreint, pouvant être mis à l'arrêt en un temps extrêmement bref, de l'ordre d'une dizaine de millisecondes, n'interférant pas avec les commandes des autres soupapes, pouvant être utilisé avec des distribution à attaque directe comme des distributions à basculeurs : culbuteurs, linguets , etc. et permettant de plus de rattraper les jeux de fonctionnement ; un tel dispositif d'utilisation extrêmement souple permet de passer d'un fonctionnement quatre soupapes à un fonctionnement deux soupapes ou bien encore de passer d'un fonctionnement quatre cylindres à un fonctionnement trois cylindres en équipant toutes les soupapes d'un cylindre.The object of the present invention is to overcome these drawbacks by providing a valve control device of limited size, which can be stopped in an extremely short time, of the order of ten milliseconds, does not interfere with the controls of the other valves, which can be used with direct drive distribution such as rocker distributions: rockers, latches, etc. and allowing more to catch the operating clearances; such an extremely flexible use device makes it possible to pass from a four-valve operation to a two-valve operation or else to pass from a four-cylinder operation to a three-cylinder operation by equipping all the valves with a cylinder.

La présente invention concerne un dispositif de commande de soupape à fonction de mise à l'arrêt, pour moteurs à combustion interne, comportant un poussoir hydraulique propre à transmettre ou non la poussée d'une came, portée par un arbre à cames, à une tige de soupape à l'encontre de moyens de rappel élastiques, ce poussoir hydraulique comportant deux pistons séparés par un volume de liquide, notamment d'huile.The present invention relates to a valve control device with a shutdown function, for internal combustion engines, comprising a hydraulic tappet capable of transmitting or not the thrust of a cam, carried by a camshaft, to a valve stem against elastic return means, this hydraulic tappet comprising two pistons separated by a volume of liquid, in particular oil.

Selon l'invention le dispositif de commande de soupape comprend des moyens de distribution propres à faire communiquer le volume, compris entre les deux pistons, soit avec des moyens de liaison à une source de liquide sous pression, soit avec des moyens de liaison à un réservoir de décharge de liquide, ces moyens de distribution étant pilotés par une source de liquide haute pression en fonction du régime et/ou de la charge du moteur.According to the invention, the valve control device comprises distribution means suitable for communicating the volume, comprised between the two pistons, either with means for connection to a source of pressurized liquid, or with means for connection with a liquid discharge tank, these distribution means being controlled by a high liquid source pressure depending on engine speed and / or load.

Selon une autre caractéristique de l'invention, les moyens de distribution comprennent un premier distributeur hydraulique, comportant notamment un tiroir mobile dans son logement, présentant au moins un conduit de passage de fluide, ce tiroir pouvant occuper deux positions limites, une première position limite dans laquelle le tiroir met en communication le volume compris entre les deux pistons et les moyens de liaison à une source de liquide sous pression tandis que toute communication entre ledit volume et les moyens de liaisons à un réservoir de décharge de liquide est coupée et une seconde position limite dans laquelle le tiroir met en communication ledit volume et les moyens de liaison à un réservoir de décharge de liquide tandis que toute communication entre ledit volume et les moyens de liaisons à une source de liquide sous pression est coupée et un second distributeur hydraulique permettant de manoeuvrer ledit premier distributeur à partir d'une source de liquide haute pression en fonction du régime et/ou de la charge du moteur.According to another characteristic of the invention, the distribution means comprise a first hydraulic distributor, comprising in particular a movable drawer in its housing, having at least one fluid passage duct, this drawer being able to occupy two limit positions, a first limit position wherein the drawer connects the volume between the two pistons and the means of connection to a source of pressurized liquid while all communication between said volume and the means of connection to a liquid discharge tank is cut and a second limit position in which the slide valve connects said volume and the means of connection to a liquid discharge tank while all communication between said volume and the means of connection to a source of pressurized liquid is cut off and a second hydraulic distributor allowing to operate said first distributor from a source of liquid high pressure depending on engine speed and / or load.

Selon une autre caractéristique de l'invention, le tiroir du premier distributeur hydraulique définit dans son logement deux chambres, une première chambre, dans laquelle sont disposés des moyens élastiques de pression qui agissent sur le tiroir, et une seconde chambre faisant partie desdits moyens de liaisons à un réservoir de décharge de liquide ; ces chambres sont reliées, l'une à une source de liquide haute pression, l'autre à un réservoir de décharge de liquide et inversement, par l'intermédiaire du second distributeur hydraulique du type : piloté à quatre voies et deux positions.According to another characteristic of the invention, the drawer of the first hydraulic distributor defines in its housing two chambers, a first chamber, in which are arranged elastic pressure means which act on the drawer, and a second chamber forming part of said means of connections to a liquid discharge tank; these chambers are connected, one to a high liquid source pressure, the other to a liquid discharge tank and vice versa, via the second hydraulic distributor of the type: piloted with four ways and two positions.

Selon une autre caractéristique de l'invention, le volume compris entre les deux pistons est limité axialement par les deux pistons et transversalement par un alésage, recevant coulissant les deux pistons, dans lequel s'ouvrent au moins un évidement qui communique également avec le logement du premier distributeur hydraulique, la longueur axiale de l'évidement étant suffisante pour assurer une communication permanente entre ledit volume et ledit évidement.According to another characteristic of the invention, the volume between the two pistons is limited axially by the two pistons and transversely by a bore, slidingly receiving the two pistons, in which open at least one recess which also communicates with the housing of the first hydraulic distributor, the axial length of the recess being sufficient to ensure permanent communication between said volume and said recess.

Selon une autre caractéristique de l'invention, les moyens de liaison à une source de liquide sous pression comprennent notamment une cavité formant amortisseur hydraulique, cette cavité débouchant dans le logement dudit premier distributeur, des moyens formant clapet et un réducteur de pression assurant la régulation de la pression du liquide alimentant ladite cavité.According to another characteristic of the invention, the means for connecting to a source of pressurized liquid notably comprise a cavity forming a hydraulic shock absorber, this cavity opening into the housing of said first distributor, means forming a valve and a pressure reducing valve ensuring regulation of the pressure of the liquid supplying said cavity.

Selon une autre caractéristique de l'invention, ledit tiroir mobile est constitué par un fourreau sensiblement cylindrique, coaxial avec le poussoir hydraulique, comportant une extrémité élargie formant piston de manoeuvre , ce fourreau présentant au moins une lumière formant conduit de passage de fluide.According to another characteristic of the invention, said movable drawer consists of a substantially cylindrical sheath, coaxial with the hydraulic plunger, comprising an enlarged end forming an operating piston, this sheath having at least one lumen forming a conduit for the passage of fluid.

Selon une autre caractéristique de l'invention, l'alésage dans lequel coulissent les deux pistons forme des moyens de butée destinés à coopérer avec des épaulement portés par les deux pistons de façon à limiter le déplacement relatif de ces pistons et en particulier à cantonner ledit volume à l'intérieur dudit alésage.According to another characteristic of the invention, the bore in which the two pistons form stop means intended to cooperate with shoulders carried by the two pistons so as to limit the relative movement of these pistons and in particular to confine said volume inside said bore.

Selon une autre caractéristique de l'invention, le piston, du poussoir hydraulique, destiné à venir en contact avec la came de manoeuvre est soumis à l'action de moyens élastiques de pression propres à écarter ce piston de la came.According to another characteristic of the invention, the piston of the hydraulic pusher intended to come into contact with the operating cam is subjected to the action of elastic pressure means capable of moving this piston away from the cam.

Selon une autre caractéristique de l'invention, la source de liquide haute pression comprend notamment une pompe d'alimentation, un accumulateur et un dispositif de décharge de type conjoncteur-disjoncteur.According to another characteristic of the invention, the source of high pressure liquid comprises in particular a supply pump, an accumulator and a discharge device of the contactor-circuit breaker type.

Selon une autre caractéristique de l'invention, le pilotage des moyens de distribution est intégré à la commande d'allumage du moteur suivant une cartographie prédéterminée en fonction du régime et de la charge, le temps de réponse desdits moyens étant pris en compte par le calculateur.According to another characteristic of the invention, the control of the distribution means is integrated into the ignition control of the engine according to a predetermined map as a function of the speed and of the load, the response time of said means being taken into account by the calculator.

L'invention concerne également un poussoir hydraulique comportant deux pistons séparés par un volume de liquide, notamment d'huile, agencé pour un dispositif de commande de soupape à fonction de mise à l'arrêt selon l'invention.The invention also relates to a hydraulic tappet comprising two pistons separated by a volume of liquid, in particular oil, arranged for a valve control device with a shutdown function according to the invention.

On comprendra mieux les buts, aspects et avantages de la présente invention, d'après la description donnée ci après d'un mode de réalisation de l'invention, donné à titre d'exemple non limitatif, en se référant aux dessins annexés, sur lesquels :

  • la figure 1 est, en élévation, une vue latérale en coupe longitudinale partielle du dispositif de commande de soupape selon l'invention, en position de fonctionnement ;
  • la figure 2 est une vue similaire à la figure 1, le dispositif de commande étant mis à l'arrêt.
The objects, aspects and advantages of the present invention will be better understood from the description given below of an embodiment of the invention, given by way of nonlimiting example, with reference to the appended drawings, in which:
  • Figure 1 is, in elevation, a side view in partial longitudinal section of the valve control device according to the invention, in the operating position;
  • Figure 2 is a view similar to Figure 1, the control device being stopped.

En se reportant aux dessins, notamment, à la figure 1, on peut voir un dispositif de commande d'une soupape d'admission ou d'échappement d'un moteur à combustion interne, présenté dans le cas particulier d'un mode de distribution à attaque directe .Referring to the drawings, in particular, in FIG. 1, one can see a device for controlling an intake or exhaust valve of an internal combustion engine, presented in the particular case of a mode of distribution. direct attack.

Le dispositif de commande comprend un poussoir hydraulique 1 destiné à transmettre la poussée d'une came 52 portée par un arbre à cames 5 à une soupape d'admission ou d'échappement 4, d'un moteur à combustion interne dont seules les parties intéressant l'invention ont été représentées, à l'encontre de moyens de rappel élastiques formés par un ressort en hélice 31 .The control device comprises a hydraulic pusher 1 intended to transmit the thrust from a cam 52 carried by a camshaft 5 to an intake or exhaust valve 4, of an internal combustion engine of which only the parts of interest the invention have been shown, against elastic return means formed by a helical spring 31.

Le ressort 31 travaille en compression et a tendance à rappeler la soupape 4 vers sa position de fermeture ce qui correspond, dans la représentation de la figure 1 à un mouvement vers le haut de la queue de la soupape 42.The spring 31 works in compression and tends to return the valve 4 to its closed position, which corresponds, in the representation of FIG. 1, to an upward movement of the valve stem 42.

le poussoir hydraulique 1 , comprend deux pistons 2, 3 séparés par un volume ou cavité 6 rempli de liquide, notamment d'huile. L'un des pistons, à savoir le piston 2 est destiné à venir en contact avec la came 52 tandis que l'autre piston 3 est en appui permanent contre la queue de la soupape 42 du fait de la poussée du ressort 31.the hydraulic pusher 1 comprises two pistons 2, 3 separated by a volume or cavity 6 filled with liquid, in particular oil. One of the pistons, namely the piston 2, is intended to come into contact with the cam 52 while the other piston 3 is in permanent abutment against the stem of the valve 42 due to the thrust of the spring 31.

Les pistons 2 et 3 ont leur extrémité, respectivement inférieure et supérieure, montée coulissante dans un logement 64 de la culasse 99. Le volume 6 se trouve ainsi limité axialement par les deux pistons et transversalement par cet alésage 64 .The pistons 2 and 3 have their ends, respectively lower and upper, slidably mounted in a housing 64 of the cylinder head 99. The volume 6 is thus limited axially by the two pistons and transversely by this bore 64.

Le piston 2, sensiblement cylindrique, porte une pastille supérieure 26 destinée à frotter sur la came 52 ; il comporte un épaulement 25 circonférentiel sur lequel appuient des moyens élastiques de pression, formés par un ressort en hélice 21. Ces moyens 21 , également en appui sur la culasse 99 par l'intermédiaire d'une barye sertie 22, tendent à écarter le piston 2 de la came 52 ainsi qu'à forcer le piston 2 vers le piston 3.The piston 2, which is substantially cylindrical, carries an upper pad 26 intended to rub on the cam 52; it has a circumferential shoulder 25 on which elastic pressure means bear, formed by a helical spring 21. These means 21, also bearing on the cylinder head 99 by means of a crimped barye 22, tend to spread the piston apart 2 of the cam 52 as well as forcing the piston 2 towards the piston 3.

Le piston 3, sensiblement cylindrique, est borgne ; il comporte un épaulement 35 destiné à coopérer avec un décrochement de l'alésage 64, sur son extrémité inférieure appuient des moyens élastiques de pressions, formés par un ressort en hélice 31. Ces moyens également en appui sur la culasse tendent à forcer le piston 3 vers le piston 2 .The substantially cylindrical piston 3 is blind; it has a shoulder 35 intended to cooperate with a recess of the bore 64, on its lower end support elastic pressure means, formed by a helical spring 31. These means also bearing on the cylinder head tend to force the piston 3 towards piston 2.

Autour du poussoir 1 est disposé un distributeur hydraulique 70 destiné à piloter le volume de liquide 6 compris entre les deux pistons 2 et 3. Ce distributeur hydraulique comprend un logement 75 de révolution s'étendant autour 'du poussoir 1 et dans lequel coulisse axialement au poussoir 1 un fourreau 7 cylindrique. Le fourreau 7 comporte une extrémité élargie qui forme un piston de manoeuvre 76 du fourreau 7. Le piston 76 définit dans le logement 75 deux chambres de pression, une première chambre 9 s'étendant sous le piston 76 et une seconde chambre 8 disposée au dessus du piston 76. La face inférieure du piston 76 est soumise à l'action de moyens élastiques de poussée sous la forme d'un ressort en hélice 71 en appui également dans le fond du logement 75. Le fourreau comporte deux lumières 72,73 disposées à des niveaux différents qui permettent la mise en communication du volume 6 avec respectivement des moyens de liaison à une source de liquide sous pression et des moyens de liaisons à un réservoir de décharge.Around the pusher 1 is disposed a hydraulic distributor 70 intended to control the volume of liquid 6 comprised between the two pistons 2 and 3. This hydraulic distributor comprises a housing 75 of revolution extending around the pusher 1 and in which slides axially at pusher 1 a cylindrical sheath 7. The sleeve 7 has an enlarged end which forms an operating piston 76 of the sleeve 7. The piston 76 defines in the housing 75 two pressure chambers, a first chamber 9 extending under the piston 76 and a second chamber 8 disposed above of the piston 76. The underside of the piston 76 is subjected to the action of elastic pushing means in the form of a helical spring 71 also bearing in the bottom of the housing 75. The sheath has two slots 72,73 arranged at different levels which allow the communication of the volume 6 with respectively means of connection to a source of pressurized liquid and means of connection to a discharge tank.

Le volume 6 est mis en communication avec le logement 75 du distributeur 70 par deux évidements 62, 63 pratiqués dans le corps de la culasse 99 et débouchant à la fois dans l'alésage 64 et dans le logement 75 ; la longueur axiale de ces deux évidements est suffisante pour assurer une communication permanente entre ces évidements 62, 63 et le volume 6.The volume 6 is placed in communication with the housing 75 of the distributor 70 by two recesses 62, 63 formed in the body of the cylinder head 99 and opening both into the bore 64 and into the housing 75; the axial length of these two recesses is sufficient to ensure permanent communication between these recesses 62, 63 and the volume 6.

Le logement 75 communique avec une cavité de liquide sous pression 10 alimenté par une source de pression qui peut être par exemple la pompe à huile du circuit de lubrification, un réducteur de pression 11 est interposé sur le circuit hydraulique afin de réguler la pression du liquide à une valeur prédéterminée d'environ 10 bars. Un clapet à bille anti-retour 61 est également disposé entre le réducteur 11 et la cavité 10.The housing 75 communicates with a cavity of pressurized liquid 10 supplied by a pressure source which can be for example the oil pump of the lubrication circuit, a reduction gear pressure 11 is interposed on the hydraulic circuit in order to regulate the pressure of the liquid to a predetermined value of approximately 10 bars. A non-return ball valve 61 is also disposed between the reduction gear 11 and the cavity 10.

Le déplacement du fourreau 7 du distributeur 70 est opérer par un second distributeur 12 qui pilote la pression des chambres 8 et 9. Ce distributeur 12 est un distributeur hydraulique piloté à quatre voies et deux positions. Il permet de mettre en communication les chambres 8 et 9 avec une source de liquide sous haute pression 20, environs 100 bars, ou avec un réservoir de décharge de liquide 13 et inversement.The displacement of the sheath 7 of the distributor 70 is operated by a second distributor 12 which controls the pressure of the chambers 8 and 9. This distributor 12 is a hydraulic distributor controlled with four channels and two positions. It makes it possible to put the chambers 8 and 9 into communication with a source of liquid under high pressure 20, around 100 bars, or with a liquid discharge tank 13 and vice versa.

La source de liquide haute pression 20 peut être constituée, comme schématisé, par une pompe hydraulique 14, un conjoncteur-disjoncteur 15 et un accumulateur de pression 16 .The source of high pressure liquid 20 can be constituted, as shown diagrammatically, by a hydraulic pump 14, a contactor-circuit breaker 15 and a pressure accumulator 16.

Le fonctionnement du dispositif qui vient d'être décrit est le suivant.The operation of the device which has just been described is as follows.

Le dispositif de commande de la soupape 4 est en fonctionnement ou en mode embrayé, confère figure 1. Le distributeur 12 est positionné de façon à envoyer la haute pression dans la cavité 8 tandis que la cavité 9 est mise en communication avec le réservoir de liquide 13. Le distributeur 70 ainsi alimenté, le tiroir ou fourreau 7 est maintenu bloqué en position limite basse, son extrémité formant piston 76 en appui contre l'épaulement 77, le ressort 71 étant comprimé dans la chambre 9. Le volume 6 est rempli d'huile et est en communication avec la cavité auxiliaire 10 par l'orifice 72 pratiqué dans le fourreau 7 qui met en communication l'évidement 62 avec la cavité 10. Cette cavité 10 alimentée en huile sous pression via le réducteur d'huile, sert à amortir les oscillations de la pression dues à la compressibilité de l'huile lors des déplacement du poussoir 1.The valve control device 4 is in operation or in clutched mode, as shown in FIG. 1. The distributor 12 is positioned so as to send the high pressure into the cavity 8 while the cavity 9 is placed in communication with the liquid reservoir. 13. The distributor 70 thus supplied, the drawer or sleeve 7 is kept locked in the lower limit position, its end forming a piston 76 bearing against the shoulder 77, the spring 71 being compressed in the chamber 9. The volume 6 is filled with and is in communication with the auxiliary cavity 10 through the orifice 72 formed in the sleeve 7 which places the recess 62 in communication with the cavity 10. This cavity 10 supplied with pressurized oil via the oil reducer, serves to dampen the oscillations of the pressure due to the compressibility of the oil during movement of the pusher 1.

Le distributeur 70 ainsi manoeuvré, le dispositif de commande de la soupape 4 fonctionne classiquement avec un poussoir hydraulique 1 à rattrapage de jeu. Quand le poussoir 1 est au repos, soupape 4 fermée, l'huile du circuit de graissage sous pression, en provenance du réducteur de pression 11 remplit le dispositif à savoir la cavité 10, la chambre 6 et les évidements adjacents 62, 63. Quand la came 52 agit sur le poussoir 1, un clapet à bille 61 emprisonne ce volume d'huile dont l'incompressibilité solidarise le dispositif complet : le poussoir 1 peut alors transmettre la poussée de la came 52 à la queue de soupape 42.The distributor 70 thus operated, the valve control device 4 conventionally operates with a hydraulic pusher 1 with backlash adjustment. When the pusher 1 is at rest, valve 4 closed, the oil of the lubrication system under pressure, coming from of the pressure reducer 11 fills the device, namely the cavity 10, the chamber 6 and the adjacent recesses 62, 63. When the cam 52 acts on the pusher 1, a ball valve 61 traps this volume of oil whose incompressibility secures the complete device: the pusher 1 can then transmit the thrust from the cam 52 to the valve stem 42.

Pour mettre à l'arrêt le dispositif de commande, le distributeur 12 est manoeuvré de manière à envoyer la haute pression dans la chambre 9 du distributeur 70 tandis que simultanément la chambre 8 est mise en communication avec le réservoir de décharge 13. Le déséquilibre des pressions s'exerçant sur les faces du piston 76 entraîne la remontée du fourreau 7 jusqu'à ce qu'il vienne en butée et s'immobilise en position limite haute. Le ressort 71 assure le blocage du tiroir ou fourreau 7 en position haute et évite que ce dernier ne vibre à cause du jeu existant entre le poussoir et sa butée.To stop the control device, the distributor 12 is operated so as to send the high pressure into the chamber 9 of the distributor 70 while simultaneously the chamber 8 is placed in communication with the discharge tank 13. The imbalance of the pressures exerted on the faces of the piston 76 causes the sleeve 7 to rise up until it comes into abutment and stops in the upper limit position. The spring 71 locks the drawer or sleeve 7 in the high position and prevents the latter does not vibrate because of the play existing between the pusher and its stop.

Le fourreau 7 étant en position haute, le volume 6 est mis en communication avec la chambré 8 à travers la lumière 73 tandis que toute communication avec la cavité 10 est coupée. Sous l'action du ressort 21 et de la came 52 le piston 2 est repoussé vers le piston 3, l'huile contenue dans le volume 6 est alors chassée dans la chambre vers le réservoir de décharge jusqu'à ce que le piston 2 vienne en contact avec le piston 3 et y demeure sous l'action du ressort 21. Dans une telle position la came 52 ne peut plus atteindre le piston 2, le piston 3 reste immobile, son épaulement 35 en appui contre l'alésage 64 sous l'action du ressort 31. La soupape 4 demeure donc également immobile en appui sur son siège .The sheath 7 being in the high position, the volume 6 is placed in communication with the chamber 8 through the lumen 73 while all communication with the cavity 10 is cut off. Under the action of the spring 21 and of the cam 52 the piston 2 is pushed back towards the piston 3, the oil contained in the volume 6 is then driven into the chamber towards the discharge tank until the piston 2 comes in contact with the piston 3 and remains there under the action of the spring 21. In such a position the cam 52 can no longer reach the piston 2, the piston 3 remains stationary, its shoulder 35 bearing against the bore 64 under the action of the spring 31. The valve 4 therefore also remains stationary in abutment on its seat.

Pour réactiver le dispositif de commande, il suffit de permuter l'alimentation en liquide haute pression et la mise en communication avec le réservoir de décharge des chambre 8 et 9 du distributeur 70 grâce à la manoeuvre du distributeur 12. Le déséquilibre des pressions entraîne le piston 76 et donc le fourreau solidaire 7 vers le bas ce qui a pour effet de mettre en communication le volume 6 avec la source de liquide sous pression via la cavité 10 et de couper toute communication avec la chambre 8. On se retrouve alors dans la situation précédemment décrite.To reactivate the control device, it suffices to switch the supply of high pressure liquid and the communication with the discharge tank of the chambers 8 and 9 of the distributor 70 by means of the operation of the distributor 12. The pressure imbalance causes the piston 76 and therefore the integral sleeve 7 downwards, which has the effect of bringing the volume 6 into communication with the source of liquid under pressure via the cavity 10 and cutting off all communication with the chamber 8. We then find ourselves in the previously described situation.

La pompe haute pression 14 charge l'accumulateur 16 à une pression de 100 bars environ, nécessaire pour avoir un fonctionnement des distributeurs 12 et 70, et donc un débrayage et un embrayage du dispositif de commande, extrêmement rapide. Le conjoncteur-disjoncteur hydraulique 15 permet à la pompe 14 de débiter sans pression, donc en consommant très peu pendant les périodes de repos.The high pressure pump 14 charges the accumulator 16 at a pressure of approximately 100 bars, necessary for operating distributors 12 and 70, and therefore a disengagement and a clutch of the control device, extremely fast. The hydraulic circuit breaker 15 allows the pump 14 to deliver without pressure, therefore consuming very little during the rest periods.

La commande du distributeur 12 qui pilote le fonctionnement du dispositif de commande de la soupape peut être réalisée mécaniquement et /ou électriquement en fonction d'un ou plusieurs paramêtres de marche du moteur. Une solution particulièrement intéressante est l'intégration au calculateur d'allumage déjà existant du moteur suivant une cartographie spécifique, trois dimensions par exemple en fonction du régime et de la charge, le calculateur devant prendre en compte les temps de réponse des distributeurs 12 et 70.The control of the distributor 12 which controls the operation of the valve control device can be carried out mechanically and / or electrically as a function of one or more engine operating parameters. A particularly interesting solution is the integration into the already existing ignition computer of the engine according to a specific map, three dimensions for example depending on the speed and the load, the computer having to take into account the response times of distributors 12 and 70 .

On a donc réalisé suivant l'invention un dispositif de commande de soupape pour moteur à combustion interne à fonction de mise à l'arrêt qui autorise des vitesses d'embrayage et de débrayage extrêmement rapide et ce d'une manière relativement simple.A valve control device has therefore been produced according to the invention for an internal combustion engine with a shutdown function which allows extremely fast clutch and disengage speeds and this in a relatively simple manner.

Bien entendu, l'invention n'est nullement limitée au mode de réalisation décrit et illustré qui n'a été donné qu'à titre d'exemple.Of course, the invention is in no way limited to the embodiment described and illustrated, which has been given only by way of example.

Au contraire, l'invention comprend tous les équivalents techniques des moyens décrits ainsi que leurs combinaisons si celles-ci sont effectuées suivant son esprit. Ainsi il possible d'utiliser comme tiroir pour le distributeur 70 une chemise tournante possédant une lumière et pouvant tourner grâce à un moteur pas à pas par l'intermédiaire d'une courroie.On the contrary, the invention includes all the technical equivalents of the means described and their combinations if these are carried out according to the spirit. So it is possible to use as a drawer for the dispenser 70 a folder rotating having a light and being able to rotate by means of a stepping motor by means of a belt.

Claims (10)

[1] Dispositif de commande de soupape à fonction de mise à l'arrêt, pour moteurs à combustion interne, comportant un poussoir hydraulique (1) propre à transmettre ou non la poussée d'une came (52), portée par un arbre à cames (5), à une tige de soupape (42) à l'encontre de moyens de rappel élastiques (41), ce poussoir hydraulique (1) comportant deux pistons (2,3) séparés par un volume de liquide (6), notamment d'huile, caractérisé en ce que d'une part, il comprend des moyens de distribution (70,12) propres à faire communiquer le volume (6), compris entre les deux pistons (2,3), soit avec des moyens de liaison (10,11) à une source de liquide sous pression, soit avec des moyens de liaison (8) à un réservoir de décharge de liquide (13), ces moyens de distribution (70,12) étant pilotés par une source de liquide haute pression (20) en fonction du régime et/ou de la charge du moteur, et en ce que d'autre part, lesdits moyens de distribution comprennent un premier distributeur hydraulique (70), comportant notamment un tiroir (7) mobile dans son logement (75), présentant au moins un conduit de passage de fluide (72,73), ce tiroir (7) pouvant occuper deux positions limites, une première position limite dans laquelle le tiroir (7) met en communication le volume (6) compris entre les deux pistons (2,3) et les moyens de liaison (10,11) à une source de liquide sous pression tandis que toute communication entre ledit volume (6) et les moyens de liaisons (8) à un réservoir de décharge de liquide (13) est coupée et une seconde position limite dans laquelle le tiroir (7) met en communication ledit volume (6) et les moyens de liaison (8) à un réservoir de décharge de liquide (13) tandis que toute communication entre ledit volume (6) et les moyens de liaisons (10,11) à une source de liquide sous pression est coupée et un second distributeur hydraulique (12) permettant de manoeuvrer ledit premier distributeur (70) à partir d'une source de liquide haute pression (20) en fonction du régime et/ou de la charge du moteur. [1] Valve control device with shutdown function, for internal combustion engines, comprising a hydraulic tappet (1) suitable for transmitting or not the thrust of a cam (52), carried by a shaft with cams (5), to a valve stem (42) against elastic return means (41), this hydraulic tappet (1) comprising two pistons (2,3) separated by a volume of liquid (6), in particular oil, characterized in that on the one hand, it comprises distribution means (70,12) suitable for making the volume (6) communicate, comprised between the two pistons (2,3), either with means connection (10,11) to a source of pressurized liquid, either with connection means (8) to a liquid discharge tank (13), these distribution means (70,12) being controlled by a source of high pressure liquid (20) depending on the speed and / or the engine load, and in that, on the other hand, said distribution means comprise a first distr hydraulic ibutor (70), comprising in particular a drawer (7) movable in its housing (75), having at least one fluid passage duct (72,73), this drawer (7) being able to occupy two limit positions, a first position limit within which the slide (7) communicates the volume (6) between the two pistons (2,3) and the connecting means (10,11) to a source of pressurized liquid while any communication between said volume (6) and the connecting means (8) to a liquid discharge tank (13) is cut and a second limit position in which the slide (7) communicates said volume (6) and the connecting means (8) to a liquid discharge tank (13) while all communication between said volume (6) and the means of connection (10, 11) to a source of pressurized liquid is cut off and a second hydraulic distributor (12) making it possible to operate said first distributor (70) from a source high pressure liquid (20) depending on the speed and / or the engine load. [2] Dispositif de commande de soupape selon la revendication 1, caractérisé par le fait que le tiroir (7) du premier distributeur hydraulique (70) définit dans son logement (75) deux chambres, une première chambre (9), dans laquelle sont disposés des moyens élastiques de pression (71) qui agissent sur le tiroir (7), et une seconde chambre (8) faisant partie moyens de liaisons à un réservoir de décharge de liquide (13) ; ces chambres sont reliées, l'une à une source de liquide haute pression (20), l'autre à un réservoir de décharge de liquide (13) et inversement, par l'intermédiaire du second distributeur hydraulique (12) du type : piloté à quatre voies et deux positions. [2] Valve control device according to claim 1, characterized in that the slide (7) of the first hydraulic distributor (70) defines in its housing (75) two chambers, a first chamber (9), in which are disposed elastic pressure means (71) which act on the slide (7), and a second chamber (8) forming part of means for connection to a liquid discharge tank (13); these chambers are connected, one to a source of high pressure liquid (20), the other to a liquid discharge tank (13) and vice versa, via the second hydraulic distributor (12) of the type: piloted with four channels and two positions. [3] Dispositif de commande de soupape selon l'une quelconque des revendications 1 à à 2, caractérisé par le fait que le volume (6) compris entre les deux pistons (2,3) est limité axialement par les deux pistons (2,3) et transversalement par un alésage (64), recevant coulissant les deux pistons (2,3), dans lequel s'ouvrent au moins un évidement (62,63) qui communique également avec le logement (75) du premier distributeur hydraulique (70), la longueur axiale de l'évidement (62,63) étant suffisante pour assurer une communication permanente entre ledit volume (6) et ledit évidement (62,63). [3] Valve control device according to any one of claims 1 to 2, characterized in that the volume (6) between the two pistons (2,3) is axially limited by the two pistons (2, 3) and transversely by a bore (64), slidingly receiving the two pistons (2,3), in which at least one recess (62,63) opens which also communicates with the housing (75) of the first hydraulic distributor (70), the axial length of the recess (62,63) being sufficient to ensure permanent communication between said volume (6) and said recess (62,63). [4] Dispositif de commande de soupape selon l'une quelconque des revendications 1 à 3, caractérisé par le fait que les moyens de liaison à une source de liquide sous pression comprennent notamment une cavité (10) formant amortisseur hydraulique, cette cavité (10) débouchant dans le logement (75) dudit premier distributeur hydraulique (70), des moyens formant clapet (61) et un réducteur de pression (11) assurant la régulation de la pression du liquide alimentant ladite cavité (6). [4] Valve control device according to any one of claims 1 to 3, characterized in that the means for connecting to a source of pressurized liquid notably comprise a cavity (10) forming a hydraulic damper, this cavity (10 ) opening into the housing (75) of said first hydraulic distributor (70), valve means (61) and a pressure reducer (11) regulating the pressure of the liquid supplying said cavity (6). [5] Dispositif de commande de soupape selon la revendication 4, caractérisé par le fait ledit tiroir mobile est constitué par un fourreau (7) sensiblement cylindrique, coaxial avec le poussoir hydraulique (1), comportant une extrémité élargie (76) formant piston de manoeuvre, ce fourreau (7) présentant au moins une lumière (72,73) formant conduit de passage de fluide. [5] Valve control device according to claim 4, characterized in that said movable slide is constituted by a sleeve (7) substantially cylindrical, coaxial with the hydraulic plunger (1), having an enlarged end (76) forming piston operation, this sheath (7) having at least one lumen (72,73) forming a fluid passage duct. [6] Dispositif de commande de soupape selon l'une quelconque des revendications 4 à 5, caractérisé par le fait que l'alésage (64) dans lequel coulissent les deux pistons (2,3) du poussoir (1) forme des moyens de butée destinés à coopérer avec des épaulements (25,35) portés par les deux pistons (2,3) de façon à limiter le déplacement relatif de ces pistons (2,3) et en particulier à cantonner ledit volume (6) à l'intérieur dudit alésage (64). [6] Valve control device according to any one of claims 4 to 5, characterized in that the bore (64) in which the two pistons (2,3) of the tappet (1) slide form means of stop intended to cooperate with shoulders (25,35) carried by the two pistons (2,3) so as to limit the relative displacement of these pistons (2,3) and in particular in confining said volume (6) inside said bore (64). [7] Dispositif de commande de soupape selon l'une quelconque des revendications 1 à 6, caractérisé par le fait que le piston (2) du poussoir hydraulique (1) est soumis à l'action de moyens élastiques (21) propres à écarter ce piston (2) de la came de manoeuvre (52). [7] Valve control device according to any one of claims 1 to 6, characterized in that the piston (2) of the hydraulic tappet (1) is subjected to the action of elastic means (21) capable of spreading this piston (2) of the operating cam (52). [8] Dispositif de commande de soupape selon l'une quelconque des revendications 1 à 7, caractérisé par le fait que la source de liquide haute pression (20) comprend notamment une pompe d'alimentation (14), un accumulateur (16) et un dispositif de décharge (15) de type conjoncteur disjoncteur. [8] Valve control device according to any one of claims 1 to 7, characterized in that the source of high pressure liquid (20) comprises in particular a supply pump (14), an accumulator (16) and a discharge device (15) of the circuit-breaker type. [9] Dispositif de commande de soupape selon l'une quelconque des revendications 1 à 8, caractérisé par le fait que le pilotage des moyens de distribution (70,12) est intégré à la commande d'allumage du moteur suivant une cartographie prédéterminée en fonction du régime et de la charge, le temps de réponse moyens (70,12) étant pris en compte par le calculateur. [9] Valve control device according to any one of claims 1 to 8, characterized in that the control of the distribution means (70,12) is integrated into the engine ignition control according to a predetermined map in as a function of speed and load, the average response time (70.12) being taken into account by the computer. [10] Poussoir hydraulique (1) comportant deux pistons (2,3) séparés par un volume (6) de liquide, notamment d'huile, agencé pour un dispositif de commande de soupape à fonction de mise à l'arrêt selon l'une quelconque des revendications 1 à 9. mise à l'arrêt selon l'une quelconque des revendications 1 à 10. [10] Hydraulic tappet (1) comprising two pistons (2,3) separated by a volume (6) of liquid, in particular oil, arranged for a valve control device with stop function according to any one of claims 1 to 9. shutdown according to any one of claims 1 to 10.
EP92400025A 1991-01-08 1992-01-07 Deactivating valve operating device for an internal combustion engine Withdrawn EP0498682A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9100141A FR2671377A1 (en) 1991-01-08 1991-01-08 VALVE CONTROL DEVICE WITH SHUTDOWN FUNCTION FOR INTERNAL COMBUSTION ENGINE.
FR9100141 1991-01-08

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EP1493945A1 (en) * 2003-07-02 2005-01-05 The Channel Tunnel Group Limited Device for converting an angular motion into a rectilinear motion
WO2006042785A1 (en) * 2004-10-15 2006-04-27 Robert Bosch Gmbh Method for operating an internal combustion engine
EP3156619A1 (en) * 2015-10-13 2017-04-19 C.R.F. Società Consortile per Azioni System and method for variable actuation of a valve of an internal combustion engine, with a device for dampening pressure oscillations
WO2018065011A1 (en) * 2016-10-05 2018-04-12 Schaeffler Technologies AG & Co. KG Hydraulic gas exchange valve train comprising a damper chamber connected to a pressure chamber by a throttle
CN110005498A (en) * 2019-05-15 2019-07-12 杰锋汽车动力系统股份有限公司 A kind of two-stage variable air valve lift range mechanism for internal combustion engine

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CN110615516A (en) * 2019-09-19 2019-12-27 河南盛润水处理技术有限公司 A settling chamber inner wall cleaning equipment for handling metal waste water

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1493945A1 (en) * 2003-07-02 2005-01-05 The Channel Tunnel Group Limited Device for converting an angular motion into a rectilinear motion
FR2857074A1 (en) * 2003-07-02 2005-01-07 Channel Tunnel Group Ltd DEVICE FOR CONVERTING ANGULAR MOVEMENT INTO LINEAR MOVEMENT
WO2006042785A1 (en) * 2004-10-15 2006-04-27 Robert Bosch Gmbh Method for operating an internal combustion engine
EP3156619A1 (en) * 2015-10-13 2017-04-19 C.R.F. Società Consortile per Azioni System and method for variable actuation of a valve of an internal combustion engine, with a device for dampening pressure oscillations
US10156163B2 (en) 2015-10-13 2018-12-18 C.R.F. Societa Consortile Per Azioni System and method for variable actuation of a valve of an internal-combustion engine, with a device for dampening pressure oscillations
WO2018065011A1 (en) * 2016-10-05 2018-04-12 Schaeffler Technologies AG & Co. KG Hydraulic gas exchange valve train comprising a damper chamber connected to a pressure chamber by a throttle
CN110005498A (en) * 2019-05-15 2019-07-12 杰锋汽车动力系统股份有限公司 A kind of two-stage variable air valve lift range mechanism for internal combustion engine

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FR2671377B1 (en) 1994-12-09

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