EP3207234B1 - Device for compensating for the operating clearances of an engine - Google Patents

Device for compensating for the operating clearances of an engine Download PDF

Info

Publication number
EP3207234B1
EP3207234B1 EP15753643.4A EP15753643A EP3207234B1 EP 3207234 B1 EP3207234 B1 EP 3207234B1 EP 15753643 A EP15753643 A EP 15753643A EP 3207234 B1 EP3207234 B1 EP 3207234B1
Authority
EP
European Patent Office
Prior art keywords
engine
chamber
compensation device
piston
transmission device
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
EP15753643.4A
Other languages
German (de)
French (fr)
Other versions
EP3207234A1 (en
Inventor
Benoit SCHWENCK
Sylvain Bigot
François Besson
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.)
MCE5 Development SA
Original Assignee
MCE5 Development SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MCE5 Development SA filed Critical MCE5 Development SA
Publication of EP3207234A1 publication Critical patent/EP3207234A1/en
Application granted granted Critical
Publication of EP3207234B1 publication Critical patent/EP3207234B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/044—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of an adjustable piston length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

Definitions

  • the invention relates to a device for compensating the operating clearances of an engine, and in particular a variable volumetric ratio engine.
  • An engine transmission device comprises a set of moving components providing or coming into play when transmitting the translational movement of a combustion piston in a cylinder to a rotational movement of a crankshaft.
  • the operating games must be perfectly controlled. Too large, they lead to excessive acoustic emission of the engine during its operation, accelerated degradation of its components, or even its destruction for example by de-gearing components mobile. Too small, zero or negative, they lead to excessive friction between the moving components and therefore to a degraded engine performance, its blockage or even its destruction.
  • static effort is meant a constant effort during a motor cycle.
  • the static force is calibrated to oppose the maximum forces that apply to the transmission device, especially for the engine operating conditions (regime, load) causing the greatest effort.
  • the static force ensures the permanent contact of the moving components of this device. It is therefore relatively important.
  • This abutment requires assembly fine adjustment and specific to each subassembly associated with a cylinder of the engine. This operation is not particularly desirable at the industrial level for reasons of cost.
  • the position of the adjusted stop has the further disadvantage of being fixed, and not to compensate for the phenomena related to differential expansion between the housing and the transmission elements, nor the offsets related for example to wear parts.
  • the need for calibration of the holding force is particularly marked for a variable volumetric ratio motor, as described in the cited documents of the state of the art, and according to which a static holding force is applied to a side of a control rack whose longitudinal movement ensures the control of the volumetric ratio. Indeed, it is particularly important in this case to limit the static value of the holding force so as not to block or limit the movement of the control rack, in particular by sliding against the wall of the engine block.
  • An object of the invention is to provide a device for compensating the operating clearances of a motor obviating the aforementioned drawbacks.
  • the object of the invention proposes a device for compensating the operating clearances of an engine according to the features of claim 1.
  • the compensation device allows the slow movements of the transmission device by applying a moderate holding force during these movements. It is opposed to the rapid movement of the transmission device, corresponding mainly to the peak of effort related to the combustion of the mixture in the cylinder, by applying a high holding force during these movements.
  • the compensation device of the invention thus makes it possible to control the operating clearances existing between the mobile members of the transmission device by applying a moderate average holding force during the engine cycle, and without exerting a mechanical stop.
  • the figure 1 presents an overall cross section, and schematically, of the device for compensating the functional clearances of an engine according to the invention and used in the case of a variable volumetric ratio engine.
  • an engine block 100 comprises at least one cylinder 110 in which is displaced in translation a combustion piston 2 causing the rotation of a crankshaft 9 by means of a transmission device 1.
  • the transmission device 1 comprises a transmission member 3 secured to the combustion piston 2 and cooperating on the one hand with a rolling guide device 4 resting on a wall of the engine block 100 and on the other hand with a first side d a toothed wheel 5.
  • the transmission member 3 is provided on one of its faces with a first rack of large dimension whose teeth cooperate with that of the toothed wheel 5.
  • the transmission member 3 is also provided, in contrast to this first rack, another rack whose teeth of small dimensions cooperate with those of the roller 40 of the rolling guide device 4, integral with the engine block 100.
  • the toothed wheel 5 cooperates with a connecting rod 6 connected to the crankshaft 9 in order to carry out the transmission of the movement.
  • the toothed wheel 5 cooperates, on a second side opposite the transmission member 3, with a control rack 7 adapted to move longitudinally along an opposite wall of the engine block 100 and driven by a device control unit 12 comprising a control cylinder, whose piston cylinder is guided in a cylinder cylinder 112 of the engine block 100.
  • the control rack 7 has teeth that cooperate with those of the toothed wheel 5 and may have a raceway which cooperates with a raceway of the toothed wheel 5.
  • the control rack 7 also has on its opposite side a surface support 76 on which is exerted, in the particular configuration represented on the figure 1 , the force of maintaining a pressure device 10 integral with the engine block 100.
  • the pressing device (10) is configured to adjust the holding force at the instantaneous transverse displacement speed of the transmission device (1) in the engine block (100).
  • the control rack 7 and the control device 12 cooperate with the pressing device 10 so as to allow at least a vertical directional translation of the control rack.
  • the pressure device 10 is integral with the engine block 100 and exerts the holding pressure on the transmission device 1 whose main components have just been listed.
  • the pressing device 10 can be incorporated in the transmission device 1, for example in the control rack 7 or the rolling guide device 4, and exert a force on one of the walls. of the engine block 100.
  • the holding force is adjustable at the instantaneous speed of transverse displacement of the transmission device 1 in the engine block 100.
  • the invention thus makes it possible to tolerate the slow displacements of the first mode which are necessary for the proper functioning of the engine; and effectively counter the rapid movements of the second mode that could go against the proper functioning of the engine or degrade performance.
  • the holding force is therefore not static as is the case in known solutions of the state of the art. Nor does it specifically depend on the position of the transmission device 1 in the engine block 100.
  • the slow mode of displacement is preponderant, so that the average force applied to the transmission device during a motor cycle is relatively small; and much less important than that applied in the solutions of the state of the art.
  • the average friction forces between the moving components are reduced, the motor efficiency is improved, and the dimensioning of the components of the transmission device 1, the motor unit 100, and the hydraulic power source can be reduced.
  • An adjusted holding force means that the force exerted is variable according to the amplitude and / or the direction of the instantaneous speed of the transmission device 1.
  • the holding force will be first value.
  • the holding force In the absence of displacement or for instantaneous speeds of low displacement, the holding force will present a second value, less than the first.
  • the second value is greater than a threshold force value, non-zero, that in all circumstances the pressing device exerts on the transmission device 1.
  • the threshold value of the holding force ensures the cohesion and the cooperation of the mobile components of the transmission device 1 and its support on the opposite wall of the engine block 100 in the absence of peak effort exerted on the transmission device 1.
  • cohesion and cooperation is meant that the moving components of the transmission device 10 are in contact or have a controlled clearance that does not affect the operation of the engine.
  • the holding force can evolve continuously and continuously with the instantaneous transverse speed of the transmission device 1. It can also evolve from increasing and discontinuous manner, for example by step, with this speed.
  • the first value of the holding force is determined to ensure the cohesion and cooperation of the mobile components of the transmission device 1 during peaks of effort.
  • This first value can be variable with the speed of displacement. It can also be adjusted according to the load or the operating speed of the engine.
  • the figure 2 represents a particular embodiment of a pressing device 10 for exerting a holding force according to the invention.
  • the pressing device 10 may consist of a chamber 21, for example cylindrical, engaged in an orifice arranged in the engine block 100.
  • the pressing device 10 is assembled in the engine block by attachment means 22, comprising for example a flange secured to the device and bolts screwed into the engine block 100.
  • the chamber 21 is provided with a piston 23, confining the fluid in the chamber 21, and able to evolve in translation in this chamber.
  • the holding force is exerted on the transmission device 1 via the piston head 23.
  • Sealing means are arranged between the cylinder and the piston 23.
  • the piston 23 comprises a projecting central portion 24, releasing an annular space with the inner surface of the piston liner 23, for accommodating a spring 25, as will be discussed in detail later.
  • the piston head 23 has an exposed surface 20 adapted to cooperate with a bearing surface 76 of the control rack 7.
  • the chamber 21 is filled with a fluid such as oil, water or a gas.
  • a fluid such as oil, water or a gas.
  • This may for example be the engine lubricating oil.
  • it is a hydraulic fluid.
  • the chamber 21 is also provided with at least one calibrated leak orifice 28. This allows a flow of the fluid outside the chamber, in particular when a pressure is applied to the fluid via the piston.
  • the chamber 21 is supplied with fluid by a pressure source such as an accumulator (not shown in FIG. figure 2 ) connected fluidly to the chamber 21 for example by supply means such as a conduit and / or a channel 30 arranged in the chamber 21 and opening into a supply zone 31 of the chamber 21.
  • a pressure source such as an accumulator (not shown in FIG. figure 2 ) connected fluidly to the chamber 21 for example by supply means such as a conduit and / or a channel 30 arranged in the chamber 21 and opening into a supply zone 31 of the chamber 21.
  • a check valve 32 arranged between the chamber and the source of pressure ensures the maintenance of a minimum permanent pressure of the fluid within the chamber, identical to the pressure present in the source, and interrupts any power supply when, under the effect of a force exerted on the piston 23, the pressure of the fluid in the chamber exceeds the pressure of the fluid in the source.
  • the check valve 32 may comprise a ball 33 positioned in a bore of the chamber 21 and closing a supply channel from the feed zone 31 when the fluid pressure of the chamber 1 brings to the stop of the canal.
  • the combined arrangement of the piston 23 evolving in a chamber 21 filled with a fluid and having at least one calibrated leakage orifice 28, the pressure source connected to the chamber 21 and the nonreturn valve 32 between the source and the chamber 21 results in a device adapted to provide a force adjusted to the speed of movement of the piston 23.
  • the fluid contained in the chamber 21 flows through the calibrated leak orifice without generating significant overpressure in the chamber; and the piston 23 exerts a low resistance force substantially equivalent to its precharging threshold value.
  • the fluid contained in the chamber can not flow sufficiently and rises in pressure, the piston 23 then exerts a high resistance force much greater than the precharging threshold value.
  • the relationship linking the force to the speed can be calibrated by adjusting for example the dimension of the calibrated leakage orifice 28 of the chamber 21.
  • the chamber 21 is also provided with a spring 25, for example helical as shown in FIG. figure 2 .
  • a spring 25 for example helical as shown in FIG. figure 2 .
  • the spring 25 may be disposed in the annular space formed between the central portion 24 and the inner surface of the piston liner 23, as shown in FIG. figure 2 but it can also be arranged outside the room.
  • the pressure exerted by the hydraulic portion of the pressure device 10 complements the pressure exerted by the spring 25.
  • This hydraulic portion may then have a smaller dimension and in particular have a reduced fluid static pressure.
  • the spring 25 may be chosen so that it contributes between 20% and 40% to the level of threshold force exerted by the pressing device 10. Preferably, this contribution will be chosen at 33%.
  • the presence of the spring 25 also ensures a better reactivity of the pressing device 10 during the oil replenishment phases during which the piston 23 must nevertheless quickly exert pressure on the control rack 7.
  • the presence of the spring 25 allows the engine to operate in a degraded mode in case of failure of the hydraulic part of the pressing device 10 by guaranteeing the functionality of the pressing device 10 over a limited engine operating range.
  • the pressing device 10 may comprise a calibrated leakage orifice 28 fluidly connected to the pressure source. This connection can be made by conduits if the pressure source is offset, or the calibrated leakage orifice 28 can directly supply a reservoir of this pressure source.
  • the chamber 21, the piston 23 and the check valve 31 may advantageously be integrated in an independent capsule then forming an independent pressing device 10.
  • the pressure source may be fluidically connected to all the pressure devices 10 of the engine in the context of a centralized hydraulic management.
  • the calibrated leakage orifice 28 can be disposed in the piston 23 itself and open at the exposed surface 23, in particular to lubricate the surfaces. contact of the control rack 7 and the pressing device 10.
  • a pump of the hydraulic unit can be provided for adjusting the static pressure of the fluid in the pressure source, and consequently the static pressure of the fluid in the pressing device 10. This adjustment can be determined according to the load and the operating speed. engine operation.
  • the hydraulic unit may include a computer, connected to sensors to measure among others the level of load and the speed. The computer determines a target static pressure and drives the pump to bring the static pressure of the accumulator to the target static pressure.
  • the particular configuration of the pressing device 10 represented on the figure 2 has a single calibrated leak orifice 28; but additional calibrated leak holes may have been provided.
  • the figure 2bis presents another embodiment of a pressing device 10 for exerting a holding force according to the invention.
  • the pressing device 10 is associated with a pressure source 33 consisting of a reservoir 34, comprising a sealed membrane confining the fluid in the reservoir 34 of the source.
  • An opening 36 of the source makes it possible to introduce a gas, making it possible to pressurize the fluid contained in the tank 34.
  • the calibrated leakage orifice is integrated with the check valve 37. It comprises a ball 38 positioned in a bore of the chamber communicating towards the source of pressure 33. A spring 39 is positioned in the bore, between the ball 38 and a wall of the pressure source.
  • the pressing device 10 can also form a mechanical stop for the transmission device 1.
  • This stop is exerted for example when the end of the piston liner 23 or the central portion 24 of it comes into contact with the bottom of the chamber 21.
  • This mechanical stop is however not intended to be solicited in normal operation of the engine, but may be a safety means to prevent disengagement of the mobile components of the device transmission 1 in case of anomalies such as a failure of the hydraulic system of the engine, and in addition to the spring when it is present.
  • FIG 3 is a graphical representation of the evolution of certain parameters of a 4-stroke engine with variable volumetric ratio during a motor cycle, ie during a rotation of 720 ° of the crankshaft.
  • the engine is equipped with a hydraulic cylinder exerting a static force on the transmission device of this engine.
  • the figure 3a presents the evolution of the pressure in the cylinder. There is a steep peak of pressure corresponding to the explosion of the combustion mixture in the cylinder.
  • the figure 3b presents the displacement of the transmission device during the engine cycle; and the figure 3c represents the speed of the transmission device during the engine cycle.
  • These figures show the slow mode of movement, exhibiting displacements of small amplitudes (of the order of 0.1 mm) and of low speed during most of the engine cycle.
  • the figure 3d represents the pressure applied by the hydraulic cylinder on the transmission device. It is noted that it has a static level of about 6kN.
  • the figure 4 is a graphical representation of the evolution of the parameters of a variable volumetric ratio engine, comprising the pressing device 10 of the invention, thus exerting a holding force adjusted to the instantaneous speed of transverse displacement of the transmission device.
  • the pressing device 10 is made by an independent capsule, comprising a piston operating in a chamber filled with a fluid and having at least one calibrated leakage orifice, an external pressure source of 30 bar is connected to the chamber, and a non-return valve arranged between the source and the chamber.
  • figure 4a represents the evolution of the pressure in the cylinder, similar to what has been shown in figure 3a in the solution of the state of the art.
  • the Figures 4b and 4c respectively show the displacement and the speed of the transmission device 10 during the engine cycle.
  • the slow motion mode exhibits displacements of amplitudes similar to those represented on the figure 3b , of the order of 0.1mm. Note, however, that during the fast mode of travel, the displacement of the transmission device 1, remains less than 0.4 mm which prevents its abutment with the motor unit 100.
  • pressing device 10 for the purposes of the complete description of the invention, it may in some cases be preferred, without departing from the scope of the invention, to use other forms of pressing device providing the same functions as those described. It may thus be for example a device comprising shock absorption means based on viscous or highly viscous polymer as is disclosed in US5495923 ; or including electromagnetic shock absorbing means as disclosed in US7537097

Description

DOMAINE DE L'INVENTIONFIELD OF THE INVENTION

L'invention concerne un dispositif de compensation des jeux de fonctionnement d'un moteur, et notamment d'un moteur à rapport volumétrique variable.The invention relates to a device for compensating the operating clearances of an engine, and in particular a variable volumetric ratio engine.

ARRIERE PLAN TECHNOLOGIQUE DE L'INVENTIONBACKGROUND OF THE INVENTION

Un dispositif de transmission de moteur comprend un ensemble de composants mobiles assurant ou entrant en jeux lors de la transmission du mouvement de translation d'un piston de combustion dans un cylindre à un mouvement de rotation d'un vilebrequin.An engine transmission device comprises a set of moving components providing or coming into play when transmitting the translational movement of a combustion piston in a cylinder to a rotational movement of a crankshaft.

On connaît de l'état de la technique des moteurs comportant un dispositif de transmission susceptible de se déplacer transversalement, c'est à dire dans une direction perpendiculaire à l'axe de translation du piston de combustion, dans un bloc-moteur. Ce déplacement trouve son origine dans les jeux de fonctionnement existant entre les composants mobiles du dispositif de transmission. Ces jeux de fonctionnement sont notamment affectés par les tolérances de fabrication et d'assemblage des composants mobiles, leurs usures, leur déformation en charge, et par la dilatation différentielle des pièces du moteur soumis à des températures différentes ou formées de matériaux présentant des coefficients de dilatation différents.Known from the state of the art engines having a transmission device capable of moving transversely, that is to say in a direction perpendicular to the axis of translation of the combustion piston, in an engine block. This displacement has its origin in the operating clearances existing between the mobile components of the transmission device. These operating clearances are notably affected by the manufacturing and assembly tolerances of the moving components, their wear, their deformation under load, and by the differential expansion of the parts of the engine subjected to different temperatures or formed of materials having different dilation.

Les jeux de fonctionnement doivent être parfaitement contrôlés. Trop grands, ils conduisent à une émission acoustique excessive du moteur lors de son fonctionnement, à une dégradation accélérée de ses composants, voire à sa destruction par exemple par désengrenage des composants mobiles. Trop petits, nuls ou négatifs, ils conduisent à des frottements excessifs entre les composants mobiles et donc à un rendement moteur dégradé, à son blocage ou même à sa destruction.The operating games must be perfectly controlled. Too large, they lead to excessive acoustic emission of the engine during its operation, accelerated degradation of its components, or even its destruction for example by de-gearing components mobile. Too small, zero or negative, they lead to excessive friction between the moving components and therefore to a degraded engine performance, its blockage or even its destruction.

Les documents US2010/206270 , EP1740810 et EP1979591 divulguent des dispositifs de réglage du jeu de fonctionnement existant entre les composants mobiles d'un dispositif de transmission, ces dispositifs comprenant un ressort ou un vérin hydraulique, solidaire du bloc-moteur, et exerçant un effort transversal de maintien du dispositif de transmission pour le maintenir en contact avec une paroi opposée du bloc-moteur.The documents US2010 / 206270 , EP1740810 and EP1979591 disclose devices for adjusting the operating clearance existing between the moving components of a transmission device, these devices comprising a spring or a hydraulic cylinder, integral with the engine block, and exerting a transverse force for holding the transmission device for the transmission device. keep in contact with an opposite wall of the engine block.

Ces documents prévoient l'application d'un effort statique sur le dispositif de transmission. Par effort statique, on entend un effort constant au cours d'un cycle moteur. L'effort statique est calibré pour s'opposer aux efforts maximums qui s'appliquent au dispositif de transmission, notamment pour les conditions de fonctionnement du moteur (régime, charge) engendrant les plus grands efforts. L'effort statique assure le contact permanent des composants mobiles de ce dispositif. Il est donc relativement important.These documents provide for the application of a static force on the transmission device. By static effort is meant a constant effort during a motor cycle. The static force is calibrated to oppose the maximum forces that apply to the transmission device, especially for the engine operating conditions (regime, load) causing the greatest effort. The static force ensures the permanent contact of the moving components of this device. It is therefore relatively important.

On note que ces documents prévoient un mode de réalisation permettant de contrôler l'effort exercé, par exemple par un vérin hydraulique, suivant les conditions de fonctionnement du moteur. Mais, dans ce mode de réalisation, lorsque le moteur fonctionne à charge et en régime stabilisé, l'effort exercé par le vérin hydraulique n'est pas modifié.Note that these documents provide an embodiment for controlling the force exerted, for example by a hydraulic cylinder, depending on the operating conditions of the engine. But, in this embodiment, when the engine operates under load and steady state, the force exerted by the hydraulic cylinder is not changed.

Cet effort relativement important et permanent induit au sein du dispositif de transmission des frottements qui affectent le rendement du moteur, et impose le dimensionnement adéquat des pièces de transmission, du carter, ainsi que de la source d'alimentation hydraulique.This relatively large and permanent force induces within the transmission device friction which affects the efficiency of the engine, and imposes adequate sizing of the transmission parts, the housing, and the hydraulic power source.

Il est donc parfois choisi de calibrer l'effort de maintien statique à un niveau inférieur aux efforts maximums qui s'appliquent au dispositif de transmission, mais à un niveau néanmoins suffisant pour couvrir une partie de la plage de fonctionnement moteur. Cette solution n'est toutefois pas satisfaisante car elle nécessite d'avoir recours à une butée mécanique pour limiter les jeux de fonctionnement dès que le déplacement devient excessif.It is therefore sometimes chosen to calibrate the static holding force at a level below the maximum forces that apply to the transmission device, but at a level sufficient to cover a portion of the engine operating range. This solution is however not satisfactory because it requires the use of a mechanical stop to limit the operating clearance as soon as the displacement becomes excessive.

Cette butée nécessite au montage un réglage fin et spécifique à chaque sous-ensemble associé à un cylindre du moteur. Cette opération n'est particulièrement pas souhaitable sur le plan industriel pour des raisons de coûts.This abutment requires assembly fine adjustment and specific to each subassembly associated with a cylinder of the engine. This operation is not particularly desirable at the industrial level for reasons of cost.

La position de la butée réglée présente de plus l'inconvénient d'être fixe, et de ne compenser ni les phénomènes liés aux dilatations différentielles entre le carter et les éléments de transmission, ni les décalages liés par exemple aux usures de pièces.The position of the adjusted stop has the further disadvantage of being fixed, and not to compensate for the phenomena related to differential expansion between the housing and the transmission elements, nor the offsets related for example to wear parts.

Lorsque cette dernière est sollicitée en fonctionnement, les chocs sont directement transmis au carter moteur ce qui induit un surdimensionnement et une usure accélérée des pièces impactées, et une augmentation du niveau acoustique.When the latter is stressed in operation, the shocks are directly transmitted to the crankcase which induces oversizing and accelerated wear of the impacted parts, and an increase in sound level.

Le besoin de calibration de l'effort de maintien est particulièrement marqué pour un moteur à rapport volumétrique variable, tel que décrit dans les documents cités de l'état de la technique, et selon lesquels un effort statique de maintien est appliqué sur un côté d'une crémaillère de commande dont le déplacement longitudinal assure le contrôle du rapport volumétrique. En effet, il est particulièrement important dans ce cas de limiter la valeur statique de l'effort de maintien afin de ne pas bloquer ou limiter les facultés de déplacement de la crémaillère de commande, notamment par glissement contre la paroi du bloc moteur.The need for calibration of the holding force is particularly marked for a variable volumetric ratio motor, as described in the cited documents of the state of the art, and according to which a static holding force is applied to a side of a control rack whose longitudinal movement ensures the control of the volumetric ratio. Indeed, it is particularly important in this case to limit the static value of the holding force so as not to block or limit the movement of the control rack, in particular by sliding against the wall of the engine block.

OBJET DE L'INVENTIONOBJECT OF THE INVENTION

Un but de l'invention est de proposer un dispositif de compensation des jeux de fonctionnement d'un moteur obviant aux inconvénients précités.An object of the invention is to provide a device for compensating the operating clearances of a motor obviating the aforementioned drawbacks.

BREVE DESCRIPTION DE L'INVENTIONBRIEF DESCRIPTION OF THE INVENTION

En vue de la réalisation de ce but, l'objet de l'invention propose un dispositif de compensation des jeux de fonctionnement d'un moteur selon les caractéristiques de la revendication 1.In order to achieve this goal, the object of the invention proposes a device for compensating the operating clearances of an engine according to the features of claim 1.

Ainsi, le dispositif de compensation autorise les mouvements lents du dispositif de transmission en appliquant un effort de maintien modéré pendant ces mouvements. Il s'oppose au mouvement rapide du dispositif de transmission, correspondant principalement au pic d'effort lié à la combustion du mélange dans le cylindre, en appliquant un effort de maintien élevé pendant ces mouvements.Thus, the compensation device allows the slow movements of the transmission device by applying a moderate holding force during these movements. It is opposed to the rapid movement of the transmission device, corresponding mainly to the peak of effort related to the combustion of the mixture in the cylinder, by applying a high holding force during these movements.

Le dispositif de compensation de l'invention permet donc de contrôler les jeux de fonctionnement existants entre les organes mobiles du dispositif de transmission en appliquant un effort moyen de maintien modéré au cours du cycle du moteur, et sans exercer une buté mécanique.The compensation device of the invention thus makes it possible to control the operating clearances existing between the mobile members of the transmission device by applying a moderate average holding force during the engine cycle, and without exerting a mechanical stop.

Selon d'autres caractéristiques avantageuses et non limitatives de l'invention, prises seules ou en combinaison :

  • le dispositif de transmission comprend :
    • un dispositif de guidage à roulement prenant appui sur une paroi du bloc moteur ;
    • un organe de transmission, solidaire d'un piston de combustion, coopérant d'une part avec le dispositif de guidage à roulement et d'autre part à avec un premier côté d'une roue dentée ;
    • une crémaillère de commande coopérant avec un second côté de la roue dentée, et apte à se déplacer longitudinalement sur une paroi opposée du bloc moteur ;
    • une bielle coopérant avec la route dentée et relié à un vilebrequin du moteur.
  • le dispositif presseur est solidaire du bloc moteur.
  • le dispositif presseur exerce la pression de maintien sur la crémaillère de commande.
  • l'effort de maintien présente une valeur seuil.
  • le dispositif presseur comprend un ressort.
  • l'orifice de fuite calibré est fluidiquement connecté à la source de pression.
  • la chambre, le cylindre et le clapet antiretour sont intégrés dans une capsule autonome.
  • l'orifice de fuite calibré débouche sur la surface exposée du piston.
  • le dispositif presseur est fluidiquement connecté à une centrale hydraulique.
According to other advantageous and nonlimiting features of the invention, taken alone or in combination:
  • the transmission device comprises:
    • a rolling guide device bearing on a wall of the engine block;
    • a transmission member, integral with a combustion piston, cooperating on the one hand with the rolling guide device and on the other hand with a first side of a toothed wheel;
    • a control rack cooperating with a second side of the gear wheel, and adapted to move longitudinally on an opposite wall of the engine block;
    • a connecting rod cooperating with the toothed road and connected to a crankshaft of the engine.
  • the pressure device is integral with the engine block.
  • the pressing device exerts the holding pressure on the control rack.
  • the holding force has a threshold value.
  • the pressing device comprises a spring.
  • the calibrated leak orifice is fluidly connected to the pressure source.
  • the chamber, the cylinder and the non-return valve are integrated in a self-contained capsule.
  • the calibrated leak orifice opens onto the exposed surface of the piston.
  • the pressure device is fluidly connected to a hydraulic unit.

BREVE DESCRIPTION DES DESSINSBRIEF DESCRIPTION OF THE DRAWINGS

L'invention sera mieux comprise à la lumière de la description qui suit des modes de réalisation particuliers et non limitatifs de l'invention en référence aux figures ci-jointes parmi lesquelles :

  • la figure 1 représente une coupe d'ensemble schématique d'une configuration particulière du dispositif de compensation;
  • la figure 2 représente une vue en coupe d'une configuration particulière du dispositif presseur;
  • la figure 3 est une représentation graphique de l'évolution de certains paramètres au cours d'un cycle moteur d'un moteur à rapport volumétrique variable selon l'état de la technique.
  • la figure 4 est une représentation graphique de l'évolution de certains paramètres au cours d'un cycle moteur d'un moteur à rapport volumétrique variable selon l'invention.
The invention will be better understood in the light of the following description of the particular and nonlimiting embodiments of the invention with reference to the attached figures among which:
  • the figure 1 represents a schematic overall section of a particular configuration of the compensation device;
  • the figure 2 represents a sectional view of a particular configuration of the pressing device;
  • the figure 3 is a graphical representation of the evolution of certain parameters during an engine cycle of a variable volumetric ratio engine according to the state of the art.
  • the figure 4 is a graphical representation of the evolution of certain parameters during a motor cycle of a variable volumetric ratio motor according to the invention.

DESCRIPTION DETAILLEE DE L'INVENTIONDETAILED DESCRIPTION OF THE INVENTION

La figure 1 présente une coupe d'ensemble, et schématique, du dispositif de compensation des jeux fonctionnels d'un moteur selon l'invention et mis en oeuvre dans le cas d'un moteur à rapport volumétrique variable.The figure 1 presents an overall cross section, and schematically, of the device for compensating the functional clearances of an engine according to the invention and used in the case of a variable volumetric ratio engine.

Sur cette figure 1, un bloc moteur 100 comprend au moins un cylindre 110 dans lequel se déplace en translation un piston de combustion 2 entraînant la rotation d'un vilebrequin 9 par l'intermédiaire d'un dispositif de transmission 1.On this figure 1 , an engine block 100 comprises at least one cylinder 110 in which is displaced in translation a combustion piston 2 causing the rotation of a crankshaft 9 by means of a transmission device 1.

Le dispositif de transmission 1 comprend un organe de transmission 3 solidaire du piston de combustion 2 et coopérant d'une part avec un dispositif de guidage à roulement 4 prenant appui sur une paroi du bloc moteur 100 et d'autre part avec un premier côté d'une roue dentée 5.The transmission device 1 comprises a transmission member 3 secured to the combustion piston 2 and cooperating on the one hand with a rolling guide device 4 resting on a wall of the engine block 100 and on the other hand with a first side d a toothed wheel 5.

L'organe de transmission 3 est pourvu sur l'une de ses faces d'une première crémaillère de forte dimension dont les dents coopèrent avec celle de la roue dentée 5. L'organe de transmission 3 est également pourvu, à l'opposé de cette première crémaillère, d'une autre crémaillère dont les dents de faibles dimensions coopèrent avec celles du rouleau 40 du dispositif de guidage à roulement 4, solidaire du bloc-moteur 100.The transmission member 3 is provided on one of its faces with a first rack of large dimension whose teeth cooperate with that of the toothed wheel 5. The transmission member 3 is also provided, in contrast to this first rack, another rack whose teeth of small dimensions cooperate with those of the roller 40 of the rolling guide device 4, integral with the engine block 100.

La roue dentée 5 coopère avec une bielle 6 reliée au vilebrequin 9 afin de réaliser la transmission du mouvement.The toothed wheel 5 cooperates with a connecting rod 6 connected to the crankshaft 9 in order to carry out the transmission of the movement.

La roue dentée 5 coopère, sur un second côté à l'opposé de l'organe de transmission 3, avec une crémaillère de commande 7 apte à se déplacer longitudinalement le long d'une paroi opposée du bloc-moteur 100 et pilotée par un dispositif de contrôle 12 comportant un vérin de commande, dont le piston de vérin est guidé dans un cylindre de vérin 112 du bloc moteur 100.The toothed wheel 5 cooperates, on a second side opposite the transmission member 3, with a control rack 7 adapted to move longitudinally along an opposite wall of the engine block 100 and driven by a device control unit 12 comprising a control cylinder, whose piston cylinder is guided in a cylinder cylinder 112 of the engine block 100.

La crémaillère de commande 7 comporte des dents qui coopèrent avec celles de la roue dentée 5 et peut présenter une piste de roulement qui coopère avec une piste de roulement de la roue dentée 5. La crémaillère de commande 7 comporte également sur son côté opposé une surface d'appui 76 sur laquelle s'exerce, dans la configuration particulière représentée sur la figure 1, l'effort de maintien d'un dispositif presseur 10 solidaire du bloc-moteur 100.The control rack 7 has teeth that cooperate with those of the toothed wheel 5 and may have a raceway which cooperates with a raceway of the toothed wheel 5. The control rack 7 also has on its opposite side a surface support 76 on which is exerted, in the particular configuration represented on the figure 1 , the force of maintaining a pressure device 10 integral with the engine block 100.

Comme cela sera exposé dans le détail par la suite, le dispositif presseur (10) est configuré pour ajuster l'effort de maintien à la vitesse instantanée de déplacement transversal du dispositif de transmission (1) dans le bloc-moteur (100.)As will be explained in detail below, the pressing device (10) is configured to adjust the holding force at the instantaneous transverse displacement speed of the transmission device (1) in the engine block (100).

La crémaillère de commande 7 et le dispositif de commande 12 coopèrent avec le dispositif presseur 10 de manière à autoriser au minimum une translation de direction verticale de la crémaillère de commande.The control rack 7 and the control device 12 cooperate with the pressing device 10 so as to allow at least a vertical directional translation of the control rack.

Dans le mode particulier de mise en oeuvre de l'invention représenté sur la figure 1, le dispositif presseur 10 est solidaire du bloc-moteur 100 et exerce la pression de maintien sur le dispositif de transmission 1 dont les principaux composants viennent d'être énumérés.In the particular embodiment of the invention shown in the figure 1 , the pressure device 10 is integral with the engine block 100 and exerts the holding pressure on the transmission device 1 whose main components have just been listed.

Dans une alternative à ce mode de mise en oeuvre, le dispositif presseur 10 peut être incorporé au dispositif de transmission 1, comme par exemple à la crémaillère de commande 7 ou au dispositif de guidage à roulement 4, et exercer un effort sur une des parois du bloc moteur 100.In an alternative to this embodiment, the pressing device 10 can be incorporated in the transmission device 1, for example in the control rack 7 or the rolling guide device 4, and exert a force on one of the walls. of the engine block 100.

Selon l'invention, l'effort de maintien est ajustable à la vitesse instantanée de déplacement transversal du dispositif de transmission 1 dans le bloc moteur 100.According to the invention, the holding force is adjustable at the instantaneous speed of transverse displacement of the transmission device 1 in the engine block 100.

Au cours du cycle moteur, différents phénomènes induisent des déplacements transversaux du dispositif de transmission 1 selon deux modes :

  • un premier mode de déplacement lent, lié aux écarts existant entre la géométries ou la position réelle des pièces et leur géométrie idéale, ces écarts pouvant être liés à des déformation sous effort, aux tolérances de fabrication, aux phénomènes de dilatations différentielles et d'usures. Ces mouvements ont une période égale à une révolution du vilebrequin 9.
  • Un second mode de déplacement rapide, résultant principalement du pic d'effort correspondant à la combustion du mélange dans le cylindre, et résultant également de l'inertie des organes mobiles du dispositif de transmission 1 en mouvement.
During the motor cycle, various phenomena induce transverse displacements of the transmission device 1 according to two modes:
  • a first mode of slow displacement, related to the gaps between the geometries or the actual position of the parts and their ideal geometry, these deviations being able to be linked to deformation under stress, to manufacturing tolerances, differential expansion phenomena and wear. These movements have a period equal to a revolution of the crankshaft 9.
  • A second mode of rapid displacement, resulting mainly from the peak force corresponding to the combustion of the mixture in the cylinder, and also resulting from the inertia of the moving members of the transmission device 1 in motion.

En ajustant l'effort de maintien à la vitesse de déplacement du dispositif de transmission, l'invention permet donc de tolérer les déplacements lents du premier mode qui sont nécessaires au bon fonctionnement du moteur ; et de contrer efficacement les déplacements rapides du second mode qui pourraient aller à l'encontre du bon fonctionnement du moteur ou en dégrader les performances.By adjusting the holding force at the speed of displacement of the transmission device, the invention thus makes it possible to tolerate the slow displacements of the first mode which are necessary for the proper functioning of the engine; and effectively counter the rapid movements of the second mode that could go against the proper functioning of the engine or degrade performance.

L'effort de maintien n'est donc pas statique comme c'est le cas dans les solutions connues de l'état de la technique. Il ne dépend pas non plus spécifiquement de la position du dispositif de transmission 1 dans le bloc moteur 100.The holding force is therefore not static as is the case in known solutions of the state of the art. Nor does it specifically depend on the position of the transmission device 1 in the engine block 100.

Au cours d'un cycle moteur, le mode lent de déplacement est prépondérant, si bien que l'effort moyen appliqué au dispositif de transmission au cours d'un cycle moteur est relativement peu important ; et bien moins important que celui appliqué dans les solutions de l'état de la technique. En conséquence, les efforts moyens de frottements entre les composants mobiles sont réduits, le rendement moteur est amélioré, et le dimensionnement des composants du dispositif de transmission 1, du bloc moteur 100, et de la source d'alimentation hydraulique peuvent être réduit.During a motor cycle, the slow mode of displacement is preponderant, so that the average force applied to the transmission device during a motor cycle is relatively small; and much less important than that applied in the solutions of the state of the art. As a result, the average friction forces between the moving components are reduced, the motor efficiency is improved, and the dimensioning of the components of the transmission device 1, the motor unit 100, and the hydraulic power source can be reduced.

D'autre part, en dehors des périodes de fonctionnement en mode rapide, qui ne sont pas prépondérantes au cours d'un cycle moteur, les frottements résultants de l'effort de maintien exercé par le dispositif presseur 10 sur la crémaillère de commande 7 sont faibles. Les déplacements de la crémaillère de commande ne sont pas limités.On the other hand, outside periods of fast mode operation, which are not predominant during a motor cycle, the friction resulting from the holding force exerted by the pressing device 10 on the control rack 7 are weak. The movements of the control rack are not limited.

Un effort de maintien ajusté signifie que l'effort exercé est variable suivant l'amplitude et/ou la direction de la vitesse instantanée du dispositif de transmission 1.An adjusted holding force means that the force exerted is variable according to the amplitude and / or the direction of the instantaneous speed of the transmission device 1.

Lorsque le dispositif de transmission 1 présente une vitesse transversale instantanée dirigée en direction du dispositif presseur 10, qui peut par exemple résulter des efforts appliqués à ce dispositif de transmission 1 suite à la combustion du mélange dans le cylindre, l'effort de maintien présentera une première valeur.When the transmission device 1 has an instantaneous transverse speed directed towards the pressing device 10, which may for example result from the forces applied to this transmission device 1 following the combustion of the mixture in the cylinder, the holding force will be first value.

En l'absence de déplacement ou pour des vitesses instantanées de déplacement faible, l'effort de maintien présentera une seconde valeur, inférieure à la première.In the absence of displacement or for instantaneous speeds of low displacement, the holding force will present a second value, less than the first.

De manière préférée, la seconde valeur est supérieure à une valeur d'effort seuil, non nulle, qu'en toutes circonstances le dispositif presseur exerce sur le dispositif de transmission 1. La valeur seuil de l'effort de maintien assure la cohésion et la coopération des composants mobiles du dispositif de transmission 1 et son appui sur la paroi opposée du bloc moteur 100 en l'absence de pic d'effort exercé sur le dispositif de transmission 1.Preferably, the second value is greater than a threshold force value, non-zero, that in all circumstances the pressing device exerts on the transmission device 1. The threshold value of the holding force ensures the cohesion and the cooperation of the mobile components of the transmission device 1 and its support on the opposite wall of the engine block 100 in the absence of peak effort exerted on the transmission device 1.

Par « cohésion et coopération » on signifie que les composants mobiles du dispositif de transmission 10 sont en contacts ou présentent un jeu contrôlé n'affectant pas le fonctionnement du moteur.By "cohesion and cooperation" is meant that the moving components of the transmission device 10 are in contact or have a controlled clearance that does not affect the operation of the engine.

L'effort de maintien peut évoluer de manière croissante et continue avec la vitesse instantanée transversale du dispositif de transmission 1. Il peut également évoluer de manière croissante et discontinue, par exemple par palier, avec cette vitesse.The holding force can evolve continuously and continuously with the instantaneous transverse speed of the transmission device 1. It can also evolve from increasing and discontinuous manner, for example by step, with this speed.

La première valeur de l'effort de maintien est déterminée pour assurer la cohésion et la coopération des composants mobiles du dispositif de transmission 1 lors des pics d'efforts. Cette première valeur peut être variable avec la vitesse de déplacement. Elle peut être également ajustée suivant la charge ou le régime du fonctionnement du moteur.The first value of the holding force is determined to ensure the cohesion and cooperation of the mobile components of the transmission device 1 during peaks of effort. This first value can be variable with the speed of displacement. It can also be adjusted according to the load or the operating speed of the engine.

La figure 2 représente un mode de réalisation particulier d'un dispositif presseur 10 permettant d'exercer un effort de maintien conforme à l'invention.The figure 2 represents a particular embodiment of a pressing device 10 for exerting a holding force according to the invention.

Le dispositif presseur 10 peut être constitué d'une chambre 21, par exemple cylindrique, engagée dans un orifice aménagé dans le bloc moteur 100. Le dispositif presseur 10 est assemblé dans le bloc moteur par des moyens d'attache 22, comprenant par exemple une bride solidaire du dispositif et des boulons vissés dans le bloc moteur 100.The pressing device 10 may consist of a chamber 21, for example cylindrical, engaged in an orifice arranged in the engine block 100. The pressing device 10 is assembled in the engine block by attachment means 22, comprising for example a flange secured to the device and bolts screwed into the engine block 100.

La chambre 21 est munie d'un piston 23, confinant le fluide dans la chambre 21, et pouvant évoluer en translation dans cette chambre. L'effort de maintien est exercé sur le dispositif de transmission 1 par l'intermédiaire de la tête du piston 23. Des moyens assurant 27 l'étanchéité sont disposés entre le cylindre et le piston 23.The chamber 21 is provided with a piston 23, confining the fluid in the chamber 21, and able to evolve in translation in this chamber. The holding force is exerted on the transmission device 1 via the piston head 23. Sealing means are arranged between the cylinder and the piston 23.

Le piston 23 comprend une partie centrale 24 saillante, dégageant un espace annulaire avec la surface interne de la chemise du piston 23, permettant d'y loger un ressort 25, comme cela sera exposé dans le détail par la suite.The piston 23 comprises a projecting central portion 24, releasing an annular space with the inner surface of the piston liner 23, for accommodating a spring 25, as will be discussed in detail later.

La tête du piston 23 présente une surface exposée 20 apte à coopérer avec une surface d'appui 76 de la crémaillère de commande 7.The piston head 23 has an exposed surface 20 adapted to cooperate with a bearing surface 76 of the control rack 7.

La chambre 21 est emplie d'un fluide tel que de l'huile, de l'eau ou un gaz. Il peut s'agir par exemple de l'huile de lubrification du moteur. De manière préférée, il s'agit d'un fluide hydraulique.The chamber 21 is filled with a fluid such as oil, water or a gas. This may for example be the engine lubricating oil. Preferably, it is a hydraulic fluid.

La chambre 21 est également munie d'au moins un orifice de fuite calibré 28. Celui-ci autorise un écoulement du fluide en dehors de la chambre en particulier lorsqu'une pression est appliquée au fluide par l'intermédiaire du piston.The chamber 21 is also provided with at least one calibrated leak orifice 28. This allows a flow of the fluid outside the chamber, in particular when a pressure is applied to the fluid via the piston.

La chambre 21 est alimentée en fluide par une source de pression tel qu'un accumulateur (non représenté sur la figure 2) connectée fluidiquement à la chambre 21 par exemple par des moyens d'alimentation tels que un conduit et/ou un canal 30 aménagé dans la chambre 21 et débouchant dans une zone d'alimentation 31 de la chambre 21.The chamber 21 is supplied with fluid by a pressure source such as an accumulator (not shown in FIG. figure 2 ) connected fluidly to the chamber 21 for example by supply means such as a conduit and / or a channel 30 arranged in the chamber 21 and opening into a supply zone 31 of the chamber 21.

Un clapet antiretour 32 disposé entre la chambre et la source de pression assure le maintien d'une pression minimale permanente du fluide au sein de la chambre, identique à la pression présente dans la source, et interrompt toute alimentation lorsque, sous l'effet d'un effort exercé sur le piston 23, la pression du fluide dans la chambre excède la pression du fluide dans la source.A check valve 32 arranged between the chamber and the source of pressure ensures the maintenance of a minimum permanent pressure of the fluid within the chamber, identical to the pressure present in the source, and interrupts any power supply when, under the effect of a force exerted on the piston 23, the pressure of the fluid in the chamber exceeds the pressure of the fluid in the source.

Comme cela est bien connu en soit, le clapet antiretour 32 peut comprendre une bille 33 positionnée dans un alésage de la chambre 21 et venant obturer un canal d'alimentation provenant de la zone d'alimentation 31 lorsque la pression du fluide de la chambre l'amène en butée du canal.As is well known in itself, the check valve 32 may comprise a ball 33 positioned in a bore of the chamber 21 and closing a supply channel from the feed zone 31 when the fluid pressure of the chamber 1 brings to the stop of the canal.

L'agencement combiné du piston 23 évoluant dans une chambre 21 emplie d'un fluide et présentant au moins un orifice de fuite calibré 28, de la source de pression connectée à la chambre 21 et du clapet anti retour 32 entre la source et la chambre 21 résulte en un dispositif apte à fournir un effort ajusté à la vitesse de déplacement du piston 23. Pour de faibles vitesses, le fluide contenu dans la chambre 21 s'écoule à travers l'orifice de fuite calibré sans générer de surpression conséquente dans la chambre; et le piston 23 exerce un effort de résistance faible sensiblement équivalent à sa valeur seuil de précharge. Pour une vitesse élevée, le fluide contenu dans la chambre ne peut s'écouler suffisamment et monte en pression, le piston 23 exerce alors un effort de résistance élevé très supérieur à la valeur seuil de précharge.The combined arrangement of the piston 23 evolving in a chamber 21 filled with a fluid and having at least one calibrated leakage orifice 28, the pressure source connected to the chamber 21 and the nonreturn valve 32 between the source and the chamber 21 results in a device adapted to provide a force adjusted to the speed of movement of the piston 23. For low speeds, the fluid contained in the chamber 21 flows through the calibrated leak orifice without generating significant overpressure in the chamber; and the piston 23 exerts a low resistance force substantially equivalent to its precharging threshold value. For a high speed, the fluid contained in the chamber can not flow sufficiently and rises in pressure, the piston 23 then exerts a high resistance force much greater than the precharging threshold value.

La relation liant l'effort à la vitesse peut-être calibrée en ajustant par exemple la dimension de l'orifice de fuite calibré 28 de la chambre 21.The relationship linking the force to the speed can be calibrated by adjusting for example the dimension of the calibrated leakage orifice 28 of the chamber 21.

De manière avantageuse, la chambre 21 est également munie d'un ressort 25, par exemple hélicoïdal comme représenté sur la figure 2. Il peut s'agir également d'un ressort du type « Belleville ». Le ressort 25 peut être disposé dans l'espace annulaire formé entre la partie centrale 24 et la surface interne de la chemise du piston 23, comme cela est représenté sur la figure 2, mais il peut également être disposé en dehors de la chambre.Advantageously, the chamber 21 is also provided with a spring 25, for example helical as shown in FIG. figure 2 . It can also be a "Belleville" style spring. The spring 25 may be disposed in the annular space formed between the central portion 24 and the inner surface of the piston liner 23, as shown in FIG. figure 2 but it can also be arranged outside the room.

Quel que soit son emplacement choisi, la pression exercée par la partie hydraulique du dispositif presseur 10 vient en complément de la pression exercée par le ressort 25. Cette partie hydraulique peut alors avoir un dimensionnement plus réduit et notamment présenter une pression statique de fluide réduite. On pourra par exemple choisir le ressort 25 pour qu'il contribue entre 20% et 40% au niveau d'effort seuil exercé par le dispositif presseur 10. Préférentiellement cette contribution sera choisie à 33%. La présence du ressort 25 assure également une meilleure réactivité du dispositif presseur 10 lors des phases de réapprovisionnement en huile au cours desquels le piston 23 doit néanmoins rapidement exercer une pression sur la crémaillère de commande 7. Finalement, la présence du ressort 25 permet au moteur de fonctionner dans un mode dégradé en cas de panne de la partie hydraulique du dispositif presseur 10 en garantissant la fonctionnalité du dispositif presseur 10 sur une plage de fonctionnement moteur limitée.Whatever its chosen location, the pressure exerted by the hydraulic portion of the pressure device 10 complements the pressure exerted by the spring 25. This hydraulic portion may then have a smaller dimension and in particular have a reduced fluid static pressure. For example, the spring 25 may be chosen so that it contributes between 20% and 40% to the level of threshold force exerted by the pressing device 10. Preferably, this contribution will be chosen at 33%. The presence of the spring 25 also ensures a better reactivity of the pressing device 10 during the oil replenishment phases during which the piston 23 must nevertheless quickly exert pressure on the control rack 7. Finally, the presence of the spring 25 allows the engine to operate in a degraded mode in case of failure of the hydraulic part of the pressing device 10 by guaranteeing the functionality of the pressing device 10 over a limited engine operating range.

Le dispositif presseur 10 peut comprendre un l'orifice de fuite calibré 28 fluidiquement connecté à la source de pression. Cette connexion peut être réalisée par des conduits si la source de pression est déportée, ou l'orifice de fuite calibré 28 peut directement alimenter un réservoir de cette source de pression.The pressing device 10 may comprise a calibrated leakage orifice 28 fluidly connected to the pressure source. This connection can be made by conduits if the pressure source is offset, or the calibrated leakage orifice 28 can directly supply a reservoir of this pressure source.

La chambre 21, le piston 23 et le clapet antiretour 31 peuvent être avantageusement intégrés dans une capsule autonome formant alors un dispositif presseur 10 indépendant.The chamber 21, the piston 23 and the check valve 31 may advantageously be integrated in an independent capsule then forming an independent pressing device 10.

Dans le cas où la source de pression est déportée, celle-ci peut-être fluidiquement connectée à l'ensemble des dispositifs presseurs 10 du moteur dans le cadre d'une gestion hydraulique centralisée.In the case where the pressure source is remote, it may be fluidically connected to all the pressure devices 10 of the engine in the context of a centralized hydraulic management.

Lorsque le fluide de la chambre 21 est constitué par l'huile de lubrification du moteur, l'orifice de fuite calibré 28 peut être disposé dans le piston 23 lui-même et déboucher au niveau de la surface exposée 23, pour notamment lubrifier les surfaces de contact de la crémaillère de commandes 7 et du dispositif presseur 10.When the fluid of the chamber 21 is constituted by the lubricating oil of the engine, the calibrated leakage orifice 28 can be disposed in the piston 23 itself and open at the exposed surface 23, in particular to lubricate the surfaces. contact of the control rack 7 and the pressing device 10.

Une pompe de la centrale hydraulique peut être prévue pour ajuster la pression statique du fluide dans la source de pression, et par voie de conséquence la pression statique du fluide dans le dispositif presseur 10. Cet ajustement peut être déterminé suivant la charge et le régime de fonctionnement du moteur. À cet effet, la centrale hydraulique peut comprendre un calculateur, connecté à des capteurs permettant de mesurer entre autre le niveau de charge et le régime. Le calculateur détermine une pression statique cible et pilote la pompe pour amener la pression statique de l'accumulateur à la pression statique cible.A pump of the hydraulic unit can be provided for adjusting the static pressure of the fluid in the pressure source, and consequently the static pressure of the fluid in the pressing device 10. This adjustment can be determined according to the load and the operating speed. engine operation. For this purpose, the hydraulic unit may include a computer, connected to sensors to measure among others the level of load and the speed. The computer determines a target static pressure and drives the pump to bring the static pressure of the accumulator to the target static pressure.

La configuration particulière du dispositif presseur 10 représenté sur la figure 2 présente un unique orifice de fuite calibré 28 ; mais des orifices de fuites calibrés additionnels peuvent avoir été prévus.The particular configuration of the pressing device 10 represented on the figure 2 has a single calibrated leak orifice 28; but additional calibrated leak holes may have been provided.

La figure 2bis présente un autre mode de réalisation d'un dispositif presseur 10 permettant d'exercer un effort de maintien conforme à l'invention.The figure 2bis presents another embodiment of a pressing device 10 for exerting a holding force according to the invention.

On retrouve sur cette figure le piston 23, la chambre 21 et le ressort 25 du mode de réalisation précédent. Dans ce nouveau mode de réalisation, le dispositif presseur 10 est associé à une source de pression 33 constituée d'un réservoir 34, comportant une membrane étanche confinant le fluide dans le réservoir 34 de la source. Une ouverture 36 de la source permet d'introduire un gaz, permettant de mettre sous pression le fluide contenu dans le réservoir 34. On forme ainsi un dispositif presseur 10 intégré dans une capsule compacte, intégrant également la source.This figure shows the piston 23, the chamber 21 and the spring 25 of the previous embodiment. In this new embodiment, the pressing device 10 is associated with a pressure source 33 consisting of a reservoir 34, comprising a sealed membrane confining the fluid in the reservoir 34 of the source. An opening 36 of the source makes it possible to introduce a gas, making it possible to pressurize the fluid contained in the tank 34. This forms a pressure device 10 integrated in a compact capsule, also integrating the source.

Dans ce mode de réalisation, l'orifice de fuite calibré est intégré au clapet antiretour 37. Il comprend une bille 38 positionnée dans un alésage de la chambre communiquant vers la source de pression 33. Un ressort 39 est positionné dans l'alésage, entre la bille 38 et une paroi de la source de pression.In this embodiment, the calibrated leakage orifice is integrated with the check valve 37. It comprises a ball 38 positioned in a bore of the chamber communicating towards the source of pressure 33. A spring 39 is positioned in the bore, between the ball 38 and a wall of the pressure source.

Lorsque la pression du fluide dans la source excède la pression du fluide dans la chambre 21, la bille est repoussée vers le cylindre pour permettre le passage du fluide et l'équilibrage des pressions.When the pressure of the fluid in the source exceeds the pressure of the fluid in the chamber 21, the ball is pushed towards the cylinder to allow the passage of the fluid and the balancing of the pressures.

Lorsque la pression du fluide de la chambre 21 excède légèrement la pression du fluide de la source ; le ressort retient le déplacement de la bille et autorise la circulation du fluide vers la source, formant ainsi l'orifice de fuite calibré 29.When the fluid pressure of the chamber 21 slightly exceeds the fluid pressure of the source; the spring retains the displacement of the ball and allows the flow of fluid to the source, thus forming the calibrated leakage orifice 29.

Lorsque la pression du fluide de la chambre 21 excède fortement la pression du fluide de la source, le ressort est comprimé de telle sorte que la bille obture complétement l'orifice de fuite calibré 29.When the pressure of the fluid of the chamber 21 greatly exceeds the pressure of the fluid of the source, the spring is compressed so that the ball completely closes the calibrated leakage orifice 29.

Ainsi, il est possible de créer une discontinuité dans la relation liant la vitesse du piston à l'effort de maintien. Lorsque le piston présente une vitesse conduisant à l'obturation de l'orifice calibré, la pression exercée par le piston du dispositif de maintien 10 atteint sa valeur nominale.Thus, it is possible to create a discontinuity in the relationship between the speed of the piston and the holding force. When the piston has a speed leading to the closing of the calibrated orifice, the pressure exerted by the piston of the holding device 10 reaches its nominal value.

Quelque soit le mode de réalisation choisi du dispositif presseur 10, celui-ci peut également former une butée mécanique pour le dispositif de transmission 1. Cette butée est exercée par exemple lorsque l'extrémité de la chemise du piston 23 ou la partie centrale 24 de celui-ci entre en contact avec le fond de la chambre 21. Cette butée mécanique n'est toutefois pas prévue pour être sollicitée en fonctionnement normal du moteur, mais peut constituer un moyen de sécurité permettant d'éviter le désengrènement des composants mobiles du dispositif de transmission 1 en cas d'anomalies comme par exemple une panne du système hydraulique du moteur, et en complément du ressort lorsque celui-ci est présent.Whatever the chosen embodiment of the pressing device 10, it can also form a mechanical stop for the transmission device 1. This stop is exerted for example when the end of the piston liner 23 or the central portion 24 of it comes into contact with the bottom of the chamber 21. This mechanical stop is however not intended to be solicited in normal operation of the engine, but may be a safety means to prevent disengagement of the mobile components of the device transmission 1 in case of anomalies such as a failure of the hydraulic system of the engine, and in addition to the spring when it is present.

Les avantages de la présente invention sont illustrés en référence aux figures 3 et 4. La figure 3 est une représentation graphique de l'évolution de certains paramètres d'un moteur 4 temps à rapport volumétrique variable au cours d'un cycle moteur, c'est à dire au cours d'une rotation de 720° du vilebrequin. Le moteur est muni d'un vérin hydraulique exerçant un effort statique sur le dispositif de transmission de ce moteur.The advantages of the present invention are illustrated with reference to figures 3 and 4 . The figure 3 is a graphical representation of the evolution of certain parameters of a 4-stroke engine with variable volumetric ratio during a motor cycle, ie during a rotation of 720 ° of the crankshaft. The engine is equipped with a hydraulic cylinder exerting a static force on the transmission device of this engine.

La figure 3a présente l'évolution de la pression dans le cylindre. On note un pic abrupte de pression correspondant à l'explosion du mélange de combustion dans le cylindre.The figure 3a presents the evolution of the pressure in the cylinder. There is a steep peak of pressure corresponding to the explosion of the combustion mixture in the cylinder.

La figure 3b présente le déplacement du dispositif de transmission au cours du cycle moteur ; et la figure 3c représente la vitesse du dispositif de transmission au cours du cycle moteur. On observe bien sur ces figures le mode de déplacement lent, présentant des déplacements de faibles amplitudes (de l'ordre de 0,1mm) et de faible vitesse pendant la majeure partie du cycle moteur. On observe bien également le mode de déplacement rapide, présentant des déplacements de plus grandes amplitudes (jusque 0,4mm) et vitesse (excédant +/- 100mm/s), sensiblement compris entre la position angulaire de 360° et la position angulaire de 420° du vilebrequin, et correspondant au pic de pression dans le cylindre. On précise que pendant ce pic, le dispositif de transmission entre en butée mécanique avec la paroi du moteur, comme en témoigne l'écrêtement du déplacement à +0,4mm sur la figure 3b, ainsi que la variation de vitesse brutale qui est visible sur la figure 3c.The figure 3b presents the displacement of the transmission device during the engine cycle; and the figure 3c represents the speed of the transmission device during the engine cycle. These figures show the slow mode of movement, exhibiting displacements of small amplitudes (of the order of 0.1 mm) and of low speed during most of the engine cycle. We also observe the fast mode of movement, with displacements of greater amplitudes (up to 0.4mm) and speed (exceeding +/- 100mm / s), substantially between the angular position of 360 ° and the angular position of 420 Crankshaft, and corresponding to the pressure peak in the cylinder. It is specified that during this peak, the transmission device comes into mechanical abutment with the wall of the engine, as evidenced by the clipping of the displacement at + 0.4mm on the figure 3b , as well as the sudden speed variation that is visible on the figure 3c .

La figure 3d représente la pression appliquée par le vérin hydraulique sur le dispositif de transmission. On note qu'il présente un niveau statique d'environ 6kN.The figure 3d represents the pressure applied by the hydraulic cylinder on the transmission device. It is noted that it has a static level of about 6kN.

La figure 4 est une représentation graphique de l'évolution des paramètres d'un moteur à rapport volumétrique variable, comprenant le dispositif presseur 10 de l'invention, exerçant donc un effort de maintien ajusté à la vitesse instantanée de déplacement transversal du dispositif de transmission.The figure 4 is a graphical representation of the evolution of the parameters of a variable volumetric ratio engine, comprising the pressing device 10 of the invention, thus exerting a holding force adjusted to the instantaneous speed of transverse displacement of the transmission device.

Dans le cas particulier de la figure 4, le dispositif presseur 10 est réalisé par une capsule autonome, comprenant un piston évoluant dans une chambre emplie d'un fluide et présentant au moins un orifice de fuite calibré, une source externe de pression de 30 bars est connectée à la chambre, et un clapet antiretour disposé entre la source et la chambre.In the particular case of figure 4 , the pressing device 10 is made by an independent capsule, comprising a piston operating in a chamber filled with a fluid and having at least one calibrated leakage orifice, an external pressure source of 30 bar is connected to the chamber, and a non-return valve arranged between the source and the chamber.

La figure 4a représente l'évolution de la pression dans le cylindre, similairement à ce qui a été représenté en figure 3a dans la solution de l'état de la technique.The figure 4a represents the evolution of the pressure in the cylinder, similar to what has been shown in figure 3a in the solution of the state of the art.

Les figures 4b et 4c présentent respectivement le déplacement et la vitesse du dispositif de transmission 10 au cours du cycle moteur. Le mode de déplacement lent présente des déplacements d'amplitudes similaires à ceux représentées sur la figure 3b, de l'ordre de 0,1mm. On note toutefois qu'au cours du mode de déplacement rapide, l'amplitude de déplacement du dispositif de transmission 1, reste inférieur à 0,4 mm ce qui prévient sa mise en butée avec le bloc moteur 100.The Figures 4b and 4c respectively show the displacement and the speed of the transmission device 10 during the engine cycle. The slow motion mode exhibits displacements of amplitudes similar to those represented on the figure 3b , of the order of 0.1mm. Note, however, that during the fast mode of travel, the displacement of the transmission device 1, remains less than 0.4 mm which prevents its abutment with the motor unit 100.

Ce résultat est d'autant plus remarquable que l'effort exercé par le dispositif presseur 10 sur le dispositif de transmission, représenté sur la figure 4d, est du même niveau que la solution selon l'état de la technique de la figure 3c, en dehors de la période correspondant au pic abrupte de pression. Ainsi, pendant le mode de déplacement lent, cet effort est de l'ordre de 6kN ; et pendant le mode de déplacement rapide, cet effort atteint brièvement un maximum de 16kN. L'invention permet donc pour un effort identique, pendant la majeure partie du cycle moteur, d'éviter la mise en buté du dispositif de transmission 1 sur la paroi du bloc moteur 100.This result is all the more remarkable in that the force exerted by the pressing device 10 on the transmission device, represented on the figure 4d , is of the same level as the solution according to the state of the art of the figure 3c , outside the period corresponding to the sudden peak of pressure. Thus, during the slow displacement mode, this effort is of the order of 6 kN; and during the fast moving mode, this effort briefly reaches a maximum of 16kN. The invention therefore makes it possible, for an identical effort, during the major part of the engine cycle, to avoid the abutment of the transmission device 1 on the wall of the engine block 100.

Bien entendu, l'invention n'est pas limitée aux modes de mise en oeuvre décrits et on peut y apporter des variantes de réalisation sans sortir du cadre de l'invention tel que défini par les revendications.Of course, the invention is not limited to the embodiments described and variations can be made without departing from the scope of the invention as defined by the claims.

En particulier, bien que l'on ait décrit l'application de l'effort de maintien par le dispositif presseur 10 sur la crémaillère de commande 7, il est tout à fait possible sans sortir du cadre de l'invention que cet effort s'applique à d'autres éléments du dispositif de transmission 1. On peut notamment prévoir de disposer le dispositif presseur entre la paroi du bloc moteur et le dispositif de guidage à roulement 4.In particular, although it has been described the application of the holding force by the pressing device 10 on the control rack 7, it is quite possible without departing from the scope of the invention that this effort applied to other elements of the transmission device 1. In particular, it is possible to arrange the presser device between the wall of the engine block and the rolling guide device 4.

Et bien que l'on ait représenté en relation avec la figure 2 un dispositif presseur 10 particulier pour les besoins de la description complète de l'invention, on pourra dans certains cas préférer, sans sortir du cadre de l'invention, utiliser d'autres formes de dispositif presseur assurant les mêmes fonctions que celles décrites. Il pourra ainsi s'agir par exemple d'un dispositif comprenant des moyens d'absorption de chocs à base de polymère visqueux ou hyper visqueux comme cela est divulgué dans US5495923 ; ou comprenant des moyens électromagnétiques d'absorption de chocs comme divulgué dans US7537097 And although we have represented in relation to the figure 2 a particular pressing device 10 for the purposes of the complete description of the invention, it may in some cases be preferred, without departing from the scope of the invention, to use other forms of pressing device providing the same functions as those described. It may thus be for example a device comprising shock absorption means based on viscous or highly viscous polymer as is disclosed in US5495923 ; or including electromagnetic shock absorbing means as disclosed in US7537097

Claims (14)

  1. A device for compensating the operating clearances of an engine comprising:
    - a transmission device (1) likely to move transversely in an engine block (100) during an engine cycle;
    - a pressing device (10) exerting a holding force on the transmission device (1) and comprising a piston (23) which moves in a chamber (21) filled with a fluid and a pressure source connected to the chamber (21);
    with the compensation device being characterized in that the pressing device (10) comprises a check-valve (32, 37) between the source and the chamber (21); and in that the chamber (21) has at least one calibrated drain port (28, 29) intended to adjust the holding force to the instantaneous speed of transverse movement of the transmission device (1) in the engine block (100).
  2. A compensation device according to claim 1, wherein the transmission device (1) comprises:
    - a rolling guide device (4) bearing against a wall of the engine block (100);
    - a transmission member (3), secured to a combustion piston, which co-operates, on the one hand, with the rolling guide device (4) and, on the other hand, with a first side of a toothed wheel (5);
    - a control rack (7) which cooperates with a second side of the toothed wheel (5) and which is adapted to move longitudinally on an opposite wall of the engine block (100);
    - a connecting rod (6) which cooperates with the toothed wheel (5) and which is connected to a crankshaft (9) of the engine.
  3. A compensation device according to claim 2, wherein the pressing device (10) is secured to the engine block.
  4. A compensation device according to one of claims 2 or 3, wherein the pressing device (10) exerts the holding force on the control rack (7).
  5. A compensation device according to one of the preceding claims, wherein the holding force has a threshold value.
  6. A compensation device according to one of the preceding claims, wherein the pressing device (10) comprises a spring (25).
  7. A compensation device according to the preceding claim, wherein the spring (25) is accommodated in the chamber (21).
  8. A compensation device according to one of the preceding claims, wherein the calibrated drain port (29) is integrated in the check-valve (37).
  9. A compensation device according to one of the preceding claims, w herein the calibrated drain port (28, 29) is fluidly connected to the pressure source.
  10. A compensation device according to one of the preceding claims, wherein the calibrated drain port (28) opens on the exposed surface (20) of the piston (23).
  11. A compensation device according to one of the preceding claims, wherein the chamber (21), the piston (23) and the check-valve (31) are integrated into a self-contained capsule.
  12. A compensation device according to the preceding claim, wherein the pressure source is also integrated in the self-contained capsule.
  13. A compensation device according to claim 1, wherein the pressing device (10) is fluidly connected to a hydraulic power system.
  14. A variable compression ratio engine comprising the compensation device according to any one of claims 1 to 13.
EP15753643.4A 2014-10-13 2015-08-05 Device for compensating for the operating clearances of an engine Active EP3207234B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1459791A FR3027051B1 (en) 2014-10-13 2014-10-13 DEVICE FOR COMPENSATING THE OPERATING GAMES OF AN ENGINE.
PCT/EP2015/068105 WO2016058724A1 (en) 2014-10-13 2015-08-05 Device for compensating for the operating clearances of an engine

Publications (2)

Publication Number Publication Date
EP3207234A1 EP3207234A1 (en) 2017-08-23
EP3207234B1 true EP3207234B1 (en) 2019-01-16

Family

ID=52450317

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15753643.4A Active EP3207234B1 (en) 2014-10-13 2015-08-05 Device for compensating for the operating clearances of an engine

Country Status (8)

Country Link
US (1) US10202899B2 (en)
EP (1) EP3207234B1 (en)
JP (1) JP6603316B2 (en)
KR (1) KR102076039B1 (en)
CN (1) CN107110015B (en)
ES (1) ES2718933T3 (en)
FR (1) FR3027051B1 (en)
WO (1) WO2016058724A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3029977B1 (en) 2014-12-12 2018-11-30 MCE 5 Development DEVICE FOR TRANSMITTING AN ENGINE, IN PARTICULAR FOR A VARIABLE COMPRESSION AND / OR CYLINDER RATE ENGINE.
FR3051838B1 (en) 2016-05-24 2018-09-07 MCE 5 Development DEVICE FOR GUIDING A PISTON OF A COMBUSTION PISTON FOR A VARIABLE COMPRESSION RATE MOTOR
FR3063307B1 (en) * 2017-02-28 2019-03-29 MCE 5 Development PRESS DEVICE FOR EXERCISING A HOLDING EFFORT ON A TRANSMISSION DEVICE AND MOTOR PROVIDED WITH SUCH A DEVICE.
FR3081929B1 (en) * 2018-06-04 2020-09-18 MCE 5 Development SHIRT DEVICE FOR CONTROL CYLINDER OF AN INTERNAL COMBUSTION ENGINE
US11187184B2 (en) * 2019-03-29 2021-11-30 Vianney Rabhi Articulated plenum for transfer-expansion-regeneration combustion engine
CN110594017A (en) * 2019-09-05 2019-12-20 辽宁工程技术大学 Variable compression ratio mechanism of automobile engine

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4433649A (en) * 1981-11-27 1984-02-28 Shin Hi B Engine
JPS60185003U (en) * 1984-05-18 1985-12-07 マツダ株式会社 Zero lash adjustment device
JPH06137226A (en) * 1992-10-28 1994-05-17 Toyoda Gosei Co Ltd Fuel shutoff device
PL170036B1 (en) 1993-04-28 1996-10-31 Urzadzen Mechanicznych Kamax S Elastomeric shock an/or vibration absorber
US5674053A (en) * 1994-04-01 1997-10-07 Paul; Marius A. High pressure compressor with controlled cooling during the compression phase
JPH09209787A (en) * 1996-02-02 1997-08-12 Nissan Motor Co Ltd Compression ratio-variable direct injection diesel engine
WO2005012758A1 (en) 2003-07-31 2005-02-10 The Foundation For The Promotion Of Industrial Science Electromagnetic damper controller
FR2867515B1 (en) * 2004-03-11 2006-06-02 Vianney Rabhi ADJUSTING DEVICE FOR VARIABLE VOLUMETRIC RATIO ENGINE
FR2896539B1 (en) * 2006-01-26 2008-05-02 Vianney Rabhi PRESS DEVICE FOR MOTOR WITH VARIABLE VOLUMETRIC RATIO.
FR2896535B1 (en) * 2006-01-26 2008-05-02 Vianney Rabhi OIL PROJECTION COOLING AND LUBRICATION DEVICE FOR VARIABLE VOLUMETRIC RATIO ENGINE
FR2919022B1 (en) * 2007-07-19 2012-10-26 Vianney Rabhi HYDRAULIC POWER PLANT FOR VARIABLE COMPRESSION RATE MOTOR.
CN103541819B (en) * 2012-07-17 2017-08-08 瓦锡兰瑞士公司 Large-scale reciprocating-piston combustion engine and its control device and control method
KR101338461B1 (en) * 2012-11-02 2013-12-10 현대자동차주식회사 Variable compression ratio apparatus
KR101382318B1 (en) * 2012-12-17 2014-04-10 기아자동차 주식회사 Variable compression ratio device and internal combustion engine using the same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
FR3027051A1 (en) 2016-04-15
JP6603316B2 (en) 2019-11-06
KR102076039B1 (en) 2020-02-11
JP2017531759A (en) 2017-10-26
EP3207234A1 (en) 2017-08-23
FR3027051B1 (en) 2016-11-25
KR20170085040A (en) 2017-07-21
CN107110015A (en) 2017-08-29
US20170234215A1 (en) 2017-08-17
US10202899B2 (en) 2019-02-12
ES2718933T3 (en) 2019-07-05
CN107110015B (en) 2020-01-10
WO2016058724A1 (en) 2016-04-21

Similar Documents

Publication Publication Date Title
EP3207234B1 (en) Device for compensating for the operating clearances of an engine
EP1979591B1 (en) Pressure device for a variable compression ratio engine
CA2762767C (en) Shock absorber and landing gear provided with such a shock absorber
FR2727733A1 (en) TORQUE SENSOR, IN PARTICULAR FOR TRANSMISSIONS OF VEHICLES
FR2689591A1 (en) Transmission with winding member.
FR3043720B1 (en) VARIABLE VOLUMETRIC RATIO ENGINE
BE1016615A5 (en) TRANSMISSION.
EP3308026B1 (en) Drained-chamber hydraulic system
EP3480458A1 (en) Hydraulic machine comprising improved braking system
EP2795165B1 (en) Drain for dynamic sealing assembly
FR2771788A1 (en) CONICAL DISC TRANSMISSION MECHANISM
WO2018158527A1 (en) Pressure device for exerting a holding force on a transmission device and engine provided with such a device
FR2914716A1 (en) Hydraulic bump stop for adaptable compensation hydraulic shock absorber of motor vehicle, has compressible unit transforming deflection of stopping component such that stiffness and cutin point of compensation module increases
FR2552514A1 (en) DAMPER OF THE FLUIDIC TYPE
EP2917605B1 (en) Shock absorber piston and shock absorber comprising same
EP2126334A2 (en) Fuel injector for internal combustion engine
FR3098561A1 (en) HYDRAULIC STOP FOR SHOCK ABSORBER
WO2021089940A1 (en) Variable-length connecting rod for an engine with a controlled compression ratio
EP1978277B1 (en) Compensation module for a hydraulic shock absorber of a vehicle and shock absorber equipped with such a compensation module
EP4069959A1 (en) Hydraulic control system for a variable compression ratio engine
FR2914726A1 (en) HYDRAULIC VALVE AND ADAPTABLE COMPENSATION SHOCK ABSORBER EQUIPPED WITH SUCH A HYDRAULIC VALVE FORMING A COMPENSATION MODULE
FR3085431A1 (en) PILOT VOLUMETRIC RATIO
FR3034153A1 (en) FREEWHEEL HUB WITH NOISE REDUCTION DEVICE
EP1978276A1 (en) Hydraulic valve and hydraulic damper comprising such a valve and unit comprising two dampers connected together
FR2964162A1 (en) VOLUMETRIC HYDROSTATIC MACHINE

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170413

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180308

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

INTG Intention to grant announced

Effective date: 20181114

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602015023671

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1089866

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190215

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: ABREMA AGENCE BREVET ET MARQUES, GANGUILLET, CH

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190116

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: NL

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

Effective date: 20190116

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2718933

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20190705

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1089866

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190116

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

Ref country code: LT

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

Effective date: 20190116

Ref country code: PL

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

Effective date: 20190116

Ref country code: NO

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

Effective date: 20190416

Ref country code: PT

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

Effective date: 20190516

Ref country code: FI

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

Effective date: 20190116

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

Ref country code: RS

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

Effective date: 20190116

Ref country code: GR

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

Effective date: 20190417

Ref country code: HR

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

Effective date: 20190116

Ref country code: LV

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

Effective date: 20190116

Ref country code: BG

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

Effective date: 20190416

Ref country code: IS

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

Effective date: 20190516

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602015023671

Country of ref document: DE

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

Ref country code: AL

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

Effective date: 20190116

Ref country code: CZ

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

Effective date: 20190116

Ref country code: AT

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

Effective date: 20190116

Ref country code: DK

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

Effective date: 20190116

Ref country code: EE

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

Effective date: 20190116

Ref country code: SK

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

Effective date: 20190116

Ref country code: RO

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

Effective date: 20190116

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

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

Ref country code: SM

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

Effective date: 20190116

26N No opposition filed

Effective date: 20191017

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

Ref country code: SI

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

Effective date: 20190116

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

Ref country code: TR

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

Effective date: 20190116

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

Ref country code: MC

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

Effective date: 20190116

Ref country code: LU

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

Effective date: 20190805

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190831

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

Ref country code: IE

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

Effective date: 20190805

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

Ref country code: BE

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

Effective date: 20190831

REG Reference to a national code

Ref country code: CH

Ref legal event code: PFUS

Owner name: RABHI, VIANNEY, FR

Free format text: FORMER OWNER: RABHI, VIANNEY, FR

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

Ref country code: CY

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

Effective date: 20190116

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

Ref country code: HU

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

Effective date: 20150805

Ref country code: MT

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

Effective date: 20190116

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

Ref country code: MK

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

Effective date: 20190116

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

Ref country code: IT

Payment date: 20230825

Year of fee payment: 9

Ref country code: GB

Payment date: 20230822

Year of fee payment: 9

Ref country code: CH

Payment date: 20230902

Year of fee payment: 9

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

Ref country code: SE

Payment date: 20230821

Year of fee payment: 9

Ref country code: FR

Payment date: 20230825

Year of fee payment: 9

Ref country code: DE

Payment date: 20230821

Year of fee payment: 9

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

Ref country code: ES

Payment date: 20231027

Year of fee payment: 9