MXPA01002263A

MXPA01002263A - Hydraulically-assisted engine valve actuator

Info

Publication number: MXPA01002263A
Application number: MXPA/A/2001/002263A
Authority: MX
Inventors: De Ojeda William; K Das Pranab
Original assignee: International Truck And Engine Corporation
Priority date: 2000-03-02
Filing date: 2001-03-02
Publication date: 2002-07-25

Abstract

A hydraulically-assisted engine valve actuator for assisting in the actuation of an engine valve, includes a servo piston being operably coupled to the engine valve. A translatable pilot valve is in fluid communication with the servo piston andthe main piston and is operably coupled to and controlled by a pilot valve positioning system. The pilot valve positioning system controls a translational stroke of the pilot valve to meter hydraulic fluid under pressure to and from the servo piston. A stroke magnifier magnifies a stroke of the pilot valve positioning system.

Description

ENGINE VALVE ACTIVATOR ASSISTED BY HYDRAULIC ENVIRONMENT Related Requests The present application is a continuation request in part of the United States Patent Application Serial No. 09 / 152,497, filed September 9, 1998. The present application also claims the benefit of the provisional application of the United States. No. 60 / 172,984, filed on December 20, 1999 and incorporated herein by reference in its entirety.

Technical Field The present invention relates to internal combustion engines. More specifically, the present invention relates to the operation of a motor valve.

BACKGROUND OF THE INVENTION It is desirable that an engine valve actuator aided by hydraulic means provide flexible operation of the engine valve under a wide band of operating conditions of the engine. The motor valve actuator aided by hydraulic means provides JU • ,.

Variable valve timing of closing and opening and variable elevation as desired to obtain greater engine efficiencies. Currently, hydraulic fluid is supplied to hydraulically operated valves through tubes normally referred to as channels. The valve movement profiles in the current hydraulic operation designs depend on a preset constant value of the oil pressure in the supply channels because the channel pressures can not be adjusted too fast to modulate the valve profiles . The constant values of the channel pressure lead to constant valve profiles regardless of the engine rpm. The current hydraulic performance schemes add complexity to the design of the engine. Some hydraulic performance designs rely on additional hydraulic supply channels at constant pressure levels. In addition, the hydraulic performance that depends on the on / off operations of the solenoid valve (spool or rod) require motor valve position detectors for reliable timing of the solenoids and for safe operation. The plurality of detectors needed, in addition adds complexity to the engine. There is a need to provide such performance of J _, _ valve to do all this in as economical a way as possible. A linear motor provides an excellent source of control performance for the valve actuator. However, a linear motor is considerably more expensive than a solenoid. A solenoid should be used if its limitations may be adequate. The actuator of the valve must show simplicity of module. There should be no double dependencies to minimize the criticality of certain machining tolerances. The concentricity requirements of the device should be as lenient as possible. The valve actuator must easily adjust the valve clearance ends that occur in a diesel cycle engine. It is not strange that in a few minutes after starting a motor cooled valve grows 0.020 inches due to the increase in temperature of the valve. It is useful if the valve control module is not directly coupled to the engine valve so that it is not necessary to design complexities in the control module to take into account the valve clearance.

SUMMARY OF THE INVENTION The motor valve actuator aided by the hydraulic means of the present invention allows flexible operation of the engine valve: variable valve timing of opening and closing and variable elevation of the valve. In addition, the mechanical components necessary to effect the hydraulic operation are relatively simple, minimizing by this means the additional motor components, necessary. No detectors or mechanical damping mechanisms are needed. In addition, the hydraulic performance of the present invention is designed to provide uniform performance over a wide range of temperatures and viscosities of the hydraulic fluid. The aforementioned advantages of the present invention are effected by the use of a fine needle control. Fine needle control provide modulation of engine valve profiles: variation of engine profiles at different engine speeds, variation in the shape of the profiles at a certain rpm. The present invention also allows aggressive valve openings and closures that result in better volumetric efficiency of the engine.

The hydraulic-assisted motor valve actuator of the present invention is not sensitive to pressure variations in the high-pressure channel, that is, the modulation of the movement of the motor valve is capable of tolerating a substantial variation of the pressure (above a predetermined threshold pressure) 5 in the high pressure channel. The device of the present invention only requires a high pressure supply line. The low pressure line in one embodiment of the present invention is shared by the existing lubricant oil supply already available. In the case of engines with a fuel injection system that incorporates a high-pressure channel for the performance of the fuel injector, the same supply of high-pressure liquid is used for the actuation of the valve in order to also minimize the components added to the engine. In the case of the present invention, the output is That is to say, the position of the valve of the motor follows very closely the input of the hydraulic actuator. By Thus, the device of the present invention does not require the additional complexity of requiring a detector to measure the position of the motor valve for a feedback control. The exact control of the valve seat is achieved by exact control of the needle at the end of the piston stroke.

The present invention also offers very good operating performance at cold temperature despite the fact that the hydraulic acting liquid is preferably lubricating oil. The proportional flow areas of the hydraulic fluid passages are not so small as to compromise operation under variable operating temperatures. This is especially important in cold temperature operation since the viscosity of the hydraulic fluid, particularly the lubricating oil, is significantly higher when the engine is cold after the engine has warmed up. In one embodiment, the present invention incorporates a main needle and piston that are decoupled from the engine valve. A secondary piston is coupled to the engine valve to provide actuation of the engine valve. The hydraulic coupling between the secondary piston and the main piston is automatically adjusted to suit the motor gap. In addition, the main piston stroke acts as an amplifier of the length of the piston stroke allowing the use of a solenoid controller. The linear stroke of a solenoid is limited to approximately 4 mm. A common motor valve requires an opening stroke of approximately 12 mm. In one embodiment, a 3: 1 ratio between the main piston and • - & ••; The secondary piston provides a three times effective increase in the stroke of the solenoid piston to effect the full opening stroke of the engine valve. In addition, the mechanical components required for valve actuation by the present invention do not significantly increase engine complexity, i.e., only some modifications to an existing cylinder head are necessary in order to incorporate the valve actuator module. of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a side elevational view in section of the motor valve actuator aided by hydraulic means of the present invention coupled to a motor valve; Figures 2a-2b depict the opening cycle of the valve. Specifically, Figure 2a is a side elevational view in section of the valve actuator with the actuator and the valve in the retractable, closed configuration; Figure 2b is a side elevational view in section of the valve actuator with the actuator needle beginning translation to the right and the valve in the retractable, closed configuration; Figure 2c is a side elevational view in section of the valve actuator with the actuator needle in a position to the right of the valve approaching the open extended configuration; Figure 2b is a side elevational view of the valve actuator with the needle of the actuator and valve stopped in the open, extended configuration; Figures 3a-3b depict a valve closing cycle. Specifically, Figure 3a is a side elevational view in section of the valve accouter with the needle of the actuator and the valve in the extended, open configuration. Figure 3b is a side elevational view of the valve actuator with the actuator needle and the valve in open, extended configuration, the actuator needle having moved to the left exposing the extension chamber to the hydraulic fluid at low pressure; Figure 3c is a sectional elevation side view of the valve actuator with the valve in transition between the extended open configuration and the retractable, closed configuration, the actuator needle having moved to the left exposing the extension chamber to the hydraulic fluid at low pressure. Figure 3b is a side elevational view in section of the valve actuator with the needle of the actuator and the valve in the retractable, closed configuration; Figures 4a-4b depict some actuators and valve parameters as a function of time, the valve being actuated or the actuator of the valve of the present invention. Specifically, Figure 4a is a graph of the actuator and the displacement of the valve over time; Figure 4b is a graph of the flow of hydraulic fluid at high pressure to the actuator over time; Figure 4c is a graph of the force on the actuator piston and the spring force of the valve over time; Figure 4d is a graph of the pressure of the actuator in the chambers of the extender and the retractor over time; Figures 5a-5b are hydraulic diagrams showing the opening cycle of the valve and the closing cycle of the valve in sequence. Specifically, Figure 5a is a sectional elevation side view of the valve actuator with the actuator and the valve in the retractable configuration, closed just prior to the downward stroke of the valve; Figure 5b is a side elevational view in section of the valve actuator with the actuator needle starting translation down and the valve in the retractable, closed configuration; Figure 5c is a side elevational view in section of the valve actuator with the actuator needle in a downward position and the valve approaching the extended, open configuration; Figure 5d is a side elevational view in section of the valve actuator with the needle of the actuator and the valve stopped in the open, extended configuration; Figure 5e is a side elevational view in section of the valve actuator with the actuator needle starting the upward retraction and the valve in the open, extended configuration; Figure 5f is a side elevational view of the valve actuator with the actuator needle and the valve in the extended, open configuration, the actuator needle having been retracted upwardly exposing the extension chamber to the hydraulic fluid at low pressure and the valve in the closed, retractable configuration; Figure 6 is a sectional view of one embodiment of a valve actuator; Figure 7a is a sectional view of a mode of the valve actuator of Figure 6 in the closed position of the engine valve; Figure 7b is a sectional view of a mode of the valve actuator of Figure 6 in the open position in the engine valve stroke; Figure 7c is a sectional view of a mode of the valve actuator of Figure 6 in the closed position of the engine valve stroke; Figure 7d is a sectional view of a mode of the valve actuator of Figure 6 in the valve clearance position of the valve; Figure 8 is a perspective view of 6 valve actuators of the present invention assembled for mounting on a 6-cylinder in-line engine; Figure 9 is a perspective view of a valve actuator of the present invention; Figure 10 is a plan view of the valve actuator of Figure 9; Figure 11 is a view of an elevation cut taken along line A-A of Figure 10; Figure 12 is an elevation view of a section taken along line B-B of Figure 10; Figure 13 is a first exploded view of the valve actuator of Figure 9; Figure 14 is a second exploded view of the valve actuator of Figure 9; Figure 15a is an elevation view of a cut taken a. along line 15a-15a of Figure 13 depicting the engine valve in the closed position; Figure 15b is a mirror image of a sectional view, in elevation taken along the line 15b-15b of Figure 13, showing the engine valve in the closed position; Figure 16a is the cross-sectional view of Figure 15a with the engine valve in the opening stroke; Figure 16b is a cross-sectional view of Figure 15b with the engine valve shown in the opening stroke of the valve; Figure 17a is a sectional view of Figure 15a with the engine valve in the closing stroke; Figure 17b is a cross-sectional view of Figure 15b with the engine valve in the closing stroke; Figure 18a is the cross-sectional view of Figure 15a during the adjustment of the valve; and Figure 18b is the cross-sectional view of claim 15b during clearance adjustment.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT The hydraulically assisted motor valve actuator of the present invention is shown generally at 10 in Figures I-5f. In Figure 1, the actuator 10 is shown coupled to a motor head 12. The motor head 12 has a valve 14 located so that it can be moved therein. The valve 14 opens and closes an intake / exhaust passage 16. The intake / exhaust passage 16 is an intake passage or an exhaust passage depending on whether the valve 14 is an intake valve or an exhaust valve. For the purposes of the present invention shown in Figures 1 - 5f, the valve 14 can be an intake valve or an exhaust valve. In the representation of Figure 1, the valve 14 is in the closed configuration seated on a valve seat 18. An elongated cylindrical stem of the valve 20 is carried so that it can be moved within a valve guide 22. A seat valve 24 mounted on the head of the motor 12 prevents liquids from leaking around the stem of the valve 20. A coil valve spring 26 is located concentric with the valve stem 20 and has a first end that rests on the valve stem 20. motor head 12. The second end of the valve spring 26 is retained within the rotator of the valve 28. The spring of the valve 26 is preferably maintained in a state of compression between the rotator of the valve 28 and the motor head 12 when the valve is in the open or closed configurations, the compression of the spring of the valve 26 becomes larger when the valve 14 is open. A valve retainer 30 has a portion thereof located within a groove of the retainer 32 formed circumferential to the stem of the valve 20. The valve retainer 30 holds the rotator or rotary positioner of the valve 28 in clutch with the rod of the valve. valve 20. The hydraulic actuator 10 of the present invention includes three main components: the actuator housing 40, the actuator piston 42 and the needle 44. With reference to FIGURE 2a, the actuator housing 40 is preferably formed of three components: the box body located at the center 46, a lid of the box 48 and an insert of the box 50. With reference again to Figure 1, the body of the box 46 of the box of the ^^ j ^ actuator 40 has a cylindrical hole 50 defined concentric with the longitudinal axis of the actuator housing 40. A low pressure hydraulic passage (LP) 54 is defined between the body of housing 46 and the insert of housing 50 The hydraulic passageway LP 54 extends from the outside of the actuator housing 40 to intersect the cylindrical bore 52. A piston bore 58a, 58b is defined concentric with the longitudinal axis of the actuator housing 40 and the body of the housing. 46 and the insert of box 50, respectively. The piston hole 58a, 58b is generally cylindrical, having a diameter that is substantially less than the diameter of the cylindrical bore 52. A high pressure hydraulic passage (HP) 56 is defined between the body of the box 46 and the cover of the box 48. The hydraulic passage HP 56 intersects the piston hole 58a. A needle hole 60 is defined in the case cover 48 of the actuator case 40. A seal seal O 62 is defined circumferentially to the hole of the needle 60. The actuator piston 42 has a cylindrical piston body 64. and a piston head 66. The piston body 64 has a generally cylindrical, elongated shape. The piston body 64 is operatively coupled at a first end to the end of the valve stem 20 of the valve 14. The needle hole 72 is defined at the second end of the piston body 64. The needle hole 72 extends approximately to half the longitudinal dimension of the piston body 64. The hole of the needle 72 is concentric with the longitudinal axis of the actuator piston 42. The piston body 64 is slidably located within the piston bore 58a, 58b. The piston head 66 has a generally cylindrical shape. The diameter of the piston head 66 is substantially greater than the diameter of the piston body 64. The piston head 66 is located within the cylindrical bore 52 defined within the actuator housing 40. As shown in FIG. 1, the The piston head 66 divides the cylindrical hole 52 into a left chamber of the variable volume extender 68 and a right chamber of the variable volume retractor 70. The piston body 64 can be moved into the piston bore 58a, 58b, and the head of the piston piston 66 can be moved with it into the cylindrical bore 52. This translation in the cylindrical bore 52 acts to simultaneously change the volume of the camera of the extender 68 and the camera of the retractor 70, increasing the volume of a camera while decreasing the volume of the another camera. A plurality of fluted passages 74 extends through the piston body 64 to accommodate the flow of the hydraulic fluid from the passage of the LP liquid 54 to the chamber of the extension 68 (depending on the position of the needle 44) and to the chamber of the retractor 70. A plurality of fluted passages 76 extends through the piston body 64 to accommodate the flow of hydraulic fluid from the passage of the liquid HP 56 to the chamber of the extension 68. The third component of the hydraulic actuator 10 is the needle 44. The needle 44 is a cylindrical rod, generally elongated. The needle 44 is located at least partially in the hole of the needle 72 defined in which a ring O 65 located in the groove for the ring seal O 62 effects a hydraulic seal between the needle 44 and the hole of the needle 60. The needle 44 is positioned so that it can be moved by sliding into the needle hole 60 and the needle hole 72. The needle 44 extends beyond the lid of the box 48 and is operably coupled to a needle positioning mechanism 80. In the representation of Figure 1, the positioning mechanism of the needle 80 is a solenoid. The positioning mechanism of the .ufe .i needle 80 can also be the lobe of a cam or variable speed motor or other convenient positioner as desired. The end of the inwardly directed needle 44 is formed to form a spool valve that includes a first end slit 82. The slit 82 has a diameter that is substantially less than the inside diameter of the needle hole 72, defining by this means an annular hydraulic passage between the first end slot 82 and the hole of the needle 72. A second slot 84 is defined at approximately the center point along the longitudinal axis of the needle 44. The second slot 84 also has a diameter which is substantially smaller than the diameter of the hole of the needle 72, thereby defining an annular hydraulic passage between the second slot 84 and the hole of the needle 72.

Operation of the invention During operation, the motor valve actuator aided by hydraulic means 10 depends on the low and high pressure liquid. A source of low pressure hydraulic fluid, such as a motor lubricating oil, under pressure when the oil circulates through the motor for lubrication purposes, is operably coupled to the LP 54 hydraulic passage. A source of liquid at high pressure, such as a motor oil under pressure as necessary to operate some fuel injectors for the engine. This source can be operably coupled to the HP 56 hydraulic passage. A high pressure source is thus described in connection with a hydraulically driven unitary fuel injector system, controlled by electronic means in U.S. Patent Nos. 5,191,867 and 5,392,749 which are they are hereby incorporated by reference. The translational movement of the needle 44 sensitive to the entrance of the needle positioning mechanism 80 distributes the hydraulic fluid in and out of the chamber of the extender 68 and the chamber of the retractor 70 defined by the position of the piston head 66 of the actuator piston 42 for acting on the piston head 66 in such a manner (described in detail in the following section) that the actuator piston 42 (and the position of the valve 14) closely follow the translational movement of the needle 44. The piston actuator 42 acts directly on the valve of the motor 14, the valve of the motor 14 being pushed to the closed position by the spring of the valve 26. The spring of the valve 26 always exerts a force directed to the left on the actuator piston 42, as shown in Figures l-3d. The actuator piston 42 has sufficient force directed to the right, when motivated by the high pressure hydraulic fluid, to overcome the opposing thrust of the spring 26 and the opposing force of any of the combustion forces acting on the engine valve 14. to open the valve 14. The translational movement of the needle 44 is not opposed by the spring 26 or the combustion forces and therefore only requires that a needle positioning mechanism 80 exerts a minimum force to effect the translation. The needle 44 can be controlled effectively to describe an opening / closing profile of the prescribed valve. In a preferred embodiment, the driving force necessary to move the needle 44 is less than 12 pounds and more preferably is approximately 6 pounds for convenience. The translational position of the needle 44 controls the position of the valve of the motor 14. The positioning of the valve 14 requires a force input much greater than the input of the force required for the position of the needle 44. This input force greater is available by means of the high pressure hydraulic fluid acting in the chamber of the extension 68 acting on the actuator piston 42. In this sense, the actuator 10 is a system servo follower The control of the needle 44 is maintained by the needle positioning system 80. The needle 44 acts as a servo pilot with the actuator piston 42 being the main servo stage and following the needle 44. The force required to drive the needle 44 is relatively small compared to the forces following the needle 44. This greatly reduces the mass and complexity of the components necessary to effect the activation of the valve 14. Figures 2a-2d represent the opening stroke of the valve 14, progressing sequentially from the closed position in Figure 2a to the open position in Figure 2d. In Figure 2a, the valve of the engine 14 is initially resting against the seat of the valve 18 by the pushing action exerted by the spring of the valve 26. The needle 44 and the actuator piston 42 are fully retracted to the position more the left. The low pressure liquid enters the hydraulic passage LP 54 and flows through the fluted passages 74 to fill the chamber of the retractor 70 and then flows through the hydraulic passage defined by the first end slot 82 to flood the chamber of the extension 68 of the actuator piston 42. With the low pressure hydraulic fluid acting on both sides 69, 71 of the piston head 66, the actuator piston 42 is in a state of hydraulic balance. No hydraulically generated force is acting to counteract the force of the spring 26. With reference to Figure 2b, the positioning mechanism of the needle 80 moves the needle 44 to the right, first, such translation advances the shoulder 83 of the first slit end 82 of the needle 44, sealing the chamber of the extender 68 from the chamber of the retractor 70. Secondly, as the needle 44 continues the translation to the right, the needle 44 allows the supply of the liquid at high pressure from the hydraulic passage HP 56 so that it flows through the second groove 84 and through the grooved passages 76. The high pressure liquid communicates with the chamber of the extension 68 and pushes on the side face of the extension 69 of the piston head 66 The side face of the extender 69 forms a portion of the chamber of the extender 68 of variable volume. It should be noted that the low pressure liquid is always «, * ._ *. acting on the side face of the retractor 71 of the piston head that forms a portion of the retractor chamber 70. The high pressure oil in the extension chamber 68 drives the actuator piston 42 and the engine valve 14 to the open position (Figure 2c) by overcoming the opposing force of the spring 26 and the opposing force of the liquid at low pressure acting on the side 71 of the piston head 66 which forms a portion of the retractor chamber 70. In a preferred embodiment, the liquid a High pressure operates in a pressure range of approximately 450 psi to 3000 psi and the low pressure liquid operates at a pressure of approximately 50 psi. The translation speed to the right of the needle 44 determines the area of the opening of the hydraulic passage defined between the second groove 84 and the grooved passages 76 towards the chamber of the extension 68 and hereby measures the liquid at high pressure of the supply at high pressure in the passage of the liquid HP 56 that is available to act on the side 69 of the piston head 66 forming a portion of the chamber of the extension 68. This measurement allows the control of the opening profile of the valve 26, as desired. The faster the needle 44 continues the movement to the right, the lower the pressure reduction on the high pressure oil and the greater the volume of the high pressure liquid supply that the needle 44 allows to communicate with the chamber of the extension 68 to act on the side 69 of the piston head 66 forming a portion of the chamber of the extension 68. The high-pressure liquid in the chamber of the extension 68 drives the actuator piston 42 and the valve of the engine 14 to the open position, overcoming the force of the spring 26 and the opposing force of the low pressure liquid acting on the side 71 of the piston head 66 forming a portion of the retractor chamber 70. On the other hand, the slower the displacement of the needle 44, smaller the area of the hydraulic passage defined by the second groove 84 that opens to the grooved passages 76 and therefore to the chamber of the extension 68 and greater the reduction effect. n pressure on the high pressure oil. The resulting volume of oil at lower high pressure in the chamber of the extender 68 results in less force available to overcome the force of the spring 26, the compressive or combustion forces acting to close the valve of the engine 14 and the opposing force of the liquid at low pressure acting on the side 71 of the piston head 66 forming a portion of the chamber of the retractor 70. This in turn gives rise to a slower movement of the actuator piston 42 and gives rise to a valve profile which is characterized by the slower opening movement of the valve of the motor 14. With reference to FIG. 2d, when the needle 44 is brought to a stop at its greatest right-hand translation point, the pressure in the extension chamber 68 and the inertia of the actuator piston 42 causes the actuator piston 42 and the valve 14 to continue their movement to the right for a short distance until the shoulder 85 of the second slit 84 of the guja 44 seals fluted conduit 76, preventing liquid at high pressure from affecting the protractor chamber 68 of actuator piston 42. Then equilibrium is ensured between the liquid trapped in the chamber of protractor 68 by needle 44 and the opposing spring thrust 26. The closing stroke of the valve 14 effected by the actuator 10 is shown in sequence in Figures 3a-3d. With reference to Figure 3a, the needle 44 and the actuator piston 42 are initially positioned so that the engine valve 14 is not seated in Ji- Uil. some elevation (at least partially open) as a result of the last action in the opening stroke mentioned with reference to Figure 2d above. The needle 44 seals the protractor chamber 68 from both high and low pressure oil supplies, as already described with reference to Figure 2d. With reference to Figure 3b, the needle positioning mechanism 80 retracts the needle 44, causing the needle 44 to move to the left. The movement of the needle 44 opens the circumference defined by the hydraulic passage to the first end slot 82. for hydraulically connecting the camera of the extender 68 with the camera of the retractor 70. As already indicated above, the camera of the retractor 70 is always exposed to the supply of oil at low pressure in the hydraulic passage LP 54. The camera of the The extension 68 is isolated from the high pressure oil in the hydraulic passage HP 56 by the needle 44 near the second groove 84. The second groove 84 is positioned to isolate the fluted passages 76 from the high pressure liquid supply in the passage 54. The high-pressure liquid in the chamber of the extender 68 flows into the chamber of the retractor 70 until the chamber of the extender 68 and the chamber of the retractor 70 is iil .i i. they find themselves in a state of hydraulic pressure equilibrium. The force of the spring 26, which is always acting on the actuator piston 42 drives the valve of the motor 14 and the actuator piston 42 to the left towards the closed position, as shown in Figure 3c. The speed at which the needle 44 is retracted is determined by the needle positioning mechanism 80 and determines the area of the hydraulic passage communicating hydraulically between the retractor chamber 70 and the extension chamber 68, thereby measuring the high-pressure hydraulic flow of the chamber of the extender 68 towards the chamber of the retractor 70. The force of the spring 26 acts to push the valve of the motor 14 and the actuator piston 42 to the closed position as the liquid at high pressure discharge from the chamber of the extension 68. The faster the needle 44 moves to the left, the greater the area and the faster the speed at which the oil is discharged from the chamber of the extender 68 to the chamber of the retractor 70. The oil in the chamber of the extension 68 it must be moved so that the valve 14 closes. The speed of movement of the needle 44 closely controls the closing speed of the valve 14. The control of the speed of translation of the needle 44 hereby produces a close control of the profile of the closure of the valve 14. When the needle 44 it is brought to a stop, as shown in Figure 3d, the force of the spring 26 and the inertia act to continue the movement to the left of the actuator piston 42 towards the closed position for a small amount of travel after stopping the needle 44. Such travel continues until the chamber of the extender 68 is closed off from the first end slot 82. Then a balance between the hydraulic pressure and the chamber of the extender 68 and the chamber of the retractor 70 is ensured. The force of the spring 26 it continues to act on the actuator piston 42 and valve 14, keeping the valve in the closed, seated position. Figures 4a-4d depict a comparison of a profile of the exhaust valve 14 of the cam valve train engine with a non-cam profile effected by the present invention wherein an aggressive valve opening is selected and controlled around a lower dead center. Figures 4b-4d depict the flow rate of the actuator, the piston forces and the actuator pressures corresponding to the movement shown in Figure 4a. Figure 4a shows the movement profile of the engine piston, the profile of the cam valve train of a traditional system, the needle piston of the present invention and the response of the actuator piston of the present invention and the engine valve for the entry of the needle position. Figure 4a shows how closely the outlet in the form of movement of the valve 14 tracks the entry in the shape of the position of the needle 44, obviating the need for a detector to track the position of the valve 14. The Figure 4b represents the flow velocity of the high pressure oil necessary to effect a cycle of opening and closing of the valve. Figure 4c shows the force of the high pressure oil acting on the actuator 42 compared to the opposing force of the spring 26. The 4d indicates that the pressure necessary to keep the valve open stabilizes at approximately 400 psi after 0.02 seconds. Almost any high pressure hydraulic fluid that is above the threshold of about 400 psi is adequate to operate the actuator 10 as designed. Returning now to FIGS. 5a-5f, a hydraulic diagram of the operation of a mode of the hydraulic actuator 10 is shown in sequence through a downward stroke of the valve 14 and a rising stroke of the valve 14. To effect the downward stroke of the the valve 14, there are two descending movements that should be considered. First, the actuator piston 42 is coupled to the valve 14 and urges the valve 14 in the downward direction as shown. Second, the needle 44 moves into the needle bore 72 defined in the actuator piston 42 under the influence of the needle positioning mechanism 80 to control the movement of the actuator piston 42. Before the beginning of the down stroke of the valve 14, the actuator piston 42 and the needle 44 are in their fully retracted and ascending positions as shown in Figure 5a. The high pressure lubricating oil available in the high pressure hydraulic passage 56 from a high pressure channel floods the chamber 90 and flows into the second slot 84. The second slot 84 is sealed at its most downward end by the shoulder 86 of the needle 44 sealingly clutching the actuator piston 42. Lubricating oil for low pressure motor available in the low pressure hydraulic passage 54 from a low pressure channel floods the chamber of the retractor 70. Lubricating oil for low pressure motor is prevented from entering the chamber of the extension 68 by an obturating clutch of the shoulder 88 of the needle 44 with the pin of the actuating piston 42. The valve 14 is kept in its fully seated upward arrangement, as shown in Figure 5a, by the action of the lubricating oil for low pressure motor acting on the surface of the retractor 71 of the piston head 66, in combination with the on the thrust exerted by the valve spring 26. See Figure 1. Figure 5b represents the start of the downward stroke of the valve 14. In Figure 5b, the needle 44 is moved downward relative to the drive piston 42 under the acting influence of the needle positioning mechanism 80. This downward translation removes the shoulder 86 from the clutch needle 44 with the actuator piston 42 to create a hydraulic passage through the second slit 84 towards the chamber of the extender 68. The oil lubricant for high-pressure motor flows through the second slit 84 towards the chamber of the extension 68 and pushes on the surface of the extension 69 of the piston head 66. The force exerted by the lubricating oil for high-pressure motor is sufficient for overcome the stopping force exerted by the lubricating oil at engine pressure acting on the surface of the retractor 71 in combination with the thrust exerted by the r then the valve 26 and any combination of forces acting on the valve 14. Accordingly, the translation of the actuator piston 42 and the coupled valve 14 starts by pulling very closely downward the translation of the needle 44. The flow of the lubricating oil for motor at high pressure towards the chamber of the extension 68 is represented by the arrows A. The chamber of the extension 68 remains sealed from the chamber of the retractor 70 by the obturating action of the shoulder 88 in an obturating relationship with the head of the piston 66. The oil continuous low pressure to flood the chamber of the retractor 70. Figure 5c represents the valve 14 when the valve 14 approaches the down position, fully open, not seated. In the representation of Figure 5c, needle 44 has moved downward to its full stroke. The actuator piston 42 is slightly delayed behind the needle 44. Accordingly, as indicated by the arrows A, the lubricating oil for high-pressure motor continues to flood the chamber of the extension 68 and to act on the surface of the extension 69, pushing hereby the actuator piston 42 and the valve 14 in the downward direction. Figure 5d depicts the valve 14, the actuator piston 42 and the needle 44 all in their fully descending positions. As compared to Figure 5c, the drive piston 42 has continued the downward translation slightly relative to the needle 44 after the movement of the needle 44 has ceased. This translation generally results from the inertia of the actuator piston 42 and the valve 14. This translation seals the chamber of the extension 68 by the action of the shoulder 86 of the needle 44 again engaging the actuator piston 42 in an obturating manner., the shoulder 88 of the needle 44 is in sealing clutch with the actuator piston 42, thereby isolating the retractor chamber 70 from the extension chamber 68. In this position, there is no lubricating oil flow for high pressure motor or of lubricating oil for low-pressure engine. This is a practically static position. The lubricating oil for high pressure engine is sealed inside the chamber of the extension 68 creating a hydraulic seal, preventing the lubricating oil for engine at lower pressure acting on the surface of the retractor 61 of the piston head 66 (in combination with the thrust of the valve spring 26) move the actuator piston 42 in an upward direction. The flow in or out of the chamber of the retractor 70 ceases since all the passages are sealed and there is no movement of the sealing piston 42. With reference to Figure 5e, the start of the upward stroke of the valve 14 is shown. In Figure 5e, the needle 44 is moved upwards slightly under the influence of the needle positioning mechanism 80. Such upward translation removes the obturating clutch to the shoulder 88 with the actuator piston 42. The shoulder 86 remains in sealing engagement with the piston actuator 42. The translation of the needle 44 opens a hydraulic passage of the chamber of the extension 68 through the first slit 82 and then through the chamber of the retractor 70. The pressure of the hydraulic fluid at high pressure (lubricating oil for motor) trapped in the extension chamber 68 is dissipated into the chamber of the retractor 70 as indicated by the arrow B. With the dissipation of the hydraulic seal as shown in Figure 5d, there is a hydraulic balance in the chambers 68, 70 and the spring thrust of the valve 26 is therefore free to act on the valve 14 and the actuator piston 42. With reference to Figure 5f, the upward thrust of the spring of the valve 26 (shown in Figure 1) acting on the valve 14 pushes the actuator piston 42 upwards. The upward movement of the actuator piston 42 substantially displaces all the hydraulic fluid acting from the chamber of the extension 68 towards the chamber of the retractor 70, as represented by the arrows B. As indicated in Figure 5f, the shoulder 88 is disengaged from the piston actuator 42 to allow the continuous flow of the engine lubricating oil from the chamber of the extender 68 to the chamber of the retractor 70. The needle 44 is retracted upwardly with the actuator piston 42 causing the shoulder 86 to maintain a sealing engagement with the actuator piston 42, thereby isolating the high-pressure motor lubricating oil from the protractor chamber 68. This completes the upward stroke of the valve 14. Another preferred embodiment of the present invention is shown in Figures 6 and Id.

With reference to Figure 6 and the Id, the actuator module of the valve 100 of the present invention is used with a valve 112 preferably located in a head 120 of an internal combustion engine. The valve 112 has a stem of the valve 114. An upper end of a valve spring 116 is retained by a valve rotator 118. The lower end (not shown) of the valve spring 116 is traditionally retained in the head 120. The head 120 has a main piston bore 122 and a pilot piston bore 124 defined therein. The holes 122, 124 are generally parallel and offset in a separate relationship. A secondary piston hole 128 of somewhat smaller diameter is defined concentric with the bore of the pulse piston 124. The secondary piston bore 128 and the pulse piston bore 124 are coaxial with the longitudinal axis of the valve stem of the motor. 114. A low pressure oil passage 130 is defined in the head 120 extending between the main piston bore 122 and the secondary piston bore 128. A high pressure oil passage 132 is defined in the head extending between and in coupling with the main piston bore 122 and the impulse piston bore 124. A low pressure channel 134 is defined in the head 120. The low pressure channel 134 is hydraulically coupled with the bore of the main piston 122. The pressure channel of lubricant 134 preferably transports lubricating oil for motor to normal pressures of lubricating oil for motor of approximate 50 psi. A high-pressure channel 136 is also defined in the head 120. The high-pressure channel 136 is hydraulically coupled to the bore of the piston 122. The high-pressure channel 136 preferably carries a high-pressure acting liquid for the actuation of the valve 112. The high-pressure actuating liquid is preferably high-pressure engine lubricating oil by a special pump, the high pressure being in the range of 1000 to 4000 psi. The low pressure channel 134 and the high pressure channel 136 are selectively in hydraulic communication with the main piston bore 122. A low oil pressure line of smaller volume 138 is defined in the head 120. The low line pressure 138, like the low pressure channel 134, preferably convey motor lubricating oil at the pressures of the engine lubricating oil. The low pressure oil line 138 is in hydraulic communication with the secondary piston bore 138. The actuator module of the valve 100 of the present invention includes five main components: the controller 120, the needle 142, the main piston 144, the pulse piston 146 and secondary piston 148. Controller 140 is preferably fixedly coupled with head 120. Controller 140 has a controller case 150 having a lower portion 152 that is located obturatorly within an upper extension elongated from the main piston hole 122. The lower margin 154 of the lower piston 152 defines in part a control chamber 156. The control chamber 156 will be described in greater detail below. A sloping cylindrical shoulder 158 having an open portion aligned with the low pressure oil passage 130 protrudes towards the volume defined by the hole of the main piston 122. The controller 140 further includes a solenoid 160. The solenoid 160 has a fixed armature 162 and a moveable core 164 located within the armature 162. The core 164 has a drive rod 166 that is slidably located within a hole defined in the lower portion 152 of the controller case 150. The drive rod 166 pushes the needle 142 or, in one embodiment, needle 142 may be t formed as a portion of actuator rod 166. Solenoid 160 has a linear stroke of less than about 6 mm and more preferably is about 4 mm. The needle 142 is the second component of the actuator module of the valve 100. The needle 142 is a generally elongated metal rod having an axis is longitudinally coaxial with the longitudinal axis of the main piston bore 122. The cylindrical periphery of the needle 142 has a groove generally located at the center 168. The upper and lower margins of the groove 168 are defined by a low shoulder. pressure 170 and by a high pressure shoulder 172. The slit 168, in cooperation with the low pressure shoulder 170 and the high pressure shoulder 172, defines in part an annular hydraulic passage 174 between the needle 142 and the bore of the 180 needle defined in the piston Main 144. On the needle 142 (and the actuator rod 166) an upward thrust is exerted by a return spring 176 located partially within the needle bore 180 and is concentric with the longitudinal axis of the needle bore 180. return spring 176 acts on the lower margin of the needle 142. The return spring 176 is retained within the hole of the main piston 122 by a ratchet 178 located within the hole of the main piston 122. The main piston 144 is the third component of the piston. valve actuator module 100. The main piston 144 is movably located within the hole of the main piston 122. To simplify the machining tolerances, the main piston 144 is dependent only on the concentricity of the main piston 22 hole. Thus, the needle 142 is dependent only on the concentricity of the hole of the needle 180 defined in the main piston 144. The multiple it is dependencies, so different from the only dependencies of the present invention, and undesirable in view of the fact that these can greatly increase the requirements for a highly accurate concentricity of the multiple holes dependent on the components that can be moved from a valve actuator. . The main piston 144 has an upwardly directed piston head 182. The piston head 182 defines in part the control chamber 156. A low pressure groove 184 is defined in the outer periphery of the main piston 144. A hydraulic passage 186 is defines in the lower margin of the low pressure groove 184 and extends through the main piston 144 to hydraulically couple the low pressure channel 134 to the hole of the needle 180. The lower margin of the hydraulic passage 186 is defined by a low pressure shoulder 188. A first high pressure groove 190 is also defined on the outer periphery of the main piston 144 below and hydraulically isolated from the low pressure groove 184. A hydraulic passage 192 is defined in the lower margin of the first high pressure groove 190 and extends through the main piston 144 to hydraulically couple the needle hole 180 and the passage of the high pressure oil 132 defined in the head 120. A second high pressure groove 193 is also defined on the outer periphery of the main piston 144 below and isolated from the first high pressure groove 190. A high pressure hydraulic passage 194 is defined in the upper margin of the second high groove. Pressure 193 and extends through the wall of the main piston 144 to hydraulically couple the high-pressure channel 136 defined in the head 120 with the hole of the needle 180 defined in the main piston 144. The upper margin of the hydraulic passage to high pressure 194 is a high pressure shoulder 195. In the main piston 144 an upward thrust is exerted by a return spring 196 acting on the lower margin of the main piston 144. The return spring 196 is located concentric with the return spring 176 of the needle 142. The return spring 196 of the main piston 144 is also retained within the hole of the main piston 122 by the ratchet 178. It should be noted that the needle 142 and the main piston 144 are displaced from the valve motor 112 and are structurally decoupled from the motor valve 112. This acts to uncouple the needle 142 and the main piston 144 from the effects of the valve clearance of the motor valve 112. The fourth component of the valve actuator module 100 is the impulse piston 146. The impulse piston 146 is located so that it can be moved within the bore of the impulse piston 124 defined in the head 120. The impulse piston 146 has an upper margin that has a pulse piston head 198 which is exposed to the acting hydraulic fluid flowing in the high-pressure oil passage 132. The impulse piston 146 pushes on the piston of the engine valve 112. The downward movement of the impulse piston 146 acts on the piston rod of the piston. motor valve 114 for opening the motor valve 112. The fifth component of the valve actuator module 100 is the secondary piston 148. The secondary piston 148 it is pushed down by a secondary piston spring 200 which resides in the bore of the secondary piston 128. The spring of the secondary piston 200 is retained within the bore 128 by a pawl 202. The secondary piston 148 has a secondary piston head 204. The secondary piston head 204 defines in part the control chamber 156. An elongate piston rod 206 extends through a hole 207 defined in the head 120. The bore 207 extends between the control chamber 156 and the passageway of the piston. high pressure oil 132. The piston rod 206 has a distal end 208 which pushes on the head of the impulse piston 198. The distal end 208 is kept in contact with the head of the impulse piston 198 by the thrust exerted by the spring of the secondary piston 200. The control chamber 156 has a variable volume and is preferably kept filled and filled with the engine oil of the oil line lubricant 138. The control chamber 156 has a check valve 210 interposed between the control chamber 156 and the low pressure oil line 138. The check valve 210 is pushed to a closed position by sealing the control chamber 156 of the low pressure line 138 by a spring of the check valve 212. The check valve 210 will not be seated by the low pressure motor oil pressure in the low pressure line 138 when the pressure in the low pressure line 138 exceed the force generated on the check valve 210 by the combination of the pressure in the control chamber 156 and the thrust exerted on the check valve 210 by the spring of the check valve 212. The operation of the valve actuator module 100 can be seen with reference to Figures la-Id. Figure 7a (like Figure 6) represents the engine valve 112 in the closed position. The spring of the motor valve 116 holds the motor valve 112 in the closed up position. The needle 142 and the main piston 144 are in the completely retracted upward position. The piston head 182 of the main piston 144 pushes on the shoulder 158 of the controller box 150, the shoulder 158 acting as a detent for the main piston 144. The low pressure regulation area, AL, defined by the interaction of the low pressure shoulder 170 of the reel slot 168 and the low pressure shoulder 188 of the hydraulic passage 186, is open, allowing the pressure channel of the lubricant 134. to be in hydraulic communication with the head of the pulse piston 198. Accordingly, the pressure PD acting on the pulse piston 146 is equal to the pressure of the channel a Lubricant pressure 134. In this position, the high pressure regulation area AH, defined by the interaction between the high pressure shoulder 172 of the slit 168 and the high pressure shoulder 195, is closed. When the shoulders 172, 195 overlap, the high pressure regulation area AH is closed, thereby sealing the high pressure channel 136. With reference to Figure 7b, the motor valve 112 is shown in its fully open arrangement . When comparing Figures 7a and 7b, it is observed that the stroke, Ss, of the solenoid 160 is approximately one-half the stroke, SD, of the impulse piston 146 and the valve of the engine 112. The main piston 144 under the influence of the liquid in the control chamber 156 is used to, in effect, double the length of the stroke Ss of the solenoid 160 to obtain the stroke SD of the engine valve 112. The ratio of the area of the secondary piston 148 to the area of the main piston 144 determines the amplification of the race. By suitable sizing of the pistons 144, 148 it is possible to obtain ratios greater than 1: 1 and up to 1: 6. However, a ratio of about 1: 2 is preferred where the solenoid 160 gives a linear stroke of about 6 mm and a stroke of 12 mm of the motor valve 112 is desired. In Figure 7b, the needle 142 is completely shown extended down. The high-pressure oil is sent from the high-pressure channel 136 through the high-pressure hydraulic passage 194. The high-pressure regulation area AH (defined by the separate shoulders 172, 195) opens allowing the operating liquid to high pressure pass through an annular hydraulic passage 124, the high-pressure oil passage 132 to act on the head of the pulse piston 198. The high pressure acting liquid drives the pulse piston 146 and the motor valve 112 towards down to the open position of the engine valve. The low pressure regulation area AL, is closed (the shoulders 170, 188 being in an overlapped relationship) avoiding hydraulic communication with the low pressure channel 134. The secondary piston 148 is coupled to the impulse piston 146 by means of the impulse exerted by the spring 200. As the secondary piston 148 moves downward, the oil in the control chamber 156 is pumped to push down on the piston head 182 of the main piston 144. Accordingly, the main piston 144 it moves down slightly by retracing the translation of the needle 142. With reference to Figure 7c, the closing stroke of the actuator module of the valve 100 and the valve of the motor 112 is represented. The closing stroke starts by the upward retraction of the the needle 142 when starting from the solenoid 160. As the solenoid 160 retracts, the return spring 176 acts upwardly on the needle 142 for udar in the retraction of the needle 142. The retraction of the needle 142 in relation to the main piston 144 opens the area of regulation of low pressure AL, to the channel of low pressure 134. The oil at high pressure acting on the head of the piston of impulse 198 escapes through the high-pressure oil passage 132, the annular hydraulic passage 174 and the low-pressure regulating area AL to the low-pressure channel 134. Once the liquid acting at high pressure is no longer acting on the head of the pulse piston 198, the spring of the valve 116 acts to return the valve of the motor 112 to its closed position. When the impulse spring 146 moves upwards, the secondary piston 148 also moves upwards. When the secondary piston 148 moves upwards it modifies the volume of the control chamber 156. The return spr196 which acts upwards on the main piston 144 pumps the liquid in the control chamber 156 towards the secondary piston 148. The translation risof the main piston 144 occurs by slightly retardthe retraction of the needle 142. this translation with retracement ensures that the high-pressure regulatarea (AH) remains closed durthe upward translation of the needle 142 and the main piston 144. The adjustment of the Slack occurs as shown in Figure 7d. A certain amount of liquid leakage is designated to the control chamber 156. As a result of this leakage, the main piston 144 sits against the shoulder 158, thereby endits upward translation slightly beyond the secondary piston 148 completits upward translation. The secondary piston 148 continues its upward translation after the seatof the main piston 144. Such upward translation momentarily decreases the pressure in the control chamber 156 to a pressure that is less than the pressure in the low pressure line 138. This momentary decrease in the pressure in the control chamber 156 gives rise to the pressure of the oil in the low pressure line 138 acton the check valve 210 to compress the sprof the check valve 212 and to admit a quantity of filler oil towards the chamber 156. By always seatthe main piston 144 past the secondary piston 148, there is always a short period durwhich the control chamber 156 can be completely filled without considerchanges in the longitudinal dimension (clearance) of the piston rod. motor valve 114. With such adjustment of the valve clearance, the point where the pulse piston 146 stops ne in its retracted position is not important in the action of the valve. The effect of the retention position of the present invention 146 on the volume of the control chamber 156 is counteracted by the automatic replenishment of the control chamber 156. The volume of the control chamber 156 may change due to the gappof the valve, but the variable volume of the control chamber 156 is always filled as described in the above. The aforementioned arrangement always guarantees that the main piston 144 sits on each upward stroke. This is very important because of the crucial relationship between the main piston 144 and the needle 142, especially with respect to the low pressure regulation area AL and the high pressure regulation area, AH. A misalignment of the needle 142 and the main piston 144, which would result from the main piston 144 not seatin its retracted stroke, can greatly affect the desired flow of the liquids in the actuator module of the valve 100. Another mode of the actuator the valve of the present invention is shown in Figures 8-18b. In these figures, equal numbers represent equal components as already described. The actuator module of the valve 100 as shown in Figures 8-18b gives rise to a number of advantages includreduction of the size of the solenoid, more efficient use of the packand elimination of the effects of valve growth ( clearance) and wear of the valve seat. To obtain such advantages, the impulse piston 146 is decoupled from the needle 142 to facilitate packarrangements and to effect height reduction. Such decouplallows the realization of a check valve 210 on the volume of the couplliquid (the control chamber 156) which serves as a hydraulic lifter. The decouplfurther allows a variable ratio between the needle 142 and the impulse piston 146. The shorter the needle 142, the stroke allows a more compact solenoid unit (controller 140), since it is the solenoid 140 that generates the stroke of the needle 142. With reference to Figure 8, a series of six valve actuator modules 100 is mounted on a valve actuator unit 222. In addition to the six actuator modules of the Valves 100, the valve actuator unit 222 includes an underlying adapter plate 224. The adapter 224 may be mounted directly to the head of an inline six-cylinder internal combustion engine. A plurality of holes 226 is defined in the adapter plate 224 through which it is possible to insert the screws for the threaded clutch with the threaded holes defined in the motor head. Preferably, there is a hole 226 at either end of the actuator unit of the valve 222 and a similar hole 226 defined between each of the actuator modules of the valves 100. The actuator modules of the valves 100 in turn are coupled to the adapter plate 224 by screws extending down through the holes 228 (see Figure 10) into threaded clutch with the holes defined in the adapter plate 224. A unit of elongated oil channels 230 preferably extends to all along the six actuator modules of the valves 100 and is coupled thereto by means of screws 232 which pass through the holes defined in the flanges of the channels 234 in threaded clutch with the holes defined in the individual valve actuator bodies 236. The oil channel unit 230 includes a high pressure oil inlet 238 and a low pressure oil inlet 230. The admission High pressure oil 238 is hydraulically coupled to the high pressure channel 136 and the low pressure oil inlet 230 is hydraulically coupled to the pressure lubrication channel 134. Each of the valve actuator modules 100 preferably serves both inlet valves and escapes 112 associated with the cylinder with which the valve actuator module is matched. In the example shown, the cylinder has an intake valve and an exhaust valve 112. Accordingly, each valve actuator module 100 includes two seats of the main components of the valve actuator module 100, including the controller 140, the needle 142, the main piston 144, the impulse piston 146 and the secondary piston 148. The aforementioned series of components are located in a side-by-side relationship along the longitudinal axis of the valve actuator unit 222. This is easily seen in the Figure 8 is represented by the side-by-side relationship of the two controller boxes 150 of each valve actuator module 100. It is evident that a valve actuator module 100 can be constructed to serve a cylinder having more than two valves 112 For example, if the cylinder has four valves, a mirror image of the exemplary valve actuator module 100 can be constructed to service all the valves of a four-valve cylinder. Otherwise, each controller box 150 can control the intake valves or exhaust valves through a traditional valve bridge as is known in the art for four-valve engine cylinders. With reference to Figures 9 and 10, the valve actuator module 100 includes two main components of the box: the actuator body of the valve 236 and the pulse piston body 242. The pulse piston body 242 is coupled to the piston body 242. valve actuator body 236 by a plurality of screws 244 inserted through the holes 244 defined in the flanges 246 and thus in the threaded holes 248 defined in the body of the valve actuator 236. (See also Figures 13 and 14). The controller box 150 and the needle spring box 151 are secured to the body of the valve actuator 236 and the pulse piston body 242 respectively by the screws 250. One of the mode differences of the valve actuator module 100 of Figures 8-18b when compared to the embodiment of Figures 6 -7d is that the embodiment of Figures 8-18b eliminates the need for the lubrication oil line 138 which is used to replenish the control chamber 156 in the embodiment of Figures 6-7d. In the embodiment of Figures 8-18b the control chamber 156 is replenished through a hydraulic coupling to the liquid lubrication channel 134 defined in the oil channel unit 230 shown in Figure 15b. With reference to Figures 13 and 14, a lubricant hydraulic pressure inlet 152 and a high pressure liquid inlet 254 are defined in a range of the valve actuator body 236. The hydraulic lubrication inlet 252 hydraulically couples the lubrication pressure channel 134 to the piston bore main 122 defined in the valve actuator body 236. The high pressure hydraulic inlet 254 hydraulically couples the high pressure channel 136 with the main piston bore 122. A high pressure liquid outlet 256 (FIG. 14) defined in an opposite margin of the valve actuator body 236 hydraulically couples the hole of the main piston 122 to the pulse piston 146 by means of the high pressure liquid inlet 258 defined in the pulse piston body 242. An outlet of liquid to pressure for lubrication, arcuate 260 defined in the body of the valve actuator 236 is hydraulically coupled The liquid pressure inlet for lubrication 262 (FIG. 13) defined in the pulse piston body 242 is adhered to. The pressure liquid intake for lubrication, arc 262 defines in part the control chamber 156. a second liquid inlet. pressure for lubrication 264 is defined in the outer margin of the body of the valve actuator 236 which is coupled with the oil channel unit 230. In Figure 13, the second pressurized liquid inlets for lubrication 234 are shown in oval form . The second pressurized fluid inlet for lubrication 264 acts to hydraulically couple the pressure channel for lubrication 134 to the control chamber 156. It is the aforementioned hydraulic communication that serves to fill the liquid supply in the control chamber 156. Accordingly, the check valve 210 is disposed in the hydraulic path extending between the second pressurized liquid inlet for lubrication 264 and the control chamber 156, see Figure 15b. In order to minimize the height dimension of the modulated valve actuator 100, the secondary piston 148 is laterally displaced from the impulse piston 146 and is not directly coupled with the impulse piston 146. The secondary piston 148 and the piston Impulse 146 are moved together (they move between a closed and an open arrangement) as a function of the secondary piston 148 being operatively coupled to the upper margin 117 of the valve rotator 118 and the impulse piston 146 being operably coupled with the upper margin 119 of the valve 112. This side-by-side arrangement effectively couples the translational movement of the secondary piston 148 to the translational movement of the impulse piston 146 without direct contact between the pistons 146, 148. The translational axes of the secondary piston 148 and the pulse piston 146 are substantially parallel and separate. The operation of the valve actuator module 100 can be seen with reference to Figures 16a-18b. Figures 16a, 16b (same as Figures 15a, 15b) represent the valve of the engine 112 in the closed position just before starting the down stroke. The spring of the motor valve 116 holds the motor valve 112 in the closed up position. The lower margin 199 of the impulse piston 146 is in contact with the upper margin 119 of the valve 112. The tip 208 of the secondary piston 148 pushes on the upper margin 117 of the valve rotator 118. Accordingly, the spring of the valve 116 it acts to position the impulse piston 146 and the secondary piston 148 in their fully retracted upward arrangements. The needle 142 and the main piston 144 are also in the retracted position, completely upwards. The piston head 182 of the main piston 144 pushes on the shoulder 158 of the controller box 150, the shoulder 158 acting as a detent for the main piston 144. The area of low pressure regulation, AL, defined by the interaction of the low pressure shoulder 170 of the reel slot 168 and the low pressure shoulder 188 of the hydraulic passage 186 is closed (the low pressure shoulders 170, 188 being superimposed), thereby sealing the lubricant pressure channel 134 of the hydraulic communication with the head of the pulse piston 198. In this position, the high pressure regulation area AH, defined by the interaction between the high pressure shoulder 172 of the slot 168 and the shoulder high pressure 195, is open. When the shoulders 172, 195 are separated (not overlapped), the high pressure regulation area AH is open, thereby sealing the high pressure channel 136. Accordingly, the pressure PD acting on the pulse piston 146 is equal to the pressure in the high pressure channel 136. This pressure currently exceeds the thrust exerted by the spring of the valve 116 to drive the valve 112 down to the open position. When the secondary piston 148 moves downward, the oil in the control chamber 156 is pumped to push down on the piston head 182 of the main piston 144. Accordingly, the main piston 144 moves downwardly slightly retarding the translation of the needle 142. With reference to Figures 17a, 17b, the engine valve 112 is shown in its fully open arrangement. The representation of Figures 17a, 17b is with the valve 112 fully open, but with the needle 142 and the main piston located to cause the closing of the valve 112. It is noted that the stroke of the solenoid 160 is approximately a half the stroke of the pulse piston 146 and engine valve 112 as already described with reference to the embodiment of Figures 6-7d. In Figures 17a, 17b, the needle 142 is shown folded up completely. The high-pressure oil of the high-pressure channel 136 is sealed off from the impulse piston 146. The high-pressure regulation area, AH (defined by the overlapping shoulders 172, 195, is closed) sealing the acting liquid at high pressure of the passage annular hydraulic 124 and the high-pressure oil passage 132. The low-pressure regulation area AL, is open (shoulders 170, 188 being separated and not in a superimposed relationship) by making hydraulic communication between the head of the impulse piston 198 and the low pressure channel 134. The secondary piston 148 is coupled to the rotator 118 by means of the thrust exerted by the spring 200. The closing stroke begins with the upward retraction of the needle 142 started by the solenoid 160. When the solenoid 160 is retracted, the return spring 176 acts upwardly on the needle 142 to assist in the retraction of the needle 142. The retraction of the needle 142 relative to the main piston 144 opens the low pressure regulation area AL to the low pressure channel 134. The high pressure oil acting on the head of the pulse piston 198 escapes through the high pressure oil passage 132, the annular hydraulic passage 174 and the low pressure regulating area AL, to the low pressure channel 134. Once the liquid acting at high pressure is no longer acting on the head of the impulse piston 198, the spring of the valve 116 acts to return the valve of the valve. 112 motor to its closed position. The pulse piston 146 is brought upwardly by the valve of the motor 112. When the impulse piston 146 moves upward, the secondary piston 148 is simultaneously carried upward by the rotator moving upwardly 118. When the secondary piston 148 becomes moving upwards modifies the volume of the control chamber 156. The return spring 196 which acts upwards on the main piston 144 pumps the liquid in the control chamber 156 towards the secondary piston 148. The upward translation of the main piston 144 occurs , slightly retarding the interaction of the needle 142. Such delayed translation ensures that the high pressure regulation area (AH) remains closed during the upward translation of the needle 142 and the main piston 144. The adjustment of the gap occurs as shown in FIG. Figures 18a, 18b. A certain amount of liquid leakage is designated to the control chamber 156. As a result of such leakage, the main piston 144 sits against the shoulder 158, thereby terminating its upward translation slightly beyond the secondary piston 148 completing its translation upward. The secondary piston 148 continues its upward translation after the seating of the main piston 144. Such upward translation momentarily decreases the pressure in the control chamber 156 to a pressure that is lower than the pressure in the low pressure line 138. This momentary decrease in the pressure in the control chamber 156 causes the pressure of the oil in the low pressure line 138 acting on the check valve 210 to compress the spring of the check valve 212 and to admit a quantity of filling of the oil into the chamber control 156. By seating the main piston 144 past the secondary piston 148, there is always a short period during which the control chamber 156 can be completely filled without considering changes in the longitudinal dimension (clearance) of the valve stem. of the engine 114. Variations within the spirit and scope of the invention described are equally and comprised by the aforementioned description.

Claims

1. An engine valve actuator aided by hydraulic means to assist in the activation of a motor valve comprises: a pulse piston operably coupled to the engine valve for actuation of the engine valve and being displaceable by a force that acts on this one, being the force generated by a liquid under pressure; and a needle valve that can be moved, the needle valve being in hydraulic communication with a source of liquid under pressure and also being in hydraulic communication with the actuator piston, the needle valve effecting the dosing of the fluid under pressure to generate a force on the impulse piston, the needle valve being structurally decoupled from the engine valve.

2. The hydraulic-assisted motor valve actuator of claim 1 further includes a main piston, the main piston being in hydraulic communication with the needle valve and being hydraulically coupled operably to the engine valve and structurally decoupled from the engine valve.

3. The hydraulic-assisted motor valve actuator of claim 2, wherein the main piston can be moved to effectively amplify an actuating stroke of the needle valve to effect an amplified stroke of the engine valve.

The hydraulic-assisted motor valve actuator of claim 3, wherein a translation speed of the pulse piston is related to a translation speed of the needle valve to effect a desired profile of opening and closing of the valve. engine valve.

The hydraulic assisted motor valve actuator of claim 3, wherein the main piston and the needle valve each have a single dependence for the indulgent concentricity requirements.

6. The hydraulic-assisted motor valve actuator of claim 1, wherein the gap of the motor valve is automatically adjusted.

7. The hydraulic-assisted motor valve actuator of claim 6 further includes a secondary piston, the secondary piston being hydraulically coupled operably to the main piston so that a movement of the secondary piston produces a corresponding and related movement, opposite of the main piston.

The hydraulic-assisted motor valve actuator of claim 7, wherein the secondary piston is hydraulically coupled operably to the main piston by means of a control chamber.

The hydraulic assisted motor valve actuator of claim 8, wherein the control chamber can be operably coupled to a liquid source under pressure, with a check valve located between the control chamber and the source of the liquid, the check valve opening in response to a certain pressure in the control chamber to admit filling liquid to the control chamber.

The hydraulic assisted motor valve actuator of claim 1, wherein a controller is operably coupled to the needle valve, the controller including a needle positioning mechanism.

The hydraulic assisted motor valve actuator of claim 10, wherein the needle locating mechanism is a solenoid.

The hydraulic-assisted motor valve actuator of claim 9, wherein a leak of selected liquid in the control chamber gives rise to the main piston being seated in retraction before the secondary valve is seated in retraction to guarantee the seating of the main piston in each retraction event.

13. The hydraulic-assisted motor valve actuator of claim 12, wherein the seating of the main piston causes a drop in pressure in the control chamber, the pressure drop acting to cause the opening of the check valve.

14. The hydraulic-assisted motor valve actuator of claim 13, wherein the volume of the control chamber is variable as a function of the valve clearance.

The hydraulic-assisted motor valve actuator of claim 3, wherein the actuation stroke of the needle valve is amplified by a factor related to the ratio of the secondary piston to the main piston.

16. The hydraulic-assisted motor valve actuator of claim 15, wherein the ratio of the secondary piston to the main piston is selectively variable between more than 1: 1 and less than 6: 1.

17. An engine valve actuator aided by hydraulic means to assist in the activation of a motor valve comprises: a servo piston being operably coupled to the engine valve; an auxiliary valve that can be moved while in hydraulic communication with the servo piston and the power piston and being operatively coupled to and controlled by a positioning system of the auxiliary valve, the auxiliary valve positioning system controlling a translational stroke of the valve auxiliary to measure hydraulic fluid under pressure to and from the servo piston; and a stroke amplifier to amplify a stroke of the auxiliary valve positioning system.

18. The hydraulic assisted motor valve actuator of claim 17, wherein the stroke amplifier includes a main piston, the main piston being in hydraulic communication with the auxiliary valve and being hydraulically coupled operably to the engine valve and structurally decoupled from the engine valve.

19. The hydraulic-assisted motor valve actuator of claim 18, wherein the main piston can be moved to effectively amplify the actuation stroke of the auxiliary valve to effect an amplified stroke of the engine valve.

The hydraulic-assisted motor valve actuator of claim 19, wherein a translation speed of the servo piston is related to a translation speed of the auxiliary valve to effect a desired profile of opening and closing of the valve the motor.

21. The hydraulic-assisted motor valve actuator of claim 20, wherein the main piston and the auxiliary valve have a single dependence for the indulgent concentricity requirements.

22. The hydraulic-assisted motor valve actuator of claim 1, wherein the gap of the motor valve is automatically adjusted.

23. The hydraulic assisted motor valve actuator of claim 22, the stroke amplifier further includes a secondary piston, the secondary piston being hydraulically coupled operably with the main piston so that a movement of the secondary piston produces a corresponding and opposite movement of the main piston.

24. The hydraulic-assisted motor valve actuator of claim 23, wherein the secondary piston is hydraulically coupled operably to the main piston by means of a plenum chamber. • control .

25. The motor valve actuator aided by hydraulic means 5 of claim 24, wherein the control chamber can be operably coupled to a source of liquid under pressure, a check valve being located between the control chamber and the control chamber. source of the liquid, the check valve opening in response? 10 at a certain pressure in the control chamber to admit the filling liquid into the control chamber.

26. The hydraulic assisted motor valve actuator of claim 17, wherein the positioning system of the auxiliary valve includes a solenoid.

27. The hydraulic assisted motor valve actuator of claim 26, wherein the solenoid has a linear stroke less than substantially 6 mm. ^^

28. The motor valve actuator aided by hydraulic means of claim 25, wherein a leak of The liquid selected in the control chamber leads to the main piston being seated during retraction before the secondary valve is seated during retraction to ensure the seating of the main piston in each retraction event.

29. The hydraulic-assisted motor valve actuator of claim 28, wherein the seating of the main piston causes a pressure drop in the control chamber, the pressure drop acting to cause the opening of the check valve.

30. The hydraulic-assisted motor valve actuator of claim 29, wherein the volume of the control chamber is variable as a function of the valve clearance for the engine valve.

31. The hydraulic-assisted motor valve actuator of claim 19, wherein the acting stroke of the needle valve is amplified by a factor related to the secondary piston rate to the main piston.

32. The hydraulic assisted motor valve actuator of claim 31, wherein the ratio of the secondary piston to the main piston is selectively variable between greater than 1: 1 and less than 6: 1.

33. A method for actuating a motor valve comprises the steps of: operably coupling a servo piston to the motor valve; moving an auxiliary valve in response to the control inputs by means of an auxiliary valve positioning system to measure the hydraulic fluid by means of the translation of the auxiliary valve relative to the servo piston to affect the servo piston and the main piston; amplify a translational stroke of the auxiliary valve positioner system; and moving the motor valve by means of the translation of the servo piston n by means of a force exerted on the servo piston by the hydraulic fluid under pressure, the hydraulic fluid under pressure making the servo piston closely follow the translation of the auxiliary valve to effect a desired profile of translational opening and closing movement of the engine valve, a stroke of the engine valve being substantially equal to the amplified stroke of the auxiliary valve positioning system.

34. The method of claim 33 further includes the step of accommodating the gap of the engine valve.

35. The method of claim 34 further includes the step of amplifying the stroke of the positioning system of the auxiliary valve by means of a main piston.

36. The method of claim 35 for securing the seating of the main piston on each retraction event of the main piston.

37. A valve actuator unit for the provision on a valve head of a bank of engine cylinders, the bank of engine cylinders includes at least two cylinders, each cylinder having at least two valves, each valve being able to circulate between an open arrangement and a closed arrangement, comprises: a plurality of valve actuator modules operably coupled to the valve head, a valve actuator module being paired to each cylinder in the cylinder bank and actuating each of the valves of the cylinder; and an oil channel unit being operably coupled to each of the plurality of valve actuator modules, the oil channel unit conveying a low pressure acting liquid and a high pressure acting liquid, the acting liquid at low pressure. pressure and the liquid acting at high pressure being in communication with each of the plurality of valve actuator modules.

38. The valve actuator unit of claim 37 further includes an adapter plate, each of the plurality of valve actuator units being operably coupled to the adapter plate, the adapter plate being operatively coupled to the head of the valve. valve.

39. The valve actuator unit of claim 37, wherein the liquid acting at low pressure is in communication with a control chamber, the control chamber being refillable by the acting liquid at low pressure in each cycle of opening and closing of the valve .

40. The valve actuator unit of claim 39, wherein the high pressure operating liquid is in communication with a pulse piston, the impulse piston being operably coupled to a valve, the high pressure acting liquid. acting on the impulse piston to open the valve.

41. The valve actuator unit of claim 40 further includes a secondary piston defining part of the volume of the control chamber.

42. The valve actuator unit of claim 42, wherein the secondary piston is spaced apart from the impulse piston and movable along an axis that is substantially parallel to a translational axis of the impulse piston.

43. The valve actuator unit of claim 42, wherein the secondary piston is operably coupled to a valve rotator, the valve rotator acting to displace the secondary piston during the valve cycle.

44. The valve actuator unit of claim 43 further includes a needle, the needle being able to act by a controller and being located in a concentric position on a main piston, the main piston acting to amplify a custom needle stroke. that the stroke of the needle affects the stroke of the valve.

45. The valve actuator unit of claim 44, wherein the main piston is in communication with the control chamber and can be displaced by a force generated by a liquid in the control chamber acting on the main piston.

46. The valve actuator unit of claim 45, wherein the needle and the main piston act cooperatively to bring the acting liquid to high pressure to and from the impulse piston for activation of the valve operably coupled to the piston. of impulse.

47. The valve actuator unit of claim 39, wherein replenishing the acting liquid in the control chamber acts to adjust the valve clearance.

48. A valve actuator module for disposing in an engine cylinder, the cylinder having at least two valves, each valve being capable of running between an open arrangement and a closed arrangement, comprises: a pulse piston operably coupled to the valve and being in selective communication with a liquid acting at low pressure and a liquid acting at high pressure, the liquid acting at high pressure acting on the impulse piston at the stroke of the valve open; an amplifier being in hydraulic communication with the impulse piston, the amplifier acting to amplify an actuating stroke commanded by a controller to proportionally increase the stroke of the valve.

49. The valve actuator unit of claim 48, wherein the liquid acting at low pressure is in communication with a control chamber, the control chamber being refillable by the acting liquid at low pressure at each closing stroke of the valve .

50. The valve actuator unit of claim 49 further includes a secondary piston defining in part a volume of a control chamber.

51. The valve actuator module of claim 50, wherein the secondary piston is spaced apart from the impulse piston and movable along an axis that is substantially parallel to a translational axis of the impulse piston.

52. The valve actuator module of claim 51, wherein the secondary piston is operably coupled to a valve rotator, the valve rotator acting to move the secondary piston during the closing stroke of the valve.

53. The valve actuator module of claim 52 further includes a needle, the needle being operable by the controller and being concentrically located on a main piston, the main piston partially comprising the amplifier and acting to amplify a needle stroke when the stroke of the needle affects the stroke of the valve.

54. The valve actuator module of claim 53, wherein the main piston is in communication with the control chamber and can be displaced by a force generated by a liquid in the control chamber acting on the main piston.

55. The valve actuator module of claim 54, wherein the needle and the main piston act cooperatively to bring the acting liquid under high pressure to and from the impulse piston for activation of the valve operably coupled to the piston. of impulse.

56. The valve actuator module of claim 49, wherein the filling of the acting liquid in the control chamber acts in part to adapt the valve clearance.

57. The valve actuator module of claim 49, wherein a volume of the control chamber is automatically variable to accommodate the valve clearance.