CA2845080A1 - Electro-hydraulic valve actuator having an alternating cam - Google Patents

Abstract

The invention relates to an electro-hydraulic valve actuator having a cylinder and an alternating cam and comprising: a valve-actuating hydraulic cylinder (2) which opens a valve of an internal combustion engine (100) using a valve-opening solenoid valve (4), a high-pressure valve-opening duct (11) and a high-pressure inflow hydraulic circuit (5), and which closes said valve using a valve-closing solenoid valve (6), a high-pressure valve-closing duct (12) and a high-pressure outflow circuit (7); and a hydraulic positive displacement pump (8) co-operating with a pump inlet non-return valve (14) and a pump outlet sealing solenoid valve (13), the outlet thereof being connected to a low-pressure circuit (9) and to a low-pressure tank (10) supplied by a replenishment pump (52) and a replenishment tank (53).

Description

ELECTRO-HYDRAULIC VALVE ACTUATOR
A CAME ALTERNATIVE
The present invention relates to an electronic valve actuator Hydraulic cylinder and reciprocating cam for internal combustion engine.
Inlet and exhaust valves of internal combustion engines alternatively open when the crankshaft of said engines reaches a some angular position. This results from the angular position ordinarily invariable of the camshaft or cams of said engines relative to that of said crankshaft, this latter position being considered on 360 degrees on the engines 2-time and over 720 degrees on 4-stroke engines as imagined by Messrs Nikolaus Otto and Alphonse Eugène Beau de Rochas.
To make variable the moment when said valves open relatively to the angular position of said crankshaft, the modern gasoline engines comprise at least one intake camshaft dephaser and, in addition, more often, an exhaust camshaft dephaser. These devices phase shift are usually electro-hydraulic, sometimes electrical, and allow to vary the angular position of said trees with respect to that said crankshaft.
For the majority of engines produced by the automotive industry, settings what are the opening time, the opening speed, and the lifting height of the valves are permanently fixed by the profile of the cams that operate said valves. Making said variable parameters present a large interest because of their strong impact on the filling of cylinders and on the quality of combustion. The variability of these parameters is a source significant improvement in the energy performance of engines and the control of polluting emissions of said engines. Said variability allows especially :
= Improving the filling of the cylinders of the internal combustion engine when it is used at full load, to increase the torque and power of said engine over its entire speed range. This result is obtained by triggering the opening and closing of the intake valves and exhaust at the most suitable moment for said filling, in particular

2 taking into account the aerodynamic and acoustic behavior of gases in the cylinder and in the intake and exhaust ducts of the engine;
= From reduce the pumping losses of the internal combustion engine when it works at partial load by replacing the winnowing on admission ordinarily operated by a throttle valve by a law of opening and appropriate closing of the intake valve, according to two strategies Main:
> The first of these strategies is to close the valve early intake during the intake stroke of said engine leads intake being maintained at a pressure close to the pressure during said stroke so as to trap in the cylinder of said engine the load air or fuel mixture sought, then to relax this air or mixture until the bottom dead center of the piston of said engine before re-compressing said air or mixture into the chamber of combustion to the top dead center of said piston.
D The second strategy is to close the intake valve late during the compression stroke of the engine the intake duct being maintained at a pressure close to atmospheric pressure during said stroke, an air charge or maximum fuel mixture being introduced into the cylinder during the intake stroke of the engine, then said load being partially pushed back into said conduit during the compression stroke until the remaining charge in the cylinder corresponds to the desired load, when the valve admission is closed. This last strategy operates a cycle Atkinson - more efficient at partial loads than Otto's or Beau de Rochas - and finds all its interest in engines with variable compression.
As a result of these pumping loss reduction strategies, significantly improving the efficiency of said partial-load engine;
= To improve the stability and quality of engine combustion internal combustion, in particular via better control of turbulence

3 gases in the combustion chamber obtained, for example, in finely controlling the lift height of the intake valve. said better control allows for example to improve the homogeneity of the air-fuel mixture of multi-point injection engines by providing low lift of the intake valves at low loads which has the effect of to generate finer turbulence during the passage of gases through the intake valve, said turbulence being favorable to said homogeneity. The said mastery also makes it possible to regulate the movement of tumble of air or gases in the cylinder, the said movement then transforming into fine turbulence when the engine piston reaches the top dead center, so as to improve the propagation of the flame during development of combustion. The said mastery also makes it possible swirling motion or swirl of air or gas commonly used in diesel engines, said movement being able for example to be set by shifting the opening point of the two intake valves of a same cylinder;
= To reduce both the pumped losses and the thermal losses of the internal combustion engine when the latter is operating at partial load in increasing the rate of hot residual flue gases contained in the load at the moment of combustion. Said gases do not contain oxygen, they do not participate in combustion but capture the heat released by said combustion which limits the thermal losses to the walls and therefore the fuel consumption. Being hot, said gases are bulky and reduce the volumetric efficiency of said engine with the key a reducing the need for valveing the intake duct by means of a butterfly, which limits the losses by pumping of said engine when it is used at partial load. Increase the rate of residual flue gas is especially obtained by increasing the crossing of the intake valves and exhaust, that is to say the time during which the valves intake and exhaust of the same cylinder are open simultaneously. This allows the piston of said engine to suck simultaneously fresh gases and flue gases. Increase the rate of residual burnt gases can also be obtained by opening the valve early intake for storing burnt gases in the front intake duct to reintroduce them into the cylinder during the intake stroke of said engine. As another non-limiting example, increase the rate of flue gas

4 Residuals can also be obtained by closing the valve exhaust to trap exhaust gases in the front cylinder to open the intake valve. It is noted that the recycling of gases exhaust from the previous cycle in the current cycle is also a strategy that reduces pollutant emissions and particularly the nitrogen oxides of diesel engines;
= To predict a higher volumetric ratio for the engine when this last is at fixed compression ratio, with a better performance means of said engine when used for example to propel a motor vehicle which one of the main features is to be used at continuously variable power over large amplitudes. this is obtained by controlling the effective compression ratio of the engine by the delay at the closing of the intake valve so that at high loads and low revs, only part of the piston stroke of the engine is used to compress the gases while almost the entire race said piston is used to relax said gases. According to this strategy, certain operating points of said engine may, however, use the quasi-entirety of the stroke of said piston both to compress and to to relax said gases to the extent that the charging and regime of said engine does not generate rattling or destructive combustion;
= To improve the efficiency and power of multicylinder engines supercharged turbocharger including avoiding or limiting the back-flow of exhaust gases under heavy loads. This is obtained avoiding as far as possible to open the exhaust valve as long as the pressure in the engine cylinder is less than pressure prevailing in the exhaust manifold of said engine;
= Improve efficiency of multicylinder engines when used at low power by deactivating one or more cylinder (s) of said engines.
This can be achieved by leaving the intake valve (s) closed and exhaust of the cylinder (s) deactivated (s), the cylinder (s) thus deactivated (s) operating series compression-relaxation little energy-consuming though the cylinders remained active deliver better performance due to higher load operation. We notes that according to this strategy it is possible to insert inactive cycles in a series of active cycles of the same cylinder, so as to obtain a more flexible operation of the internal combustion engine, each cylinder is then no longer deactivated that part of the time of operation of said engine, while said cylinder operates

5 normally the other part of the time;
= To improve the efficiency of 2-stroke internal combustion engines in optimizing the flue gas scavenging by the intake air operated at the end of stroke of said gases. This is achieved by optimizing the point opening and closing of the intake and exhaust valves relative to the angular position of the crankshaft of said engines so trap the desired air charge in the cylinder (s) of said engines, and to conserve the amount of residual flue gas desired in said cylinders. This strategy potentially avoids the need for to an intake and / or exhaust port, said light having various disadvantages for the operation and for the architecture of said engines;
= To improve the efficiency of pollutant post-treatment devices of the internal combustion engines, whether it is a 2 or 3-way catalyst, or a particle filter. These devices do not work at full capacity and / or being regenerated only after a certain temperature, a early opening of the exhaust valve of said engines makes it possible to truncate the throttle trigger to produce less work on the piston said engines to raise the temperature of their exhaust gas.
This strategy makes it possible in particular to accelerate the rise to service of said devices and / or to provide them with thermal energy necessary for their regeneration;
= To facilitate the design of the engine combustion chamber to alternative internal combustion with a variable compression ratio to reduce the depth of the recesses usually arranged on the cap of the pistons of said engines, or even to eliminate said recesses, the latter having the function of avoiding any collision between the pistons and the valves of said engines. This is achieved by voluntarily reducing the lift height of the valves of said engines when the ratio WO 2013/04586

6 PCT / FR2012 / 052318 The volumetric value of the latter is high, which generally corresponds to a partial load operation of said engines;
Various technologies make it possible to control all or part of the time of the opening, the duration of the opening and the lift height of the valves of alternative internal combustion engines. The camshaft phase shifters are industrialized countries and tend to become generalized, but they do not control the duration opening or the lift height of said valves. However, said phase shifters are more and more often associated with devices making variable the lift height of said valves.
These devices are marketed under various brands and / or trade names. There are valve lift variators discrete devices that include at least two cam profiles, and dimmers lifted continuously.
Amongst the discrete lift variators, there is notably the device VTec O from Honda, the Variocam Plus O from Porsche, the Valvelift system of the company Audi or the VVTL-i of the company Toyota.
Among the continuously variable valve lift variators, there is the Valvetronic developed by the BMW company and based on a lever of variable ratio, or the FIAT Multiair, which provides for a hydraulic transmission between the cam and the valve tappet with a solenoid valve back to the reservoir of the hydraulic fluid used allowing of truncate more or less the lifting of said valve.
It is noted that variable valve lift devices apply the most often to the intake valves and in rare cases to the valves exhaust. These devices usually equip only one of the engine cams, either the intake or the exhaust, mainly for reasons of cost and / or congestion.
We note that when they equip passenger vehicles produced in large series, these devices are always dependent on at least one tree to

7 cams and therefore, that their benefits depend directly on the profile of cams that said shaft.
There would be an obvious interest in breaking free from the constraint profile of cam. This is the purpose of so-called camless devices. These latter devices can in theory apply any law of opening, lifting and closing of the valves, within the limits allowed by the physics and the geometry.
There are many camless devices in prototype state like the electro-magnetic camless from the Valéo company, the Free Valve of the Cargine company, the hydro-electric device developed by the company Sturman in collaboration with the Siemens company or the Active Valve Train (AVTTm) from Lotus.
These systems most often have energy consumption and / or acoustic emissions and / or excessive space and / or cost even prohibitive.
Other defects or limitations related to these devices prohibit or push production on an industrial scale, such as reliability and / or durability difficult to guarantee throughout the life of a motor vehicle and / or a potentially insufficient controllability leading to panic of the high speed valves and / or a lack of progressivity when valves on their seat and / or ballistic mode leading to opening laws difficult to master.
These findings are at the origin of the international patent WO 2004/011780 belonging to the applicant, which describes a camless hydraulic actuator allowing the control of the lifting, the Advance to the Opening and / or the Delay at Valve closing of alternative internal combustion engines. said Actuator potentially authorizes the implementation of most of the strategies to increase the power and efficiency of internal combustion, as well as those to better control the polluting emissions of said engines.

8 In addition, said patent claims for said actuator a reliability and a cost of production potentially compatible with the specifications of a motor to automotive internal combustion produced in large series. Said actuator includes:
= at least one hydraulic cylinder connected to a high hydraulic circuit pressure through a conduit, and ensuring the opening of at least one valve;
= at least one volumetric hydraulic pump comprising at least one output and at least one input, and whose rotational speed is proportional to that of the crankshaft of the engine;
= at least one pump outlet shutter that prevents fluid expelled hydraulics at the outlet of the volumetric hydraulic pump lead into a low-pressure circuit or a tank, and to force to move towards a high pressure circuit communicating with one or more hydraulic cylinder (s) ensuring the opening of one or several valve (s);
= at least one valve opening selector that allows to direct via the high pressure circuit the hydraulic fluid expelled at the outlet of the pump volumetric hydraulics to the hydraulic cylinder of at least one valve to be opened, while prohibiting said hydraulic fluid from being directed to one or more other valve (s) to remain closed (s);
= at least one opening non-return valve placed on the high circuit pressure between the pump outlet and the hydraulic cylinder of at least one valve which allows to retain the hydraulic fluid in said hydraulic cylinder of said valve to keep it open;
= at least one valve closing selector that allows to direct the hydraulic fluid contained in the hydraulic cylinder of at least one valve held open by the opening check valve towards the inlet or inlets of the positive displacement hydraulic pump to ensure closing the at least one valve (s), and preventing the fluid hydraulic contained in their hydraulic cylinder to be introduced into the cylinder

9 hydraulic valve or other valve (s) to remain in position closed;
= and at least one pump inlet check valve that allows the fluid hydraulic low pressure circuit or tank to be admitted to the entrance or at the entrances of the positive displacement hydraulic pump when the pressure said low pressure circuit or said reservoir is greater than that of said or said inlet (s) of the positive displacement hydraulic pump.
Despite its potential advantages, the hydraulic valve actuator for internal combustion engine described in the international patent WO
2004/011780 belonging to the applicant has various limitations and disadvantages, among which:
= it is not possible to simultaneously obtain an opening law of valves for a cylinder which is different from that of another cylinder of the same internal combustion engine, for this reason, it is for example not it is possible to deactivate the valves of one of the cylinders of said engine;
= it is not possible to provide for the same valve more than one lift by motor cycle, or from a 4-stroke cycle to a 2-stroke cycle;
= the hydraulic cylinders of the valves of the internal combustion engine directly attacking said valves, lifting said valves generates a violent water hammer in the ducts of the actuator because the pressure rises abruptly in said ducts when switching on said cylinders with the volumetric hydraulic pump of said actuator, said water hammer resulting from the inertia of said valves which leads to significant acceleration efforts, the said efforts being increased by effort antagonist produced by the return spring of said valves;
= it is difficult to gently rest the engine valves to combustion internally on their seat due to a constant relationship between the flow of the hydraulic pump of said actuator and the speed of opening and closing said valves. This potentially leads to emissions excessive acoustics resulting from the shock produced between the said valves and their seat and premature wear of said seat and said valves;

= the ducts that connect the actuator to the hydraulic cylinders that open and close the valves are of great length and enclose a volume important oil which is compressed and decompressed at each maneuver said valves. This can lead to an unstable position and difficult to control said valves;
= the actuator has a certain complexity of realization due to the multitude of precise parts of which it is constituted, said complexity and

10 said parts potentially leading to a high cost price of said actuator;
= the actuator requires precise electric motors to drive way proportional the position of its lifting forks, in advance opening, and delay closing valve (s). These complex engines are potentially expensive.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the invention is distinguished from the devices valve drives known from the prior art in that it inherits Advantages of Hydraulic Valve Actuator for Internal Combustion Engine described in the international patent WO 2004/011780 belonging to the applicant, but eliminates the disadvantages and pushes the boundaries functionalities via an embodiment and means used which are radically different.
Accordingly, the electro-hydraulic valve actuator according to the invention :
= allows to predict a law of opening of the valves for a cylinder of the internal combustion engine simultaneously different from that of another cylinder of said engine;
= allows to provide an opening law for an intake valve or exhaust of a cylinder of the internal combustion engine simultaneously different from that of another valve of the same cylinder having the same function of either intake or exhaust;

11 = allows the deactivation of the valves of one or more cylinders of a same internal combustion engine;
= allows several lifts per engine cycle of the same valve;
= allows the same internal combustion engine or any of the cylinders of the same internal combustion engine to run indifferently a 2-cycle cycle or a 4-cycle cycle;
= greatly avoids or attenuates water hammer in ducts of said actuator, reducing the inertial forces generated by the parts directly attacked by the hydraulic cylinder and ensuring progressivity of lifting and removing the valves of the combustion engine internally, with a reduction of noise and instabilities of positioning said valves;
= makes it possible to rest smoothly on their seat the engine valves to internal combustion, thus avoiding any excessive acoustic emission, and any premature wear of said seats and / or said valves;
= greatly reduces the effects of the compressibility of the oil on the stability of the position of the valves of the internal combustion engine;
= has a significantly reduced cost and complexity.
The other features of the present invention have been described in the description and in the dependent secondary claims directly or indirectly from the main claim.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises:
= at least one hydraulic actuator valve actuator which comprises at minus one valve actuator piston which opens at least one valve internal combustion engine or piston compressor (s) when said cylinder is connected by a valve opening solenoid valve with at least one incoming high pressure hydraulic circuit, said cylinder

12 closing said valve when it is connected by a solenoid valve of valve closure with at least one outgoing high pressure circuit, and said cylinder ensuring the maintenance opening of said valve when is connected neither with the incoming high pressure circuit nor with the circuit high pressure exiting;
= at least one volumetric hydraulic pump comprising at least one output connected to a low pressure circuit connected to at least one low tank pressure and at least one input connected to said low pressure circuit, said pump running at a speed proportional to that of a crankshaft of internal combustion engine ;
= at least one high pressure valve opening pipe connecting the exit volumetric hydraulic pump with high hydraulic circuit Inlet pressure of the hydraulic actuator valve actuator;
= at least one high pressure valve closing pipe connecting entry volumetric hydraulic pump with high hydraulic circuit pressure exiting the hydraulic actuator valve actuator;
= at least one pump outlet shut-off solenoid valve which can prevent expelled hydraulic fluid at the outlet of the hydraulic pump volumetric return to the low pressure hydraulic circuit, so that said fluid is forced into the high pressure opening pipe of valve ;
= at least one pump inlet check valve that prevents the fluid hydraulic from the hydraulic actuator valve actuator via the High pressure valve closing duct to return directly in the low pressure hydraulic circuit, so that said fluid is strength at the inlet of the volumetric hydraulic pump, but said valve allowing said pump to suck said fluid contained in the circuit hydraulic low pressure, when the pressure of the latter is higher at the pressure prevailing in the high pressure closing pipe of valve ;

13 = at least one valve opening cam connected on the one hand to the jack hydraulic valve actuator by a mechanical transmission, and on the other hand to the valve of the internal combustion engine directly or through an intermediate transmission, said cam moving in a sense during the opening maneuvers of said valve, then in direction reverse during the closing maneuvers of said valve;
= at least one return spring of the valve opening cam which tends at recall said cam in the position it has when the engine valve internal combustion is closed;
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a cylinder hydraulic valve actuator which is rotary and a piston actuator of valve which has a pallet shape, said piston separating at least one high pressure chamber of at least one low pressure chamber so that the pressure of the hydraulic fluid can rotate said piston last being connected in rotation directly or indirectly to the cam valve opening.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a piston valve actuator that can move in a cylinder and push on a valve opening rack guided in a cylinder head that includes the internal combustion engine or the piston compressor (s), rack and pinion cooperating with a gear arranged around an axis of the opening cam of valve so as to drive said cam in rotation when said piston is moves in longitudinal translation.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a valve opening rack which is guided in the cylinder head of the engine to internal combustion by means of at least one ball or roller bearing.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a piston valve actuator moving in a cylinder and pushing a rod

14 valve opening with one of the ends of which it is articulated, said rod in turn pushing on a cam arm that directly carries or indirectly the valve opening cam with which the other end said rod is also articulated so as to drive said cam into rotation when said piston moves in longitudinal translation.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a rod valve opening which is articulated to at least one of its two ends by means of an open or closed ball joint.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a volumetric hydraulic pump with several compartments each constitute an autonomous pump comprising at least one inlet and at least one output connected to at least one actuator hydraulic cylinder valve, said autonomous pumps being rotated by the same shaft and being housed in the same housing.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a sensor position on the valve of the internal combustion engine.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a sensor angular cam position on the valve opening cam.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a cam valve opening which cooperates with a cam stop limiting the maximum angular position of said cam when the engine valve to internal combustion actuated by said cam is closed.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises an abutment of a cam which is mounted on a shock absorber or which comprises a shock absorber limiting acoustic emissions when said cam comes into contact with the cam stop.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for 5 internal combustion engine according to the present invention comprises a cam valve opening which has two open or closed joints and a lever cam contact surface, the first articulation being solidary of the internal combustion engine while the second is connected to the piston actuator valve directly by a piston touch or 10 indirectly by a push rod and said cam being able to roll and or slide on a tilting contact surface fitted on a pawl articulated rocker at one of its ends around at least one anchorage of latch secured to said motor, and provided at its other end with at least one flap touch that can push directly or indirectly on a

At least one valve of said motor for opening said valve.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a ball joint on at least one of the two open or closed joints.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a rod thrust which is articulated at each of its ends by a connection patella, the first ball joint being arranged in or at the end of the piston valve actuator while the second ball joint is arranged in or on the valve opening cam.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a cam valve opening having an effect cam contact surface lever and is rotated by means of at least one rotational arm whose one end is integral with the axis of said cam while its other end is articulated by means of a pivot connection or ball joint with the first end of an arm push rod, the second end of said rod being articulated by means of a pivot connection or ball joint with the piston actuator valve and said cam being able to roll and / or slide on a surface of rocker switch arranged on a rocker arm articulated to one of its

16 ends around at least one integral latch anchor of the engine to internal combustion, and provided at its other end with at least one touch of pawl that can push directly or indirectly on a tail that comprises at least one valve of said motor for opening said valve.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a piston valve actuator moving in a cylinder with a light piston end damping device, said light being closed in all or part of said piston when said piston reaches the vicinity of the position that he has when the valve of the internal combustion engine that he operates is closed.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a piston valve actuator moving in a cylinder with end stop piston stroke which limits the depth of introduction of said piston in said cylinder.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a low pressure reservoir which consists of at least one accumulator of compensation pressure maintained under pressure by at least one replenishment which supplies said accumulator with hydraulic fluid by sucking said fluid into at least one replenishing tank.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a valve opening solenoid valve and / or closing solenoid valve pump outlet valve and / or solenoid valve which is a tube solenoid valve consisting of at least one rectilinear tube move in longitudinal translation in a valve housing having a upper chamber and a lower chamber, said rectilinear tube comprising a first end opening into the upper chamber and a second end opening into the lower chamber, said second end which can come into contact with at least one sealing surface

17 secured to said valve housing so as to seal the tightest possible said second end.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube solenoid valve comprising sealing means between the surface external of the rectilinear tube and the valve housing which isolate the chamber upper part of the lower lower chamber.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube solenoid valve comprising at least one closing spring which tends to keep the rectilinear tube in contact with the sealing surface.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube solenoid valve comprising at least one electric actuator capable of to apply to the rectilinear tube an effort antagonistic to that produced by the spring shutter, said force being sufficient to detach the straight tube from the shutter surface when said actuator is traversed by a current electric.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube solenoid valve whose electric actuator consists of a coil of wire conductor which attracts a core or magnetic paddle when said coil is crossed by an electric current.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a electric actuator whose core or magnetic paddle is housed in the upper Room.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a electric actuator whose coil of conductive wire is housed in the upper Room.

18 The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a electric actuator whose coil of conductive wire is housed outside of the upper chamber, the magnetic field generated by said coil when it is crossed by an electric current passing through the wall external of said chamber so as to exert a force on the core or pallet magnetic.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube solenoid valve whose first end of the rectilinear tube is solidary core or magnetic paddle.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube rectilinear whose first end comprises at least one radial orifice and or axial opening into the upper chamber.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube straight line, the second end of which is troncospheric and presents a line contact with the sealing surface similar to that achieved by a ball laying on a seat.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a obturation surface which is arranged on an independent mounted part floating in the valve housing, said part being able to align with the tube rectilinear when the second end of said tube comes into contact with said area.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a housing Valve directly or indirectly via a plug intermediate, a vented hole that is closed by the piece independent on which is fitted the sealing surface.

19 The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a housing valve which is attached to the internal combustion engine and which has orifices and / or inlet-outlet ducts connecting the chamber upper and / or the lower chamber is with the hydraulic cylinder actuator valve with the positive displacement hydraulic pump via the circuit hydraulic high pressure entering, the high pressure circuit coming out or the circuit low pressure hydraulic.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube rectilinear whose section at the level of the seal that said tube constitutes with the valve housing is slightly smaller than the section of said tube at level of its contact with the sealing surface.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tube solenoid valve whose sealing means are constituted by the area external of the rectilinear tube which cooperates with the internal one of the valve housing.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a solenoid valve with a stop adjustable or not which is arranged on the rectilinear tube and which cooperates with an arranged axial stopping surface directly or indirectly in the valve housing, said stop determining the maximum distance between said tube and the sealing surface with which he cooperates.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a housing valve that can accommodate multiple solenoid valves.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment pump comprising a replenishing piston who can perform back and forth movements in a blind cylinder arranged in a blind cylinder housing so as to define a volume variable inside said cylinder, said piston also cooperating with a replenishment inlet valve and an outlet valve of replenishment, whose exit and entry respectively lead to Said volume, said inlet valve admitting hydraulic fluid in from the replenishment tank while said check valve outlet expels said fluid into the compensation pressure accumulator or in the refill pressure accumulator.
10 The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment pump whose replenishing piston is actuated in translation in a first direction by an electric actuator to solenoid mainly consisting of a magnetic core of 15 refill, a coil of wire and a cage magnetic of replenishment, and in a second sense by a spring of refill piston.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for

Internal combustion engine according to the present invention comprises a replenishment pump with a blind cylinder cover in the same metal piece as the magnetic cage of replenishment.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a a replenishing pump with a blind cylinder cover shirt in which evolves the piston of replenishment.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment pump whose blind cylinder has a light end of discharge stroke which connects said cylinder to the outlet valve of replenishment so that the refill piston closes said light at the end of the discharge stroke and is braked then stopped in her discharge stroke.

21 The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment pump whose maximum stroke of the piston of replenishment is limited in the direction of the discharge by a stop of discharge and / or in the direction of suction by a suction stop.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a electric solenoid actuator whose magnetic core replenishment is crossed by the replenishment piston on which it is rigidly mounted, said piston passing through the magnetic cage of replenishment from one side to cooperate on one side of said cage with the blind cylinder and on the other side of said cage with the spring of return of said piston.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment pump which comprises a tubular piston of replenishment that can perform back-and-forth movements in a open cylinder arranged in an open cylinder housing which is directly or indirectly with a pump casing so that said piston, said cylinder and said pump casing together define a volume variable inside said cylinder, said tubular replenishing piston cooperating with a tubular piston inlet valve consisting of a ball and of a spring, said ball bearing on a seat arranged at the end and the interior of said piston and an open cylinder outlet valve constituted a ball and a spring said ball bearing on a seat fitted at the end and outside said cylinder, said inlet valve admitting fluid hydraulic in from the replenishment tank while said check valve outlet expels said fluid into the compensation pressure accumulator or in the refill pressure accumulator.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a housing open cylinder which comprises a fluid conveying duct

22 hydraulically connecting directly or indirectly the piston inlet valve tubular with a pump inlet port that includes the pump housing.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a housing pump which comprises a hydraulic fluid outlet duct connecting directly or indirectly the cylinder outlet valve open with a Pump outlet port that includes the pump housing.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a piston tubular replenishment which is actuated in translation in a first sense by a mainly solenoidal electric actuator a magnetic replenishment core secured to said piston, a coil of conductive wire and a magnetic resupply cage, and in a second direction by a return spring of the tubular piston of replenishment.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a core magnetic replenishment which is provided with at least one core indirectly connecting the hydraulic fluid conveying conduit to the center of the replenishing tubular piston via the inlet valve of tubular piston, open cylinder housing, said core and said piston being commonly housed inside a sealed socket while said socket conveys hydraulic fluid from the conduit to said channel.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment tank which is fed with hydraulic fluid by the lubricating oil circuit of the internal combustion engine.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a replenishment tank that contains a specific hydraulic fluid and is independent of the lubricating oil circuit of the combustion engine internal.

23 The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a cylinder hydraulic valve actuator having at least one drain that recovers the hydraulic fluid leaking from said cylinder, so that said fluid returns in the replenishment tank via at least one jack drain pipe.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a volumetric hydraulic pump comprising at least one drain which recovers the hydraulic fluid leaking from said pump, so that said fluid returns in the replenishment tank via at least one draining duct of pump.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises one or several purge valves placed on the hydraulic cylinder and / or on the pump volumetric hydraulics and / or at any point in the hydraulic system incoming high pressure and / or outgoing high pressure hydraulic circuit and or of the low pressure hydraulic circuit.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a cam valve opening which is a wedge-shaped drawer that can translate under the action of the hydraulic actuator valve actuator in a guide or a slide arranged in the cylinder head of the internal combustion engine so that the wedge shape of said drawer creates a local variation of thickness which allows lift or remove the combustion engine valve from its seat internal.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a guide or slide comprising at least one roller on which rolls the drawer in form corner.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a drawer in

24 wedge shape which cooperates with a rocker latch hinged to one of its ends around at least one integral latch anchor of the engine to internal combustion, and provided at its other end with at least one touch of latch that can push directly or indirectly on the tail than comprises the valve of said motor for opening said valve.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a cam valve opening which consists of a cam finger hinged by one its ends around an axis and which has at its other end a tangential lifting surface, said surface having a shape such that it exerts radially a thrust relative to said axis on a rocker arm roll when the cam finger rotates about its said axis under the action of the hydraulic cylinder valve actuator and the latch itself being hinged at one of its ends around at least one integral latch anchor motor, and being provided at its other end with at least one pawl so that you can push directly or indirectly on a tail that comprises the valve of said motor to open said valve.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a mechanical transmission connecting the cam follower to the actuator hydraulic cylinder valve which consists of a push rod comprising at each both ends a swivel joint and / or ball joint, the first end bearing on or in the valve actuator piston, while that the second end is supported on the body of the cam finger.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a spring of a cam follower which consists of at least one helical spring who exerts a counterforce to that of the valve actuator piston and which tends to move away from one another two pivoting and / or swivel joints Guided relative to one another by at least one sliding connection, the first articulation bearing directly or not on the combustion engine internal while the second joint is supported on the body of the finger at cam.

The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a tangential lifting surface that ends with a stop that can enter contact with the roll rocker latch to limit movement 5 angular of the cam finger.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises at least a replenishment pressure accumulator which is interposed between the 10 replenishing pump and the pressure accumulator of compensation.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a 15 replenishing pressure accumulator whose output comprises a locking valve.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a 20 replenishment pressure accumulator which is connected to the accumulator compensation pressure by a conduit comprising at least one valve check valve said valve allowing the hydraulic fluid to go from the accumulator of pressure of replenishment towards the accumulator of compensation pressure and not the opposite.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises a conduit high pressure valve opening which comprises at least one valve pressure keeping positioned towards its end nearest the pump volumetric hydraulics, said valve allowing the hydraulic fluid from said pump to enter said conduit, but not from out.
The electro-hydraulic valve actuator with cylinder and reciprocating cam for internal combustion engine according to the present invention comprises at the output volumetric hydraulic pump a low tank check valve pressure positioned between said outlet and the shut-off solenoid valve Release pump, said valve allowing the hydraulic fluid to go from the outlet of the volumetric hydraulic pump to said low pressure reservoir, but not the opposite.
The actuator of electro-hydraulic valve with cylinder and reciprocating cam has for function:
- To force the hydraulic fluid discharged at the outlet of the pump hydraulic volumetric in the hydraulic actuator valve actuator at least a valve of the internal combustion engine to lift said valve with progressiveness and this, at the desired moment, and during the time necessary to lift said valve to the desired height;
then, - to keep the hydraulic fluid locked in the hydraulic cylinder valve actuator of said valve to maintain said valve open during the desired time, said time being expressed in number of degrees of crankshaft rotation of said engine;
then, - To force the hydraulic fluid contained in the hydraulic cylinder actuator valve of said valve at the inlet of the hydraulic pump volumetrically so as to gently rest said valve on its seat at moment sought while recovering most of the energy mechanic stored by the return spring of said valve when the opening of it, and most of the kinetic energy stored by said valve, said spring and the components mechanical devices which operate to actuate said valve during its race closure.
According to a particular embodiment, the electronic valve actuator Hydraulic cylinder and reciprocating cam according to the invention also comprises:
= at least one cam position sensor and / or at least one valve position;

= at least one computer that controls the different solenoid valves of said actuator;
= at least one sensor that measures the angular position of the crankshaft of the engine, which is taken into account by the computer to control the solenoid valves for valve opening, valve closing and pump outlet shutter so that the actual position of the valve measured by the cam angular position sensor and / or the valve position sensor for each angular position of the crankshaft matches the opening, the lifting height and the point the effective closure of the valve (s) considered, these different sensors, the computer and these various solenoid valves realizing a closed-loop servo device of the position of the valves.
The following description with reference to the accompanying drawings, given as non-limiting examples will make it possible to better understand the invention, the characteristics it presents, and the benefits that it is likely to to procure:
Figure 1 illustrates the schematic diagram of the electronic valve actuator Hydraulic cylinder and cam alternative according to the present invention such it can be provided to operate only one of the valves of a motor to alternative internal combustion.
FIG. 2 illustrates the block diagram of the actuator according to the invention as it can be provided to operate the eight intake valves or exhaust of a four-cylinder reciprocating internal combustion engine and four valves per cylinder, each group of two valves of the same cylinder being actuated by the same hydraulic actuator valve actuator.
FIG. 3 illustrates the block diagram of the actuator according to the invention as it can be provided to operate the eight intake valves and the eight exhaust valves of a four-cylinder and four-valve engine per cylinder each group of two valves of the same cylinder being actuated by the same hydraulic actuator valve actuator.

Figure 4 is a schematic sectional view of an example of implantation on a reciprocating internal combustion engine of the actuator according to the invention.
Figure 5 is an exploded view of the volumetric hydraulic pump of actuator according to the present invention when according to a particular mode of realization said pump is compartmentalized so as to constitute several autonomous pumps driven by the same tree and housed in the same casing.
Figure 6 is a schematic sectional view of the opening cam of valve, hydraulic cylinder valve actuator and transmission between said cylinder and said actuator cam according to the present invention.

when, according to a particular embodiment, said transmission is a rack cooperating with a pinion integral with the axis of said cam.
Figure 7 is a schematic sectional view of the opening cam of valve, hydraulic cylinder valve actuator and transmission between said cylinder and said actuator cam according to the present invention.
when, according to a particular embodiment, said transmission is a valve opening rod articulated on a cam arm that includes said cam.
Figure 8 is a schematic sectional view of the opening cam of valve, hydraulic cylinder valve actuator and transmission between said cylinder and said actuator cam according to the present invention.

when, according to a particular embodiment, said cam takes the wedge-shaped drawer that can translate between a slide to roller and a roller latch.
Figure 9 is a schematic sectional view of the valve opening cam according to the present invention when according to a particular embodiment it is actuated by a rotating hydraulic cylinder mounted directly on axis of said cam, the mechanical transmission between said cylinder and said cam being constituted of said axis.

Figures 10 and 11 are schematic sectional views, respectively open valve and closed valve, the valve opening cam, the hydraulic cylinder valve actuator and mechanical transmission between said cylinder and said cam of the actuator according to the invention, when according to a particular embodiment of said cam has two joints open or closed and a lever cam contact surface, and that said cam cooperates with a rocker latch.
Figure 12 is a schematic sectional view of a variant of the components of the actuator shown in FIGS. 10 and 11 which is distinguished in that the valve opening cam is rotated by means of an arm of rotation whose one end is integral with the axis of said cam and who cooperates with an arm push rod that transmits to it the effort produced by the piston valve actuator.
Figures 13 is a schematic sectional view of the opening cam of valve, hydraulic cylinder valve actuator and transmission between said cylinder and said actuator cam according to the present invention.

invention said cam being constituted by a cam finger hinged by one of its ends around an axis its other end having a surface tangential lifting cooperating with a rocker rocker latch.
Figures 14 and 15 are schematic sectional views of the solenoid valve valve opening and / or valve closing solenoid valve and / or the pump outlet shut-off solenoid valve according to the present invention when it takes the form of a tube solenoid valve according to a mode particular embodiment, respectively in the closed position (FIG. 14) and in open position (Figure 15).
Figure 16 is a schematic sectional view of the pump of replenishment according to the present invention and according to a first embodiment particular embodiment providing a blind cylinder.
Figure 17 is a schematic sectional view of the pump of replenishment according to the present invention and according to a second mode particular embodiment providing a tubular piston of replenishment.

Figures 18 to 20 are three-dimensional exploded views of the pump of replenishment according to the present invention and according to the second embodiment embodiment as shown in Figure 17.
5 Figure 21 illustrates the block diagram of the valve actuator electro-Hydraulic cylinder and cam alternative according to the present invention such it can be provided to operate only one of the valves of a motor to alternative internal combustion, the pump inlet check valve being replaced by a pump inlet solenoid valve mounted parallel to a 10 pump inlet pressure relief valve.
FIGS. 1 to 4 show an electro-hydraulic valve actuator at cylinder and cam alternative 1 for internal combustion engine 100.
The electro-hydraulic valve actuator 1 comprises at least one jack hydraulic valve actuator 2 comprising at least one piston valve actuator 3 which opens at least one valve 101 of the engine to internal combustion 100 or a piston compressor (s) when said cylinder 2 is connected by a valve opening solenoid valve 20 4 with at least one incoming high pressure hydraulic system 5.
Said hydraulic cylinder 2 closes said valve 101 when it is put into relationship by a valve closing solenoid valve 6 with at least one circuit high pressure outgoing 7.
Said hydraulic cylinder 2 maintains the opening of said valve when it is not in contact with the incoming high pressure circuit 5, nor with the outgoing high pressure circuit 7.
The incoming and outgoing high pressure hydraulic circuits 7 can have a flow divider known per se to share the flow to or from in from several hydraulic cylinders valve actuators 2.
The electro-hydraulic valve actuator 1 comprises at least one pump volumetric hydraulics 8 comprising on the one hand at least one output connected to a low pressure hydraulic circuit 9 connected to at least one low reservoir pressure 10 and on the other hand at least one input connected to said circuit hydraulic low pressure 9.
The low pressure reservoir 10 consists of at least one accumulator of compensation pressure 51 maintained under pressure by at least one pump replenishment 52 which feeds said accumulator 51 in fluid by drawing said fluid into at least one reservoir of replenishment 53.
It is noted that the compensation pressure accumulator 51 may be at membrane, piston or any other type known to those skilled in the art, being able to to be housed in the casing 35 of the positive displacement hydraulic pump 8 and having in particular to limit the effects of fluid compressibility on the operation of the actuator 1 according to the invention of a go, and avoid any cavitation phenomenon inside the circuit of said actuator on the other hand.
It is noted that the volumetric hydraulic pump 8 rotates at a speed proportional to that of a crankshaft 102 that the engine internal combustion 100.
The volumetric hydraulic pump 8 can be fixed displacement or displacement variable, internal gear, external gear, piston (s), screw or at pallet (s).
The volumetric hydraulic pump 8 can be attached to the engine at internal combustion 100 and can be driven by the crankshaft 102 of said motor by at least one pinion or at least one chain or at least one a belt or through a fixed ratio transmission or variable.
The drive of the volumetric hydraulic pump 8 by said crankshaft 102 can operate only mechanically or electrically via a alternator which drives an electric motor driving said pump.
energy electrical generated by said alternator may or may not be stored in a battery and the low pressure hydraulic circuit 9 may comprise a pressure sensor that returns the value of the pressure prevailing in said circuit to a calculator.

The electro-hydraulic valve actuator 1 comprises at least one duct high pressure valve opening 11 connecting the pump outlet 8 volumetric hydraulics with incoming high pressure hydraulic system of hydraulic actuator valve actuator 2.
The electro-hydraulic valve actuator 1 comprises at least one duct high pressure valve closing 12 connecting the pump inlet volumetric hydraulics 8 with the outgoing high pressure hydraulic system of hydraulic actuator valve actuator 2.
The electro-hydraulic valve actuator 1 comprises at least one pump outlet shut off solenoid valve 13 which can prevent the fluid expelled hydraulics at the outlet of the 8 volumetric hydraulic pump return to the low pressure hydraulic circuit 9, so that said fluid is forced into the high pressure valve opening pipe 11.
According to a particular embodiment of the electronic valve actuator 1, a pressure limiter 144 can be mounted parallel to the pump outlet shutoff solenoid valve 13, said limiter permitting at hydraulic fluid to pass directly from the output of the hydraulic pump volumetric 8 to the low pressure tank 10 without passing through said solenoid valve when the pressure difference across said solenoid valve exceeds a certain value.
The electro-hydraulic valve actuator 1 comprises at least one valve anti return pump input 14 which prohibits the hydraulic fluid from of hydraulic actuator valve actuator 2 via the high pressure duct of valve closure 12 to return directly into the hydraulic circuit low pressure 9, so that said fluid is forced to the inlet of the pump volumetric hydraulics 8.
Said nonreturn valve 14 allows said volumetric hydraulic pump 8 to suck up said fluid contained in the low pressure hydraulic circuit 9, when the pressure of the latter is greater than the pressure prevailing in the duct high pressure valve closing 12.

Said nonreturn valve 14 can according to a non-limiting exemplary embodiment to be consisting of a ball held on its seat by a spring.
According to a particular embodiment of the electronic valve actuator 1 shown in FIG. 21, the pump inlet check valve 14 can be replaced by a pump inlet solenoid valve 142, the latter can then be mounted parallel to an input pressure limiter of pump 143 which allows the hydraulic fluid to pass directly from the reservoir low pressure 10 at the inlet of the 8 volumetric hydraulic pump without through said solenoid valve 142 when the pressure difference at the bounds said solenoid valve exceeds a certain value. This configuration can advantageously cooperate with a non-return valve 145 of high duct valve closing pressure 12 to allow pressure to prevail in the low pressure tank 10 may be greater than necessary at the complete closure of the valve 101 of the engine 100, said configuration in particular to reduce the applied average pressure difference at the terminals of the volumetric hydraulic pump 8 to improve the energy efficiency of the electro-hydraulic valve actuator 1.
The electro-hydraulic valve actuator 1 comprises at least one cam valve opening 15 connected on the one hand to the actuator hydraulic cylinder of valve 2 by a mechanical transmission 16, and secondly to the valve 101 of the internal combustion engine 100 directly or through a intermediate transmission 17.
Said valve opening cam 15 moves in one direction during opening maneuvers of said valve 101, then in opposite directions during closing maneuvers of said valve 101.
Said intermediate transmission 17 may be a pusher, a rocker arm or a latch 18 known to those skilled in the art, the latter being able to possibly include an automatic device known in itself catch-up clearance between said cam 15 and said valve 101.
Said valve opening cam 15 is the moving parts with which they cooperate, said mechanical transmission 16 and said transmission intermediate 17 being designed so as to be as light as possible.

The electro-hydraulic valve actuator 1 has at least one spring of return 19 of the valve opening cam 15 which tends to recall said cam 15 in the position it has when the valve 101 of the engine to internal combustion 100 is closed.
Said return spring 19 may be, according to a particular mode of realization, the spring 103 ensuring the return to the closed position of said valve 101.
The valve 101 of the internal combustion engine 100 comprises a sensor of position not illustrated that can be inductive, hall effect or any other type known to those skilled in the art.
FIG. 9 shows an exemplary embodiment of the valve actuator electro-hydraulic cylinder and alternative cam 1 according to the present invention.
The electro-hydraulic valve actuator 1 comprises a hydraulic cylinder valve actuator 2 which is rotary and a valve actuator piston 3 having a pallet shape.
Said valve actuator piston 3 separates at least one upper chamber pressure 20 of at least one low pressure chamber 21 so that the pressure of the hydraulic fluid can rotate said piston 3, this last being connected in rotation directly or indirectly to the cam valve opening 15.
FIG. 6 shows another embodiment of the actuator of FIG.

electro-hydraulic valve with cylinder and alternative cam 1 according to the present invention.
The electro-hydraulic valve actuator 1 comprises an actuator piston valve 3 which can move in a cylinder 22 and push on a valve opening rack 23 guided in a cylinder head 104 that comprises the internal combustion engine 100 or the piston compressor (s).
Said valve opening rack 23 cooperates with a pinion 24 arranged around an axis 25 of the valve opening cam 15 so as to driving said cam 15 in rotation when said piston 3 moves in longitudinal translation, said rack 23 and said pinion 24 constituting the mechanical transmission 16.
5 Note that according to a particular embodiment, the pinion 24 can consist of a toothed sector of a few degrees arranged directly on the around the valve opening cam 15.
The valve opening rack 23 can be guided in the cylinder head 104 10 of the internal combustion engine 100 or by means of at least one balls or rollers 26.
FIG. 7 shows another embodiment of the actuator of FIG.

electro-hydraulic valve with cylinder and alternative cam 1 according to the present Invention.
The electro-hydraulic valve actuator 1 comprises an actuator piston valve 3 which can move in a cylinder 22 and push a rod valve opening 27 with one of the ends of which it is Speak clearly.
Said valve opening rod 27 in turn pushes on a cam arm 28 directly or indirectly includes the valve opening cam 15 with which the other end of said rod 27 is also hinged so as to drive said cam 15 in rotation when said actuator piston of valve 3 moves in longitudinal translation.
The valve opening stem 27 and the cam arm 28 constitute the mechanical transmission 16 of the electro-hydraulic valve actuator 1.
The valve opening rod 27 is articulated to at least one of its two ends by means of an open or closed ball joint 29.
The valve opening cam 15 has an angular position sensor of cam 30 which can be an encoder or any other type of angular sensor known to those skilled in the art (Figures 6, 7, 9 and 12).

The valve opening cam 15 cooperates with a cam stop, no shown, which limits the maximum angular position of said cam 15 when the valve 101 of the internal combustion engine 100 actuated by said cam 15 is closed.
The cam stop is mounted on a damper or comprises a damper limiting acoustic emissions when said valve opening cam comes in contact with the cam stop.
FIG. 5 shows an exemplary embodiment of the pump hydraulic volumetric 8 actuator electro-hydraulic valve actuator and cam alternative 1 according to the present invention.
The volumetric hydraulic pump 8 has several compartments 31 which 15 each constitute an autonomous pump comprising at least one inlet 32 and at least one output 33 connected to at least one actuator hydraulic cylinder of valve 2, said autonomous pumps being rotated by the same shaft 34 and being housed in the same housing 35.
FIGS. 10 and 11 show another embodiment of electro-hydraulic valve actuator with cylinder and reciprocating cam 1 according to the present invention.
The valve opening cam 15 has two hinges 36, 37 open or closed and a lever cam contact surface 38.
The first hinge 36 is integral with the internal combustion engine 100 while the second hinge 37 is connected to the actuator piston of valve 3 directly by a piston flap or indirectly by a rod of thrust 40.
The valve opening cam 15 can roll and / or slide on a surface of rocker switch 41 arranged on a rocker latch 42 hinged to one its ends around at least one latch anchor 43 secured to said motor 100, and provided at its other end with at least one pawl 44 that can push directly or indirectly on the tail 105 of at least a valve 101 of said motor 100 for opening said valve.

The two joints 36, 37 of the valve opening cam 15, the surface lever-action cam contact 38, the tilting contact surface 41 and the positioning of the latch anchor 43 and latch finger 44 being provided so as to provide the valve actuator piston 3 with a large arm of lever for opening the valve 101 of the internal combustion engine 100 when the latter is closed, said lever arm then becoming all the more low that the lifting height of said valve 101 is large.
Note that the pawl anchor 43 may consist of a device hydraulic valve known per se of clearance of said valve 101.
It can be seen that the shape of the valve opening cam 15, the shape of the contact surface 41 arranged on the rocker latch 42, the positioning of the integral articulation of the internal combustion engine 100 of said cam and the positioning of the pawl anchor 43 integral with said engine 100 are determined to favor the largest turnover component possible and the smallest sliding component possible to the point of contact between said cam 15 and said contact surface 41 when said valve 101 is operated in opening or closing.
The valve opening cam 15 has two articulations 36, 37 of which at least one of the two open or closed joints is a ball joint 45.
The push rod 40 is articulated at each of its ends by a bond ball joint, the first ball joint 46 being arranged in or at the end of the piston valve actuator 3 while the second link ball joint 47 is arranged in or on the valve opening cam 15.
In FIG. 8 it is shown that the valve opening cam 15 can be a wedge-shaped drawer 90 which can translate under the action of the jack hydraulic valve actuator 2 in a guide or slide 91 arranged in the cylinder head 104 of the internal combustion engine 100 so that the wedge shape of said drawer 90 creates a local variation of thickness which allows lift or remove from its seat the valve 101 of the combustion engine internal.

The guide or slide 91 of the valve opening cam 15 can be consisting of at least one roller 92 on which rolls the drawer shaped corner.
The wedge-shaped drawer 90 cooperates with a rocker latch 18 hinged to one of its ends around at least one integral latch anchor 43 said motor 100, and provided at its other end with at least one flap of latch 44 which can push directly or indirectly on the tail 105 that comprises a valve 101 of said motor 100 to open said valve.
Note that the pawl anchor 43 may consist of a device hydraulic valve known per se of clearance of said valve.
As shown in FIG. 13, the valve opening cam 15 can be consists of a cam finger 131 articulated by one of its ends around of an axis 133 and having at its other end a tangential surface of 132, said surface having a shape such that it radially exerts thrust relative to said axis 133 on a rocker rocker catch 18 when the cam finger 131 rotates about its said axis 133 under the action of hydraulic cylinder valve actuator 2.
According to this configuration, the latch 18 is itself articulated to one of its ends around at least one latch anchor 43 secured to the motor 100, while being provided at its other end with at least one flap 44 so as to be able to push directly or indirectly on the tail 105 that comprises the valve 101 of said motor to open said valve.
By observing FIG. 13, it will be noted that the mechanical transmission 1 connecting the cam finger 131 to the hydraulic cylinder valve actuator 2 can advantageously consists of a push rod 40 comprising each of its two ends 135, 136 a pivoting joint and / or ball joint, the first end 135 bearing on or in the piston actuator valve 3, while the second end 136 bears on the body of the cam finger 131.
Note also that the return spring 19 of the cam finger 13 can consist of at least one coil spring 134 which exerts a force antagonistic to that of the valve actuator piston 3, and which tends to distance from each other two swivel joints and / or ball joints 138, 139 guided relative to each other by at least one sliding connection 137, the first articulation 138 bearing directly or indirectly on the combustion engine internal 100 while the second articulation 139 is supported on the body of cam finger 131.
Also, and as a variant, the tangential lifting surface 132 can be finish by a stop 140 which can come into contact with the rocker catch at roller 18 so as to limit the angular displacement of the cam finger 131.
FIG. 12 shows another embodiment of the actuator of electro-hydraulic valve with cylinder and alternative cam 1 according to the present invention.
The valve opening cam 15 has a cam contact surface lever effect 38.
The valve opening cam 15 is rotated by means of least one rotation arm 48 whose one end is secured to the axis

25 of said cam 15 while its other end is articulated by means of a pivot connection or ball 49 with the first end of a push rod of arm 40.
The second end of said rod 40 is articulated by means of a link pivot or ball 47 with the valve actuator piston 3.
The valve opening cam 15 can roll and / or slide on a surface of rocker switch 41 arranged on a rocker latch 42 hinged to one its ends around at least one latch anchor 43 secured to the internal combustion engine 100, and provided at its other end with at least one tongue flap 44 which can push directly or indirectly on a tail 105 that includes at least one valve 101 of said motor 100 for open said valve 101.
The axis 25 of the valve opening cam 15, the cam contact surface with a lever effect 38, the tilting contact surface 41 and the positioning of anchor latch 43 and latch tab 44 are provided so as to to offer to the valve actuator piston 3 a large lever arm to open the valve 101 of the internal combustion engine 100 when the latter is closed, said lever arm then becoming all the weaker as the height of lifting of said valve 101 is large.

Note that according to a particular embodiment, the rotation arm 48 can rotating a plurality of valve opening cams 15.
It is also noted that the pawl anchor 43 may consist of a device 10 hydraulic known per se play catching said valve.
It is noted that the shape of the valve opening cam 15, the shape of the contact surface arranged on the rocker latch 42, the positioning of the integral articulation of the internal combustion engine of said cam and the 15 positioning of the anchor of the rocker integral with said engine are determined to favor the largest turnover component possible and the smallest sliding component possible to the point of contact between said cam and said surface when said valve is Maneuvered in opening or closing.
The valve actuator piston 3 moves in a cylinder 22 provided with a piston end damping light 50.
The damping light 50 is closed in whole or in part by said piston 3 when said piston 3 comes close to the position it has when the valve 101 of the internal combustion engine 100 that operates is closed.
Said damping light 50 braking said piston 3 by reduction progressive section of hydraulic fluid passage that is expelled except said hydraulic cylinder 2 when closing said valve 101.
The valve actuator piston 3 moves in a cylinder 22 provided with a piston limit stop which limits the depth introducing said piston 3 into said cylinder 22.
FIGS. 14 and 15 show an exemplary embodiment of the solenoid valve valve opening 4 and / or valve closing solenoid valve 6 and / or solenoid valve shutoff pump 13 of the valve actuator electro-hydraulic cylinder and alternative cam 1 according to the present invention.
The valve opening solenoid valve 4 and / or the closing solenoid valve valve 6 and / or the pump outlet shut-off solenoid valve 13 is a tube solenoid valve 60 consisting of at least one rectilinear tube 61 which can be moving in longitudinal translation in a valve housing 62 comprising an upper chamber 63 and a lower chamber 64.
The rectilinear tube 61 has a first end 65 opening into the upper chamber 63 and a second end 66 opening into the lower room 64.
The second end 66 of the rectilinear tube 61 can come into contact with minus a sealing surface 67 secured to said valve housing 62 so at to seal as tight as possible said second end.
The solenoid valve 60 comprises sealing means 68 between the surface external of the rectilinear tube 61 and the valve housing 62 which isolate the chamber upper 63 of the lower chamber 64.
The solenoid valve 60 comprises at least one closing spring 69 which tends to keep the rectilinear tube 61 in contact with the sealing surface 67.
The solenoid valve 60 comprises at least one electric actuator 70 able to apply to the rectilinear tube 61 an antagonistic effort to that product by the closing spring 69, said force being sufficient to lift off the tube rectilinear 61 of the shutter surface 67 when said actuator is through by an electric current.
The electric actuator 70 consists of a coil of conductive wire 71 which attracts a core or magnetic pallet 72 when said coil 71 is crossing by an electric current.
The core or magnetic pallet 72 of the electric actuator 70 can be housed in the upper chamber 63 of the valve housing 62.

The conductive wire coil 71 of the electric actuator 70 can be housed in the upper chamber 63 of the valve housing 62.
The conductive wire coil 71 of the electric actuator 70 can be housed at the outside of the upper chamber 63, the magnetic field generated by said coil 71 when traversed by an electric current passing through through of the outer wall of said chamber 63 so as to exert a force on the core or magnetic pallet 72.
The first end 65 of the rectilinear tube 61 may be integral with the core or magnetic pallet 72.
The core or magnetic pallet 72 can be made in the same room the rectilinear tube 61, or fixed on said core by gluing, screwing, crimping, or by any other means known to those skilled in the art.
The first end 65 of the rectilinear tube 61 has at least one orifice radial and / or axial 88 opening into the upper chamber 63.
The second end 66 of the rectilinear tube 61 is of troncospheric shape and has a line of contact with the sealing surface 67 similar to that made by a ball bearing on a seat.
The sealing surface 67 is arranged on an independent piece 73 float mounted in the valve housing 62, said part 73 being able to align with the rectilinear tube 61 when the second end 66 of said tube enters in contact with said sealing surface 67.
The valve housing 62 comprises directly, or indirectly via a plug intermediate 74, an orifice 75 vented which is closed by the room independent 73 on which is fitted the sealing surface 67 so that the force applied by the closing spring 69 via the rectilinear tube 61 sure said independent piece 73 and / or the force resulting from the prevailing pressure in the upper chamber 63 and / or the lower chamber 64 maintains said room 73 pressing said orifice 75 to keep it closed.

The contact surface between said independent part 73 and said housing of valve 62 can be provided with a seal, or with a ridge that increases locally the contact pressure so as to improve the seal between said part 73 and said casing 62.
The valve housing 62 is attached to the internal combustion engine 100 and has orifices and / or inlet-outlet ducts 89 relationship the upper chamber 63 and / or the lower chamber 64 is with the jack hydraulic valve actuator 2 either with hydraulic pump volumetric 8 via the incoming high pressure hydraulic circuit 5, the circuit outgoing high pressure 7 or the low pressure hydraulic circuit 9.
The section of the rectilinear tube 61 at the level of the seal that said tube constitutes with the valve housing 62 is slightly smaller than the section said tube at its contact with the sealing surface 67.
The sealing means 68 consist of the outer surface of the tube rectilinear 61 which cooperates with the internal one of the valve housing 62.
The sealing means 68 may also be constituted by the surface external of the rectilinear tube 61 which cooperates with the internal one of the housing of valve 62 in which can be accommodated at least one annular seal and / or at least one segment that can be advantageously replaced by a weak game a few microns left between the outer surface of the rectilinear tube 61 and the internal one of the valve housing 62.
On the rectilinear tube 61 may be arranged an adjustable stop or not which cooperates with an axial stopping surface provided directly or indirectly in the valve housing 62, said stopper determining the maximum distance enter said tube and the sealing surface 67 with which it cooperates.
Note that the valve housing 62 can accommodate several solenoid valves 60 as previously described.
FIG. 16 shows an exemplary embodiment of the pump of replenishment 52 of the electro-hydraulic cylinder actuator and alternative cam 1 according to the present invention.

The replenishing pump 52 comprises a piston of replenishment 54 that can perform back-and-forth movements in a blind cylinder 55 arranged in a blind cylinder housing 56 so as to define a variable volume within said cylinder.
The replenishing piston 54 cooperates with an inlet valve of replenishment 57 and a replenishment check valve 58, of which respectively the exit and the entrance open into said volume, said valve inlet 57 admitting hydraulic fluid from the tank of replenishment 53 while said outlet valve 58 expels said fluid in the compensation pressure accumulator 51 or in the accumulator Replenishment pressure 85.
The replenishing piston 54 is actuated in translation in a first sense by a solenoid electric actuator 80 mainly consisting of a magnetic replenishing core 81, a coil of conductive wire 82 and a magnetic resupply cage 83, and in a second direction by a spring 84 allowing the return of said piston of replenishment 54.
The blind cylinder housing 56 is made of the same metal part as the magnetic replenishment cage 83 of the electric actuator solenoid 80.
The blind cylinder housing 56 comprises a jacket 59 in which evolves the replenishing piston 54 of the replenishing pump 52.
The blind cylinder 55 has a delivery end-of-travel light 76 which connects said cylinder to the re-supply outlet valve 58 of kind that the replenishing piston 54 closes said light at the end of the race pressure and is braked and stopped in its delivery stroke.
It is noted that the maximum stroke of the replenishing piston 54 is limited in the direction of the discharge by a thrust block 77 and / or in the direction of suction by a suction stop 78.

The discharge stops 77 and suction 78 may consist of less a piece of elastic material with damping properties.
The magnetic replenishing core 81 is traversed by the piston of 5 Replenishment 54 on which it is rigidly mounted.
The replenishing piston 54 passes through the magnetic cage of replenishment 83 from one side to cooperate on one side of said cage with the blind cylinder 55 and on the other side of said cage with the spring of Recall 84 of said replenishing piston 54.
According to a first alternative to this arrangement, the piston of replenishment 54 can be attached to the replenishing core 81.
For this purpose, said replenishing core 81 includes means for connection with the return spring 84, the latter being rendered indirectly secured to said replenishing piston 54 so as to recall both said core and said spring.
As an alternative and as illustrated in FIGS. 17 to 20, the pump of replenishment 52 may comprise a tubular piston of replenishment 107 that can perform back and forth movements in an open cylinder 108 arranged in an open cylinder housing 109 which is integral directly or indirectly with a pump casing 126.
Thus, said piston 107, said cylinder 108 and said pump housing 126 define together a variable volume 110 inside said cylinder 108, said piston tubular replenishment 107 cooperating with an inlet valve of tubular piston 111 consisting of a ball 113 and a spring 114 ball resting on a seat 115 arranged at the end and inside of said piston 107 and an open cylinder outlet valve 112 consisting of a ball 116 and of a spring 117 said ball bearing on a seat 118 fitted at the end and outside said cylinder 109.
It is thus noted that said inlet valve 111 admits hydraulic fluid in from the replenishment tank 53 while the check valve outlet 112 expels said fluid into the pressure accumulator of compensation 51 or in the replenishing pressure accumulator 85.
According to a particular embodiment, the open cylinder casing 109 can comprise a hydraulic fluid conveyance duct 124 which connects directly or indirectly the tubular piston inlet valve 111 with a pump inlet port 125 that includes the pump housing 126.
It is also noted that the pump casing 126 comprises an outlet duct of hydraulic fluid 127 connecting directly or indirectly the valve of exit of an open cylinder 112 with a pump outlet port 128 that includes the pump casing 126.
According to the embodiment chosen, the tubular piston of replenishment 107 can be actuated in translation in a first direction by an actuator electric solenoid 119 mainly consisting of a magnetic core of replenishment 120 secured to said piston 107, a coil of wire conductor 121 and a magnetic resupply cage 122, and in a second direction by a return spring 123 of the tubular piston of replenishment 107.
According to this configuration, the magnetic replenishment core 120 may be provided with at least one core channel 129 indirectly connecting the hydraulic fluid conveyance duct 124 in the center of the tubular piston replenishment 107 via the tubular piston inlet valve 111, the open cylinder housing 109, said core 120 and said piston 111 being commonly housed inside a sealed socket 130 while said bushing 130 conveys the hydraulic fluid from the conduit 124 to the said channel 129.
The replenishing tank 53 is supplied with hydraulic fluid by the lubricating oil circuit of the internal combustion engine 100.
The replenishing tank 53 contains a hydraulic fluid specific and is independent of the lubricating oil circuit of the engine to internal combustion 100.

Said hydraulic fluid can be specially formulated so that the yield, the accuracy and durability of the electro-hydraulic valve actuator to cylinder and cam alternative 1 according to the invention are maximum, in particular thanks to a low viscosity of said fluid whatever the temperature of thermal engine operation, low compressibility, good lubricating and anti-wear characteristics or the absence of particles abrasive and corrosive or oxidizing agents.
Note that the valve actuator hydraulic cylinder 2 may comprise at least one drain, not shown, which recovers the leaking hydraulic fluid said cylinder, so that said fluid returns to the reservoir of replenishment 53 via at least one jack drain pipe.
It should be noted that the volumetric hydraulic pump 8 may comprise at least one drain, not shown, which recovers hydraulic fluid leaking from said pump, so that said fluid returns to the reservoir of replenishment 53 via at least one pump drain pipe.
The electro-hydraulic valve actuator with cylinder and reciprocating cam 1 according to the invention may comprise one or more purge valves placed on the hydraulic cylinder 2 and / or on the volumetric hydraulic pump 8 and / or at any point in the incoming high pressure hydraulic system 5 and / or of outgoing hydraulic high pressure circuit 7 and / or hydraulic circuit low pressure 9.
The at least one valve, not shown, may be of a type similar to those commonly used by those skilled in the art in any hydraulic application.
The electro-hydraulic valve actuator with cylinder and reciprocating cam 1 according to the invention may comprise at least one pressure accumulator of replenishment 85 which is interspersed between the pump replenishment 52 and the compensation pressure accumulator 51.
The replenishment pressure accumulator 85 can supply a plurality of compensation pressure accumulators 51 which supply respectively several independent circuits of valve actuators such as shown in Figures 2 and 3.

The replenishing pressure accumulator 85 supplies said compensation pressure accumulators 51 when the pressure in said circuits fall beyond a certain value.
The replenishing pressure accumulator 85 may be membrane, piston or any other type known to those skilled in the art.
The output of the replenishment pressure accumulator 85 comprises a locking valve ensuring the maintenance of the pressure in said accumulator when the internal combustion engine 100 is stopped.
The replenishing pressure accumulator 85 is connected to the compensation pressure accumulator 51 by a conduit comprising at least less a check valve 86 said valve allowing the hydraulic fluid to go from the replenishment accumulator 85 to the accumulator of compensation pressure 51 and not the opposite.
The high pressure valve opening pipe 11 comprises at least one pressure relief valve 87 positioned towards its nearest end of the volumetric hydraulic pump 8.
The pressure retaining valve 87 allows the hydraulic fluid to from said volumetric hydraulic pump 8 to enter said led but not out of it.
The pressure retaining valve 87 makes it possible in particular to avoid the depressurizing said circuit between two valve lifts 101 in order to limit acoustic emissions and increase the efficiency of the actuator according to the invention As a variant, the output of the volumetric hydraulic pump 8 comprises a check valve 141 of low pressure tank 10 positioned between said outlet and the pump outlet shut-off solenoid valve 13, said valve 141 allowing the hydraulic fluid to flow from the outlet of the hydraulic pump volumetric 8 to said low pressure tank 10, but not the opposite.

The actuator of electro-hydraulic valve with cylinder and reciprocating cam 1 can comprise at least one hydraulic circuit pressure limiter 146 placed in any point of the low-pressure hydraulic circuit 9 and / or the high pressure valve opening 11 and / or the high pressure conduit of valve closure 12, said limiter 146 allowing the hydraulic fluid contained in said circuit 9 and / or said ducts 11, 12 to return directly into the replenishing tank 53 when the pressure prevailing in said circuit 9 and / or said ducts 11, 12 exceeds a some value.
From the foregoing description, the operation of electro-hydraulic valve actuator with cylinder and reciprocating cam 1 according to the present invention.
In relation to FIG. 1 which illustrates the schematic diagram of a variant of the invention intended to control only one valve 101, and in relation with Figure 12 which proposes a particular embodiment, the operation of the actuator according to the invention is as follows:
The volumetric hydraulic pump 8 is constantly driven by the crankshaft 102 of the internal combustion engine 100.
When the valve 101 of the internal combustion engine 100 must remain closed, the valve opening solenoid valve 4 and the closing solenoid valve of valve 6 are closed while the outlet shutoff solenoid valve pump 13 is open and leaves the hydraulic fluid expelled at the outlet of the volumetric hydraulic pump 8 go to the low hydraulic circuit pressure 9, the latter supplying the input of said pump 8 in return fluid hydraulic with the same flow, via the pump inlet check valve 14.
The differential pressure between the inlet and the outlet of said pump 8 being low, the latter consumes little energy.
When the valve 101 of the internal combustion engine 100 must be Maneuvered in opening, the solenoid valve closing pump output 13 is closes and prevents the hydraulic fluid expelled at the pump outlet 8 volumetric hydraulics to return to the low hydraulic circuit pressure 9, so that said fluid is naturally forced into the conduit high valve opening pressure 11.
Once the shutoff solenoid valve pump output 13 closed, the pressure 5 at the output of 8 volumetric hydraulic pump rises rapidly and reaches the one that was previously stored in the high pressure duct valve opening 11 by the pressure retaining valve 87.
At approximately this time, the valve opening solenoid valve 4 opens so that the hydraulic fluid enters the hydraulic cylinder 10 valve actuator 2 and pushes on the valve actuator piston 3.
As illustrated in FIG. 12, while moving, the valve actuator piston pushes on the arm push rod 40, which pushes the rotation arm 48, which drives the valve opening cam 15 in rotation about Its axis 25. The rotation of said cam 15 results in the surface of lever-operated cam contact 38 provided on said cam 15 exerts a pressure on the tilting contact surface 41 fitted on the pawl 42. This has the effect of tilting said latch 42 which, in taking support on its latch anchor 43 secured to the internal combustion engine 20 100, pushes on the shank 105 of the valve 101 of said engine via its toucheau latch 44, which has the effect of opening said valve 101.
Note, in view of the arrangement illustrated in FIG. 12, that the axis 25 of the valve opening cam 15, the lever cam contact surface 38, the tilting contact surface 41 and the positioning of anchoring latch 43 and latch 44 are provided in such a way that they offer to the valve actuator piston 3 a large lever arm to open the valve 101 of the internal combustion engine 100 when the latter is closed, said lever arm then becoming all the weaker as the height 30 of lifting of said valve 101 is large.
This configuration makes it possible to accelerate progressively said valve 101 and to possibly decompress a combustion chamber 106 that includes the internal combustion engine 100, so that the pressure in said cylinder 35 in the incoming high pressure hydraulic circuit 5 and in the duct high valve opening pressure 11 increases gradually without risk or water hammer, or excitation in compression and / or decompression of the fluid hydraulics leading to instability of the angular position of the cam valve opening 15 and the longitudinal position of the valve 101 said engine.
FIG. 12 shows that the lift height of the valve 101 of the engine with internal combustion 100 can be deduced from the angular position of the cam valve opening 15 which is measured by the position sensor angle of cam 30. The measured value is returned to the calculator of management of the internal combustion engine 100.
When the desired lifting height for said valve 101 is reached, said computer opens the solenoid valve closing the pump outlet 13, this who stops the opening of said valve 101 because the hydraulic fluid expelled in output of the positive displacement hydraulic pump 8 is no longer forced into the duct high pressure valve opening 11 and so, is naturally heading towards the low pressure hydraulic system 9.
Almost simultaneously, the valve opening solenoid valve 4 closes which on the one hand, to stabilize the valve 101 in its position of set and on the other hand, to trap a certain amount of fluid hydraulic under pressure in the high pressure valve opening pipe 11 and in the incoming high pressure hydraulic circuit 5, the check valve in pressure 87 preventing said fluid from returning to the hydraulic pump volumetric 8.
It is noted that the entrapment of said fluid in said conduits by said valve can advantageously lead to lower acoustic emissions and / or better efficiency of the actuator according to the invention, in particular by reducing the volume of fluid that suddenly relaxes in the pressure accumulator of compensation 51.
Note that the valve 101 of the internal combustion engine 100 is kept open as long as the valve closing solenoid valve 6 is not opened by the computer. The opening time of the said valve 101 is determined by the objectives assigned to the control of the internal combustion engine 100, whether to improve performance in torque and power of said engine, to improve the energy efficiency, or to reduce polluting emissions.
To close said valve 101 at the desired time, the computer opens valve closing solenoid valve 6. This action has the effect of allow the hydraulic fluid contained in the actuator hydraulic cylinder of valve 2 to escape through the outgoing high pressure hydraulic circuit 7 then through the high pressure valve closing pipe 12 to be put into relationship with the inlet of the positive displacement hydraulic pump 8.
This action instantly increases the pressure at the inlet of said pump of so that said pressure becomes greater than that prevailing in the circuit low pressure hydraulic 9. This pressure difference closes the valve anti pump inlet return 14 so that the hydraulic fluid from the hydraulic actuator valve actuator 2 is forced to go through entry of said positive displacement hydraulic pump 8.
Rotated by the fluid expelled by the hydraulic cylinder actuator valve 2, said volumetric hydraulic pump 8 becomes a motor and returns to the crankshaft 102 of the internal combustion engine 100 a portion of the mechanical work that previously allowed to compress the fluid and the spring 103 of the valve 101 of said engine and tension the return spring 19 of the valve opening cam 15 and which has previously allowed to accelerate said valve, said spring, and all of the 16 mechanical and hydraulic transmission chain animated by a movement alternative of the actuator according to the invention.
Note that the valve closing solenoid valve 6 can be opened at one time, but also either proportionally or in several times.
These latter strategies of opening said solenoid valve may contribute to minimize the impact on the valve 101 of the internal combustion engine 100 when it lands on its seat, in addition to the effect of the sink variable produced by the mechanical transmission 16 and the transmission intermediate 17 as shown in FIG.
The proportional opening of said valve closing solenoid valve 6 may in particular be obtained by applying to the terminals of its coil 71 a modulated current in pulse width, this method being also known under the acronym PWM (Pulse Width Modulation). Piloting said solenoid valve is entrusted to the computer which cooperates with the sensor of cam angular position 30 and / or the angular encoder of the crankshaft 102 of the internal combustion engine 100 to control the speed of said valve 101, especially when landing on his seat.
It can be seen that the total volume of the hydraulic circuit of the actuator 1 varies in function of the position of the valve actuator piston 3 in its cylinder 22.
This variation in volume is absorbed by the pressure accumulator of compensation 51 that keeps the pressure of the hydraulic circuit low pressure 9 between two values, a minimum and a maximum.
Said minimum pressure value is sufficient on the one hand, to allow the actuator 1 according to the invention to operate without cavitation phenomenon said phenomenon being deemed destructive, and secondly, to minimize the possible position instabilities of the valve 101 of the combustion engine internal 100 induced by the compressibility of the hydraulic fluid. In all state of cause, the maximum pressure value must not exceed that which allows to the valve actuator piston 3 to take off the valve 101 from the engine to internal combustion 100 of its seat.
Note that if the minimum pressure value of the low hydraulic circuit pressure 9 falls below a certain threshold ¨ said value being monitored by a calculator by means of a pressure sensor placed at a point any of the low pressure hydraulic circuit 9 - the pump replenishment 52 replenishes the pressure accumulator of compensation 51 in hydraulic fluid by sucking said fluid into the tank 53 and repressing said fluid in said accumulator.
In FIGS. 2 and 3, it can be seen that when the actuator 1 according to the invention provides several parallel circuits each supplying several valves 101 or groups of valves not opening at the same time but belonging to the same internal combustion engine 100, a pressure accumulator of replenishment 85 can advantageously be inserted between the pump replenishment 52 and compensation pressure accumulators 51 that comprises each of said parallel circuits. In this case, only one replenishment pressure accumulator 85 supplies fluid hydraulic compensation pressure accumulator 51 that features each low pressure hydraulic circuit 9 via the non-return valve of replenishment 86 that includes each of said hydraulic circuits low pressure.
According to this configuration, it is the minimum value of the pressure that prevails in the replenishment pressure accumulator 85 which is monitored by the calculator by means of a pressure sensor, the minimum value of the pressure that prevails in each of the low pressure hydraulic circuits 9 being automatically maintained at the desired value by their check valve return of replenishment 86.
It must also be understood that the foregoing description has not been given has example and that in no way limits the scope of the invention of which we would not come out by replacing the execution details described by any other equivalent.

Claims (65)

1. Reciprocating cylinder and cam electro-hydraulic valve actuator for internal combustion engine (100), characterized in that it comprises:
.cndot. at least one valve actuator hydraulic cylinder (2) which includes at least one valve actuator piston (3) which opens at least one valve (101) of an internal combustion engine (100) or compressor with piston(s) when said cylinder (2) is connected by a solenoid valve valve opening (4) with at least one high hydraulic circuit incoming pressure (5), said cylinder (2) closing said valve (101) when it East connected by a valve closing solenoid valve (6) with at minus an outgoing high pressure circuit (7), and said cylinder (2) ensuring the maintaining said valve (101) open when it is not connected neither with the incoming high pressure circuit (5), nor with the high circuit pressure outgoing (7);
.cndot. at least one volumetric hydraulic pump (8) comprising at least an outlet connected to a low pressure hydraulic circuit (9) connected to at least a low pressure tank (10) and at least one inlet connected to said circuit low pressure hydraulic (9), said pump (8) rotating at a speed proportional to that of a crankshaft (102) of the combustion engine internal (100);
.cndot. at least one high pressure valve opening conduit (11) connecting the output of the positive displacement hydraulic pump (8) with the hydraulic circuit high pressure incoming (5) from hydraulic cylinder valve actuator (2);
.cndot. at least one high pressure valve closing conduit (12) connecting the inlet of the positive displacement hydraulic pump (8) with the hydraulic circuit high pressure exiting (7) from the valve actuator hydraulic cylinder (2);
.cndot. at least one pump outlet shutter solenoid valve (13) which can prevent hydraulic fluid being expelled at the outlet of the hydraulic pump volumetric (8) to return to the low pressure hydraulic circuit (9), so that said fluid is forced into the high pressure conduit opening valve (11);
.cndot. at least one pump inlet check valve (14) which prevents to fluid hydraulic from the valve actuator hydraulic cylinder (2) via the high pressure conduit closing valve (12) to return directly into the low pressure hydraulic circuit (9), so that said fluid is forced to the inlet of the volumetric hydraulic pump (8), but said valve (14) allowing said pump (8) to suck up said contained fluid in the low pressure hydraulic circuit (9), when the pressure of this last is greater than the pressure prevailing in the high pressure conduit valve closing (12);
.cndot. at least one valve opening cam (15) connected on the one hand to the jack hydraulic valve actuator (2) via mechanical transmission (16), and on the other hand to the valve (101) of the internal combustion engine (100) directly or via an intermediate transmission (17), said cam (15) moving in one direction during maneuvers opening of said valve (101), then in the opposite direction during closing operations of said valve (101);
.cndot. at least one return spring (19) of the opening cam valve (15) which tends to return said cam (15) to the position it has when the valve (101) of the internal combustion engine (100) is closed; 2. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 1, characterized in that the hydraulic cylinder actuator of valve (2) is rotatable and the valve actuator piston (3) has a shape in pallet, said piston (3) separating at least one high pressure chamber (20) of at least one low pressure chamber (21) so that the pressure of the fluid hydraulic can cause said piston (3) to rotate, the latter being connected in rotation directly or indirectly to the valve opening cam (15). 3. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 1, characterized in that the valve actuator piston (3) moves in a cylinder (22) and pushes on an opening rack of valve (23) guided in a cylinder head (104) which comprises the engine internal combustion (100) or the piston compressor(s), said rack (23) cooperating with a pinion (24) arranged around an axis (25) of the cam valve opening (15) so as to drive said cam (15) in rotation when said piston (3) moves in longitudinal translation. 4. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 3, characterized in that the opening rack of valve (23) is guided in the cylinder head (104) of the internal combustion engine (100) by means of at least one ball or roller bearing (26). 5. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 1, characterized in that the valve actuator piston (3) moves in a cylinder (22) and pushes a valve opening rod (27) with one of the ends of which it is articulated, said rod (27) pushing in turn on a cam arm (28) which comprises directly or indirectly the valve opening cam (15) with which the other end of said rod (27) is also articulated so as to drive said cam (15) in rotation when said piston (3) moves in translation longitudinal. 6. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 5, characterized in that the valve opening rod (27) is articulated at at least one of its two ends by means of a ball joint open or closed (29). 7. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 1, characterized in that the volumetric hydraulic pump (8) has several compartments (31) which each constitute a pump autonomous comprising at least one input (32) and at least one output (33) connected to at least one hydraulic valve actuator cylinder (2), said autonomous pumps being driven in rotation by the same shaft (34) and being housed in the same casing (35). 8. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 1, characterized in that the valve (101) of the motor internal combustion (100) includes a position sensor. 9. Reciprocating cylinder and cam electro-hydraulic valve actuator following claim 1, characterized in that the valve opening cam (15) includes a cam angular position sensor (30). 10. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the valve opening cam (15) cooperates with a cam stop which limits the maximum angular position of said cam (15) when the valve (101) of the internal combustion engine (100) actuated by said cam (15) is closed. 11.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 10, characterized in that the cam stop is mounted on a damper or includes a damper limiting acoustic emissions when said cam (15) comes into contact with the cam stop. 12. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the valve opening cam (15) comprises two joints (36, 37) open or closed and a surface lever cam contact (38), the first articulation (36) being integral with the internal combustion engine (100) while the second joint (37) is connected to the valve actuator piston (3) directly by a piston key or indirectly by a push rod (40) and said cam (15) capable of rolling and/or sliding on a rocker contact surface (41) arranged on a tilting latch (42) articulated at one of its ends around at least one latch anchor (43) secured to said motor (100), and provided at its other end with at least one latch button (44) which can push directly or indirectly on a tail (105) of at least one valve (101) of said engine (100) to open said valve (101). 13. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 12, characterized in that at least one of the two joints (36, 37) open or closed is a ball joint. 14.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 12, characterized in that the push rod (40) is articulated at each of its ends by a ball joint, the first connection ball joint (46) being arranged in or at the end of the actuator piston valve (3) while the second ball joint (47) is arranged in or on the valve opening cam (15). 15.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the valve opening cam (15) has a lever cam contact surface (38) and is driven in rotation by means of at least one rotation arm (48), one of which of the ends is integral with the axis (25) of said cam (15) while its other end is articulated by means of a pivot or ball joint (49) with there first end of an arm push rod (40), the second end of said rod (40) being articulated by means of a pivot or ball joint (47) with the valve actuator piston (3) and said cam (15) being able to roll and/or slide on a rocker contact surface (41) arranged on a tilting latch (42) articulated at one of its ends around at least one latch anchor (43) secured to the internal combustion engine (100), and muni at its other end of at least one latch button (44) which can push directly or indirectly on a tail (105) which includes at least one valve (101) of said engine (100) to open said valve (101). 16.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the valve actuator piston (3) moves in a cylinder (22) provided with an end-of-life damping light piston stroke (50), said opening being blocked in whole or in part by said piston (3) when said piston arrives in the vicinity of the position it has when the valve (101) of the internal combustion engine (100) which it operates is closed. 17.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the valve actuator piston (3) moves in a cylinder (22) provided with a piston end stop the latter limiting the depth of insertion of said piston (3) into said cylinder (22). 18. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the low pressure tank (10) is consisting of at least one compensation pressure accumulator (51) maintained under pressure by at least one replenishment pump (52) which supplies said accumulator with hydraulic fluid by sucking said fluid in at least one replenishment tank (53). 19. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the opening solenoid valve valve (4) and/or the valve closing solenoid valve (6) and/or the pump outlet shutter solenoid valve (13) is a solenoid valve tube (60) consisting of at least one rectilinear tube (61) capable of moving in longitudinal translation in a valve housing (62) comprising a chamber upper (63) and a lower chamber (64), said rectilinear tube (61) comprising a first end (65) opening into the chamber upper (63) and a second end (66) opening into the chamber lower end (64), said second end (66) being able to come into contact with at least one closing surface (67) integral with said valve housing (62) of so as to seal said second end as tightly as possible (66). 20. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the tube solenoid valve (60) comprises sealing means (68) between the external surface of the tube rectilinear (61) and the valve housing (62) which isolate the upper chamber (63) of the lower chamber (64). 21. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the tube solenoid valve (60) comprises at least one closing spring (69) which tends to maintain the tube rectilinear (61) in contact with the closing surface (67). 22. Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 19 and 21, characterized in that the tube solenoid valve (60) comprises at least one electric actuator (70) capable of applying to the tube rectilinear (61) a force antagonistic to that produced by the spring shutter (69), said force being sufficient to separate the rectilinear tube (61) from the surface shutter (67) when said actuator is crossed by a current electric. 23. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 22, characterized in that the electric actuator (70) is consisting of a coil of conductive wire (71) which attracts a core or paddle magnetic (72) when said coil is crossed by an electric current. 24. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 23, characterized in that the magnetic core or palette (72) is housed in the upper room (63). 25. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 23, characterized in that the coil of conductive wire (71) East housed in the upper room (63). 26.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 23, characterized in that the coil of conductive wire (71) East housed outside the upper chamber (63), the magnetic field generated by said coil when it is crossed by an electric current passing At through the external wall of said chamber so as to exert a force on THE
magnetic core or palette (72). 27. Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 19 and 23, characterized in that the first end (65) of the rectilinear tube (61) is integral with the core or magnetic palette (72). 28.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the first end (65) of the tube rectilinear (61) has at least one radial and/or axial orifice (88) opening in the upper room (63). 29.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the second end (66) of the tube rectilinear (61) is fruscospherical and has a line of contact with the closing surface (67) similar to that produced by a ball bearing on A
seat. 30.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the closing surface (67) is arranged on an independent part (73) mounted floating in the crankcase valve (62), said part being able to align with the straight tube (61) when the second end (66) of said tube comes into contact with said surface. 31. Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 19, 21 and 30, characterized in that the valve housing (62) comprises directly, or indirectly via an intermediate plug (74), a orifice (75) exposed to the open air which is closed by the independent part (73) on on which the sealing surface (67) is arranged. 32. Electro-hydraulic cylinder and reciprocating cam valve actuator following of claims 1 and 19, characterized in that the valve housing (62) is fixed to the internal combustion engine (100) and has orifices and/or input-output conduits (89) connecting the upper chamber (63) and/or the lower chamber (64) either with the hydraulic cylinder actuator valve (2) or with the positive displacement hydraulic pump (8) via the circuit high pressure hydraulic incoming (5), the high pressure outgoing circuit (7) Or the low pressure hydraulic circuit (9). 33. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the section of the rectilinear tube (61) At level of sealing that said tube constitutes with the valve housing (62) East slightly smaller than the section of said tube at the level of its contact with the closing surface (67). 34. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 20, characterized in that the sealing means (68) are constituted by the external surface of the rectilinear tube (61) which cooperates with that internal part of the valve housing (62). 35. Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that a stop (79) adjustable or not is arranged on the rectilinear tube (61) which cooperates with a stopping surface axial (93) arranged directly or indirectly in the valve housing (62), said stop determining the maximum distance between said tube and the surface shutter (67) with which it cooperates. 36.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 19, characterized in that the valve housing (62) can accommodate several tube solenoid valves (60). 37.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 18, characterized in that the replenishment pump (52) includes a replenishment piston (54) which can perform back and forth movements in a blind cylinder (55) arranged in a blind cylinder housing (56) so as to define a variable volume at the interior of said cylinder, said replenishment piston (54) also cooperating with a replenishment inlet valve (57) and a replenishment outlet valve replenishment (58), whose exit and entry respectively lead to in said volume, said inlet valve (57) admitting hydraulic fluid in coming from the replenishment tank (53) while said valve outlet (58) expels said fluid into the pressure accumulator of compensation (51) or in the pressure accumulator restocking (85). 38.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 37, characterized in that the replenishment piston (54) is actuated in translation in a first direction by an actuator electric solenoid (80) mainly consisting of a magnetic core of replenishment (81), a spool of conductive wire (82) and a cage magnetic replenishment (83), and in a second direction by a return spring (84) of the replenishment piston (54). 39.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 37 and 38, characterized in that the cylinder housing one-eyed (56) is made in the same metal part as the magnetic cage of restocking (83). 40.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 37, characterized in that the blind cylinder housing (56) comprises a jacket (59) in which the piston of restocking (54). 41.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 37 and 38, characterized in that the blind cylinder (55) comprises a discharge end-of-stroke light (76) which connects said cylinder to the replenishment outlet valve (58) so that the piston replenishment (54) closes said port at the end of the travel pushback and is braked then stopped in its pushback stroke. 42.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 37, characterized in that the maximum stroke of the piston of resupply (54) is limited in the direction of delivery by a delivery stop (77) and/or in the direction of suction by a stop suction (78). 43.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 37 and 38, characterized in that the magnetic core of replenishment (81) is crossed by the replenishment piston (54) on which it is rigidly mounted, said piston passing through the cage magnetic replenishment (83) from side to side to cooperate in a side of said cage with the blind cylinder (55) and on the other side of said cage with the return spring (84) of said piston (54). 44.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 18, characterized in that the replenishment pump (52) includes a tubular replenishment piston (107) which can reciprocating in an open cylinder (108) arranged in an open cylinder housing (109) which forms a direct body or indirectly with a pump housing (126) so that said piston (107), said cylinder (108) and said pump housing (126) define together a variable volume (110) inside said cylinder (108), said piston tubular replenishment (107) cooperating with a piston inlet valve tubular (111) consisting of a ball (113) and a spring (114) said ball resting on a seat (115) arranged at the end and inside said piston (107) and an open cylinder outlet valve (112) consisting of a ball (116) and a spring (117) said ball bearing on a seat (118) arranged at the end and outside of said cylinder (109), said inlet valve (111) admitting hydraulic fluid from the replenishment tank (53) while said outlet valve (112) expels said fluid into the accumulator compensation pressure (51) or in the compensation pressure accumulator restocking (85). 45.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 44, characterized in that the open cylinder housing (109) comprises a hydraulic fluid delivery conduit (124) connecting directly or indirectly the tubular piston inlet valve (111) with a pump inlet port (125) provided in the pump housing (126). 46.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 44, characterized in that the pump housing (126) comprises a hydraulic fluid outlet conduit (127) connecting directly or indirectly the open cylinder outlet valve (112) with a orifice pump outlet (128) contained in the pump housing (126). 47.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 44, characterized in that the tubular piston of replenishment (107) is actuated in translation in a first direction by an electric solenoid actuator (119) mainly consisting of a magnetic replenishment core (120) secured to said piston (107), a coil of conductive wire (121) and a magnetic cage of replenishment (122), and in a second direction by a return spring (123) of the tubular replenishment piston (107). 48.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 47, characterized in that the magnetic core of replenishment (120) is provided with at least one core channel (129) indirectly connecting the hydraulic fluid delivery conduit (124) to the center of the tubular replenishment piston (107) via the inlet valve tubular piston (111), the open cylinder housing (109), said core (120) and said piston (111) being commonly housed inside a sealed socket (130) while said socket (130) routes hydraulic fluid from the conduit (124) to said channel (129). 49.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 1 and 18, characterized in that the reservoir replenishment (53) is supplied with hydraulic fluid by the circuit lubricating oil of the internal combustion engine (100). 50.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 1 and 18, characterized in that the reservoir replenishment (53) contains a specific hydraulic fluid and is independent of the lubricating oil circuit of the internal combustion engine (100). 51.Electro-hydraulic valve actuator with cylinder and reciprocating cam following claims 1 and 18, characterized in that the hydraulic cylinder valve actuator (2) has at least one drain which collects the fluid hydraulic leaking from said cylinder, so that said fluid returns into the replenishment tank (53) via at least one drainage conduit cylinder. 52. Electro-hydraulic valve actuator with cylinder and reciprocating cam following claims 1 and 18, characterized in that the hydraulic pump volumetric (8) comprises at least one drain which recovers the hydraulic fluid leaking from said pump, so that said fluid returns to the reservoir of replenishment (53) via at least one pump drain conduit. 53.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that it comprises one or more taps bleed valves placed on the valve actuator hydraulic cylinder (2) and/or on there volumetric hydraulic pump (8) and/or at any point in the circuit incoming high pressure hydraulic system (5) and/or the high hydraulic circuit outgoing pressure (7) and/or the low pressure hydraulic circuit (9). 54.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 1, characterized in that the valve opening cam (15) is a wedge-shaped drawer (90) which can translate under the action of the jack hydraulic valve actuator (2) in a guide or slide (91) arranged in the cylinder head (104) of the internal combustion engine (100) so that the corner shape of said drawer (90) creates a local variation in thickness Who allows the valve (101) of the engine to be lifted or removed from its seat internal combustion (100). 55. Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 54, characterized in that the guide or slide (91) comprises at least one roller (92) on which the wedge-shaped drawer (90) rolls. 56.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 54, characterized in that the wedge-shaped drawer (90) cooperates with a roller tilting latch (18) articulated to one of its ends around at least one latch anchor (43) secured to the motor (100), and provided at its other end with at least one latch button (44) Who can push directly or indirectly on the tail (105) that the valve (101) of said engine to open said valve. 57.Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 1, characterized in that the valve opening cam (15) consists of a cam finger (131) articulated by one of its ends around an axis (133) and comprising at its other end a surface tangential lift (132), said surface having a shape such that it exercises radially a thrust relative to said axis (133) on a tilting latch roller (18) when the cam finger (131) rotates around its said axis (133) under the action of the hydraulic cylinder valve actuator (2) and the latch (18) being itself articulated at one of its ends around at least one anchoring latch (43) secured to the motor (100), and being provided at its other end at least one latch button (44) so as to be able to push directly or indirectly on a tail (105) which the valve (101) of said motor in order to open said valve. 58.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 1 and 57, characterized in that the mechanical transmission (16) connecting the cam finger (131) to the valve actuator hydraulic cylinder (2) consists of a push rod (40) comprising at each of its two ends (135, 136) a pivoting and/or ball joint, the first end (135) bearing on or in the valve actuator piston (3), while the second end (136) rests on the body of the finger at cam (131). 59.Electro-hydraulic cylinder and reciprocating cam valve actuator following claims 1 and 57, characterized in that the return spring (19) of the cam finger (131) consists of at least one helical spring (134) which exerts a force antagonistic to that of the valve actuator piston (3), and Who tends to move two pivoting and/or ball joints away from each other (138, 139) guided relative to each other by at least one slide connection (137), the first articulation (138) bearing directly or not on the internal combustion engine (100) while the second joint (139) bears on the body of the cam finger (131). 60.Electro-hydraulic cylinder and reciprocating cam valve actuator following claim 57, characterized in that the tangential lifting surface (132) ends in a stop (140) which can come into contact with the latch roller rocker (18) so as to limit the angular movement of the finger has cam (131). 61.Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 18, characterized in that at least one accumulator replenishment pressure (85) is interposed between the replenishment pump replenishment (52) and the compensation pressure accumulator (51). 62. Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 61, characterized in that the output of the accumulator replenishment pressure (85) has a locking valve. 63.Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 61, characterized in that the pressure accumulator replenishment (85) is connected to the pressure accumulator of compensation (51) by a conduit comprising at least one non-return valve (86), said valve allowing hydraulic fluid to go from the accumulator replenishment pressure (85) to the replenishment pressure accumulator compensation (51) and not the other way around. 64.Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 1, characterized in that the high pressure conduit opening (11) comprises at least one pressure maintaining valve (87) positioned towards its end closest to the hydraulic pump volumetric (8), said valve allowing the hydraulic fluid coming from of said pump to enter said conduit, but not to come out. 65.Electro-hydraulic valve actuator with cylinder and reciprocating cam following claim 1, characterized in that the output of the hydraulic pump volumetric (8) includes a low tank non-return valve (141) pressure (10) positioned between said outlet and the shutter solenoid valve pump outlet (13), said valve (141) allowing the hydraulic fluid to go of the output of the volumetric hydraulic pump (8) to said low reservoir pressure (10), but not the opposite.