in referring to the diagrams , the following terms will be used for brevity and clarity but are not meant to limit the scope of the claims : fluid is a liquid or gas such as hydraulic fluid or air , a spool is a flow control device such as a poppet valve or pneumatic spool or hydraulic spool for communicating fluid flow and pressure , a check valve is a one - way check valve or an adjustable pressure regulating device in combination with a one - way check valve , a piston is a piston or a diaphragm , a valve is an intake or exhaust valve of a combustion chamber of an internal combustion engine . referring to fig1 , 2 , and 6 , the present invention pertains to a device for controlling the movement of a valve 15 , which allows intake or exhaust flow of a combustion chamber through runner 15 a , with a double acting actuator piston 11 . a series of flow control devices , including solenoid actuated spools 20 & amp ; 21 used to communicate fluid to the upper chamber 13 and check valves 22 & amp ; 23 ( or as an alternate embodiment , solenoid actuated spools ) used to communicate compressible fluid to the lower chamber 14 , coordinated so as to operate the valve 15 through chamber - pressure differential . in the primary embodiment both chambers 13 & amp ; 14 receive pressure regulated compressed air . the double acting actuator piston 11 is displaceably arranged within an actuator cylinder 12 so as to separate chambers 13 & amp ; 14 , and is manufactured such that leakage between the opposing chambers 13 & amp ; 14 can be controlled ( sealed ) while allowing the necessary movement to double - actuate ( open and close ) the valve 15 . the actuator piston 11 is mechanically attached to the valve 15 stem so as to move the valve 15 within the valve 15 guide . in construction , the actuator cylinder 12 and chambers 13 & amp ; 14 are formed in a housing that may be a cast - in - place part of the engine head or mechanically fastened in place . the housing has an inlet 16 and an outlet 17 for the upper chamber 13 and an inlet 18 and an outlet 19 for the lower chamber 14 either as part of the housing , within end - cap 10 , or a combination . in addition , the housing and / or end cap ( s ) may provide for mounting pressure and / or flow control devices as described below , and connecting supply 20 b and 22 b , and exhaust 21 b and 23 b manifolds . the upper chamber inlet 16 pressure control consists of two spools 20 , which function as an ‘ xnor gate ’, actuated independently by electronically controlled solenoids 20 a . the upper chamber inlet pressure is supplied from a pressure regulated supply manifold 20 b in the preferred embodiment . the upper chamber outlet 17 pressure relief consists of a single spool 21 moved by an electronically actuated solenoid 21 a . alternately , the upper chamber outlet 17 pressure relief can be two spools , which function as an ‘ xnor gate ’, actuated independently by bistable electronically controlled solenoids . the upper chamber outlet pressure is exhausted to a pressure regulated exhaust manifold 21 b in the preferred embodiment . the lower chamber inlet 18 pressure control consists of a check valve 22 , connected to the pressure regulated supply manifold 22 b . alternately , the lower chamber inlet 18 pressure control can be a single spool actuated by an electronically controlled solenoid ( not shown ). the lower chamber outlet 19 pressure relief consists of a check valve 23 , connected to the pressure regulated exhaust manifold 23 b , to the atmosphere , or to other suitable outlet . alternately , the lower chamber outlet 19 pressure relief can be a single spool actuated by an electronically controlled solenoid . as shown in fig6 , the expected use of the present invention is a coordinated system of more than one actuator device , each actuator device mechanically connected to an intake valve 15 or an exhaust valve 15 of an internal combustion engine , one device per valve 15 . alternately , it is possible to actuate more than one valve 15 for each actuator through the use of lever arms or other mechanical connections . the bistable solenoids 20 a and ( if used ) 21 a are triggered by an electronic control circuit consisting of a microprocessor , various inputs and sensors , shift registers ( optional for small systems ), h - bridge controller circuits or ics and the connectors , power supplies , switches , relays , and the necessary circuitry and parts to connect , regulate , and protect these components . to implement the interactive features of a programmable system , additional interface connections ( obdii , usb , or equivalent , or wireless ) are required , as is a program to allow programming , configuring , and i / o with , the microprocessor . referring to fig3 and 4 , in the primary embodiment each pressure regulator and solenoid is controlled electronically so that the timing and extent of valve 15 movement is adjustable to meet engine operating parameters by a combination of pressure settings and timing signals . varying the pressure in the supply 20 b and exhaust 21 b manifolds and of the operating pressure of one - way check valves 22 and 23 ( by the pressure settings of manifold 22 b and 23 b ) enables the valve 15 to be subjected to ( relatively ) lower forces at low rpm and only subjected to higher forces at high rpm . referring to fig5 a and 5b , the method of controlling valve 15 movement relies on the cycle of pressures applied to the actuator piston 11 by differential chamber pressure , sample calculations used to develop these pressure settings and forces resulting therefrom are shown . the upper chamber high pressure provides valve 15 opening force , net of lower chamber low - through - high pressure ( transitioning as the fluid is compressed ) and then hold open force . the lower chamber high pressure provides valve 15 return force , net of upper chamber low pressure ( once upper chamber high pressure is released ). the lower chamber low pressure provides valve seat force , net of upper chamber low pressure . in summary , the lower chamber acts as a pneumatic spring , while varying pressure in the upper chamber alternately compresses and releases this pneumatic spring . more specifically , the upper chamber inlet spools 20 can be controlled as an ‘ xnor gate ’ to independently and variably control valve 15 timing , duration and lift , using the following preferred method : valve 15 timing and duration are controlled by the timing of the triggering of the inlet solenoid ( pair ) 20 a and outlet solenoid 21 a , particularly alternating states of the inlet spools 20 , actuating common ports to allow fluid flow and pressure communication , and actuation of non - common ports to block pressure communication and fluid flow , from manifold 20 b into the upper chamber 13 , only movement of one spool at a time being required to effect a state change . signal processing and inertial movement delays within the system — typically on the order of a few milliseconds , as well as engine crankshaft angle and rotational speed , are used to calculate solenoid 20 a and 21 a control trigger signal generation . discrete signals to the pair of inlet solenoids control charge - pulse duration ( therefore volume and pressure ) and offset signal timing can control valve 15 lift . for required charge - pulse durations equal to or longer than solenoid movement duration ( on the order of 5 ms ), one solenoid ( e . g . currently at logic state ‘ a ’) is triggered with or prior to the other solenoid ( e . g . currently at logic state ‘ b ’). for shorter required charge - pulse durations ( and lower valve 15 lift ), the second solenoid above is triggered slightly prior to the first solenoid above , thus allowing shortening of the charge - pulse duration to as short as the signal switching repeatability limits ( on the order of 0 . 5 ms ). in the preferred embodiment the upper chamber outlet spool 21 can be accurately controlled by a single solenoid since the outlet 17 discharge - pulse duration is not as critical as the inlet 16 charge - pulse duration and the outlet pressure is suitably controlled by the exhaust manifold 21 b , valve 15 closure ‘ lift ’ being constant 0 . the adjustment to the lower chamber low pressure is through a one - way check valve 22 , in which supply pressure can pass through the one - way check valve 22 when the lower chamber low pressure falls below a determined level . the adjustment to the lower chamber high pressure is through a one - way check valve 23 when the lower chamber high pressure exceeds a determined level . the preferred embodiment is for the one - way check valves 22 & amp ; 23 to be attached to pressure adjustable manifolds 22 b and 23 b respectively , thereby allowing dynamic adjustment during engine operation . the timing of valve 15 operation can be altered to enable smooth low rpm operation ( later intake pulse and decreased valve overlap ) and efficient high rpm operation ( earlier intake pulse and increased valve overlap ) with an almost continuous transition . the duration and lift of valve 15 operation can be altered to meet low demand ( short duration , small lift ) and high demand ( long duration , large lift ) with an almost continuous transition . in addition , unique combinations are available with this system : some valves 15 ( and thereby , combined with temporary fuel and possibly ignition spark cutout , some combustion chambers ) can be temporarily non - actuated , allowing the engine to behave as one of smaller displacement operating at increased air - flow ( higher efficiency during low demand operation ); some valves 15 timing can be staggered within an engine cylinder to promote fuel - air swirl ; some valves 15 can be actuated or non - actuated to allow engine cylinders to behave as two or more valve 15 arrangements to meet varying operating parameters . to influence vibration and temperature variation between cylinders when such non - actuation is in practice , the firing order may be adjusted while the engine is in operation , for instance by switching ( a ) pair ( s ) of cylinders separated by 360 degrees ( ½ of an engine cycle ). an increase in efficiency is expected due to removal of the throttle plate , varying valve duration and lift , and cylinder cut - out , to control fuel - air induction , thereby reducing pumping losses through the engine . an orifice restricted upper chamber outlet muffler ( not shown ) may be incorporated to provide a ‘ soft seat ’ for valve 15 closure . mechanical methods of softening the impact ( so called ‘ bump stops ’) at piston 11 travel limits may be used as well . although the primary embodiment uses both of these braking methods to reduce noise and mechanical wear , some ( or all ) applications may function normally without this ‘ braking ’ or may use a substitute method . referring to fig3 , 4 , 5 a and 5 b , a unique benefit of the primary embodiment is the flexibility for maintenance and upgrade programming of the electronic control system . this method will allow manufacturers and tuners to tailor engines for different operating conditions and demands and update in - place systems as changes are specified without changing hardware in many instances . a layered software system design is preferred wherein a main program determines overall behavior characteristics of the system and a parameter table is used to ‘ tune ’ the system . different ‘ modes ’ can be pre - programmed to allow the driver to select from a set of engine performance behaviors ( ex : ‘ economy ’, ‘ city ’, ‘ sport ’, ‘ towing ’, ‘ valet ’, etc .). the preferred embodiment uses a continuously replenished pneumatic ( air ) supply and exhaust system for speed of operation and low cost construction . one alternate embodiment could use hydraulic fluid as the upper chamber 13 circuit fluid , although this would require changes to the seals and pressure system , and the use of a recovery and storage system . a limitation of the present invention is leak - down over time . although some leak - down is unavoidable and easily dealt with , a seal failure or engine start after a long delay could lead to engine damage due to piston - valve interference . there are two strategies for dealing with this potential : primarily , the device can be restricted to use in non - interference engines . the decrease in power and efficiency can be more than recouped by turbo - charging the engine intake system . since this is common and inherently increases efficiency it is the preferred embodiment . secondly , the system can incorporate safety pumps and latches to prevent piston - valve strike under normal operation , including startup . for system reliability it is anticipated that some form of monitoring system , most likely one or more pressure sensors , will be incorporated into the electronic and / or fluid circuits . for non - interference engines , a maintenance mode may be programmed that when selected will allow the valves to operate as if the crankshaft was turning in order to check for proper operation . the present invention may provide all or some of the benefits described above , depending on the specifications ( both mechanical and electronic ) as implemented . not all of the benefits will be realized for all applications and failure to provide a desired benefit in any particular application or combination of applications should not be interpreted to limit the scope of the claims made . although the present invention has been described in considerable detail with reference to certain preferred versions thereof , it is understood that other alternates and equivalents of each of the above embodiments are within the scope of the invention . therefore , the spirit and scope of the appended claims should not be limited to the description of the preferred versions contained therein . accordingly , all such modifications are intended to be included within the scope of the invention as defined in the following claims . in the claims , means - plus - function clauses are intended to cover the structures described herein as performing the recited function and not only structural equivalents , but also equivalent structures .