EP3529485B1 - Elastomer wedge between a hp pump cam and an engine flywheel - Google Patents

Elastomer wedge between a hp pump cam and an engine flywheel Download PDF

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Publication number
EP3529485B1
EP3529485B1 EP17777939.4A EP17777939A EP3529485B1 EP 3529485 B1 EP3529485 B1 EP 3529485B1 EP 17777939 A EP17777939 A EP 17777939A EP 3529485 B1 EP3529485 B1 EP 3529485B1
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EP
European Patent Office
Prior art keywords
crankshaft
cam
engine
actuating cam
connecting ring
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.)
Active
Application number
EP17777939.4A
Other languages
German (de)
French (fr)
Other versions
EP3529485A1 (en
Inventor
Jean-Pierre Millon
Ludovic TESSIER
Dimitri BARBEAU
Emmanuel Deruyter
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
Nissan Motor Co Ltd
Original Assignee
Renault SAS
Nissan Motor Co Ltd
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Publication date
Application filed by Renault SAS, Nissan Motor Co Ltd filed Critical Renault SAS
Publication of EP3529485A1 publication Critical patent/EP3529485A1/en
Application granted granted Critical
Publication of EP3529485B1 publication Critical patent/EP3529485B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/025—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by a single piston
    • F02M59/027—Unit-pumps, i.e. single piston and cylinder pump-units, e.g. for cooperating with a camshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

Definitions

  • the present invention relates to the field of motor vehicles and relates to a high pressure fuel supply pump.
  • the invention relates more particularly to an arrangement of an activation cam of the high pressure pump, integral in rotation with a crankshaft movable in rotation inside a chamber of connecting rods in a cylinder block.
  • the invention also relates to an internal combustion engine of a motor vehicle comprising a cylinder block surrounding a crankshaft comprising a high pressure fuel pump activation cam fixed to one end of the crankshaft.
  • the invention relates to an internal combustion engine of a motor vehicle comprising a crankshaft movable in rotation about a longitudinal axis of the engine, the fuel of which is supplied to the engine by means of a high pressure pump which replaces a carburetor, said pump being actuated by the rotation of the crankshaft.
  • a high pressure pump is fixed outside the engine block and can be driven indirectly by the crankshaft via a motion transmission system, comprising pulleys and at least one transmission band which can be a chain. or a belt.
  • the high pressure pump is actuated by a cam fixed to a movable shaft in rotation about an axis parallel to the axis of the crankshaft, said shaft is driven in rotation by the crankshaft thanks to a transmission device comprising pulleys substantially coplanar and fixed at the end of the crankshaft and of the movable shaft and a belt surrounding said pulleys.
  • the publication FR3011588-A1 discloses a cam attached coaxially to a motor vehicle heat engine crankshaft to actuate a high pressure heat engine fuel supply pump. Said cam is disposed between two arms of said crankshaft.
  • the pump is conventionally a plate pump which comprises an input shaft driving in rotation a plate which is inclined with respect to the axis and which is capable of stressing the axial pistons mounted to move in chambers into which is admitted and then ejected. fuel.
  • Such a design has the advantage of being more compact than the conventional design, but it nevertheless has the drawback of requiring the provision of a block capable of accommodating an additional shaft, with what this implies in terms of complexity of molding and of additional machining of the block.
  • the document FR2 984 965 -A1 proposes an arrangement of a fuel pump at one end of a camshaft, said pump has a sliding axis coaxial with the axis of the camshaft.
  • the drawback of this type of arrangement is a significant increase in the longitudinal dimension of the engine, which is restrictive for vehicles comprising an engine compartment with reduced dimensions.
  • the publication FR3011588-A1 discloses a high pressure fuel supply pump for a heat engine of a motor vehicle, said pump is actuated by a drive cam fixed integral with and coaxial with the shaft of a crankshaft.
  • a drawback of this type of arrangement is an increase in the size of the heat engine, in particular in the longitudinal direction of the engine, which does not comply with the restrictions on the dimensions of the engine space in vehicles.
  • a particular arrangement of said pump may be orthogonal to the axis of the crankshaft and to a coupling end of said crankshaft facing the coupling face of the heat engine, said end of the crankshaft is coupled in particular with an engine flywheel of which the The object is to reduce the acyclisms of said motor.
  • a drive cam can then be attached to the coupling end of the crankshaft before an attachment point of the flywheel and surrounding the coupling end of the crankshaft.
  • said cam is mounted with a sliding fit.
  • During the operation of the engine it is rotated by the rotation of the crankshaft and is subjected to forces due to the acyclisms of the operation of the engine and to the relative deformations of the associated parts, forces which can cause axial displacement of the cam and in particular vis-à-vis - flywheel screw. It is therefore necessary to have means for holding in position relative of the cam vis-à-vis its neighboring elements of the engine such as the flywheel.
  • the object of the invention is to remedy these problems and one of the objects of the invention is an arrangement of the high pressure fuel supply pump arranged transversely to the axis of the crankshaft and at one end of the crankshaft, said pump being actuated by the rotational movements of the crankshaft via an actuating cam.
  • the object of the invention relates to an arrangement of a cam for actuating the fuel pump at one end of the crankshaft facing the flywheel of the engine while minimizing the size of the engine.
  • the object of the invention relates more particularly to a system for fixing an actuating cam arranged around a crankshaft of a heat engine of a motor vehicle surrounding a crankshaft end bordered by a flywheel, said crankshaft being housed in an engine crankcase, said cam comprising a cylindrical bearing portion extended radially by an oblong plate, characterized in that the cylindrical bearing portion of the slidably mounted cam surrounding the coupling end of the crankshaft carries a connecting ring for maintaining said cam in axial position with the crankshaft.
  • the connecting ring makes it possible to damp the shocks due to the acyclisms of the operation of the engine and makes it possible to maintain the cam in axial position against the flywheel at the end of the crankshaft.
  • the cam is mounted at the coupling end of the crankshaft to optimize the compactness of the engine. It is slidably mounted to allow easy disassembly of the crankshaft, for example during handling in a maintenance workshop. As a result of this sliding assembly, during engine operation, it is subjected to repeated shocks which can cause the cam to slide on the end of the crankshaft, which sliding can therefore cause poor contact when pressing a pump. fuel operated by said cam and therefore poor fuel supply. It is therefore necessary to keep this cam in an axial position with the crankshaft.
  • the connecting ring arranged around the cylindrical bearing part of the actuating cam has a radial face facing the engine flywheel. It therefore makes it possible to separate the actuation cam from the flywheel and to preserve a space between the actuation cam and the engine flywheel.
  • the longitudinal direction X of the engine coplanar and orthogonal with said longitudinal direction X to define a horizontal plane of the vehicle, and a vertical Z direction directed towards the top of the vehicle.
  • the longitudinal direction X is relative to the heat engine which is perpendicular to the longitudinal direction of the vehicle for an engine mounted transversely.
  • the heat engine comprises a fuel supply pump 14 arranged at a coupling end 110 of the engine, said pump being actuated by an actuating cam 15 integral in rotation with the crankshaft 10 and in contact with a flywheel 11.
  • thermal motor vehicle engines comprise a cylinder block 12 comprising at least one cylinder 13 in which a piston (not shown) is able to slide in a reciprocating movement along the axis of said cylinder, and a cylinder head (not shown) covering the upper part of the cylinder block facing the hood of the vehicle.
  • the movements of the piston are driven by a variation of a combustion chamber delimited by the at least one cylinder 13, said piston and a wall of the cylinder head.
  • the at-least one piston is linked to a crankshaft 10 arranged along a substantially horizontal X axis and orthogonal to the vertical Y axis of the at least one cylinder and the reciprocating sliding movements of the at least one piston drives a rotational movement of the crankshaft 10.
  • the sliding movements of the at least one piston are not carried out in a regular manner and produce acyclisms which have repercussions on transmission elements connected to said engine and particularly to the crankshaft.
  • the fuel feed pump 14 for injecting fuel into the combustion chamber via injectors can be a high pressure pump comprising an axis holding at a free end a drive roller resting on a drive surface. Said surface has undulations and is driven in motion by the rotation of the crankshaft.
  • said drive surface is for example a peripheral surface 24 of a plate 23 of substantially oblong shape of the actuating cam 15, which is fixed integral in rotation around its axis to the axis of the crankshaft 10.
  • a particular arrangement of said high pressure pump according to the invention is an arrangement of the high pressure fuel supply pump 14 orthogonally to the horizontal axis X of the crankshaft and to the coupling end 111 of said rotated crankshaft 10. towards the coupling face 110 of the heat engine, said end of the crankshaft is coupled in particular with the flywheel 11 of the engine, the object of which is to reduce the acyclisms of said engine.
  • the crankshaft has an axis with a first end 114 of accessories linked to a toothed wheel (not shown) capable of driving a camshaft pinion and accessory pinions such as a water pump or an air conditioning compressor (not shown) and a second diametrically opposed coupling end 111 connected to the gearbox and on which the flywheel 11 is fixed.
  • a camshaft pinion and accessory pinions such as a water pump or an air conditioning compressor (not shown) and a second diametrically opposed coupling end 111 connected to the gearbox and on which the flywheel 11 is fixed.
  • the actuating cam is fixed to the coupling end of the crankshaft before an attachment point 112 of the flywheel 11.
  • Said actuating cam 15 is rotated by the rotation of the crankshaft 11 and is subjected in particular to forces due to the acyclisms of the operation of the engine and to the relative deformations of the associated parts, forces which can cause radial and axial displacements of the cam and in particular relative to the flywheel.
  • the actuating cam 15 comprises a bearing portion 16 preferably cylindrical adapted to surround the coupling end 111 of the crankshaft 11, said bearing part 16 is extended radially by a substantially oblong plate 23 which comprises the peripheral surface 24 on which a roller of the high pressure pump 14 bears. fuel supply.
  • Said cylindrical bearing portion 16 is separate from the oblong plate 23 and is turned towards the outside of the engine when the actuating cam 15 is mounted on the crankshaft 10 and facing the flywheel 11.
  • This form of cam actuation 15 allows optimum geometric adaptation of the cam according to the geometric constraints of the cylinder block 12.
  • the cylindrical bearing portion 16 allows the connection of the actuating cam with the crankshaft 10 and it carries a substantially annular connecting ring 40 having characteristics of elasticity and flexibility.
  • said ring is made of elastomer, for example EPDM, which is an acronym for ethylene-propylene diene monomer which is an oil-resistant elastomer.
  • EPDM ethylene-propylene diene monomer which is an oil-resistant elastomer.
  • the connecting ring is fixed against a radial end wall 43 of the actuating cam, for example by gluing.
  • the connecting ring 40 therefore has a radial face 41 vis-à-vis the flywheel when the ring is mounted. It thus makes it possible to separate the flywheel 11 and the actuating cam 15.
  • the actuating cam 15 and the connecting ring 30 are housed in a receiving chamber 30 of the cylinder block 12 preferably at a longitudinal end 110 of said cylinder block on the coupling face side.
  • said receiving chamber 30 is separated from a chamber of connecting rods 31 in which the elements of the crankshaft, which are the crank pins 32 and the journals 33, are arranged by an end wall 34 of the cylinder block 12, wall surrounding a crankshaft retaining bearing.
  • the coupling end 111 of the crankshaft thus opens out from the connecting rod chamber 31 by passing through a retaining opening hollowed out in the end wall 34 and surrounding the retaining bearing of said crankshaft, in the receiving chamber 30. Said chamber.
  • a substantially cylindrical wall 35 adapted to surround the drive cam 15 and the connecting ring 40 and which extends longitudinally the cylinder block.
  • Said cylindrical wall 35 may include an orifice (not shown) for the passage of the substantially cylindrical body of the high pressure pump.
  • the actuating cam 15 can have axial movements and come into contact with the flywheel 11.
  • the connecting ring allows said cam 15 to be pushed back to separate it from the flywheel therefore. axial retention of the actuating cam.
  • the cam can also have radial relative displacements.
  • the connecting ring 40 also allows radial retention of the actuating cam. By its elastic characteristics, the connecting ring ensures optimum retention of the drive cam. It also provides shock absorption due to acyclism in engine operation.
  • the actuating cam 15 is mounted around the coupling end 111 of the crankshaft 10 with a sliding adjustment with minimal or ordinary play to allow easy removal of said cam during maintenance or repair phases. engine cleaning requiring disassembly of the crankshaft. In this advantageous way, after removal of the flywheel, it suffices to remove the drive cam by sliding it towards the outside of the crankshaft and then remove the crankshaft.
  • the connecting ring allows axial retention in position of the actuating cam.
  • Said connecting ring makes it possible, with minimal cost, to ensure the maintenance in position of the actuating cam mounted around the coupling end of the crankshaft with a sliding adjustment to facilitate the mechanical dismantling operations, and the damping of the crankshaft. shocks undergone by said cam and ensure a seal of the reception chamber of the cylinder block.
  • the cam may be an oblong plate having a fixing orifice through which the coupling end of said crankshaft passes.
  • the cam may then have a preferably circular groove in which the connecting ring is housed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Description

Domaine technique de l'inventionTechnical field of the invention

La présente invention se rapporte au domaine des véhicules automobiles et concerne une pompe haute pression d'alimentation en carburant.The present invention relates to the field of motor vehicles and relates to a high pressure fuel supply pump.

L'invention concerne plus particulièrement un agencement d'une came d'activation de la pompe haute pression, solidaire en rotation d'un vilebrequin mobile en rotation à l'intérieur d'une chambre de bielles dans un carter-cylindres.The invention relates more particularly to an arrangement of an activation cam of the high pressure pump, integral in rotation with a crankshaft movable in rotation inside a chamber of connecting rods in a cylinder block.

L'invention concerne également un moteur à combustion interne de véhicule automobile comportant un carter-cylindres entourant un vilebrequin comportant une came d'activation de pompe à carburant haute pression fixée sur une extrémité du vilebrequin.The invention also relates to an internal combustion engine of a motor vehicle comprising a cylinder block surrounding a crankshaft comprising a high pressure fuel pump activation cam fixed to one end of the crankshaft.

Etat de la techniqueState of the art

L'invention concerne un moteur à combustion interne de véhicule automobile comportant un vilebrequin mobile en rotation autour d'un axe longitudinal du moteur dont l'alimentation en carburant du moteur est effectuée grâce à une pompe haute pression qui remplace un carburateur, ladite pompe étant actionnée par la rotation du vilebrequin.The invention relates to an internal combustion engine of a motor vehicle comprising a crankshaft movable in rotation about a longitudinal axis of the engine, the fuel of which is supplied to the engine by means of a high pressure pump which replaces a carburetor, said pump being actuated by the rotation of the crankshaft.

Différents agencements de pompes haute pression fixés à un moteur thermique sont connus.Different arrangements of high pressure pumps attached to a heat engine are known.

De manière connue, une pompe haute pression est fixée extérieure au bloc moteur et peut être entraînée indirectement par le vilebrequin par l'intermédiaire d'un système de transmission de mouvement, comprenant des poulies et au moins une bande de transmission qui peut être une chaîne ou une courroie. Par exemple, la pompe haute pression est actionnée par une came fixée à un arbre mobile en rotation autour d'un axe parallèle à l'axe du vilebrequin, ledit arbre est entrainé en rotation par le vilebrequin grâce à un dispositif de transmission comprenant des poulies sensiblement coplanaires et fixées à l'extrémité du vilebrequin et de l'arbre mobile et une courroie entourant lesdites poulies.In known manner, a high pressure pump is fixed outside the engine block and can be driven indirectly by the crankshaft via a motion transmission system, comprising pulleys and at least one transmission band which can be a chain. or a belt. For example, the high pressure pump is actuated by a cam fixed to a movable shaft in rotation about an axis parallel to the axis of the crankshaft, said shaft is driven in rotation by the crankshaft thanks to a transmission device comprising pulleys substantially coplanar and fixed at the end of the crankshaft and of the movable shaft and a belt surrounding said pulleys.

La publication FR3011588-A1 divulgue une came fixée de façon coaxiale à un vilebrequin de moteur thermique de véhicule automobile pour actionner une pompe haute pression d'alimentation en carburant de moteur thermique. Ladite came est disposée entre deux bras dudit vilebrequin.The publication FR3011588-A1 discloses a cam attached coaxially to a motor vehicle heat engine crankshaft to actuate a high pressure heat engine fuel supply pump. Said cam is disposed between two arms of said crankshaft.

Un inconvénient est que cet agencement nécessite de repousser l'espace entre les deux bras ce qui peut être impactant pour l'architecture du moteur et augmente sensiblement l'encombrement dudit moteur.One drawback is that this arrangement requires the space between the two arms to be pushed back, which can have an impact on the architecture of the engine and significantly increases the size of said engine.

La pompe est conventionnellement une pompe à plateau qui comporte un arbre d'entrée entraînant en rotation un plateau qui est incliné par rapport à l'axe et qui est susceptible de solliciter des pistons axiaux montés mobiles dans des chambres dans lesquelles est admis puis éjecté le carburant.The pump is conventionally a plate pump which comprises an input shaft driving in rotation a plate which is inclined with respect to the axis and which is capable of stressing the axial pistons mounted to move in chambers into which is admitted and then ejected. fuel.

Il est connu de l'état de la technique, et notamment du document DE102011107291 un moteur comportant une pompe comportant un piston unique, dont le corps est fixé au bloc et dont le piston est entraîné alternativement par un poussoir dont l'extrémité comporte d'un galet qui est susceptible d'être sollicité par une came portée par un arbre interne au bloc du moteur, ledit arbre étant parallèle au vilebrequin et étant entraîné par ledit vilebrequin par l'intermédiaire d'un engrenage.It is known from the state of the art, and in particular from the document DE102011107291 an engine comprising a pump comprising a single piston, the body of which is fixed to the block and the piston of which is driven alternately by a pusher, the end of which comprises a roller which is capable of being biased by a cam carried by a shaft internal to the engine block, said shaft being parallel to the crankshaft and being driven by said crankshaft via a gear.

Une telle conception présente l'avantage d'être plus compacte que la conception conventionnelle, mais elle présente néanmoins l'inconvénient de nécessiter de prévoir un bloc pouvant accueillir un arbre supplémentaire, avec ce que cela implique en termes de complexité de moulage et d'usinages supplémentaires du bloc.Such a design has the advantage of being more compact than the conventional design, but it nevertheless has the drawback of requiring the provision of a block capable of accommodating an additional shaft, with what this implies in terms of complexity of molding and of additional machining of the block.

Le document FR2 984 965 -A1 propose un agencement d'une pompe à carburant à une extrémité d'un arbre à cames, ladite pompe présente un axe de coulissement coaxial avec l'axe de l'arbre à cames. L'inconvénient de ce type d'agencement est un accroissement sensible de la dimension longitudinale du moteur ce qui est contraignant pour des véhicules comportant un compartiment moteur avec des dimensions réduites.The document FR2 984 965 -A1 proposes an arrangement of a fuel pump at one end of a camshaft, said pump has a sliding axis coaxial with the axis of the camshaft. The drawback of this type of arrangement is a significant increase in the longitudinal dimension of the engine, which is restrictive for vehicles comprising an engine compartment with reduced dimensions.

La publication FR3011588-A1 divulgue une pompe haute pression d'alimentation en carburant pour un moteur thermique de véhicule automobile, ladite pompe est actionnée par une came d'entrainement fixée solidaire et coaxiale avec l'arbre d'un vilebrequin.The publication FR3011588-A1 discloses a high pressure fuel supply pump for a heat engine of a motor vehicle, said pump is actuated by a drive cam fixed integral with and coaxial with the shaft of a crankshaft.

Un inconvénient de ce type d'agencement est un accroissement de l'encombrement du moteur thermique notamment dans le sens longitudinal du moteur, peu conforme avec les restrictions des dimensions de l'espace du moteur dans les véhicules.A drawback of this type of arrangement is an increase in the size of the heat engine, in particular in the longitudinal direction of the engine, which does not comply with the restrictions on the dimensions of the engine space in vehicles.

Il est connu également un agencement de la pompe haute pression d'alimentation de carburant à l'aide d'une came disposée à une extrémité du vilebrequin tournée vers une face où sont agencés différents éléments accessoires du moteur tels que la pompe à eau ou un compresseur de climatisation. L'espace disponible est alors très réduit et un agencement particulier de la pompe haute pression entraine l'ajout d'accessoires intermédiaires entre la pompe et le vilebrequin, ce qui nuit à l'efficacité de ladite pompe.It is also known an arrangement of the high pressure fuel supply pump with the aid of a cam arranged at one end of the crankshaft facing a face where various accessory elements of the engine are arranged, such as the water pump or a air conditioning compressor. The available space is then very small and a particular arrangement of the high pressure pump entails the addition of intermediate accessories between the pump and the crankshaft, which affects the efficiency of said pump.

Un agencement particulier de ladite pompe peut être de manière orthogonale à l'axe du vilebrequin et à une extrémité d'accouplement dudit vilebrequin tournée vers la face d'accouplement du moteur thermique, ladite extrémité du vilebrequin est accouplée notamment avec un volant moteur dont l'objet est de réduire les acyclismes dudit moteur.A particular arrangement of said pump may be orthogonal to the axis of the crankshaft and to a coupling end of said crankshaft facing the coupling face of the heat engine, said end of the crankshaft is coupled in particular with an engine flywheel of which the The object is to reduce the acyclisms of said motor.

Une came d'entrainement peut alors être fixée à l'extrémité d'accouplement du vilebrequin avant un point d'accrochage du volant moteur et entourant l'extrémité d'accouplement du vilebrequin. Pour des raisons de démontage, ladite came est montée avec un ajustement glissant. Lors du fonctionnement du moteur, elle est entrainée en rotation par la rotation du vilebrequin et subit des efforts dus aux acyclismes du fonctionnement du moteur et aux déformations relatives des pièces associées, efforts qui peuvent provoquer des déplacements axiaux de la came et notamment vis-à-vis du volant d'inertie. Il est donc nécessaire de disposer de moyens de maintien en position relative de la came vis-à-vis de ses éléments voisins du moteur tels que le volant d'inertie.A drive cam can then be attached to the coupling end of the crankshaft before an attachment point of the flywheel and surrounding the coupling end of the crankshaft. For disassembly reasons, said cam is mounted with a sliding fit. During the operation of the engine, it is rotated by the rotation of the crankshaft and is subjected to forces due to the acyclisms of the operation of the engine and to the relative deformations of the associated parts, forces which can cause axial displacement of the cam and in particular vis-à-vis - flywheel screw. It is therefore necessary to have means for holding in position relative of the cam vis-à-vis its neighboring elements of the engine such as the flywheel.

Bref résumé de l'inventionBrief summary of the invention

Le but de l'invention est de remédier à ces problèmes et un des objets de l'invention est un agencement de la pompe haute pression d'alimentation en carburant disposée de façon transversale à l'axe du vilebrequin et à une extrémité du vilebrequin, ladite pompe étant actionnée par les mouvements de rotation du vilebrequin par l'intermédiaire d'une came d'actionnement.The object of the invention is to remedy these problems and one of the objects of the invention is an arrangement of the high pressure fuel supply pump arranged transversely to the axis of the crankshaft and at one end of the crankshaft, said pump being actuated by the rotational movements of the crankshaft via an actuating cam.

L'objet de l'invention concerne un agencement d'une came d'actionnement de la pompe à carburant à une extrémité du vilebrequin tournée vers le volant d'inertie du moteur en minimisant l'encombrement du moteur.The object of the invention relates to an arrangement of a cam for actuating the fuel pump at one end of the crankshaft facing the flywheel of the engine while minimizing the size of the engine.

L'objet de l'invention concerne plus particulièrement un système de fixation d'une came d'actionnement agencée autour d'un vilebrequin de moteur thermique de véhicule automobile entourant une extrémité de vilebrequin bordée par un volant d'inertie, ledit vilebrequin étant logé dans un carter-cylindres du moteur, ladite came comportant une partie d'appui cylindrique prolongée radialement par un plateau oblong,
caractérisé en ce que la partie d'appui cylindrique de la came montée glissante entourant l'extrémité d'accouplement du vilebrequin porte une bague de liaison pour maintenir en position axiale ladite came avec le vilebrequin.The object of the invention relates more particularly to a system for fixing an actuating cam arranged around a crankshaft of a heat engine of a motor vehicle surrounding a crankshaft end bordered by a flywheel, said crankshaft being housed in an engine crankcase, said cam comprising a cylindrical bearing portion extended radially by an oblong plate,
characterized in that the cylindrical bearing portion of the slidably mounted cam surrounding the coupling end of the crankshaft carries a connecting ring for maintaining said cam in axial position with the crankshaft.

De manière avantageuse, la bague de liaison permet d'amortir les chocs dus aux acyclismes du fonctionnement du moteur et permet de maintenir en position axiale la came contre le volant d'inertie à l'extrémité du vilebrequin. En effet, la came est montée à l'extrémité d'accouplement du vilebrequin pour optimiser la compacité du moteur. Elle est montée glissante pour permettre un démontage aisé du vilebrequin par exemple lors de manipulations dans un atelier de maintenance. Du fait de ce montage glissant, lors du fonctionnement du moteur, elle est soumise à des chocs répétés qui peuvent entrainer un coulissement de la came sur l'extrémité du vilebrequin, coulissement qui peut donc entrainer un mauvais contact en appui d'une pompe à carburant actionnée par ladite came et donc une mauvaise alimentation en carburant. Il est donc nécessaire de maintenir cette came en position axiale avec le vilebrequin.Advantageously, the connecting ring makes it possible to damp the shocks due to the acyclisms of the operation of the engine and makes it possible to maintain the cam in axial position against the flywheel at the end of the crankshaft. Indeed, the cam is mounted at the coupling end of the crankshaft to optimize the compactness of the engine. It is slidably mounted to allow easy disassembly of the crankshaft, for example during handling in a maintenance workshop. As a result of this sliding assembly, during engine operation, it is subjected to repeated shocks which can cause the cam to slide on the end of the crankshaft, which sliding can therefore cause poor contact when pressing a pump. fuel operated by said cam and therefore poor fuel supply. It is therefore necessary to keep this cam in an axial position with the crankshaft.

Selon d'autres caractéristiques de l'invention :

  • la bague de liaison est élastique.
According to other characteristics of the invention:
  • the connecting ring is elastic.

De manière avantageuse, la bague de liaison élastique permet de maintenir en position axiale la came d'actionnement et d'amortir les chocs dus aux acyclismes du fonctionnement du moteur thermique entrainant des déplacements axiaux de la came. En plus de l'effet de maintien en position axiale de ladite came, la bague permet grâce à ses caractéristiques de souplesse un amortissement des effets du moteur.

  • la bague de liaison est fixée à une paroi d'extrémité radiale de la came d'actionnement.
Advantageously, the elastic connecting ring makes it possible to maintain the actuating cam in an axial position and to damp the shocks due to acyclisms in the operation of the heat engine causing axial movements of the cam. In addition to the effect of maintaining said cam in the axial position, the ring allows, thanks to its flexibility characteristics, a damping of the effects of the motor.
  • the connecting ring is fixed to a radial end wall of the actuating cam.

De manière avantageuse, la bague de liaison est agencée à l'extrémité du vilebrequin tournée vers la face d'accouplement du moteur thermique, ce qui contribue à diminuer l'encombrement de l'agencement de la pompe haute pression de carburant et donc du moteur.

  • la bague de liaison est en élastomère.
Advantageously, the connecting ring is arranged at the end of the crankshaft facing the coupling face of the heat engine, which contributes to reducing the size of the arrangement of the high pressure fuel pump and therefore of the engine. .
  • the connecting ring is made of elastomer.

De manière avantageuse, la bague de liaison est en élastomère ce qui présente une facilité de fabrication avec un coût réduit.

  • la bague de liaison comporte une face radiale en vis-à-vis avec le volant moteur.
Advantageously, the connecting ring is made of elastomer, which is easy to manufacture at reduced cost.
  • the connecting ring has a radial face vis-à-vis the flywheel.

De manière avantageuse, la bague de liaison agencée autour de la partie cylindrique d'appui de la came d'actionnement présente une face radiale en vis-à-vis avec le volant moteur. Elle permet donc de séparer la came d'actionnement du volant d'inertie et de préserver un espace entre la came d'actionnement et le volant moteur.Advantageously, the connecting ring arranged around the cylindrical bearing part of the actuating cam has a radial face facing the engine flywheel. It therefore makes it possible to separate the actuation cam from the flywheel and to preserve a space between the actuation cam and the engine flywheel.

Brève description des figuresBrief description of the figures

D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la description détaillée de modes particuliers de réalisation de l'invention donnés à titre d'exemples non limitatifs, qui suit pour la compréhension de laquelle on se reportera aux dessins annexés dans lesquels :

  • la figure 1 est une vue de coupe longitudinale d'un carter-cylindres d'un moteur thermique avec un agencement particulier d'une pompe haute pression d'alimentation de carburant.
  • la figure 2 est une vue de coupe longitudinale de l'extrémité d'accouplement du vilebrequin avec une came d'actionnement d'une pompe haute pression d'alimentation de carburant.
  • la figure 3 est une vue de l'extrémité d'accouplement du vilebrequin avec une came d'actionnement d'une pompe haute pression d'alimentation de carburant et de la bague de liaison selon l'invention.
  • la figure 4 est une vue de l'extrémité d'accouplement du vilebrequin avec une came d'actionnement d'une pompe haute pression d'alimentation de carburant sans la bague de liaison selon l'invention
  • la figure 5 est une vue de coupe longitudinale de l'extrémité d'accouplement du vilebrequin avec une came d'actionnement d'une pompe haute pression d'alimentation de carburant et de la bague de liaison.
  • la figure 6 est une vue de coupe longitudinale de l'extrémité d'accouplement du carter-cylindres avec une came d'actionnement d'une pompe haute pression d'alimentation de carburant et de la bague de liaison.
  • la figure 7 est une vue schématique de la came d'actionnement.
  • la figure 8 est une vue schématique de la came d'actionnement avec la bague de liaison.
Other characteristics and advantages of the invention will become apparent on reading the detailed description of particular embodiments of the invention given by way of non-limiting examples, which follows, for the understanding of which reference is made to the accompanying drawings in which :
  • the figure 1 is a longitudinal sectional view of a cylinder block of a heat engine with a particular arrangement of a high pressure fuel supply pump.
  • the figure 2 is a longitudinal sectional view of the coupling end of the crankshaft with an actuating cam of a high pressure fuel supply pump.
  • the figure 3 is a view of the coupling end of the crankshaft with an actuating cam of a high pressure fuel supply pump and of the connecting ring according to the invention.
  • the figure 4 is a view of the coupling end of the crankshaft with an actuating cam of a high pressure fuel supply pump without the connecting ring according to the invention
  • the figure 5 is a longitudinal sectional view of the coupling end of the crankshaft with an actuating cam of a high pressure fuel supply pump and of the connecting ring.
  • the figure 6 is a longitudinal sectional view of the coupling end of the cylinder block with an actuating cam of a high pressure fuel feed pump and of the connecting ring.
  • the figure 7 is a schematic view of the actuation cam.
  • the figure 8 is a schematic view of the actuating cam with the connecting ring.

Description détaillée des figuresDetailed description of figures

Dans la description qui va suivre, des chiffres de référence identiques désignent des pièces identiques ou ayant des fonctions similaires.In the description which follows, identical reference numerals denote identical parts or having similar functions.

La description suivante est faite selon trois axes spatiaux qui sont la direction longitudinale X du moteur, la direction transversale Y coplanaire et orthogonale avec ladite direction longitudinale X pour définir un plan horizontal du véhicule, et une direction Z verticale dirigée vers le haut du véhicule. Il faut noter que la direction longitudinale X est par rapport au moteur thermique qui est perpendiculaire à la direction longitudinale du véhicule pour un moteur monté transversalement.The following description is given along three spatial axes which are the longitudinal direction X of the engine, the transverse direction Y coplanar and orthogonal with said longitudinal direction X to define a horizontal plane of the vehicle, and a vertical Z direction directed towards the top of the vehicle. It should be noted that the longitudinal direction X is relative to the heat engine which is perpendicular to the longitudinal direction of the vehicle for an engine mounted transversely.

Comme représenté en figures 1 et 2, le moteur thermique selon l'invention comprend une pompe 14 d'alimentation de carburant agencée à une extrémité d'accouplement 110 du moteur, ladite pompe étant actionnée par une came d'actionnement 15 solidaire en rotation avec le vilebrequin 10 et en contact avec un volant d'inertie 11.As shown in figures 1 and 2 , the heat engine according to the invention comprises a fuel supply pump 14 arranged at a coupling end 110 of the engine, said pump being actuated by an actuating cam 15 integral in rotation with the crankshaft 10 and in contact with a flywheel 11.

De manière connue, les moteurs thermiques de véhicule automobile comprennent un carter-cylindres 12 comportant au moins un cylindre 13 dans lequel un piston (non représenté) est apte à coulisser selon un mouvement de va-et-vient selon l'axe dudit cylindre, et une culasse (non représentée) recouvrant la partie supérieure du carter-cylindres tournée vers le capot du véhicule. Les mouvements du piston sont entrainés par une variation d'une chambre à combustion délimitée par le au-moins un cylindre 13, ledit piston et une paroi de la culasse. Le au-moins un piston est lié à un vilebrequin 10 agencé selon un axe X sensiblement horizontal et orthogonal à l'axe Y vertical du au-moins un cylindre et les mouvements de coulissement en va-et-vient du au moins un piston entraine un mouvement en rotation du vilebrequin 10. Cependant, les déplacements en coulissement du au-moins un piston ne sont pas effectués de manière régulière et produisent des acyclismes qui se répercutent sur des éléments de transmission reliés audit moteur et particulièrement au vilebrequin.In a known manner, thermal motor vehicle engines comprise a cylinder block 12 comprising at least one cylinder 13 in which a piston (not shown) is able to slide in a reciprocating movement along the axis of said cylinder, and a cylinder head (not shown) covering the upper part of the cylinder block facing the hood of the vehicle. The movements of the piston are driven by a variation of a combustion chamber delimited by the at least one cylinder 13, said piston and a wall of the cylinder head. The at-least one piston is linked to a crankshaft 10 arranged along a substantially horizontal X axis and orthogonal to the vertical Y axis of the at least one cylinder and the reciprocating sliding movements of the at least one piston drives a rotational movement of the crankshaft 10. However, the sliding movements of the at least one piston are not carried out in a regular manner and produce acyclisms which have repercussions on transmission elements connected to said engine and particularly to the crankshaft.

De manière connue également, la pompe d'alimentation à carburant 14 pour injecter du carburant dans la chambre à combustion via des injecteurs par exemple, peut être une pompe haute pression comportant un axe tenant à une extrémité libre un galet d'entrainement en appui sur une surface d'entrainement. Ladite surface présente des ondulations et est entrainée en mouvement par la rotation du vilebrequin.Also in a known manner, the fuel feed pump 14 for injecting fuel into the combustion chamber via injectors by example, can be a high pressure pump comprising an axis holding at a free end a drive roller resting on a drive surface. Said surface has undulations and is driven in motion by the rotation of the crankshaft.

Selon les figures 1, 2 et 5, ladite surface d'entrainement est par exemple une surface périphérique 24 d'un plateau 23 de forme sensiblement oblongue de la came d'actionnement 15, laquelle est fixée solidaire en rotation autour de son axe à l'axe du vilebrequin 10.According to figures 1, 2 and 5 , said drive surface is for example a peripheral surface 24 of a plate 23 of substantially oblong shape of the actuating cam 15, which is fixed integral in rotation around its axis to the axis of the crankshaft 10.

Un agencement particulier de ladite pompe haute pression selon l'invention est une disposition de la pompe haute pression d'alimentation de carburant 14 de manière orthogonale à l'axe horizontal X du vilebrequin et à l'extrémité d'accouplement 111 dudit vilebrequin 10 tournée vers la face d'accouplement 110 du moteur thermique, ladite extrémité du vilebrequin est accouplée notamment avec le volant d'inertie 11 du moteur dont l'objet est de réduire les acyclismes dudit moteur.A particular arrangement of said high pressure pump according to the invention is an arrangement of the high pressure fuel supply pump 14 orthogonally to the horizontal axis X of the crankshaft and to the coupling end 111 of said rotated crankshaft 10. towards the coupling face 110 of the heat engine, said end of the crankshaft is coupled in particular with the flywheel 11 of the engine, the object of which is to reduce the acyclisms of said engine.

Le vilebrequin comporte un axe avec une première extrémité 114 d'accessoires liée à une roue dentée (non représentée) apte à entrainer un pignon d'arbre à cames et des pignons d'accessoires tels que une pompe à eau ou un compresseur de climatisation (non représentés) et une deuxième extrémité 111 d'accouplement diamétralement opposée connectée à la boite de vitesses et sur laquelle est fixé le volant d'inertie 11.The crankshaft has an axis with a first end 114 of accessories linked to a toothed wheel (not shown) capable of driving a camshaft pinion and accessory pinions such as a water pump or an air conditioning compressor ( not shown) and a second diametrically opposed coupling end 111 connected to the gearbox and on which the flywheel 11 is fixed.

Selon la figure 1, la came d'actionnement est fixée sur l'extrémité d'accouplement du vilebrequin avant un point d'accrochage 112 du volant d'inertie 11.According to figure 1 , the actuating cam is fixed to the coupling end of the crankshaft before an attachment point 112 of the flywheel 11.

Ladite came d'actionnement 15 est entrainée en rotation par la rotation du vilebrequin 11 et subit notamment des efforts dus aux acyclismes du fonctionnement du moteur et aux déformations relatives des pièces associées, efforts qui peuvent provoquer des déplacements radiaux et axiaux de la came et notamment relatifs par rapport au volant d'inertie.Said actuating cam 15 is rotated by the rotation of the crankshaft 11 and is subjected in particular to forces due to the acyclisms of the operation of the engine and to the relative deformations of the associated parts, forces which can cause radial and axial displacements of the cam and in particular relative to the flywheel.

Selon l'invention, telle que représentée dans les figures 2 à 8, la came d'actionnement 15 comporte une partie d'appui 16 de manière préférentielle cylindrique adaptée pour entourer l'extrémité d'accouplement 111 du vilebrequin 11, ladite partie d'appui 16 est prolongée radialement par un plateau 23 sensiblement oblong qui comporte la surface périphérique 24 sur laquelle vient en appui un galet de la pompe 14 haute pression d'alimentation de carburant. Ladite partie d'appui cylindrique 16 est distincte du plateau oblong 23 et est tournée vers l'extérieur du moteur lorsque la came d'actionnement 15 est montée sur le vilebrequin 10 et en regard avec le volant d'inertie 11. Cette forme de came d'actionnement 15 permet une adaptation géométrique optimale de la came selon des contraintes géométriques du carter-cylindres 12.According to the invention, as shown in figures 2 to 8 , the actuating cam 15 comprises a bearing portion 16 preferably cylindrical adapted to surround the coupling end 111 of the crankshaft 11, said bearing part 16 is extended radially by a substantially oblong plate 23 which comprises the peripheral surface 24 on which a roller of the high pressure pump 14 bears. fuel supply. Said cylindrical bearing portion 16 is separate from the oblong plate 23 and is turned towards the outside of the engine when the actuating cam 15 is mounted on the crankshaft 10 and facing the flywheel 11. This form of cam actuation 15 allows optimum geometric adaptation of the cam according to the geometric constraints of the cylinder block 12.

Comme représenté sur les figures 4 à 6, la partie d'appui cylindrique 16 permet la liaison de la came d'actionnement avec le vilebrequin 10 et elle porte une bague de liaison 40 sensiblement annulaire présentant des caractéristiques d'élasticité et de souplesse. De manière préférentielle, ladite bague est en élastomère par exemple en EPDM qui est un sigle pour éthylène-propylène diène monomère qui est un élastomère résistant à l'huile. La bague de liaison est fixée contre une paroi d'extrémité radiale 43 de la came d'actionnement par exemple par collage. La bague de liaison 40 comporte donc une face radiale 41 en vis-à-vis avec le volant d'inertie quand la bague est montée. Elle permet ainsi de séparer le volant d'inertie 11 et la came d'actionnement 15.As shown on figures 4 to 6 , the cylindrical bearing portion 16 allows the connection of the actuating cam with the crankshaft 10 and it carries a substantially annular connecting ring 40 having characteristics of elasticity and flexibility. Preferably, said ring is made of elastomer, for example EPDM, which is an acronym for ethylene-propylene diene monomer which is an oil-resistant elastomer. The connecting ring is fixed against a radial end wall 43 of the actuating cam, for example by gluing. The connecting ring 40 therefore has a radial face 41 vis-à-vis the flywheel when the ring is mounted. It thus makes it possible to separate the flywheel 11 and the actuating cam 15.

Selon la figure 6, la came d'actionnement 15 et la bague de liaison 30 sont logées dans une chambre d'accueil 30 du carter-cylindres 12 de manière préférentielle à une extrémité longitudinale 110 dudit carter-cylindres côté face accouplement. De manière préférentielle, ladite chambre d'accueil 30 est séparée d'une chambre de bielles 31 dans laquelle sont agencés les éléments du vilebrequin que sont les manetons 32 et les tourillons 33, par une paroi d'extrémité 34 du carter-cylindres 12, paroi qui entoure un palier de maintien du vilebrequin. L'extrémité d'accouplement 111 du vilebrequin débouche ainsi de la chambre de bielles 31 en traversant une ouverture de maintien creusée dans la paroi d'extrémité 34 et entourant le palier de maintien dudit vilebrequin, dans la chambre d'accueil 30. Ladite chambre d'accueil est par exemple délimitée par une paroi sensiblement cylindrique 35 adaptée pour entourer la came d'entrainement 15 et la bague de liaison 40 et qui prolonge longitudinalement le carter-cylindres. Ladite paroi cylindrique 35 peut comporter un orifice (non représenté) pour le passage du corps sensiblement cylindrique de la pompe haute pression.According to figure 6 , the actuating cam 15 and the connecting ring 30 are housed in a receiving chamber 30 of the cylinder block 12 preferably at a longitudinal end 110 of said cylinder block on the coupling face side. Preferably, said receiving chamber 30 is separated from a chamber of connecting rods 31 in which the elements of the crankshaft, which are the crank pins 32 and the journals 33, are arranged by an end wall 34 of the cylinder block 12, wall surrounding a crankshaft retaining bearing. The coupling end 111 of the crankshaft thus opens out from the connecting rod chamber 31 by passing through a retaining opening hollowed out in the end wall 34 and surrounding the retaining bearing of said crankshaft, in the receiving chamber 30. Said chamber. reception is for example delimited by a substantially cylindrical wall 35 adapted to surround the drive cam 15 and the connecting ring 40 and which extends longitudinally the cylinder block. Said cylindrical wall 35 may include an orifice (not shown) for the passage of the substantially cylindrical body of the high pressure pump.

En effet, en fonctionnement du moteur, la came d'actionnement 15 peut avoir des déplacements axiaux et venir au contact avec le volant d'inertie 11. La bague de liaison permet de repousser ladite came 15 pour la séparer du volant d'inertie donc un maintien axial de la came d'actionnement.In fact, in operation of the engine, the actuating cam 15 can have axial movements and come into contact with the flywheel 11. The connecting ring allows said cam 15 to be pushed back to separate it from the flywheel therefore. axial retention of the actuating cam.

La came peut aussi avoir des déplacements relatifs radiaux. La bague de liaison 40 permet également un maintien radial de la came d'actionnement. Par ses caractéristiques élastiques, la bague de liaison assure un maintien optimal en place de la came d'entrainement. Elle assure également un amortissement des chocs dus aux acyclismes du fonctionnement du moteur.The cam can also have radial relative displacements. The connecting ring 40 also allows radial retention of the actuating cam. By its elastic characteristics, the connecting ring ensures optimum retention of the drive cam. It also provides shock absorption due to acyclism in engine operation.

De manière préférentielle, la came d'actionnement 15 est montée autour de l'extrémité d'accouplement 111 du vilebrequin 10 avec un ajustement glissant avec un jeu minimal ou ordinaire pour permettre le démontage aisé de ladite came lors de phases d'entretien ou de nettoyage du moteur nécessitant un démontage du vilebrequin. De cette façon avantageuse, après une dépose du volant d'inertie, il suffit de retirer la came d'entrainement en la faisant glisser vers l'extérieur du vilebrequin et ensuite déposer le vilebrequin.Preferably, the actuating cam 15 is mounted around the coupling end 111 of the crankshaft 10 with a sliding adjustment with minimal or ordinary play to allow easy removal of said cam during maintenance or repair phases. engine cleaning requiring disassembly of the crankshaft. In this advantageous way, after removal of the flywheel, it suffices to remove the drive cam by sliding it towards the outside of the crankshaft and then remove the crankshaft.

L'objectif de l'invention est atteint : la bague de liaison permet un maintien axial en position de la came d'actionnement. Ladite bague de liaison permet avec un coût minimal d'assurer le maintien en position de la came d'actionnement montée autour de l'extrémité d'accouplement du vilebrequin avec un ajustement glissant pour faciliter les opérations de démontage mécanique, et l'amortissement des chocs subis par ladite came et d'assurer une étanchéité de la chambre d'accueil du carter-cylindres.The objective of the invention is achieved: the connecting ring allows axial retention in position of the actuating cam. Said connecting ring makes it possible, with minimal cost, to ensure the maintenance in position of the actuating cam mounted around the coupling end of the crankshaft with a sliding adjustment to facilitate the mechanical dismantling operations, and the damping of the crankshaft. shocks undergone by said cam and ensure a seal of the reception chamber of the cylinder block.

Comme il va de soi, l'invention ne se limite pas aux seules formes d'exécution de cette prise, décrites ci-dessus à titre d'exemples, elle en embrasse au contraire toutes les variantes. C'est ainsi notamment que selon un autre mode de réalisation non représenté, la came peut être un plateau oblong présentant un orifice de fixation traversé par l'extrémité d'accouplement dudit vilebrequin. La came peut alors présenter une rainure de manière préférentielle circulaire dans laquelle est logée la bague de liaison.As goes without saying, the invention is not limited to the only embodiments of this plug, described above by way of examples, it embraces on the contrary all the variants thereof. Thus, in particular, according to another embodiment not shown, the cam may be an oblong plate having a fixing orifice through which the coupling end of said crankshaft passes. The cam may then have a preferably circular groove in which the connecting ring is housed.

Claims (5)

  1. System for fastening an actuating cam (15) arranged around a crankshaft (10) of a motor vehicle heat engine surrounding a crankshaft coupling end (111) bordered axially by a flywheel (11), said crankshaft being housed in a crankcase (12) of the engine, said actuating cam (15) having a cylindrical bearing part (16) extended radially by an elongate plate (23),
    characterized in that the cylindrical bearing part (16) of the actuating cam (15) that is mounted in a sliding manner surrounding the coupling end (111) of the crankshaft bears a connecting ring (40) for axially keeping said cam with the crankshaft.
  2. System for fastening an actuating cam (15) according to Claim 1, characterized in that the connecting ring (40) is elastic.
  3. System for fastening an actuating cam (15) according to Claim 1 or 2, characterized in that the connecting ring (40) is fastened to a radial end wall (43) of the actuating cam (15).
  4. System for fastening an actuating cam (15) according to any one of Claims 1 to 3, characterized in that the connecting ring (40) is made of elastomer.
  5. System for fastening an actuating cam (15) according to any one of Claims 1 to 4, characterized in that the connecting ring (40) has a radial face (41) facing the flywheel (11).
EP17777939.4A 2016-10-20 2017-09-14 Elastomer wedge between a hp pump cam and an engine flywheel Active EP3529485B1 (en)

Applications Claiming Priority (2)

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FR1660184A FR3057914B1 (en) 2016-10-20 2016-10-20 ELASTOMER BLOCK BETWEEN HP PUMP CAM AND ENGINE FLYWHEEL
PCT/FR2017/052450 WO2018073504A1 (en) 2016-10-20 2017-09-14 Elastomer wedge between a hp pump cam and an engine flywheel

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EP3529485B1 true EP3529485B1 (en) 2020-08-05

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FR3092877B1 (en) * 2019-02-19 2021-01-22 Renault Sas "Engine comprising a crankshaft equipped with a control cam and rotational guide means"

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FR3057914B1 (en) 2018-10-26
WO2018073504A1 (en) 2018-04-26
FR3057914A1 (en) 2018-04-27
EP3529485A1 (en) 2019-08-28

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