US20050046531A1 - Electromagnetic valve system - Google Patents
Electromagnetic valve system Download PDFInfo
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- US20050046531A1 US20050046531A1 US10/897,875 US89787504A US2005046531A1 US 20050046531 A1 US20050046531 A1 US 20050046531A1 US 89787504 A US89787504 A US 89787504A US 2005046531 A1 US2005046531 A1 US 2005046531A1
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
- F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0686—Braking, pressure equilibration, shock absorbing
- F16K31/0689—Braking of the valve element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/08—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet
- F16K31/082—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet using a electromagnet and a permanent magnet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
- F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
- F01L2009/2146—Latching means
- F01L2009/2148—Latching means using permanent magnet
Definitions
- the invention relates to the field of internal combustion engines. More particularly, the invention relates to a structure and process for the controlled movement, latching and/or disablement valves.
- the poppet valve driven by a camshaft has bee used in internal combustion engines for many years. Modifications to the valve train have been developed to permit changing the valve timing while the engine is in operation. When the timing control prevents the valves from opening during an engine cycle, the cylinder is disabled, and the effect of a variable displacement engine is obtained.
- the advantage of a variable displacement engine is that when less than maximum efficiency power is required, some of the cylinders may be disabled and the remaining active cylinders' power is increased so that they will operate at greater efficiency, while the engine output remains constant. This approach has had limited success in practice because the usual control activates or deactivates half the number of cylinders, and this abrupt change in output torque causes poor drivability.
- the disabling mechanism is relatively slow acting, so that more than one revolution of the crankshaft is required to make the change.
- the valve operation is very fast, independent of engine speed, and can be controlled over 630 crankshaft degrees.
- the camshaft may run at crankshaft speed with valve disablement during compression and expansion strokes for 4 stroke operation. 2 stroke operation may be used for compressor and air motor operation as a pneumatic hybrid engine.”
- An electromagnetic actuator for operating an engine valve of an internal-combustion engine includes two electromagnets; an armature movably disposed in the space between the electromagnets for reciprocation in response to electromagnetic forces generated by the electromagnets; resetting springs operatively coupled to the armature for opposing armature motions effected by the electromagnetic forces; a push rod affixed to the armature for moving therewith as a unit; and a guide for guiding the push rod.
- the guide includes a guide cylinder and a push-rod piston carried by an end of the push rod.
- the push-rod piston is slidably received in the guide cylinder.
- a setting piston is slidably received in the guide cylinder and defines, with the push-rod piston, an intermediate chamber forming part of the cylinder.
- the setting piston has an end adapted to be operatively coupled to the engine valve.
- a fluid supply introduces hydraulic fluid into the intermediate chamber.
- a fluid-control valve is provided which has an open state in which the intermediate chamber communicates with the fluid supply and a closed state in which hydraulic fluid is locked in the intermediate chamber for rigidly transmitting motions of the push-rod piston to the setting piston.
- the actuators include a permanent magnet “that eliminates the need for a holding current while the valve is fully open or closed.
- An electromagnetically operating actuator for control elements capable of making oscillatory movements in displacement machines, more particularly for flat slide shut-off valves and lift valves includes a spring system and a pair of electrically operating switching elements, over which the control element is moveable in two discrete opposite operating positions and is retained thereat by either switching magnet, the locus of the position of equilibrium of the spring system lying between the two operating positions.
- the invention is characterized by the provision of a compression device in engagement with the spring system for relocating the locus of the position of equilibrium of the spring system upon actuation of the compression device.”
- P. Pusic, Electrically Operated Cylinder Valve U.S. Pat. No. 5,074,259, 24 Dec. 1991, describes an “electrically operated cylinder valve and a valve operating device for an internal combustion engine”, in which the valve is “operated by electromagnetic means energized by electrical currents which are controlled by electronic means. The flow of currents determines the valve timing, duration, and lift according to requirements for optimal engine performance under different operating conditions.”
- J. Nitkiewicz, Method and Apparatus for Detecting Engine Valve Motion U.S. Pat. No. 5,769,043, 23 Jun. 1998, describes a “method of and apparatus for detecting engine valve motion are provided in an internal combustion engine having an electromechanical or electromagnetic valve actuator with a ferrous component that moves in a linear path with the reciprocating motion of an engine valve between its open and closed positions.
- the apparatus includes a stationary magnetic field source mounted in the actuator and having an axis aligned with the linear path and positioned such that, at its closest position of travel, the ferrous component alters the magnetic field flux of the magnetic field source.
- a sensor mounted in the longitudinal path between the stationary magnetic field source and the ferrous component and sufficiently spaced from the magnetic field source responds to an amplified change in magnetic field flux at its closest travel position, sensing the change in the magnetic field flux of the stationary magnetic field source caused by the presence and absence of the ferrous component in the closest travel position as an indicator of engine valve motion.”
- a solenoid valve which “comprises a first coil, a plunger, a first and a second opening in the valve, and a latching mechanism placed in association with the first opening.
- the latching mechanism causes latching, with a predetermined latching force, of the plunger to the first opening, and energization of the first coil along a predetermined first polarity causes at least a reduction of the latching force.
- the plunger has a first end towards the first opening and a second end towards the second opening, and a magnetic field extensor extends a first pole of the magnetic field produced by the first coil to the first end of the plunger.
- the extensor comprises a hollow cylindrical ferrous member terminated by a ferrous endpiece and is movable, with the plunger, relative to the first opening.”
- an actuator assembly for an electromagnetically-actuated, spring-loaded positioning system in displacement engines, such as for lifting valves in internal combustion engines.
- the positioning mechanism comprises a three-spring system and two electrically-operated, opposed actuating solenoids, by means of which the actuator may be moved therebetween, and held at, two discreet, mutually-opposite operating positions.
- the actuator assembly further comprises an anchor plate having integrally attached upper and lower stems, wherein the lower stem engages the upper flanged end of a valve stem and, upon reciprocation of the anchor plate, transfers movement to the valve stem which moves the valve from a closed to an open position, or vice-versa.
- the actuator assembly is symmetrically biased by upper and lower halves of the three-spring system.
- the upper spring system includes a first spring disposed to engage the upper stem and stressed to force the actuator assembly to the open position of the valve head.
- the lower spring system comprises: A second spring disposed to engage the lower stem and stressed to move the actuator assembly to the closed position of the valve head; and A third spring disposed to engage a stamp flange on the upper end of the valve stem which spring is stressed to assist the second spring in moving the actuator assembly to the closed position of the valve head.
- Spring constants of each spring are selected to provide a constant neutral point of the spring system over the service life of the actuator assembly.”
- control valve assembly adapted for a fuel injector includes a valve seat with fluid inlet and fluid outlet.
- a poppet valve controls the flow of fluid through the valve seat.
- a pair of electrical actuators are selectively operably energized for releasing the poppet and moving the poppet to valve open and closed positions.
- Split fuel injection can be provided using either sequential operation or concurrent operation, i.e., phasing. Permanent magnets, holding current and residual magnetism enable the latching of the poppet valve in each of the valve open and closed positions.”
- Electromechanically Actuated Valve with Multiple Lifts and Soft Landing U.S. Pat. No. 5,647,311, 15 Jul. 1997
- Electromechanically Actuated Valve with Multiple Lifts U.S. Pat. No. 5,692,463, 2 Dec. 1997, describe an “electromechanically actuated valve for use as an intake or exhaust valve in an internal combustion engine.
- the valve is actuated by a electromechanical actuator assembly which includes a first electromagnet, a second electromagnet and a third electromagnet.
- a first disk is mounted to the valve in a gap between the second and third electromagnets
- a second disk is slidably mounted to the valve between an insert and the first electromagnet.
- An extension on the second electromagnet extends to the second disk, allowing the second disk to move the second electromagnet relative to the third electromagnet, thereby changing the gap and thus the valve lift.
- electromechanical valve system which is latchable with little or no applied energy in either an open or a closed position. Such a system would be a major technological breakthrough. Furthermore, it would be advantageous to provide an electromechanical valve system which allows a soft landing at either end of movement. Such a system would be a further technological breakthrough. As well, it would be advantageous to provide an electromechanical valve system which is readily controllable to increase or decrease the local magnetic flux, such as to promote movement of the valve, or to provide a soft landing of the valve at either end of movement. In addition, it would be advantageous to provide an electromechanical valve system which provides energy recovery, feed back, and/or feed forward sensing and control. Such a system would be a further technological breakthrough.
- a valve is linearly moveable between a first closed position and a second open position.
- a first spring is compressed when the valve is in the first closed position
- a second valve spring is compressed when the valve is in the second open position.
- An electromagnetic actuation assembly and a permanent magnet is combined with the valve, such that the valve is latchable in either a closed or open position, and is readily movable between positions through application of energy to the electromagnetic circuitry.
- the electromagnetic circuitry is controllable to increase or decrease the local magnetic flux, such as to promote movement of the valve, or to provide a soft landing of the valve at either end of movement.
- FIG. 1 is a partial cross sectional view of an electromagnetic valve system
- FIG. 2 is a top schematic view of a permanent magnet clapper
- FIG. 3 is a partial cutaway view of a Model 1 single solenoid magnetic valve control system
- FIG. 4 is a chart showing material characteristics for a permanent magnet
- FIG. 5 is a chart which shows magnetic induction as a function of magnetic field intensity for core material
- FIG. 6 is a chart which shows magnetic force of the permanent magnet as a function of displacement variation for a single solenoid magnetic valve control system
- FIG. 7 is a chart which shows incremental inductance as a function of current for a given air gap for a single solenoid magnetic valve control system
- FIG. 8 is a chart which shows incremental magnetic force as a function of current for a given air gap for a single solenoid magnetic valve control system
- FIG. 9 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 12 volts, with no eddy current;
- FIG. 10 is a transient analysis chart which shows current as a function of time for an applied voltage of 12 volts, with no eddy current;
- FIG. 11 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 24 volts, with no eddy current;
- FIG. 12 is a transient analysis chart which shows current as a function of time for an applied voltage of 24 volts, with no eddy current;
- FIG. 13 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 12 volts, with eddy current effects;
- FIG. 14 is a transient analysis chart which shows current as a function of time for an applied voltage of 12 volts, with eddy current effects;
- FIG. 15 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 24 volts, with eddy current effects;
- FIG. 16 is a transient analysis chart which shows current as a function of time for an applied voltage of 24 volts, with eddy current effects;
- FIG. 17 is a partial cutaway view of a Model 2 double solenoid, three-leg magnetic valve control system
- FIG. 18 is a chart which shows magnetic force of the permanent magnet as a function of displacement variation for a double solenoid, three-leg magnetic valve control system
- FIG. 19 is a chart which shows incremental inductance as a function of current for a given air gap for a double solenoid three leg magnetic valve control system
- FIG. 20 is a chart which shows incremental magnetic force as a function of current for a given air gap for a double three-leg solenoid magnetic valve control system
- FIG. 21 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 12 volts, including eddy current, for a double solenoid three-leg magnetic valve control system;
- FIG. 22 is a transient analysis chart which shows current as a function of time for an applied voltage of 12 volts, including eddy current, for a double solenoid three-leg magnetic valve control system;
- FIG. 23 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 24 volts, including eddy current, for a double solenoid three-leg magnetic valve control system;
- FIG. 24 is a transient analysis chart which shows current as a function of time for an applied voltage of 24 volts, including eddy current, for a double solenoid three-leg magnetic valve control system;
- FIG. 25 is a partial cutaway view of a Model 3 double solenoid, three leg flux return path magnetic valve control system
- FIG. 26 is a chart which shows magnetic force of the permanent magnet as a function of displacement variation for a double solenoid, three-leg flux return path magnetic valve control system
- FIG. 27 is a chart which shows incremental inductance as a function of current for a given air gap for a double solenoid three leg flux return path magnetic valve control system
- FIG. 28 is a chart which shows incremental magnetic force as a function of current for a given air gap for a double three-leg flux return path solenoid magnetic valve control system
- FIG. 29 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system without current;
- FIG. 30 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system without current;
- FIG. 31 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system with an applied current;
- FIG. 32 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system with an applied current;
- FIG. 33 is a first cutaway view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies
- FIG. 34 is a second cutaway view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies
- FIG. 35 is a top schematic view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies
- FIG. 36 is a first cutaway view of a preferred electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies;
- FIG. 37 is a second cutaway view of a preferred electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies;
- FIG. 38 is a schematic view of an electromagnetic valve system having a reciprocating disk clapper comprised of a ferrous or magnetic material;
- FIG. 39 is a schematic view of an electromagnetic valve system which comprises a permanent magnet reciprocating disk clapper;
- FIG. 40 is a schematic view of a controller and power module linked to an electromagnetic valve system
- FIG. 41 is a detailed schematic view of control and power circuitry associated with an electromagnetic valve system
- FIG. 42 is a schematic diagram of generic structures and functionality throughout different embodiments of electromagnetic valve systems.
- FIG. 43 is a cutaway view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies, with the valve in a closed position;
- FIG. 44 is a top schematic view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies
- FIG. 45 is a detailed cross-sectional view of a mechanical spring disabler mechanism
- FIG. 46 is a detailed partial cross-sectional view of a mechanical valve disabler system in a first position with a disabler set
- FIG. 47 is a detailed partial cross-sectional view of a mechanical valve disabler system in a second disabled position with a disabler set
- FIG. 48 is a detailed partial cross-sectional view of a mechanical valve disabler system in a first enabled and closed position
- FIG. 49 is a detailed partial cross-sectional view of a mechanical valve disabler system in a second enabled and opened position
- FIG. 50 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a first position with a disabler set;
- FIG. 51 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a second disabled position with a disabler set;
- FIG. 52 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a first enabled and closed position
- FIG. 53 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a second enabled and opened position
- FIG. 54 is a partial detailed cutaway view of a spring latch mechanism
- FIG. 55 is a profile view of a reverse profile cam lobe.
- FIG. 1 is a partial cross sectional view of an electromagnetic valve system 10 a .
- a valve 12 having a stem 14 , is linearly moveable within a cylinder head 16 , such as through a valve guide 18 .
- the valve 12 is linearly moveable between a closed position 20 a and an open position 20 b , to allow flow into or out of a manifold port 22 .
- the valve 12 comprises a valve face 24 at one end of the stem 14 .
- a clapper 26 is affixed to the stem 14 , such that movement of the clapper results in movement of the valve 12 .
- a valve spring 28 is located between the head 16 and the clapper 26 , which biases the valve 12 toward a closed position 20 a .
- a disable spring 30 is located on an opposing surface of the clapper 26 , to bias the valve 12 toward an open position 20 b .
- the disable spring 30 is typically affixed in relation to the cylinder head 16 , such as by a retainer 32 .
- a first permanent magnet 34 a and first electromagnet 36 a are located on one side of the clapper 26
- a second permanent magnet 34 b and first electromagnet 36 b are located on the opposing side of the clapper 26 .
- the magnetic flux of the second permanent magnet 34 b provides an attractive magnetic force to retain the clapper 26 , such as to latch the valve 12 in the closed position 20 a .
- the magnetic flux of the second permanent magnet 34 a provides an attractive magnetic force to retain the clapper 26 , such as to latch the valve 12 in the open position 20 b.
- the electromagnetic coils 36 a , 36 b typically comprise a toroidal core 56 ( FIG. 3 ), around which electrically conductive wire 54 is wound. Electrical current 57 ( FIG. 3 ) is controllably applied in either direction, such as through the wire 54 , such that the electromagnetic coils 36 a , 36 b are operable to provide a magnetic flux in either vertical direction.
- the electromagnetic valve system 10 a is readily moveable between positions 20 a , 20 b .
- Applied energy to the electromagnets 36 acts to increase or decrease the total magnetic attraction of the clapper 26 .
- the disable spring 30 comprises stored potential energy.
- the clapper 26 and valve 12 move linearly downward toward the open position.
- the valve spring 28 is compressed.
- the first electromagnetic coil 34 a may preferably be energized as the valve approaches the open position 20 b , such as to increase the attractive, i.e. pulling, magnetic force 82 .
- the first electromagnetic coil 36 a may preferably be energized near the end of travel, as the valve 12 approaches the open position 20 b , such as to slow the advance of the clapper 26 , and provide a soft landing in the open position 20 b .
- the magnetic flux provided by some permanent magnets 34 increases significantly at short distances, such as to increase the attractive, i.e. pulling, magnetic force 82 .
- Activation of the electromagnetic coil 36 a to provide a soft landing typically comprises a short time period, such as a pulse, to slow the approach of the clapper 26 .
- the valve spring 28 comprises stored potential energy.
- the clapper 26 and valve 12 move linearly upward toward the closed position 20 a .
- the disable spring 30 is compressed.
- the second electromagnetic coil 36 b may preferably be energized as the valve 12 approaches the closed position 20 a , such as to increase the attractive, i.e. pulling, magnetic force 82 .
- the second electromagnetic coil 36 b may preferably be energized near the end of travel, as the valve 12 approaches the closed position 20 a , such as to slow the advance of the clapper 26 , and provide a soft landing in the closed position 20 a Activation of the electromagnetic coil 36 a to provide a soft landing typically comprises a short time period, such as a pulse, to slow the approach of the clapper 26 .
- the clapper comprises one or more permanent magnets 42 .
- the clapper comprises magnetically attractive, i.e. ferrous material.
- FIG. 2 shows a partial detailed top view of a clapper 26 comprising a plurality of radially aligned permanent magnets 42 .
- each of the magnets 42 is radially aligned toward the valve stem 14 , wherein the north poles 44 face inward, and wherein the south poles 46 face outward.
- FIG. 3 is a partial cutaway view of a Model 1 single solenoid magnetic valve control system 10 b , in which a permanent magnet clapper 26 a is affixed to the stem 14 of a valve, and is moveable between a first electromagnet 36 a and a second electromagnet 36 b .
- the electromagnetic coils 36 a , 36 b are located within yoke assemblies 52 a , 52 b , and comprise wire coils 54 on a core 56 .
- the clapper 26 comprises a magnetic region 42 within a clapper yoke 58 .
- FIG. 4 is a chart 60 showing material demagnetization characteristic curves 66 , 68 for a permanent magnet 42 , comprised of Sm 2 Co 17 , as a function of magnetic field 64 at various temperatures.
- FIG. 5 is a chart 70 which shows 76 magnetic induction 72 as a function of magnetic field intensity 74 for core material, comprised of steel, having a density of 7.9 g/cm3, and an electrical conductivity of 1.03e7 (1/ohm ⁇ m).
- FIG. 6 is a chart 80 which shows 86 magnetic force 82 of the permanent magnet 42 as a function of displacement variation 84 for a single solenoid magnetic valve control system 10 .
- the magnetic attraction force increases significantly.
- the attractive force of a Type One clapper 26 provides 416 N of attractive force.
- FIG. 21 is a chart showing material characteristics for a permanent magnet material used in some embodiments of the clapper 26 , for a magnet comprising SmsCo17, having a density of 7.5 g/cm3, a conductivity of 1.16e6 (1/ ⁇ m), and a rated operating temperature of 150 degrees C.
- FIG. 22 is a chart which shows magnetic induction as a function of magnetic field intensity for core material, for a steel density of 7.9 g/cm3, and an electrical conductivity of 1.03e7 (1/ ⁇ m)
- the winding comprises 24 AWG copper wire, having a bare diameter of 0.511 mm, and a conductivity of 5.8e7 (1/ ⁇ m).
- the valve stem 14 comprises non-metallic material, and comprised a total mass of 80 gm, and the spring constant for the first spring 39 and for the second spring 30 is 30600 N/m.
- FIG. 7 is a chart 90 which shows 96 incremental inductance 92 as a function of current 94 for an air gap of 30 ⁇ m in a single solenoid magnetic valve control system 10 x .
- FIG. 8 is a chart 100 which shows 106 incremental magnetic force 82 as a function of current 94 for an air gap of 30 ⁇ m in a single solenoid magnetic valve control system 10 x.
- FIG. 9 is a transient analysis chart 110 which shows 114 displacement 84 as a function of time 112 for an applied voltage of 12 volts, with no eddy current, for a time period of 16.5 msec.
- FIG. 10 is a transient analysis chart 120 which shows 124 current 94 as a function of time 112 for an applied voltage of 12 volts, with no eddy current.
- FIG. 11 is a transient analysis chart 130 which shows 134 displacement 84 as a function of time 112 for an applied voltage of 24 volts, with no eddy current.
- FIG. 12 is a transient analysis chart 140 which shows 144 current 94 as a function of time 112 for an applied voltage of 24 volts, with no eddy current.
- FIG. 13 is a transient analysis chart 150 which shows 154 displacement 84 as a function of time 112 for an applied voltage of 12 volts, with eddy current effects, in which there is no latching achieved between a clapper 26 and an electromagnet assembly 36 .
- FIG. 14 is a transient analysis chart 160 which shows 164 current 94 as a function of time 112 for an applied voltage of 12 volts, with eddy current effects.
- FIG. 15 is a transient analysis chart 170 which shows 174 displacement 84 as a function of time 112 for an applied voltage of 24 volts, with eddy current effects.
- FIG. 16 is a transient analysis chart 180 which shows 184 current 94 as a function of time 112 for an applied voltage of 24 volts, with eddy current effects.
- FIG. 17 is a partial cutaway view 190 of a Model 2 double solenoid, three leg magnetic valve control system 10 c , in which a permanent magnet clapper 26 a is affixed to the stem 14 of a valve 12 , and is moveable between a first electromagnet 34 a and a second electromagnet 34 b .
- the electromagnetic coils 36 a , 36 b are located within yoke assemblies 52 a , 52 b , and comprise wire coils 54 on a core 56 .
- the clapper 26 comprises aligned magnetic regions 42 a , 42 b within a clapper yoke 58 .
- FIG. 18 is a chart 200 which shows 204 magnetic force 82 of the permanent magnet as a function of displacement 84 variation for a double solenoid, three leg magnetic valve control system 10 c.
- FIG. 19 is a chart 210 which shows incremental inductance 92 , comprising individual coil inductance 214 a , 214 b and combined mutual inductance 216 , as a function of current 94 for a given air gap for a double solenoid three leg magnetic valve control system 10 c.
- FIG. 20 is a chart 220 which shows 224 incremental magnetic force 82 as a function of current 94 for a given air gap for a double three leg solenoid magnetic valve control system 10 c.
- FIG. 21 is a transient analysis chart 230 which shows 234 displacement 84 as a function of time 112 for an applied voltage of 12 volts, including eddy current, for a double solenoid three leg magnetic valve control system 10 c .
- FIG. 22 is a transient analysis chart 240 which shows 244 current 94 as a function of time 112 for an applied voltage of 12 volts, including eddy current, for a double solenoid three leg magnetic valve control system 10 c.
- FIG. 23 is a transient analysis chart 250 which shows 254 displacement 84 as a function of time 112 for an applied voltage of 24 volts, including eddy current, for a double solenoid three leg magnetic valve control system 10 c .
- FIG. 24 is a transient analysis chart 260 which shows 264 a , 264 b current 94 as a function of time for an applied voltage of 24 volts, including eddy current, for a double solenoid three leg magnetic valve control system 10 c.
- FIG. 25 is a partial cutaway view 270 of a Model 3 double solenoid, three leg flux return path magnetic valve control system 10 d , in which a permanent magnet clapper 26 a is affixed to the stem 14 of a valve 12 , and is moveable between a first electromagnet 34 a and a second electromagnet 34 b .
- the electromagnetic coils 34 a , 34 b are located within yoke assemblies 52 a , 52 b , and comprise wire coils 54 on a core 56 .
- the clapper 26 comprises magnetic region 42 a , 42 b within a clapper yoke 58 .
- FIG. 26 is a chart 280 which shows 284 magnetic force of the permanent magnet as a function of displacement variation for a double solenoid, three leg flux return path magnetic valve control system.
- FIG. 27 is a chart which shows incremental inductance as a function of current for a given air gap for a double solenoid three leg flux return path magnetic valve control system.
- FIG. 28 is a chart which shows incremental magnetic force as a function of current for a given air gap for a double three leg flux return path solenoid magnetic valve control system.
- FIG. 29 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system without current.
- FIG. 30 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system without current.
- FIG. 31 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system with an applied current.
- FIG. 32 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system with an applied current.
- FIG. 33 is a first cutaway view 190 of an electromagnetic valve actuation system 10 e comprising discrete spring and electromagnet assemblies, with the valve 12 in a closed position 20 a .
- FIG. 34 is a second cutaway view 200 of an electromagnetic valve actuation system 10 e comprising discrete spring and electromagnet assemblies, with the valve 12 in an open position 20 b .
- FIG. 35 is a top schematic view 206 of an electromagnetic valve actuation system 10 e comprising discrete spring and electromagnet assemblies 198 a , 198 b.
- a spring keeper 192 affixed to the valve stem 14 moves linearly to transfer energy between the disable spring 30 and the valve spring 28 .
- a clapper 26 affixed to the valve stem 14 moves between an upper magnet assembly 198 b and a lower magnet assembly 198 a .
- the upper magnet assembly 198 b comprises an upper permanent magnet 34 b and an upper electromagnet 36 b
- the lower magnet assembly comprises a lower permanent magnet 34 a and a lower electromagnet 36 a.
- the springs 28 , 30 are preferably fastened the far bearing ends, and are not fastened to the spring keeper 192 , such that the springs 28 , 30 are preferably isolated from the dynamic mass of the valve system 10 e during a portion of the valve movement.
- the springs 28 , 30 are rated at 660 lbs./per inch.
- the valve stem shaft is non-magnetic.
- the clapper 26 shown in FIG. 33 and FIG. 34 also comprises a mechanical sleeve 195 , such as to accurately affix the clapper 26 to the valve stem 14 .
- the permanent magnets 34 a , 34 b provide a latching means for the clapper 25 , in either the closed position 20 a or the open position 20 b .
- the permanent magnet 34 a holds the valve spring 28 compressed in the valve open position 20 b , whereby the valve spring 28 retains a high level of potential energy.
- the permanent magnet 34 b holds the disable spring 30 compressed in the valve closed position 20 a , whereby the disable spring 30 retains a high level of potential energy.
- an applied energy to the upper electromagnet 36 b is controllably energized to release the clapper from the closed position 20 a .
- an electromagnetic flux is generated by the electromagnet 36 b , which opposes the permanent magnet flux of the upper permanent magnet 34 b .
- the valve 12 begins to open.
- the applied force of the upper permanent magnet 34 b which has a constant flux, is reduced.
- the valve 12 opens and the clapper 26 moves away from the upper magnet assembly 198 b , whereby the applied flux density from the permanent magnet 34 b falls off very rapidly, such that the attractive force decreases rapidly.
- the spring keeper 192 moves and advances toward the middle region 193 , the spring forces are equal, and the kinetic energy of the system reaches a maximum.
- the spring keeper 192 continues to move, a whereby the kinetic energy of the moving mass of the assembly 195 is converted to stored potential energy in the valve spring 28 .
- the moving mass of the assembly 195 is typically equal to the combined mass of the clapper 26 , the valve 12 , the keeper 192 , and at least a portion of the springs 28 , 30 .
- the kinetic mass of the valve train 195 is minimized by the configuration of the valve spring 28 and the disable spring 30 , whereby kinetic energy is transferred between the valve spring 28 and the disable spring 30 , in a central region 193 of movement, and whereby the mass of either the first or second spring 28 , 30 is substantially isolated from the effective mass of valve train 195 for a portion of movement.
- valve spring 28 is compressed by further downward movement of the valve assembly 195 , comprising the clapper 296 the valve 12 , and spring keeper 192 , while the disable spring 30 becomes isolated from the assembly 195 ( FIG. 34 ).
- valve assembly 195 When the valve assembly 195 approaches the end of travel, e.g. such as toward an open position 20 b , the valve 12 , clapper 26 , and spring keeper 192 decelerate, as the kinetic energy of the valve assembly 195 is transformed to stored potential energy in the valve spring 28 . Near the limit of travel, the applied flux from the lower permanent magnet 34 a provides an attractive force to latch the valve 12 in the open position 20 b.
- the attractive force from between the permanent magnets 34 and the electromagnets 36 is proportional to the displacement distance 84 , i.e. there is a strong attractive force at the very end region of travel.
- energy may be controllably applied to the approaching electromagnet 36 , to promote a ‘soft’ landing.
- the spring keeper 192 compresses the valve spring 28 to the bottom limit of movement, i.e. wherein the clapper 26 approaches the bottom magnet assembly 198 a , the clapper 26 contacts and latches to the lower magnet assembly 198 a , since the magnet force 82 increases as the clapper 26 approaches the magnet assembly 198 a .
- the magnetic holding force is larger than the opposing valve spring force, such that the valve 12 latches in the open position 20 b.
- valve 12 latches in either the closed position 20 a or in the open position 20 b , without the application of energy.
- Release from either latch condition is controllable through applied energy signal, such as from an external control 302 ( FIG. 40 , FIG. 41 ).
- an external controller 302 sends a signal, i.e. energy pulse, to the appropriate magnet assembly 198 , which is latched to the clapper 26 .
- the applied pulse overcomes the permanent magnet attraction force, such that the compressed spring, e.g. the valve spring 28 , acts upon the assembly 195 , which moves toward the opposite position.
- FIG. 36 is a first cutaway view 210 of a preferred electromagnetic valve actuation system 10 f comprising discrete spring 224 and electromagnet 226 assemblies, in a closed position 20 a .
- FIG. 37 is a second cutaway view of a preferred electromagnetic valve actuation system 10 f comprising discrete spring 224 and electromagnet 226 assemblies, in an open position 20 b .
- the electromagnetic valve actuation system 10 f comprises a single axially polarized, single, non-moving permanent magnet 34 , and a single electromagnet and coil 36 .
- the spring assembly 224 comprises two separate springs 28 , 30 , which act independently, i.e. the springs 28 , 30 are alternately isolated from the dynamic mass of the valve assembly 195 , which reduces the spring moving mass, and reduces spring friction.
- the permanent magnet 34 is preferably square or rectangular, in vertical cross section, to provide an increased magnetic flux over the footprint of the cylinder head 16 .
- the square or rectangular permanent magnet 34 has more flux than a round one of equal diameter, which allows springs 28 , 30 having higher spring forces to be used.
- the electromagnetic valve actuation system 10 f also preferably comprises full width magnet poles 212 , 214 , to carry more magnetic flux.
- the clapper 26 is typically cylindrical in profile, to allow rotation of the valve 12 .
- valve stem 14 screws into the clapper 26 , and is preferably held with a locking compound 227 , such as LOCTITETM, such that the spring keeper 192 is mechanically affixed to the valve assembly 195 .
- LOCTITETM LOCTITETM
- the spring keeper 192 acts as a piston, to balance the manifold pressure.
- the fixed ends 228 of the springs 28 , 30 are screwed into position, to retain the springs in a perpendicular position, with the vertical forces equally distributed across the springs 28 , 30 .
- the valve seat and the opening stop 222 stops the keeper 192 near seating, to provide adjustment for temperature and wear.
- the free lengths of the springs 28 , 30 preferably overlap slightly, so that the moving spring mass 195 can transfer kinetic energy at the mid point 193 ( FIG. 34 ).
- valve 12 is shown in the closed position 20 a .
- the coil 36 is energized to oppose the permanent magnet flux (PMF) and effectively cancel the PMF holding force, which causes the disabler spring 30 force to accelerate the valve 12 in the opening direction 20 b.
- PMF permanent magnet flux
- the keeper 192 contacts the valve spring 28 .
- the disabler spring 30 delivers kinetic energy to the valve spring 28 , by the time the disabler spring 30 reaches a free length, where the disable spring 30 stops moving.
- the valve spring 28 absorbs the kinetic energy, and decelerates the moving mass 195 toward the open position 20 b.
- the controlled movement of the valve system 10 f from the open position 20 b to the closed position 20 a is provided by the reverse of the opening motion.
- the coil 36 is energized to oppose the permanent magnet flux (PMF) and effectively cancel the PMF holding force, which causes the valve spring 28 force to accelerate the valve 12 in the closing direction 20 a.
- PMF permanent magnet flux
- the keeper 192 contacts the disable spring 30 .
- the valve spring 28 delivers kinetic energy to the disable spring 30 , by the time the valve spring 28 reaches a free length, where the valve spring 28 stops moving.
- the disable spring 30 absorbs the kinetic energy, and decelerates the moving mass 195 toward the closed position 20 a .
- the assisting flux from the coil 36 is typically proportionately decreased, so that the keeper 192 arrives at the top position with close to zero speed, and the magnetic force PMF from the permanent magnet 34 holds the valve 12 closed 20 a.
- FIG. 38 is a schematic view 240 of an electromagnetic valve system 10 g having a clapper 26 comprised of a ferrous or magnetic material, wherein the clapper 26 comprises a reciprocating disk.
- the permanent magnets 34 are integrated within the electromagnets 36 , which provides magnetic attraction to the disk 26 without the need for electrical energy.
- a “reverse” electrical pulse to the appropriate electromagnet 36 e.g. 36 a , cancels the permanent magnet field to cause the release of the disk 26 .
- the springs 28 , 30 then force the disk 26 and connected valve 12 to the opposing permanent/electromagnet 34 , 36 .
- the disk 26 is attracted to the opposing permanent/electromagnet, where it comes to rest.
- the electromagnetic valve system 10 h provides latching, either open or closed, without requiring power, even after the engine is turned off. Only a brief current pulse is required to cause the valve 12 to switch to the opposing position 20 a , 20 b . Thus, power is only consumed for a brief period.
- the permanent magnet clapper 26 approaches the electromagnet 36 , the changing magnetic field is preferably converted to electrical energy, to be returned to a power module 304 ( FIG. 40 , FIG. 41 ).
- the electromagnets 36 a , 36 b additionally repel the clapper 26 , such as to provide for fast valve speeds.
- FIG. 39 is a schematic view of an electromagnetic valve system 10 h which comprises a permanent magnet clapper 26 , wherein the clapper 26 comprises a permanent magnet reciprocating disk.
- the reciprocating disk clapper 26 is attached to the engine valve 12 , such as by a rod that passes through one electromagnet 36 .
- Electromagnets 36 a , 36 b are placed at both ends of the disk travel.
- the electromagnets 36 have the ability to controllably attract or repel the permanent magnet clapper 26 , depending on the polarity of the voltage applied to the electromagnet 36 .
- the permanent magnet 36 in not in close proximity to the electromagnet (within approximately 0.05 inches), the only forces acting on the magnet clapper are spring forces.
- the two springs 28 , 30 accelerate and decelerate the disk 26 and valve 12 to the opposing valve positions 20 a , 20 b.
- the electromagnetic valve system 10 h provides latching, either open or closed, without requiring power, even after the engine is turned off. Only a brief current pulse is required to cause the valve 12 to switch to the opposing position 20 a , 20 b . Thus, power is only consumed for a brief period.
- the permanent magnet clapper 26 approaches the electromagnet 36 , the changing magnetic field is preferably converted to electrical energy, to be returned to an energy exchange and storage system ( FIG. 41 ), e.g. such as a battery or an LC circuit.
- the electromagnets 36 a , 36 b additionally repel the permanent magnet clapper 26 , such as to provide for fast valve speeds.
- the electromagnetic valve system 10 h is typically comprises low eddy current, i.e. low loss, materials as well as energy recovery circuitry, will help reduce energy consumption. Some embodiments of the electromagnetic valve system 10 h provide soft landing controls, such that the valve 12 and/or disk 26 do not “slam” into other engine parts as the valve comes to rest.
- the soft landing control typically comprises the provision of a short electrical repelling force to the appropriate electromagnet 36 , as the disk 26 approaches. In some system embodiments, at least a portion of the energy required for the soft landing pulse is provided from the energy recovery circuitry.
- FIG. 40 is a schematic view 300 of a controller 302 and power module 304 linked to an electromagnetic valve system 10 .
- FIG. 41 is a detailed schematic view 350 of control 302 and power circuitry 304 associated with an electromagnetic valve system 10 . While the exemplary system 10 is similar in detail to system 10 e , as seen in FIG. 33 and FIG. 34 , the controller 302 and power module 304 are readily used throughout the various system embodiments 10 .
- the electromagnetic valve systems 10 can be used for a wide variety of applications.
- the electromagnetic valve system 10 is able to controllably open and or close a valve 12 at any time, and is not mechanically limited to camshaft and/or a crankshaft.
- valves 12 The opening and/or closing of valves 12 is readily accomplished at any time within an engine cycle. Furthermore, one or more valves 12 are readily latched in either an open or a closed position, such that one or more cylinders may readily be disabled.
- valve timing and duration is readily controlled and modified.
- the electromagnetic valve system provides real-time profiling of valve operation, such as to provide longer valve duration, to alter valve timing for opening and/or closing.
- Valve trains in conventional engines are linked through a camshaft to the crankshaft of the engine, such that operation of the valve train is inherently linked to the crankshaft speed.
- the electromagnetic valve system is inherently independent of the speed the engine.
- the electronic valve system can readily operate in a somewhat conventional manner, whereby the opening and closing of valves is synchronized to the crankshaft speed.
- the electromagnetic valve system 10 is readily controlled for any different operation conditions, such as for changes in ambient temperature, pressure, humidity, and/or internal friction.
- the electromagnetic valve system 10 is also readily controlled for differing demands for power and/or torque, demands for acceleration or deceleration.
- the time to open and/or close a valve 12 in a conventional engine is mechanically linked to a cam profile.
- the time to open and/or close a valve 12 in the electromagnetic valve system 10 is independent of the mechanical limitations of a cam.
- the transit time, the time to open or close a valve 12 is controllable in the electromagnetic valve system 10 , whereby a latched valve 12 is readily released and moved to an opposite position 20 .
- the initial release of a valve 12 is enhanced by a strong electromagnetic pulse, to quickly accelerate the clapper 26 from the latched position.
- valve open period is readily and precisely controlled, such that a cylinder can be filled with an air-fuel charge more completely and fully, which at a low engine speed in some embodiments, provides a higher torque output, e.g. 15-20 percent, as compared to a conventional cam-driven engine.
- the speed at which a valve 12 is determined by the applied power to the latching electromagnet is determined by the applied power to the latching electromagnet. Therefore, while there is an advantage to opening and/or closing a valve rapidly, the applied energy is typically increased to provide a fast release from a latched position.
- a desired valve speed and energy consumption maximum is determined, to provide sufficient valve speed while conserving applied energy.
- the applied forces on the valve assembly 195 include the opposing force applied by the spring 28 , 30 , e.g. the valve spring 28 , and the attractive magnetic force between the clapper 26 and the appropriate electromagnet assembly 134 .
- the attractive force of a permanent magnet 34 increases significantly at small distances 84 , such that the valve 12 readily latches to the endpoint 20 at the end of travel.
- Some embodiments of the electromagnetic valve system 10 include soft landing means to prevent a hard landing of the valve assembly 195 at a latch position, whereby a small amount of energy is applied by the electromagnet 36 to provide a controlled opposing force between the permanent magnet 34 and the electromagnet 36 during landing. The resultant applied flux opposes the attractive flux of the permanent magnet 34 , to provide a soft landing.
- the resistance force on the landing is dependent on friction within the assembly, whereby the potential and kinetic energy of the system, from the compressed spring, is reduced, due to friction.
- valve 12 may never reach the end of the travel, in which too much kinetic energy is lost, due to friction.
- the clapper 26 may not reach and latch to the electromagnet 36 and permanent magnet 34 , and the assembly oscillates, and energy dissipates due to friction, until the two spring forces are equal.
- the electromagnetic valve system 10 therefore typically comprises means to input energy into the assembly 10 , such as to provide an opposing electromagnetic flux to initiate movement of the valve 12 from a latched position, or to provide an attractive force by the appropriate electromagnet 36 at the end of travel, to assure that the assembly latches at the end position.
- the electromagnets are preferably used to initiate travel, i.e. to overcome the attractive force of the permanent magnet in a latch position; to input energy to the valve train, such as to promote valve speed and/or to overcome friction; to provide an attractive force to between the permanent magnet at the end of a travel; and/or to provide an opposing force at the end of a travel, to promote a soft landing.
- the applied energy to the electromagnets 36 is typically controlled by the processor 302 , and may comprise a variety of formats, such as steps or pulses.
- the controller 302 is preferably configured to modify the applied energy, such as to compensate for operating conditions or desired performance parameters 370 a - 370 n , such as but not limited to temperature, friction, long-time wear characteristics, seating of the valve, and/or cylinder pressure applied to the face of a valve.
- Electromagnets are also used as system sensors.
- the clapper 26 moves in relation to the electromagnets 36 . Since the permanent magnet 36 is a flux carrying element, relative movement of the clapper 26 in relation to the electromagnets 34 and/or permanent magnet can be sensed by analysis of the flux at the electromagnets.
- the controller 302 detects the rate of change of flux, whereby the speed of the clapper 26 and valve 12 is indicated.
- the controller 302 determines the location from the speed at one or more points, such that the controller 302 can determine the movement and response of the valve train through one or more strokes 20 a , 20 b.
- the controller 302 preferably analyzes the movement of the valve train, and can modify the applied energy, based upon the acquired information, such as to increase energy, decrease applied energy, and/or to change the timing if applied energy, either to enhance a current operating condition, or to enhance a dynamic operating condition, e.g. to provide a different power or torque under an acceleration condition, or to conserve fuel during deceleration. Therefore, in the electromagnetic valve system 10 , the magnets are preferably used both as a driving force, and as a means for sensing and control.
- the active mass of the electromagnetic valve assembly is equal to the combined sum of the mass of the valve 12 , the mass of the clapper 26 , and approximately half of each spring 28 , 30 , Wherein one side of each spring 28 , 30 moves, and the opposing end of each spring 28 , 30 is affixed.
- the estimated active mass is approximately half that of the total mass of each spring 28 , 30 .
- the kinetic energy of the system 10 at the midpoint of motion i.e. wherein the potential energy stored by the springs is a minimum, is approximately equal to 1 ⁇ 2 mv2.
- the assembly can be considered to be a single, dynamic compound spring, which may also comprise the central clapper 26 , which is controllable electronically to impart force, to take force out, and also to determine the speed at which the shaft is moving.
- the valve train comprises both a valve spring 28 and a disable spring 30 , which alternately are connected or are disconnected from the dynamic valve train 195 .
- each spring 28 , 30 is extended from a compressed position, to a free length position. At the free length position, the spring is isolated of the moving mass 195 of the valve train 195 , which reduces the dynamic mass of the valve train.
- the springs 28 , 30 are fixed to the head 16 at each end, but are not affixed to the permanent magnet.
- the clapper 26 During the periodic motion of the valve train, as the clapper approaches the central region 193 of travel, the clapper 26 approaches and contacts the approaching spring which is at a resting, i.e. free length, position. When the clapper contacts the oncoming spring 28 , 30 , the clapper 26 briefly contact with both springs 28 , 30 , whereby the kinetic energy of the system is transferred, and the valve 12 and clapper 26 continue to move, while compressing the second spring 28 , 30 , toward the second end 20 , e.g. toward the open position 20 b.
- the dynamic valve assembly 195 exchanges kinetic energy within the central region 193 , such as through an impact, or through a small overlapping region, e.g. wherein the first spring is almost fully extended, and wherein the second spring begins to be compressed.
- the stationary permanent magnets 34 can be provided in a wide variety of form factors, such as a rectangular structure, to provide a greater magnetic flux field than a system having axial restrictions, e.g. such as for a cylindrical movable permanent magnet.
- the alternate electromagnetic valve system 10 seen in FIG. 36 and FIG. 37 provides design flexibility, since the stationary permanent magnets can be configured across the cylinder head, e.g. such as perpendicular to the line between valve centerlines.
- the magnets used for different system embodiments 10 are comprised of a wide variety of magnetic materials, such as suited for the desired thermal environment.
- the permanent magnets 34 are comprised of neodymium.
- the permanent magnets 34 are comprised of samarium cobalt.
- the present magnet 34 fully seated, with no air gap, provides a latching force of 124 pounds.
- square (1.25 inch by 1.25 inch) stationary permanent magnets 34 provide a latching force of about 320 lbs.
- the preferred use of permanent magnets 34 having high magnetic flux properties provides light valve train mass, as well as corresponding fast valve train response times, such as stroke times approaching 1-2 milleseconds.
- the dynamic mass 195 of the valve train includes both that of the valve spring 28 and the disable spring 30 for only a brief transition region 193 in the center of travel, when both springs 28 , 30 are close to their released free-length position, and where the kinetic energy of the valve train is high, and wherein the stored potential energy of the springs is low.
- While some embodiments of the electromagnetic valve system 10 may have a transition length equal to zero, in most system embodiments, there is a transition region 193 greater than zero, such that a smooth energy transfer occurs between the first dynamic portion 195 and the second dynamic portion 195 , i.e. as energy is transferred between springs 28 , 30 .
- Movement of the electromagnetic valve system 10 from the open position 20 b to the closed position 20 a is similar to the actions required to move the electromagnetic valve system from the closed position 20 b to the open position 20 a .
- Electromagnetic energy is applied to the latching electromagnetic coil 36 , such that the stored potential energy in the valve spring 28 overcomes the latching force.
- the valve train 195 moves toward the closed position 20 a , wherein energy may be controllably applied to increase the attractive force at the closing end, as the disable spring is compressed.
- energy to the electromagnetic coil 36 may be applied at the closing end, to provide a soft landing in the closed position 20 a.
- additional energy may controllably be applied by the electromagnetic coils, such as to compensate for friction within the system.
- the applied energy may provide an electromagnetic force which aids the permanent magnet to the latch position, by pulling the clapper 26 into a latch position, within the last portion of travel, in the closing and/or opening direction, e.g. for the last 0.010 to 0.020′′.
- control of the electromagnetic valve system 10 is extremely versatile, allowing: controlled opening and closing of a valve, independent of engine crankshaft position; assisted latch completion and/or release, and preferably providing a soft landing. Based on information from previous valve train movement, the electromagnetic valve system 10 can be dynamically adjusted, such as to after valve timing and/or duration, and/or to adjust opening and/or closing energy parameters.
- Some preferred embodiments of the electromagnetic valve system 10 provide electrical energy exchange between the mechanical valve train and an energy storage system which is connected to the electromagnetic coils, whereby the energy efficiency of the system is improved.
- the energy storage module 370 shown in FIG. 41 preferably comprises an LC circuit 372 , comprising an inductor 374 and a capacitor 376 .
- Stored energy from the capacitor 376 is released from the circuit to the electromagnetic coil 36 .
- excess system energy is recovered from the electromagnetic coil 36 , by storage into the capacitor 76 .
- more energy is applied to the capacitor 376 , such that the increased energy 356 is released to the electromagnetic coil 356 .
- the electrical oscillation 378 of the LC circuit is preferably matched to the mechanical oscillation of the valve train 10 . Based on system operation, the proper level of energy stored in the capacitor 376 is adjusted.
- the electromagnetic valve system 10 is preferably controllable for steady state operation as well as for changing operation conditions. For example, for conditions which require more or less torque, the operation curves of valve timing and/or duration are readily controlled.
- a map is provided and stored of the dynamic characteristics of the engine under different controllable parameters. Based upon the map and desired engine operation, the controller 302 may readily change the operating parameters of the electromagnetic valve system 10 , to achieve the desired result.
- FIG. 42 is a schematic diagram of generic structures and functionality throughout different embodiments of electromagnetic valve systems 10 .
- the electromagnetic valve system 10 generally comprises:
- the permanent magnet system 404 in electromagnetic valve system 10 a may preferably comprise both a permanent magnet clapper 26 affixed to the valve 12 , as well as permanent magnets 34 a , 34 b.
- the permanent magnet system 404 in electromagnetic valve system 10 e comprises both stationary lower and upper permanent magnets 34 a , 34 b , as well as central magnetic circuits 196 a , 196 b , which conduct magnetic energy, such as to aid in movement and/or latching 408 of the clapper 26 .
- the permanent magnet system 404 in electromagnetic valve system 10 f comprises a single permanent magnet 34 , as well as pole blocks 212 , 214 , which conduct magnetic energy, such as to aid in movement and/or latching 408 of the clapper 26 .
- the permanent magnet system 404 in electromagnetic valve system 10 g comprises both stationary lower and upper permanent magnets 34 a , 34 b , such as to aid in movement and/or latching 408 of the clapper 26 .
- the permanent magnet system 404 in electromagnetic valve system 10 h comprises a permanent magnet clapper 26 affixed to the valve 12 , which latches 408 to electromagnetic coil 36 b when the valve 12 is located at the closed position 20 a , and latches 408 to electromagnetic coil 36 a when the valve 12 is located at the open position 20 b.
- the permanent magnet system 404 in electromagnetic valve system 10 i comprises a permanent magnet 34 and one or more magnetically conductive armatures or yokes 453 , which conduct magnetic energy, such as to aid in movement and/or latching 408 of the clapper 26 .
- magnetic field from the permanent magnet system 404 provides a permanent magnet latching force 408 , e.g. 408 a , 408 b , to the valve assembly 12 which is sufficient to hold the valve assembly 12 is in any of the first closed position 20 a and the second open position 20 b .
- energy can be supplied to the electromagnetic system 406 , to help latch the valve assembly 12 in any of the first closed position 20 a and the second open position 20 b , such as but not limited to compensation for diminished strength of the permanent magnet system 404 .
- FIG. 43 is a cutaway view 450 of an electromagnetic valve actuation system 10 i comprising discrete spring and electromagnet assemblies, with the valve 12 in a closed position 20 a .
- FIG. 44 is a top schematic view 460 of an electromagnetic valve actuation system 10 i comprising discrete spring and electromagnet assemblies 36 a , 36 b . While two electromagnets are shown, a single electromagnet may be used. In the preferred embodiment, both electromagnets are actuated together.
- a spring keeper 192 affixed to the valve stem 14 moves linearly to transfer energy between the disable spring 30 and the valve spring 28 .
- a clapper 26 affixed to the valve stem 14 moves between a magnet assembly 34 and electromagnet assemblies 36 a , 36 b .
- the valve stem is a compound structure that has a portion with a threaded end that engages with another portion that has complementary threads.
- the magnet assembly 34 comprises a permanent magnet. Note that in some embodiments, both a north pole of the permanent magnet and a south pole of the permanent magnet are used to attract or repel the electromagnet.
- the springs 28 , 30 are preferably fastened by their ends farthest from the keeper 192 , and are not fastened to the spring keeper 192 , such that the springs 28 , 30 are preferably isolated from the dynamic mass of the valve system 10 i during a portion of the valve movement.
- the springs 28 , 30 are rated at 660 lbs./per inch.
- the valve stem shaft is non-magnetic.
- the permanent magnet 34 provides a latching means for the clapper 26 , in either the closed position 20 a or the open position 20 b . As seen in FIG. 43 , the permanent magnet 34 holds the valve spring 28 compressed in the valve open position 20 b , whereby the valve spring 28 retains a high level of potential energy.
- an applied energy to the electromagnets 36 a , 36 b is controllably energized to release the clapper from the closed position 20 a .
- an electromagnetic flux is generated by the electromagnets 36 a , 36 b , which opposes the permanent magnet flux of the permanent magnet 34 .
- the applied opposing electromagnetic flux reduces the permanent magnet holding force below that of the spring force applied by the disable spring 30 , the valve 12 begins to open.
- the applied force of the permanent magnet 34 which has a constant flux, is reduced.
- the valve 12 opens and the clapper 26 moves away from the permanent magnet 34 , whereby the applied flux density from the permanent magnet 34 falls off very rapidly, such that the attractive force decreases rapidly.
- the spring keeper 192 moves and advances toward the middle region 193 , the spring forces are equal, and the kinetic energy of the system reaches a maximum.
- the spring keeper 192 continues to move, a whereby the kinetic energy of the moving mass of the assembly is converted to stored potential energy in the valve spring 28 .
- the moving mass of the assembly is typically equal to the combined mass of the clapper 26 , the valve 12 , the keeper 192 , and at least a portion of the springs 28 , 30 .
- the kinetic mass of the valve train is minimized by the configuration of the valve spring 28 and the disable spring 30 , whereby kinetic energy is transferred between the valve spring 28 and the disable spring 30 , in a central region 193 of movement, and whereby the mass of either the first or second spring 28 , 30 is substantially isolated from the effective mass of valve train for a portion of movement.
- valve spring 28 is compressed by further downward movement of the valve assembly, comprising the clapper 26 , the valve 12 , and spring keeper 192 , while the disable spring 30 becomes isolated from the assembly ( FIG. 43 ).
- valve 12 , clapper 26 , and spring keeper 192 decelerate, as the kinetic energy of the valve assembly is transformed to stored potential energy in the valve spring 28 .
- the applied flux from the electromagnets 36 a , 36 b provide an attractive force to latch the valve 12 in the open position 20 b.
- the attractive force from between the permanent magnet 34 and the electromagnets 36 a , 36 b is proportional to the displacement distance, i.e. there is a strong attractive force at the very end region of travel.
- energy may be controllably applied to the approaching electromagnets 36 a , 36 b , to promote a ‘soft’ landing.
- the clapper 26 contacts and latches to the electromagnet assembly core because the magnet force increases as the clapper 26 approaches the electromagnets 36 a , 36 b .
- the magnetic holding force is larger than the opposing valve spring force, such that the valve 12 latches in the open position 20 b .
- the core 453 may be made of solid or laminated materials.
- the clapper may also be made of a laminate, preferably a continuous spiral to match the flux of the core.
- a laminated structure is less expensive to build and lighter in weight, and resists the generation of eddy currents, which distort the flux distribution and lose energy.
- the preferred permanent magnet has dimensions of 3/16′′ ⁇ 11 ⁇ 2′′ ⁇ 11 ⁇ 2′′.
- the valve 12 latches in either the closed position 20 a or in the open position 20 b , with the application of minimal energy.
- the latching is provided entirely by magnetic energy provided by the permanent magnet 34 , such that no external energy is required to be applied to any of the electromagnets 36 a , 36 b.
- Release from either latch condition is controllable through applied energy signal, such as from an external control 302 ( FIG. 40 , FIG. 41 ).
- an external controller 302 sends a signal, i.e. energy pulse, to the electromagnets 36 a , 36 b , which is latched to the clapper 26 .
- the applied pulse overcomes the permanent magnet attraction force, such that the compressed spring, e.g. the valve spring 28 , acts upon the assembly, which moves toward the opposite position.
- FIG. 45 is a detailed partial cross-sectional view of a valve disabler system 610 a .
- a valve 612 is moveable in relation to a head 616 having a valve port 617 .
- the valve comprises a valve face 613 at a first end 611 a , which is sealable in relation to a valve seat 615 .
- the valve 612 also includes a valve stem 614 which extends from the first end 611 a to a second end 611 b .
- a valve cap 616 is located at the second end 611 b , such as a valve cap assembly 616 , e.g. comprising a cap & retainers.
- a valve spring 618 provides a compressive force between the valve 612 and a spring landing 620 , which may be an integral portion of the head 616 .
- the valve spring 618 retains the valve 612 in a normally closed position 21 a ( FIG. 46 ) in relation to the head 616 .
- the compression of the valve spring 618 provides a bias force against the valve cap 616 .
- a disable spring 622 is also affixed to the valve cap 616 , and provides tension to controllably open the valve 612 .
- the disable spring 622 is also affixed to a ring holder 624 , such as by a first holder landing 626 .
- a cam spring 630 is located between the ring holder 624 , such as by a second holder landing 628 , and controllably provides a compressive force between the ring holder 624 and a movable cam cap 632 .
- a rotatable camshaft 634 having a cam lobe 636 , controllably acts upon the cam cap 632 , to compress the cam spring 630 .
- the valve disabler system 610 a includes a disabler latch 640 , which is movable between an unlatched, i.e. valve enabled, position 652 a , and a latched, i.e. valve disabled, position 652 b .
- the disabler latch 640 is in a latched position, such that rotation of the camshaft 634 does not result in movement of the valve 612 toward an open position 21 b ( FIG. 49 ).
- FIG. 46 is a partial cutaway view 660 of a valve disabler system 610 a in an uncompressed, disabled state 662 .
- FIG. 47 is a partial cutaway view 670 of a valve disabler system 610 a in a compressed, disabled state 672 . As seen in FIG. 46 and FIG. 47 , when the ring holder 624 is confined by the latched position 652 b by the disable latch 640 , rotation of the camshaft 634 does not result in the opening of the valve 612 .
- the cam lobe profile 636 acts to push the cam cap 632 from a top position 650 a toward a lower position 650 b , which compresses the cam spring 630 .
- the ring holder 624 is prevented from vertical movement, by the disable latch 640 being located in the locked position 652 b .
- the valve 612 remains closed 21 a.
- FIG. 48 is a partial cutaway view 680 of a valve disabler system 610 a in an uncompressed, enabled state 682 .
- FIG. 49 is a partial cutaway view 690 of a valve disabler system 610 a in a compressed, enabled state 692 .
- FIG. 48 and FIG. 46 when the ring holder 624 is not confined, due to the enabled position 652 a of the disable latch 640 , rotation of the camshaft 634 results in the opening 21 b of the valve 612 .
- the cam lobe profile 636 acts to push the cam cap 632 from a top position 650 a toward a lower position 650 b , which compresses the cam spring 630 .
- the disable latch 640 is in the enable position 652 a , the ring holder 624 is allowed to move vertically.
- the extended lobe region 636 of the camshaft 634 acts upon the cam spring cap 632 and cam spring 630 , to compress the cam spring 630 .
- the ring holder 624 which is in contact with the second lower end of the cam spring 630 , moves downward in reaction to the compressive force from the cam spring 630 , since the disable latch 640 is in the open “valve enabled” position 652 a .
- the lower end of the disable spring 622 is also connected to the ring holder 624 , such that the reactive downward movement of the ring holder creates tension in the disable spring 622 .
- the valve 612 is vertically affixed to the upper second end of the disable spring 622 , such that the valve opens 21 b in reaction to tension in the disable spring 622 , whereby the valve face 613 extends from the valve seat 615 .
- FIG. 50 is a detailed partial cross-sectional view 700 of an alternate mechanical valve disabler system 610 b in a first position with a disabler set.
- FIG. 51 is a detailed partial cross-sectional view 710 of an alternate mechanical valve disabler system 610 b in a second disabled position with a disabler set.
- FIG. 52 is a detailed partial cross-sectional view 720 of an alternate mechanical valve disabler system 610 b in a first enabled and closed position.
- FIG. 53 is a detailed partial cross-sectional view 730 of an alternate mechanical valve disabler system 610 b in a second enabled and opened position.
- FIG. 54 is a detailed partial cross-sectional view 740 of a spring disabler mechanism 742 in contact with a valve cap 744 located between a valve spring 28 and a disable spring 30 .
- FIG. 55 is a schematic profile 770 of a disabler cam lobe 772 .
- the lobe 772 is preferably designed to accelerate the disable spring 30 and disable spring holder down with just enough forced delivered during approximately one sixth turn of a camshaft 34 , so as to reach a fully compressed position with zero speed (as is done with the conventional camshaft/poppet valve system). In some embodiments, 1 ⁇ 4 revolution is sufficient, since no deceleration is required.
- the disabler solenoid 742 is released as soon as the disabler spring holder 744 begins to move downward, allowing the clapper to move along the outer surface of the holder.
- the rebound spring pushes the clapper along the outer surface of the holder, locking it in place.
- FIG. 54 shows the angled locking surface for both the valve cap and disabler spring holder.
- the solenoid when energized, overcomes the solenoid spring force, and allows the disabler spring holder to move up.
- the disabler spring is restrained from moving up to hold the spring compressed.
- the lobe surface restrains the holder in the up position.
- valve disabler system and its methods of use are described herein in connection with an engine, such as an internal combustion engine, the apparatus and techniques can be implemented for a wide variety of alternate internal combustion and/or hybrid engines, or any combination thereof, as desired. Furthermore, the apparatus and techniques can be implemented for a wide variety of valves and/or actuators, or any combination thereof, as desired.
Abstract
Systems are provided for electromagnetic actuation of a valve mechanism. A valve is linearly moveable between a first closed position and a second open position. A first spring is compressed when the valve is in the first closed position, and a second valve spring is compressed when the valve is in the second open position. An electromagnetic actuation assembly and a permanent magnet is combined with the valve, such that the valve is latchable in either a closed or open position, and is readily movable between positions through application of energy to the electromagnetic circuitry. The electromagnetic circuitry is controllable to increase or decrease the local magnetic flux, such as to promote movement of the valve, or to provide a soft landing of the valve at either end of movement. Some system embodiments provide energy recovery, feed back, and/or feed forward sensing and control. The electromagnetic valve system can be implemented for a wide variety of engines, valves and actuators, such as for variable valve timing, valve disablement, and/or hybrid engine and energy storage applications.
Description
- This application claims priority to U.S. Provisional Patent Application No. 60/490,195, filed 25 Jul. 2003, which is incorporated herein by reference.
- This application is also a Continuation in Part of U.S. application Ser. No. 10/674,743, filed 29 Sep. 2003, which claims priority to U.S. Provisional Patent Application No. 60/417,264, filed 9 Oct. 2002, which is incorporated herein by reference.
- The invention relates to the field of internal combustion engines. More particularly, the invention relates to a structure and process for the controlled movement, latching and/or disablement valves.
- The poppet valve driven by a camshaft has bee used in internal combustion engines for many years. Modifications to the valve train have been developed to permit changing the valve timing while the engine is in operation. When the timing control prevents the valves from opening during an engine cycle, the cylinder is disabled, and the effect of a variable displacement engine is obtained. The advantage of a variable displacement engine is that when less than maximum efficiency power is required, some of the cylinders may be disabled and the remaining active cylinders' power is increased so that they will operate at greater efficiency, while the engine output remains constant. This approach has had limited success in practice because the usual control activates or deactivates half the number of cylinders, and this abrupt change in output torque causes poor drivability. Furthermore, the disabling mechanism is relatively slow acting, so that more than one revolution of the crankshaft is required to make the change.
- While some electromagnetic valve mechanisms have been implemented to operate valves, the energy required to operate the system is typically prohibitive. Energy is often required to retain a valve in either an open or a closed position. Furthermore, the mass of the valve train in such systems is typically substantial, and the movement and landing of componentry is often problematic.
- D. Moyer, Cam Activated Electrically Controlled Engine Valve, U.S. Pat. No. 6,302,069, 16 Oct. 2001, describes “an engine valve control responsive to electrical signals from a controller to open and close a valve. Power to move the valve comes from a camshaft. A disabler spring is compressed by a cam lobe and held compressed by its solenoid while the valve is held from opening by its solenoid. When the valve solenoid releases the valve, a half oscillation between the disabler spring and valve spring opens the valve and the valve solenoid than holds it open. The disabler solenoid then releases the disabler spring. When the valve solenoid releases its spring, a half oscillation of the two springs closes the valve with a soft landing. The valve operation is very fast, independent of engine speed, and can be controlled over 630 crankshaft degrees. The camshaft may run at crankshaft speed with valve disablement during compression and expansion strokes for 4 stroke operation. 2 stroke operation may be used for compressor and air motor operation as a pneumatic hybrid engine.”
- D. Moyer, Fast Acting Engine Valve Control with Soft Landing, U.S. Pat. No. 6,302,068, 16 October 2001, describes “an engine valve control responsive to electrical signals from a controller to open and close valves. Power to move the valves comes from a conventional camshaft. A disabler spring is compressed by a cam lobe and held compressed by a first solenoid, and the valve is held from opening by a second solenoid. When the second solenoid releases the valve, a ½ oscillation between the disabler spring and valve spring opens the valve and a third solenoid holds the valve open. The first solenoid then releases the disabler spring. When the third solenoid releases the valve spring, a ½ oscillation of the two springs closes the valve with a soft landing and the second solenoid again holds the valve closed. The valve operation is very fast, independent of engine speed, and can be controlled over 270 crankshaft degrees. The solenoids, used for holding only, are very small and require little power. The camshaft runs at crankshaft speed. By disabling the cylinders during compression and expansion strokes, 4 stroke operation is used for gasoline motor operation. 2 stroke operation is used for compressor and air motor operation as a pneumatic hybrid.”
- D. Moyer, Engine Valve Disabler, U.S. Pat. No. 6,260,525, 17 Jul. 2001, describes “A method for improving efficiency and reducing emissions of an internal combustion engine. Variable displacement engine capabilities are achieved by disabling engine valves during load changes and constant load operations. Active cylinders may be operated at minimum BSFC by intermittently disabling other cylinders to provide the desired net torque. Disabling is begun by early closing of the intake valve to provide a vacuum at BDC which will result in no net gas flow across the piston rings, and minimum loss of compression energy in the disabled cylinder; this saving in engine friction losses is significant with multiple disablements.”
- D. Moyer, Fuel Efficient Valve Control, U.S. Pat. No. 5,975,052, 2 Nov. 1999, describes “A method for improving efficiency and reducing emissions of an internal combustion engine. Variable displacement engine capabilities are achieved by disabling engine valves during load changes and constant load operations. Active cylinders may be operated at minimum BSFC by intermittently disabling other cylinders to provide the desired net torque. Disabling is begun by early closing of the intake valve to provide a vacuum at BDC which will result in no net gas flow across the piston rings, and minimum loss of compression energy in the disabled cylinder; this saving in engine friction losses is significant with multiple disablements.
- E. Lohse and U. Muller, Electromagnetic Actuator for a Cylinder Valve Including an Integrated Valve Lash Adjuster, U.S. Pat. No. 6,047,673, 11 Apr. 2000, describe “An electromagnetic actuator for operating an engine valve of an internal-combustion engine includes two electromagnets; an armature movably disposed in the space between the electromagnets for reciprocation in response to electromagnetic forces generated by the electromagnets; resetting springs operatively coupled to the armature for opposing armature motions effected by the electromagnetic forces; a push rod affixed to the armature for moving therewith as a unit; and a guide for guiding the push rod. The guide includes a guide cylinder and a push-rod piston carried by an end of the push rod. The push-rod piston is slidably received in the guide cylinder. A setting piston is slidably received in the guide cylinder and defines, with the push-rod piston, an intermediate chamber forming part of the cylinder. The setting piston has an end adapted to be operatively coupled to the engine valve. A fluid supply introduces hydraulic fluid into the intermediate chamber. Further, a fluid-control valve is provided which has an open state in which the intermediate chamber communicates with the fluid supply and a closed state in which hydraulic fluid is locked in the intermediate chamber for rigidly transmitting motions of the push-rod piston to the setting piston.
- M. Theobald, B. Lequesne, and R. Henry, Control of Engine Load via Electromagnetic Valve Actuators, Paper No. 940816, International Congress & Exposition, Detroit, Mich., February 28-Mar. 3, 1994, describes a single-cylinder research engine equipped with programmable valve actuators. The actuators include a permanent magnet “that eliminates the need for a holding current while the valve is fully open or closed.
- F. Pischinger and P. Kreuter, Electromagnetically Operating Actuator, U.S. Pat. No. 4,455,543, 19 Jun. 1984, describe “An electromagnetically operating actuator for control elements capable of making oscillatory movements in displacement machines, more particularly for flat slide shut-off valves and lift valves, includes a spring system and a pair of electrically operating switching elements, over which the control element is moveable in two discrete opposite operating positions and is retained thereat by either switching magnet, the locus of the position of equilibrium of the spring system lying between the two operating positions. The invention is characterized by the provision of a compression device in engagement with the spring system for relocating the locus of the position of equilibrium of the spring system upon actuation of the compression device.”
- D. Bonvallet, Variable Lift Electromagnetic Valve Actuator System, U.S. Pat. No. 4,777,915, 18 Oct. 1988, describes a “housing on the cylinder head of an engine operatively supports an upper solenoid and a tubular lower solenoid such that therein working pole faces are opposed to each other for operatively effecting movement of an armature fixed to the free stem end of a poppet valve having its stem extending up through the lower solenoid. Upper and lower springs each have one end thereof positioned in the upper and lower solenoids, respectively, and the lower solenoid has an actuator operatively connected thereto to effect axial position of the lower solenoid, while the upper solenoid has a lash adjuster operatively associated therewith.”
- P. Pusic, Electrically Operated Cylinder Valve, U.S. Pat. No. 5,074,259, 24 Dec. 1991, describes an “electrically operated cylinder valve and a valve operating device for an internal combustion engine”, in which the valve is “operated by electromagnetic means energized by electrical currents which are controlled by electronic means. The flow of currents determines the valve timing, duration, and lift according to requirements for optimal engine performance under different operating conditions.”
- J. Nitkiewicz, Method and Apparatus for Detecting Engine Valve Motion, U.S. Pat. No. 5,769,043, 23 Jun. 1998, describes a “method of and apparatus for detecting engine valve motion are provided in an internal combustion engine having an electromechanical or electromagnetic valve actuator with a ferrous component that moves in a linear path with the reciprocating motion of an engine valve between its open and closed positions. The apparatus includes a stationary magnetic field source mounted in the actuator and having an axis aligned with the linear path and positioned such that, at its closest position of travel, the ferrous component alters the magnetic field flux of the magnetic field source. A sensor mounted in the longitudinal path between the stationary magnetic field source and the ferrous component and sufficiently spaced from the magnetic field source responds to an amplified change in magnetic field flux at its closest travel position, sensing the change in the magnetic field flux of the stationary magnetic field source caused by the presence and absence of the ferrous component in the closest travel position as an indicator of engine valve motion.”
- F. Schlomi, J. Rogozinski, V. Ivanov, and U. Arkashevski, Solenoid Valve with Permanent Magnet, U.S. Pat. No. 6,199,587, 13 Mar. 2001, describe a solenoid valve which “comprises a first coil, a plunger, a first and a second opening in the valve, and a latching mechanism placed in association with the first opening. The latching mechanism causes latching, with a predetermined latching force, of the plunger to the first opening, and energization of the first coil along a predetermined first polarity causes at least a reduction of the latching force. The plunger has a first end towards the first opening and a second end towards the second opening, and a magnetic field extensor extends a first pole of the magnetic field produced by the first coil to the first end of the plunger. The extensor comprises a hollow cylindrical ferrous member terminated by a ferrous endpiece and is movable, with the plunger, relative to the first opening.”
- P. Kreuter and K. Schmitz, Electromagnetically Operated Adjusting Device, U.S. Pat. No. 5,199,392, 6 Apr. 1993, describe “an actuator assembly for an electromagnetically-actuated, spring-loaded positioning system in displacement engines, such as for lifting valves in internal combustion engines. The positioning mechanism comprises a three-spring system and two electrically-operated, opposed actuating solenoids, by means of which the actuator may be moved therebetween, and held at, two discreet, mutually-opposite operating positions. The actuator assembly further comprises an anchor plate having integrally attached upper and lower stems, wherein the lower stem engages the upper flanged end of a valve stem and, upon reciprocation of the anchor plate, transfers movement to the valve stem which moves the valve from a closed to an open position, or vice-versa. The actuator assembly is symmetrically biased by upper and lower halves of the three-spring system. The upper spring system includes a first spring disposed to engage the upper stem and stressed to force the actuator assembly to the open position of the valve head. The lower spring system comprises: A second spring disposed to engage the lower stem and stressed to move the actuator assembly to the closed position of the valve head; and A third spring disposed to engage a stamp flange on the upper end of the valve stem which spring is stressed to assist the second spring in moving the actuator assembly to the closed position of the valve head. Spring constants of each spring are selected to provide a constant neutral point of the spring system over the service life of the actuator assembly.”
- D. Maley, R. Shinogle, M. Sommars, and O. Sturman, Fuel Injection Control Valve with Dual Solenoids, U.S. Pat. No. 5,494,219, 27 Feb. 1996, describe a “control valve assembly adapted for a fuel injector includes a valve seat with fluid inlet and fluid outlet. A poppet valve controls the flow of fluid through the valve seat. A pair of electrical actuators are selectively operably energized for releasing the poppet and moving the poppet to valve open and closed positions. Split fuel injection can be provided using either sequential operation or concurrent operation, i.e., phasing. Permanent magnets, holding current and residual magnetism enable the latching of the poppet valve in each of the valve open and closed positions.”
- F. Liang and C. Hammann, Electromechanically Actuated Valve with Multiple Lifts and Soft Landing, U.S. Pat. No. 5,647,311, 15 Jul. 1997, and Electromechanically Actuated Valve with Multiple Lifts, U.S. Pat. No. 5,692,463, 2 Dec. 1997, describe an “electromechanically actuated valve for use as an intake or exhaust valve in an internal combustion engine. The valve is actuated by a electromechanical actuator assembly which includes a first electromagnet, a second electromagnet and a third electromagnet. A first disk is mounted to the valve in a gap between the second and third electromagnets, and a second disk is slidably mounted to the valve between an insert and the first electromagnet. An extension on the second electromagnet extends to the second disk, allowing the second disk to move the second electromagnet relative to the third electromagnet, thereby changing the gap and thus the valve lift. A first spring, mounted between the second electromagnet and first disk, and a second spring, mounted between the first disk and an actuator housing, create an oscillatory system which drives most of the valve movement during engine operation, thus reducing power requirements to actuate the valves while increasing the responsiveness of the valves.”
- While other prior art valve systems which use electromagnetic force to move a valve, there is no provision to promote eliminate or reduce a hard landing, which typically results in extremely short valve life, in a structure which retains a valve in either an open or a closed position, within little or no added energy.
- It would be advantageous to provide an electromechanical valve system which is latchable with little or no applied energy in either an open or a closed position. Such a system would be a major technological breakthrough. Furthermore, it would be advantageous to provide an electromechanical valve system which allows a soft landing at either end of movement. Such a system would be a further technological breakthrough. As well, it would be advantageous to provide an electromechanical valve system which is readily controllable to increase or decrease the local magnetic flux, such as to promote movement of the valve, or to provide a soft landing of the valve at either end of movement. In addition, it would be advantageous to provide an electromechanical valve system which provides energy recovery, feed back, and/or feed forward sensing and control. Such a system would be a further technological breakthrough.
- Systems are provided for electromagnetic actuation of a valve mechanism. A valve is linearly moveable between a first closed position and a second open position. A first spring is compressed when the valve is in the first closed position, and a second valve spring is compressed when the valve is in the second open position. An electromagnetic actuation assembly and a permanent magnet is combined with the valve, such that the valve is latchable in either a closed or open position, and is readily movable between positions through application of energy to the electromagnetic circuitry. The electromagnetic circuitry is controllable to increase or decrease the local magnetic flux, such as to promote movement of the valve, or to provide a soft landing of the valve at either end of movement. Some system embodiments provide energy recovery, feed back, and/or feed forward sensing and control. The electromagnetic valve system can be implemented for a wide variety of engines, valves and actuators, such as for variable valve timing, valve disablement, and/or hybrid engine and energy storage applications.
-
FIG. 1 is a partial cross sectional view of an electromagnetic valve system; -
FIG. 2 is a top schematic view of a permanent magnet clapper; -
FIG. 3 is a partial cutaway view of aModel 1 single solenoid magnetic valve control system; -
FIG. 4 is a chart showing material characteristics for a permanent magnet; -
FIG. 5 is a chart which shows magnetic induction as a function of magnetic field intensity for core material; -
FIG. 6 is a chart which shows magnetic force of the permanent magnet as a function of displacement variation for a single solenoid magnetic valve control system; -
FIG. 7 is a chart which shows incremental inductance as a function of current for a given air gap for a single solenoid magnetic valve control system; -
FIG. 8 is a chart which shows incremental magnetic force as a function of current for a given air gap for a single solenoid magnetic valve control system; -
FIG. 9 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 12 volts, with no eddy current; -
FIG. 10 is a transient analysis chart which shows current as a function of time for an applied voltage of 12 volts, with no eddy current; -
FIG. 11 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 24 volts, with no eddy current; -
FIG. 12 is a transient analysis chart which shows current as a function of time for an applied voltage of 24 volts, with no eddy current; -
FIG. 13 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 12 volts, with eddy current effects; -
FIG. 14 is a transient analysis chart which shows current as a function of time for an applied voltage of 12 volts, with eddy current effects; -
FIG. 15 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 24 volts, with eddy current effects; -
FIG. 16 is a transient analysis chart which shows current as a function of time for an applied voltage of 24 volts, with eddy current effects; -
FIG. 17 is a partial cutaway view of aModel 2 double solenoid, three-leg magnetic valve control system; -
FIG. 18 is a chart which shows magnetic force of the permanent magnet as a function of displacement variation for a double solenoid, three-leg magnetic valve control system; -
FIG. 19 is a chart which shows incremental inductance as a function of current for a given air gap for a double solenoid three leg magnetic valve control system; -
FIG. 20 is a chart which shows incremental magnetic force as a function of current for a given air gap for a double three-leg solenoid magnetic valve control system; -
FIG. 21 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 12 volts, including eddy current, for a double solenoid three-leg magnetic valve control system; -
FIG. 22 is a transient analysis chart which shows current as a function of time for an applied voltage of 12 volts, including eddy current, for a double solenoid three-leg magnetic valve control system; -
FIG. 23 is a transient analysis chart which shows displacement as a function of time for an applied voltage of 24 volts, including eddy current, for a double solenoid three-leg magnetic valve control system; -
FIG. 24 is a transient analysis chart which shows current as a function of time for an applied voltage of 24 volts, including eddy current, for a double solenoid three-leg magnetic valve control system; -
FIG. 25 is a partial cutaway view of aModel 3 double solenoid, three leg flux return path magnetic valve control system; -
FIG. 26 is a chart which shows magnetic force of the permanent magnet as a function of displacement variation for a double solenoid, three-leg flux return path magnetic valve control system; -
FIG. 27 is a chart which shows incremental inductance as a function of current for a given air gap for a double solenoid three leg flux return path magnetic valve control system; -
FIG. 28 is a chart which shows incremental magnetic force as a function of current for a given air gap for a double three-leg flux return path solenoid magnetic valve control system; -
FIG. 29 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system without current; -
FIG. 30 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system without current; -
FIG. 31 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system with an applied current; -
FIG. 32 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system with an applied current; -
FIG. 33 is a first cutaway view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies; -
FIG. 34 is a second cutaway view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies; -
FIG. 35 is a top schematic view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies; -
FIG. 36 is a first cutaway view of a preferred electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies; -
FIG. 37 is a second cutaway view of a preferred electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies; -
FIG. 38 is a schematic view of an electromagnetic valve system having a reciprocating disk clapper comprised of a ferrous or magnetic material; -
FIG. 39 is a schematic view of an electromagnetic valve system which comprises a permanent magnet reciprocating disk clapper; -
FIG. 40 is a schematic view of a controller and power module linked to an electromagnetic valve system; -
FIG. 41 is a detailed schematic view of control and power circuitry associated with an electromagnetic valve system; -
FIG. 42 is a schematic diagram of generic structures and functionality throughout different embodiments of electromagnetic valve systems; -
FIG. 43 is a cutaway view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies, with the valve in a closed position; -
FIG. 44 is a top schematic view of an electromagnetic valve actuation system comprising discrete spring and electromagnet assemblies; -
FIG. 45 is a detailed cross-sectional view of a mechanical spring disabler mechanism; -
FIG. 46 is a detailed partial cross-sectional view of a mechanical valve disabler system in a first position with a disabler set; -
FIG. 47 is a detailed partial cross-sectional view of a mechanical valve disabler system in a second disabled position with a disabler set; -
FIG. 48 is a detailed partial cross-sectional view of a mechanical valve disabler system in a first enabled and closed position; -
FIG. 49 is a detailed partial cross-sectional view of a mechanical valve disabler system in a second enabled and opened position; -
FIG. 50 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a first position with a disabler set; -
FIG. 51 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a second disabled position with a disabler set; -
FIG. 52 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a first enabled and closed position; -
FIG. 53 is a detailed partial cross-sectional view of an alternate mechanical valve disabler system in a second enabled and opened position; -
FIG. 54 is a partial detailed cutaway view of a spring latch mechanism; and -
FIG. 55 is a profile view of a reverse profile cam lobe. -
FIG. 1 is a partial cross sectional view of anelectromagnetic valve system 10 a. Avalve 12, having astem 14, is linearly moveable within acylinder head 16, such as through avalve guide 18. Thevalve 12 is linearly moveable between aclosed position 20 a and anopen position 20 b, to allow flow into or out of amanifold port 22. - The
valve 12 comprises avalve face 24 at one end of thestem 14. Aclapper 26 is affixed to thestem 14, such that movement of the clapper results in movement of thevalve 12. Avalve spring 28 is located between thehead 16 and theclapper 26, which biases thevalve 12 toward aclosed position 20 a. A disablespring 30 is located on an opposing surface of theclapper 26, to bias thevalve 12 toward anopen position 20 b. The disablespring 30 is typically affixed in relation to thecylinder head 16, such as by aretainer 32. - A first
permanent magnet 34 a andfirst electromagnet 36 a are located on one side of theclapper 26, and a secondpermanent magnet 34 b andfirst electromagnet 36 b are located on the opposing side of theclapper 26. In aclosed position 20 a, the magnetic flux of the secondpermanent magnet 34 b provides an attractive magnetic force to retain theclapper 26, such as to latch thevalve 12 in theclosed position 20 a. Similarly, in anopen position 20 b, the magnetic flux of the secondpermanent magnet 34 a provides an attractive magnetic force to retain theclapper 26, such as to latch thevalve 12 in theopen position 20 b. - The electromagnetic coils 36 a,36 b typically comprise a toroidal core 56 (
FIG. 3 ), around which electricallyconductive wire 54 is wound. Electrical current 57 (FIG. 3 ) is controllably applied in either direction, such as through thewire 54, such that theelectromagnetic coils - In operation, the
electromagnetic valve system 10 a is readily moveable betweenpositions electromagnets 36 acts to increase or decrease the total magnetic attraction of theclapper 26. - From a
closed position 20 a, applied energy to the secondelectromagnetic coil 36 b provides a magnetic flux in a generally opposite direction to the magnetic flux from the secondpermanent magnet 34. In theclosed position 20 a, the disablespring 30 comprises stored potential energy. When the total magnetic force 82 (FIG. 6 ) becomes less than the force from the potential energy of the compressed disablespring 30, theclapper 26 andvalve 12 move linearly downward toward the open position. As the clapper contacts thevalve spring 28, thevalve spring 28 is compressed. As the valve approaches theopen position 20 b, the magnetic flux of the firstpermanent magnet 34 provides an attractive magnetic flux. The firstelectromagnetic coil 34 a may preferably be energized as the valve approaches theopen position 20 b, such as to increase the attractive, i.e. pulling,magnetic force 82. - In addition, the first
electromagnetic coil 36 a may preferably be energized near the end of travel, as thevalve 12 approaches theopen position 20 b, such as to slow the advance of theclapper 26, and provide a soft landing in theopen position 20 b. The magnetic flux provided by somepermanent magnets 34 increases significantly at short distances, such as to increase the attractive, i.e. pulling,magnetic force 82. Activation of theelectromagnetic coil 36 a to provide a soft landing typically comprises a short time period, such as a pulse, to slow the approach of theclapper 26. - Similarly, from an
open position 20 b, applied energy to the firstelectromagnetic coil 36 a provides a magnetic flux in a generally opposite direction to the magnetic flux from the firstpermanent magnet 34 a. In theopen position 20 b, thevalve spring 28 comprises stored potential energy. When the totalmagnetic force 82 becomes less than the potential energy, theclapper 26 andvalve 12 move linearly upward toward theclosed position 20 a. As theclapper 26 contacts the disablespring 30, the disablespring 30 is compressed. As thevalve 12 approaches theclosed position 20 a, the magnetic flux of the secondpermanent magnet 34 b provides an attractive magnetic flux. The secondelectromagnetic coil 36 b may preferably be energized as thevalve 12 approaches theclosed position 20 a, such as to increase the attractive, i.e. pulling,magnetic force 82. - In addition, the second
electromagnetic coil 36 b may preferably be energized near the end of travel, as thevalve 12 approaches theclosed position 20 a, such as to slow the advance of theclapper 26, and provide a soft landing in theclosed position 20 a Activation of theelectromagnetic coil 36 a to provide a soft landing typically comprises a short time period, such as a pulse, to slow the approach of theclapper 26. - In some embodiments of the
electromagnetic valve system 10, the clapper comprises one or morepermanent magnets 42. In alternate embodiments of theelectromagnetic valve system 10, the clapper comprises magnetically attractive, i.e. ferrous material. -
FIG. 2 shows a partial detailed top view of aclapper 26 comprising a plurality of radially alignedpermanent magnets 42. As seen inFIG. 2 , each of themagnets 42 is radially aligned toward thevalve stem 14, wherein thenorth poles 44 face inward, and wherein thesouth poles 46 face outward. -
FIG. 3 is a partial cutaway view of aModel 1 single solenoid magneticvalve control system 10 b, in which a permanent magnet clapper 26 a is affixed to thestem 14 of a valve, and is moveable between afirst electromagnet 36 a and asecond electromagnet 36 b. The electromagnetic coils 36 a,36 b are located withinyoke assemblies core 56. Theclapper 26 comprises amagnetic region 42 within aclapper yoke 58. -
FIG. 4 is achart 60 showing material demagnetizationcharacteristic curves permanent magnet 42, comprised of Sm2Co17, as a function ofmagnetic field 64 at various temperatures. -
FIG. 5 is achart 70 which shows 76 magnetic induction 72 as a function ofmagnetic field intensity 74 for core material, comprised of steel, having a density of 7.9 g/cm3, and an electrical conductivity of 1.03e7 (1/ohm·m). -
FIG. 6 is achart 80 which shows 86magnetic force 82 of thepermanent magnet 42 as a function ofdisplacement variation 84 for a single solenoid magneticvalve control system 10. As seen inFIG. 6 , at close separation distances 88, the magnetic attraction force increases significantly. For example, at a separation distance of 0.03 mm, the attractive force of a Type Oneclapper 26 provides 416 N of attractive force. -
FIG. 21 is a chart showing material characteristics for a permanent magnet material used in some embodiments of theclapper 26, for a magnet comprising SmsCo17, having a density of 7.5 g/cm3, a conductivity of 1.16e6 (1/ø·m), and a rated operating temperature of 150 degrees C. -
FIG. 22 is a chart which shows magnetic induction as a function of magnetic field intensity for core material, for a steel density of 7.9 g/cm3, and an electrical conductivity of 1.03e7 (1/ø·m) - In some embodiments of the invention, the winding comprises 24 AWG copper wire, having a bare diameter of 0.511 mm, and a conductivity of 5.8e7 (1/ø·m). The valve stem 14 comprises non-metallic material, and comprised a total mass of 80 gm, and the spring constant for the first spring 39 and for the
second spring 30 is 30600 N/m. -
FIG. 7 is achart 90 which shows 96incremental inductance 92 as a function of current 94 for an air gap of 30 μm in a single solenoid magnetic valve control system 10 x.FIG. 8 is achart 100 which shows 106 incrementalmagnetic force 82 as a function of current 94 for an air gap of 30 μm in a single solenoid magnetic valve control system 10 x. -
FIG. 9 is atransient analysis chart 110 which shows 114displacement 84 as a function oftime 112 for an applied voltage of 12 volts, with no eddy current, for a time period of 16.5 msec.FIG. 10 is atransient analysis chart 120 which shows 124 current 94 as a function oftime 112 for an applied voltage of 12 volts, with no eddy current. - Considering Conductivity (Including Eddy Current).
FIG. 11 is atransient analysis chart 130 which shows 134displacement 84 as a function oftime 112 for an applied voltage of 24 volts, with no eddy current.FIG. 12 is atransient analysis chart 140 which shows 144 current 94 as a function oftime 112 for an applied voltage of 24 volts, with no eddy current. -
FIG. 13 is atransient analysis chart 150 which shows 154displacement 84 as a function oftime 112 for an applied voltage of 12 volts, with eddy current effects, in which there is no latching achieved between aclapper 26 and anelectromagnet assembly 36.FIG. 14 is atransient analysis chart 160 which shows 164 current 94 as a function oftime 112 for an applied voltage of 12 volts, with eddy current effects. -
FIG. 15 is atransient analysis chart 170 which shows 174displacement 84 as a function oftime 112 for an applied voltage of 24 volts, with eddy current effects.FIG. 16 is atransient analysis chart 180 which shows 184 current 94 as a function oftime 112 for an applied voltage of 24 volts, with eddy current effects. -
Model 3 System Details.FIG. 17 is a partialcutaway view 190 of aModel 2 double solenoid, three leg magneticvalve control system 10 c, in which a permanent magnet clapper 26 a is affixed to thestem 14 of avalve 12, and is moveable between afirst electromagnet 34 a and asecond electromagnet 34 b. The electromagnetic coils 36 a,36 b are located withinyoke assemblies core 56. Theclapper 26 comprises alignedmagnetic regions clapper yoke 58. -
FIG. 18 is achart 200 which shows 204magnetic force 82 of the permanent magnet as a function ofdisplacement 84 variation for a double solenoid, three leg magneticvalve control system 10 c. -
FIG. 19 is achart 210 which showsincremental inductance 92, comprisingindividual coil inductance mutual inductance 216, as a function of current 94 for a given air gap for a double solenoid three leg magneticvalve control system 10 c. -
FIG. 20 is achart 220 which shows 224 incrementalmagnetic force 82 as a function of current 94 for a given air gap for a double three leg solenoid magneticvalve control system 10 c. -
FIG. 21 is atransient analysis chart 230 which shows 234displacement 84 as a function oftime 112 for an applied voltage of 12 volts, including eddy current, for a double solenoid three leg magneticvalve control system 10 c.FIG. 22 is atransient analysis chart 240 which shows 244 current 94 as a function oftime 112 for an applied voltage of 12 volts, including eddy current, for a double solenoid three leg magneticvalve control system 10 c. -
FIG. 23 is atransient analysis chart 250 which shows 254displacement 84 as a function oftime 112 for an applied voltage of 24 volts, including eddy current, for a double solenoid three leg magneticvalve control system 10 c.FIG. 24 is atransient analysis chart 260 which shows 264 a,264 b current 94 as a function of time for an applied voltage of 24 volts, including eddy current, for a double solenoid three leg magneticvalve control system 10 c. - Flux Return Path Embodiments.
FIG. 25 is a partialcutaway view 270 of aModel 3 double solenoid, three leg flux return path magneticvalve control system 10 d, in which a permanent magnet clapper 26 a is affixed to thestem 14 of avalve 12, and is moveable between afirst electromagnet 34 a and asecond electromagnet 34 b. The electromagnetic coils 34 a,34 b are located withinyoke assemblies core 56. Theclapper 26 comprisesmagnetic region clapper yoke 58. -
FIG. 26 is achart 280 which shows 284 magnetic force of the permanent magnet as a function of displacement variation for a double solenoid, three leg flux return path magnetic valve control system. -
FIG. 27 is a chart which shows incremental inductance as a function of current for a given air gap for a double solenoid three leg flux return path magnetic valve control system. -
FIG. 28 is a chart which shows incremental magnetic force as a function of current for a given air gap for a double three leg flux return path solenoid magnetic valve control system. - Flux Fields.
FIG. 29 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system without current. -
FIG. 30 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system without current. -
FIG. 31 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model II double three leg flux solenoid magnetic valve control system with an applied current. -
FIG. 32 is a schematic cross sectional view showing equi-potential magnetic force lines for a Model III double three leg flux solenoid return path magnetic valve control system with an applied current. -
FIG. 33 is a firstcutaway view 190 of an electromagneticvalve actuation system 10 e comprising discrete spring and electromagnet assemblies, with thevalve 12 in aclosed position 20 a.FIG. 34 is a secondcutaway view 200 of an electromagneticvalve actuation system 10 e comprising discrete spring and electromagnet assemblies, with thevalve 12 in anopen position 20 b.FIG. 35 is a topschematic view 206 of an electromagneticvalve actuation system 10 e comprising discrete spring andelectromagnet assemblies - A
spring keeper 192 affixed to thevalve stem 14 moves linearly to transfer energy between the disablespring 30 and thevalve spring 28. Aclapper 26 affixed to thevalve stem 14 moves between anupper magnet assembly 198 b and alower magnet assembly 198 a. Theupper magnet assembly 198 b comprises an upperpermanent magnet 34 b and anupper electromagnet 36 b, while the lower magnet assembly comprises a lowerpermanent magnet 34 a and alower electromagnet 36 a. - As seen in
FIG. 33 andFIG. 34 . thesprings spring keeper 192, such that thesprings valve system 10 e during a portion of the valve movement. In one exemplary embodiment, thesprings electromagnetic valve system 10 e, the valve stem shaft is non-magnetic. Theclapper 26 shown inFIG. 33 andFIG. 34 also comprises amechanical sleeve 195, such as to accurately affix theclapper 26 to thevalve stem 14. - The
permanent magnets clapper 25, in either theclosed position 20 a or theopen position 20 b. As seen inFIG. 34 , thepermanent magnet 34 a holds thevalve spring 28 compressed in the valveopen position 20 b, whereby thevalve spring 28 retains a high level of potential energy. Similarly, as seen inFIG. 33 , thepermanent magnet 34 b holds the disablespring 30 compressed in the valve closedposition 20 a, whereby the disablespring 30 retains a high level of potential energy. - From the
closed position 20 a, wherein theclapper 26 is latched against theupper magnet assembly 198 b, an applied energy to theupper electromagnet 36 b is controllably energized to release the clapper from theclosed position 20 a. Upon activation of energy to thefirst electromagnet 36 b, an electromagnetic flux is generated by theelectromagnet 36 b, which opposes the permanent magnet flux of the upperpermanent magnet 34 b. When the applied opposing electromagnetic flux reduces the permanent magnet holding force below that of the spring force applied by the disablespring 30, thevalve 12 begins to open. - As the
valve 12 begins to open, the applied force of the upperpermanent magnet 34 b, which has a constant flux, is reduced. As thevalve 12 opens and theclapper 26 moves away from theupper magnet assembly 198 b, whereby the applied flux density from thepermanent magnet 34 b falls off very rapidly, such that the attractive force decreases rapidly. - Similarly, as the
valve 12 begins to close, the applied force of the lowerpermanent magnet 34 a, which has a constant flux, is reduced. As thevalve 12 closes and theclapper 26 moves away from thelower magnet assembly 198 b. The applied flux density from thepermanent magnet 34 a falls off very rapidly, such that the attractive force decreases rapidly. - As the
spring keeper 192 moves and advances toward themiddle region 193, the spring forces are equal, and the kinetic energy of the system reaches a maximum. Thespring keeper 192 continues to move, a whereby the kinetic energy of the moving mass of theassembly 195 is converted to stored potential energy in thevalve spring 28. The moving mass of theassembly 195 is typically equal to the combined mass of theclapper 26, thevalve 12, thekeeper 192, and at least a portion of thesprings - In preferred embodiments of the
electromagnetic actuation system 10, the kinetic mass of thevalve train 195 is minimized by the configuration of thevalve spring 28 and the disablespring 30, whereby kinetic energy is transferred between thevalve spring 28 and the disablespring 30, in acentral region 193 of movement, and whereby the mass of either the first orsecond spring valve train 195 for a portion of movement. - For example, as seen in
FIG. 33 andFIG. 34 , as thespring keeper 192 moves beyond thecentral region 193, thevalve spring 28 is compressed by further downward movement of thevalve assembly 195, comprising the clapper 296 thevalve 12, andspring keeper 192, while the disablespring 30 becomes isolated from the assembly 195 (FIG. 34 ). - When the
valve assembly 195 approaches the end of travel, e.g. such as toward anopen position 20 b, thevalve 12,clapper 26, andspring keeper 192 decelerate, as the kinetic energy of thevalve assembly 195 is transformed to stored potential energy in thevalve spring 28. Near the limit of travel, the applied flux from the lowerpermanent magnet 34 a provides an attractive force to latch thevalve 12 in theopen position 20 b. - As described above, the attractive force from between the
permanent magnets 34 and theelectromagnets 36 is proportional to thedisplacement distance 84, i.e. there is a strong attractive force at the very end region of travel. In preferred embodiments of the invention, therefore, energy may be controllably applied to the approachingelectromagnet 36, to promote a ‘soft’ landing. - When the
spring keeper 192 compresses thevalve spring 28 to the bottom limit of movement, i.e. wherein theclapper 26 approaches thebottom magnet assembly 198 a, theclapper 26 contacts and latches to thelower magnet assembly 198 a, since themagnet force 82 increases as theclapper 26 approaches themagnet assembly 198 a. At the limit of travel, the magnetic holding force is larger than the opposing valve spring force, such that thevalve 12 latches in theopen position 20 b. - In the
electromagnetic valve system 10 e shown inFIG. 33 andFIG. 34 , thevalve 12 latches in either theclosed position 20 a or in theopen position 20 b, without the application of energy. - Release from either latch condition is controllable through applied energy signal, such as from an external control 302 (
FIG. 40 ,FIG. 41 ). As seen inFIG. 41 , anexternal controller 302 sends a signal, i.e. energy pulse, to the appropriate magnet assembly 198, which is latched to theclapper 26. The applied pulse overcomes the permanent magnet attraction force, such that the compressed spring, e.g. thevalve spring 28, acts upon theassembly 195, which moves toward the opposite position. -
FIG. 36 is a firstcutaway view 210 of a preferred electromagneticvalve actuation system 10 f comprisingdiscrete spring 224 andelectromagnet 226 assemblies, in aclosed position 20 a.FIG. 37 is a second cutaway view of a preferred electromagneticvalve actuation system 10 f comprisingdiscrete spring 224 andelectromagnet 226 assemblies, in anopen position 20 b. The electromagneticvalve actuation system 10 f comprises a single axially polarized, single, non-movingpermanent magnet 34, and a single electromagnet andcoil 36. - The
spring assembly 224 comprises twoseparate springs springs valve assembly 195, which reduces the spring moving mass, and reduces spring friction. - The
permanent magnet 34 is preferably square or rectangular, in vertical cross section, to provide an increased magnetic flux over the footprint of thecylinder head 16. The square or rectangularpermanent magnet 34 has more flux than a round one of equal diameter, which allowssprings - The electromagnetic
valve actuation system 10 f also preferably comprises fullwidth magnet poles clapper 26 is typically cylindrical in profile, to allow rotation of thevalve 12. - In the exemplary embodiment shown in
FIG. 36 andFIG. 37 , the valve stem 14 screws into theclapper 26, and is preferably held with a lockingcompound 227, such as LOCTITE™, such that thespring keeper 192 is mechanically affixed to thevalve assembly 195. In some system embodiments, thespring keeper 192 acts as a piston, to balance the manifold pressure. - In some system embodiments, the fixed ends 228 of the
springs springs opening stop 222 stops thekeeper 192 near seating, to provide adjustment for temperature and wear. - The free lengths of the
springs spring mass 195 can transfer kinetic energy at the mid point 193 (FIG. 34 ). - System Operation. As seen in
FIG. 36 , thevalve 12 is shown in theclosed position 20 a. To open thevalve 12, thecoil 36 is energized to oppose the permanent magnet flux (PMF) and effectively cancel the PMF holding force, which causes thedisabler spring 30 force to accelerate thevalve 12 in theopening direction 20 b. - As the
valve 12 moves away from the magnet pole, the PMF decreases, and theopening 12 flux is proportionately decreased, so as to minimize the magnetic force. When thekeeper 192 approaches themidpoint 193, thekeeper 192 contacts thevalve spring 28. Thedisabler spring 30 delivers kinetic energy to thevalve spring 28, by the time thedisabler spring 30 reaches a free length, where the disablespring 30 stops moving. Thevalve spring 28 absorbs the kinetic energy, and decelerates the movingmass 195 toward theopen position 20 b. - During the valve motion, friction and windage typically absorb a small portion of the kinetic energy, which slows the valve motion. When the
keeper 192 passes the mid-point 193, thecoil 36 is energized in the opposite direction, to assist the PMF of thepermanent magnet 34, and to make up the kinetic energy lost to friction and windage. The assisting flux from thecoil 36 is typically proportionately decreased, so that thekeeper 192 arrives at thestop 222 with close to zero speed, and the magnetic force PMF from thepermanent magnet 34 holds thevalve 12 open 20 b. - The controlled movement of the
valve system 10 f from theopen position 20 b to theclosed position 20 a is provided by the reverse of the opening motion. To close thevalve 12, thecoil 36 is energized to oppose the permanent magnet flux (PMF) and effectively cancel the PMF holding force, which causes thevalve spring 28 force to accelerate thevalve 12 in the closingdirection 20 a. - Similarly, as the
valve 12 moves away from the magnet pole, the PMF decreases, and theopening 12 flux is proportionately decreased, so as to minimize the magnetic force. When thekeeper 192 approaches themidpoint 193, thekeeper 192 contacts the disablespring 30. Thevalve spring 28 delivers kinetic energy to the disablespring 30, by the time thevalve spring 28 reaches a free length, where thevalve spring 28 stops moving. The disablespring 30 absorbs the kinetic energy, and decelerates the movingmass 195 toward theclosed position 20 a. As well, the assisting flux from thecoil 36 is typically proportionately decreased, so that thekeeper 192 arrives at the top position with close to zero speed, and the magnetic force PMF from thepermanent magnet 34 holds thevalve 12 closed 20 a. -
FIG. 38 is aschematic view 240 of anelectromagnetic valve system 10 g having aclapper 26 comprised of a ferrous or magnetic material, wherein theclapper 26 comprises a reciprocating disk. In some system embodiments, thepermanent magnets 34 are integrated within theelectromagnets 36, which provides magnetic attraction to thedisk 26 without the need for electrical energy. - A “reverse” electrical pulse to the
appropriate electromagnet 36, e.g. 36 a, cancels the permanent magnet field to cause the release of thedisk 26. Thesprings disk 26 and connectedvalve 12 to the opposing permanent/electromagnet disk 26 is attracted to the opposing permanent/electromagnet, where it comes to rest. - The
electromagnetic valve system 10 h provides latching, either open or closed, without requiring power, even after the engine is turned off. Only a brief current pulse is required to cause thevalve 12 to switch to the opposingposition permanent magnet clapper 26 approaches theelectromagnet 36, the changing magnetic field is preferably converted to electrical energy, to be returned to a power module 304 (FIG. 40 ,FIG. 41 ). In some embodiments, theelectromagnets clapper 26, such as to provide for fast valve speeds. -
FIG. 39 is a schematic view of anelectromagnetic valve system 10 h which comprises apermanent magnet clapper 26, wherein theclapper 26 comprises a permanent magnet reciprocating disk. Thereciprocating disk clapper 26 is attached to theengine valve 12, such as by a rod that passes through oneelectromagnet 36. Electromagnets 36 a,36 b are placed at both ends of the disk travel. Theelectromagnets 36 have the ability to controllably attract or repel thepermanent magnet clapper 26, depending on the polarity of the voltage applied to theelectromagnet 36. When thepermanent magnet 36 in not in close proximity to the electromagnet (within approximately 0.05 inches), the only forces acting on the magnet clapper are spring forces. The two springs 28,30 accelerate and decelerate thedisk 26 andvalve 12 to the opposing valve positions 20 a,20 b. - The
electromagnetic valve system 10 h provides latching, either open or closed, without requiring power, even after the engine is turned off. Only a brief current pulse is required to cause thevalve 12 to switch to the opposingposition permanent magnet clapper 26 approaches theelectromagnet 36, the changing magnetic field is preferably converted to electrical energy, to be returned to an energy exchange and storage system (FIG. 41 ), e.g. such as a battery or an LC circuit. In some embodiments, theelectromagnets permanent magnet clapper 26, such as to provide for fast valve speeds. - The
electromagnetic valve system 10 h is typically comprises low eddy current, i.e. low loss, materials as well as energy recovery circuitry, will help reduce energy consumption. Some embodiments of theelectromagnetic valve system 10 h provide soft landing controls, such that thevalve 12 and/ordisk 26 do not “slam” into other engine parts as the valve comes to rest. The soft landing control typically comprises the provision of a short electrical repelling force to theappropriate electromagnet 36, as thedisk 26 approaches. In some system embodiments, at least a portion of the energy required for the soft landing pulse is provided from the energy recovery circuitry. - System Control and Power Circuitry.
FIG. 40 is aschematic view 300 of acontroller 302 andpower module 304 linked to anelectromagnetic valve system 10.FIG. 41 is a detailedschematic view 350 ofcontrol 302 andpower circuitry 304 associated with anelectromagnetic valve system 10. While theexemplary system 10 is similar in detail tosystem 10 e, as seen inFIG. 33 andFIG. 34 , thecontroller 302 andpower module 304 are readily used throughout the various system embodiments 10. - System Advantages. The
electromagnetic valve systems 10 can be used for a wide variety of applications. Theelectromagnetic valve system 10 is able to controllably open and or close avalve 12 at any time, and is not mechanically limited to camshaft and/or a crankshaft. - The opening and/or closing of
valves 12 is readily accomplished at any time within an engine cycle. Furthermore, one ormore valves 12 are readily latched in either an open or a closed position, such that one or more cylinders may readily be disabled. - In applications for an internal combustion engine, valve timing and duration is readily controlled and modified. For example, in some engine applications, the electromagnetic valve system provides real-time profiling of valve operation, such as to provide longer valve duration, to alter valve timing for opening and/or closing.
- Valve trains in conventional engines are linked through a camshaft to the crankshaft of the engine, such that operation of the valve train is inherently linked to the crankshaft speed. In contrast, the electromagnetic valve system is inherently independent of the speed the engine.
- During a steady state operation of an engine, e.g. at a constant load and speed, the electronic valve system can readily operate in a somewhat conventional manner, whereby the opening and closing of valves is synchronized to the crankshaft speed.
- In contrast to conventional valve systems, however, the
electromagnetic valve system 10 is readily controlled for any different operation conditions, such as for changes in ambient temperature, pressure, humidity, and/or internal friction. - The
electromagnetic valve system 10 is also readily controlled for differing demands for power and/or torque, demands for acceleration or deceleration. - Furthermore, the time to open and/or close a
valve 12 in a conventional engine is mechanically linked to a cam profile. In contrast, the time to open and/or close avalve 12 in theelectromagnetic valve system 10 is independent of the mechanical limitations of a cam. The transit time, the time to open or close avalve 12, is controllable in theelectromagnetic valve system 10, whereby a latchedvalve 12 is readily released and moved to anopposite position 20. In some preferred embodiments of theelectromechanical valve system 10, the initial release of avalve 12 is enhanced by a strong electromagnetic pulse, to quickly accelerate theclapper 26 from the latched position. - Therefore, the time to open or close as
valve 12 is readily minimized in theelectromagnetic valve system 10, and is independent of engine speed, whereby the valve open period is readily and precisely controlled, such that a cylinder can be filled with an air-fuel charge more completely and fully, which at a low engine speed in some embodiments, provides a higher torque output, e.g. 15-20 percent, as compared to a conventional cam-driven engine. - In the
electromagnetic valve system 10, the speed at which avalve 12 is determined by the applied power to the latching electromagnet. Therefore, while there is an advantage to opening and/or closing a valve rapidly, the applied energy is typically increased to provide a fast release from a latched position. In some embodiments of the electromagnetic control system 302 (FIG. 40 ), a desired valve speed and energy consumption maximum is determined, to provide sufficient valve speed while conserving applied energy. - Soft Landing. As described above, as the valve approaches an
endpoint 20, such as anopen position 20 b or aclosed position 20 a, the applied forces on thevalve assembly 195 include the opposing force applied by thespring valve spring 28, and the attractive magnetic force between theclapper 26 and theappropriate electromagnet assembly 134. As seen inFIG. 6 , the attractive force of apermanent magnet 34 increases significantly atsmall distances 84, such that thevalve 12 readily latches to theendpoint 20 at the end of travel. - Some embodiments of the
electromagnetic valve system 10 include soft landing means to prevent a hard landing of thevalve assembly 195 at a latch position, whereby a small amount of energy is applied by theelectromagnet 36 to provide a controlled opposing force between thepermanent magnet 34 and theelectromagnet 36 during landing. The resultant applied flux opposes the attractive flux of thepermanent magnet 34, to provide a soft landing. - Energy Loss and Input. In the
electromagnetic valve system 10, the resistance force on the landing is dependent on friction within the assembly, whereby the potential and kinetic energy of the system, from the compressed spring, is reduced, due to friction. - For example, in a system which has too much friction, the
valve 12 may never reach the end of the travel, in which too much kinetic energy is lost, due to friction. Under such a condition, theclapper 26 may not reach and latch to theelectromagnet 36 andpermanent magnet 34, and the assembly oscillates, and energy dissipates due to friction, until the two spring forces are equal. - The
electromagnetic valve system 10 therefore typically comprises means to input energy into theassembly 10, such as to provide an opposing electromagnetic flux to initiate movement of thevalve 12 from a latched position, or to provide an attractive force by theappropriate electromagnet 36 at the end of travel, to assure that the assembly latches at the end position. - Electromagnetic Energy Input. In the
electromagnetic valve system 10, the electromagnets are preferably used to initiate travel, i.e. to overcome the attractive force of the permanent magnet in a latch position; to input energy to the valve train, such as to promote valve speed and/or to overcome friction; to provide an attractive force to between the permanent magnet at the end of a travel; and/or to provide an opposing force at the end of a travel, to promote a soft landing. - The applied energy to the
electromagnets 36 is typically controlled by theprocessor 302, and may comprise a variety of formats, such as steps or pulses. - The
controller 302 is preferably configured to modify the applied energy, such as to compensate for operating conditions or desiredperformance parameters 370 a-370 n, such as but not limited to temperature, friction, long-time wear characteristics, seating of the valve, and/or cylinder pressure applied to the face of a valve. - Use of Electromagnets as Sensors. In some preferred embodiments of the
electromagnetic valve system 10, theelectromagnets 36 are also used as system sensors. - In the
electromagnetic valve system 10, theclapper 26 moves in relation to theelectromagnets 36. Since thepermanent magnet 36 is a flux carrying element, relative movement of theclapper 26 in relation to theelectromagnets 34 and/or permanent magnet can be sensed by analysis of the flux at the electromagnets. - For example, the
controller 302 detects the rate of change of flux, whereby the speed of theclapper 26 andvalve 12 is indicated. Thecontroller 302 determines the location from the speed at one or more points, such that thecontroller 302 can determine the movement and response of the valve train through one ormore strokes - The
controller 302 preferably analyzes the movement of the valve train, and can modify the applied energy, based upon the acquired information, such as to increase energy, decrease applied energy, and/or to change the timing if applied energy, either to enhance a current operating condition, or to enhance a dynamic operating condition, e.g. to provide a different power or torque under an acceleration condition, or to conserve fuel during deceleration. Therefore, in theelectromagnetic valve system 10, the magnets are preferably used both as a driving force, and as a means for sensing and control. - Active Valve Train Mass. In most embodiments of the
electromagnetic valve system 10, the active mass of the electromagnetic valve assembly is equal to the combined sum of the mass of thevalve 12, the mass of theclapper 26, and approximately half of eachspring spring spring spring spring - The kinetic energy of the
system 10 at the midpoint of motion, i.e. wherein the potential energy stored by the springs is a minimum, is approximately equal to ½ mv2. - While the
electromagnetic valve system 10 is described as having a both avalve spring 28 and a disablespring 30, the assembly can be considered to be a single, dynamic compound spring, which may also comprise thecentral clapper 26, which is controllable electronically to impart force, to take force out, and also to determine the speed at which the shaft is moving. - In some embodiments of the
electromagnetic valve system 10, the valve train comprises both avalve spring 28 and a disablespring 30, which alternately are connected or are disconnected from thedynamic valve train 195. - During the periodic motion of the valve train, each
spring mass 195 of thevalve train 195, which reduces the dynamic mass of the valve train. In this embodiment, thesprings head 16 at each end, but are not affixed to the permanent magnet. - During the periodic motion of the valve train, as the clapper approaches the
central region 193 of travel, theclapper 26 approaches and contacts the approaching spring which is at a resting, i.e. free length, position. When the clapper contacts the oncomingspring clapper 26 briefly contact with bothsprings valve 12 andclapper 26 continue to move, while compressing thesecond spring second end 20, e.g. toward theopen position 20 b. - The
dynamic valve assembly 195 exchanges kinetic energy within thecentral region 193, such as through an impact, or through a small overlapping region, e.g. wherein the first spring is almost fully extended, and wherein the second spring begins to be compressed. - In embodiments of the
electromagnetic valve system 10 in which springs 28,30 are periodically isolated from thedynamic valve train 195, there is a reduction in the mass of thevalve train 195. In addition, there is a reduction in spring friction for the system, since the springs are periodically isolated from the motion of thevalve train 195. - Geometry Considerations. In addition to improvements in dynamic valve train mass and response, some preferred embodiments of the
electromagnetic valve system 10, such as seen inFIG. 36 andFIG. 37 , provide design freedom within an engine environment. The stationarypermanent magnets 34 can be provided in a wide variety of form factors, such as a rectangular structure, to provide a greater magnetic flux field than a system having axial restrictions, e.g. such as for a cylindrical movable permanent magnet. - In the head of typical engine there is typically a fixed distance between the centerline of an
exhaust valve 102 and the centerline of theintake valve 102. For a fixed separation distance, the alternateelectromagnetic valve system 10 seen inFIG. 36 andFIG. 37 provides design flexibility, since the stationary permanent magnets can be configured across the cylinder head, e.g. such as perpendicular to the line between valve centerlines. - Magnet Composition and Performance. The magnets used for
different system embodiments 10 are comprised of a wide variety of magnetic materials, such as suited for the desired thermal environment. In some preferred embodiments of theelectromagnetic valve system 10, thepermanent magnets 34 are comprised of neodymium. In some high temperature engine environments, thepermanent magnets 34 are comprised of samarium cobalt. - In one embodiment, the
present magnet 34, fully seated, with no air gap, provides a latching force of 124 pounds. In another embodiment, square (1.25 inch by 1.25 inch) stationarypermanent magnets 34 provide a latching force of about 320 lbs. - In the
electromagnetic valve system 10, the preferred use ofpermanent magnets 34 having high magnetic flux properties provides light valve train mass, as well as corresponding fast valve train response times, such as stroke times approaching 1-2 milleseconds. - The
dynamic mass 195 of the valve train includes both that of thevalve spring 28 and the disablespring 30 for only abrief transition region 193 in the center of travel, when both springs 28,30 are close to their released free-length position, and where the kinetic energy of the valve train is high, and wherein the stored potential energy of the springs is low. - While some embodiments of the
electromagnetic valve system 10 may have a transition length equal to zero, in most system embodiments, there is atransition region 193 greater than zero, such that a smooth energy transfer occurs between the firstdynamic portion 195 and the seconddynamic portion 195, i.e. as energy is transferred betweensprings - Movement of the
electromagnetic valve system 10 from theopen position 20 b to theclosed position 20 a is similar to the actions required to move the electromagnetic valve system from theclosed position 20 b to theopen position 20 a. Electromagnetic energy is applied to the latchingelectromagnetic coil 36, such that the stored potential energy in thevalve spring 28 overcomes the latching force. Thevalve train 195 moves toward theclosed position 20 a, wherein energy may be controllably applied to increase the attractive force at the closing end, as the disable spring is compressed. As before, energy to theelectromagnetic coil 36 may be applied at the closing end, to provide a soft landing in theclosed position 20 a. - At either end of movement, additional energy may controllably be applied by the electromagnetic coils, such as to compensate for friction within the system. For example. the applied energy may provide an electromagnetic force which aids the permanent magnet to the latch position, by pulling the
clapper 26 into a latch position, within the last portion of travel, in the closing and/or opening direction, e.g. for the last 0.010 to 0.020″. - Therefore, control of the
electromagnetic valve system 10 is extremely versatile, allowing: controlled opening and closing of a valve, independent of engine crankshaft position; assisted latch completion and/or release, and preferably providing a soft landing. Based on information from previous valve train movement, theelectromagnetic valve system 10 can be dynamically adjusted, such as to after valve timing and/or duration, and/or to adjust opening and/or closing energy parameters. - Electric Energy Storage. Some preferred embodiments of the
electromagnetic valve system 10 provide electrical energy exchange between the mechanical valve train and an energy storage system which is connected to the electromagnetic coils, whereby the energy efficiency of the system is improved. - The
energy storage module 370 shown inFIG. 41 preferably comprises anLC circuit 372, comprising an inductor 374 and acapacitor 376. Stored energy from thecapacitor 376 is released from the circuit to theelectromagnetic coil 36. Similarly, excess system energy is recovered from theelectromagnetic coil 36, by storage into thecapacitor 76. In conditions where the electromagnetic valve system needs more energy, more energy is applied to thecapacitor 376, such that the increasedenergy 356 is released to theelectromagnetic coil 356. - In some
system embodiments 10, the electrical oscillation 378 of the LC circuit is preferably matched to the mechanical oscillation of thevalve train 10. Based on system operation, the proper level of energy stored in thecapacitor 376 is adjusted. - Feed Forward and Feed Backward Control. The
electromagnetic valve system 10 is preferably controllable for steady state operation as well as for changing operation conditions. For example, for conditions which require more or less torque, the operation curves of valve timing and/or duration are readily controlled. - In some system embodiments, a map is provided and stored of the dynamic characteristics of the engine under different controllable parameters. Based upon the map and desired engine operation, the
controller 302 may readily change the operating parameters of theelectromagnetic valve system 10, to achieve the desired result. - Overview of Electromagnetic Valve Systems Having Permanent Magnet Latching.
FIG. 42 is a schematic diagram of generic structures and functionality throughout different embodiments ofelectromagnetic valve systems 10. As seen inFIG. 42 , theelectromagnetic valve system 10 generally comprises: -
- a
valve assembly 12 which is linearly movable between a firstclosed position 20 a and a secondopen position 20 b; - a
spring assembly 405, e.g. such as avalve spring 28 and a disablespring 30, in communication with thevalve assembly 12, wherein the spring assembly has a first spring assembly position, when thevalve assembly 12 is in the firstclosed position 20 a, and a second spring assembly position when thevalve assembly 12 is in the secondopen position 20 b; - an
electromagnet assembly 406, such as comprising one ormore electromagnets 36; and - a
permanent magnet system 404, such as one or morepermanent magnets 34, and/or aclapper 26 at least partially comprising a permanent magnetic material; - wherein the magnetic field from the
permanent magnet system 404 provides an attractive latching force 408, e.g. 408 a,408 b tovalve assembly 12 when thevalve assembly 12 is in any of the firstclosed position 20 a and the secondopen position 20 b.
- a
- As seen in
FIG. 1 , thepermanent magnet system 404 inelectromagnetic valve system 10 a may preferably comprise both apermanent magnet clapper 26 affixed to thevalve 12, as well aspermanent magnets - As seen in
FIG. 33 andFIG. 34 , thepermanent magnet system 404 inelectromagnetic valve system 10 e comprises both stationary lower and upperpermanent magnets magnetic circuits clapper 26. - As seen in
FIG. 36 andFIG. 37 , thepermanent magnet system 404 inelectromagnetic valve system 10 f comprises a singlepermanent magnet 34, as well as pole blocks 212,214, which conduct magnetic energy, such as to aid in movement and/or latching 408 of theclapper 26. - As seen in
FIG. 38 , thepermanent magnet system 404 inelectromagnetic valve system 10 g comprises both stationary lower and upperpermanent magnets clapper 26. - As seen in
FIG. 39 , thepermanent magnet system 404 inelectromagnetic valve system 10 h comprises apermanent magnet clapper 26 affixed to thevalve 12, which latches 408 toelectromagnetic coil 36 b when thevalve 12 is located at theclosed position 20 a, and latches 408 toelectromagnetic coil 36 a when thevalve 12 is located at theopen position 20 b. - As seen in
FIG. 42 andFIG. 43 , thepermanent magnet system 404 inelectromagnetic valve system 10 i comprises apermanent magnet 34 and one or more magnetically conductive armatures oryokes 453, which conduct magnetic energy, such as to aid in movement and/or latching 408 of theclapper 26. - In some system embodiments magnetic field from the
permanent magnet system 404 provides a permanent magnet latching force 408, e.g. 408 a,408 b, to thevalve assembly 12 which is sufficient to hold thevalve assembly 12 is in any of the firstclosed position 20 a and the secondopen position 20 b. In other system embodiments, energy can be supplied to theelectromagnetic system 406, to help latch thevalve assembly 12 in any of the firstclosed position 20 a and the secondopen position 20 b, such as but not limited to compensation for diminished strength of thepermanent magnet system 404. - Presently Preferred Embodiment of the Invention.
FIG. 43 is acutaway view 450 of an electromagneticvalve actuation system 10 i comprising discrete spring and electromagnet assemblies, with thevalve 12 in aclosed position 20 a.FIG. 44 is a topschematic view 460 of an electromagneticvalve actuation system 10 i comprising discrete spring andelectromagnet assemblies - A
spring keeper 192 affixed to thevalve stem 14 moves linearly to transfer energy between the disablespring 30 and thevalve spring 28. Aclapper 26 affixed to thevalve stem 14 moves between amagnet assembly 34 andelectromagnet assemblies magnet assembly 34 comprises a permanent magnet. Note that in some embodiments, both a north pole of the permanent magnet and a south pole of the permanent magnet are used to attract or repel the electromagnet. - As seen in
FIG. 43 , thesprings keeper 192, and are not fastened to thespring keeper 192, such that thesprings valve system 10 i during a portion of the valve movement. In one exemplary embodiment, thesprings electromagnetic valve system 10 i, the valve stem shaft is non-magnetic. - The
permanent magnet 34 provides a latching means for theclapper 26, in either theclosed position 20 a or theopen position 20 b. As seen inFIG. 43 , thepermanent magnet 34 holds thevalve spring 28 compressed in the valveopen position 20 b, whereby thevalve spring 28 retains a high level of potential energy. - From the
closed position 20 a, wherein theclapper 26 is latched against the poles encompassingpermanent magnet 34, an applied energy to theelectromagnets closed position 20 a. Upon activation of energy to theelectromagnets electromagnets permanent magnet 34. When the applied opposing electromagnetic flux reduces the permanent magnet holding force below that of the spring force applied by the disablespring 30, thevalve 12 begins to open. - As the
valve 12 begins to open, the applied force of thepermanent magnet 34, which has a constant flux, is reduced. As thevalve 12 opens and theclapper 26 moves away from thepermanent magnet 34, whereby the applied flux density from thepermanent magnet 34 falls off very rapidly, such that the attractive force decreases rapidly. - As the
spring keeper 192 moves and advances toward themiddle region 193, the spring forces are equal, and the kinetic energy of the system reaches a maximum. Thespring keeper 192 continues to move, a whereby the kinetic energy of the moving mass of the assembly is converted to stored potential energy in thevalve spring 28. The moving mass of the assembly is typically equal to the combined mass of theclapper 26, thevalve 12, thekeeper 192, and at least a portion of thesprings - In preferred embodiments of the
electromagnetic actuation system 10, the kinetic mass of the valve train is minimized by the configuration of thevalve spring 28 and the disablespring 30, whereby kinetic energy is transferred between thevalve spring 28 and the disablespring 30, in acentral region 193 of movement, and whereby the mass of either the first orsecond spring - For example, as seen in
FIG. 43 , as thespring keeper 192 moves beyond thecentral region 193, thevalve spring 28 is compressed by further downward movement of the valve assembly, comprising theclapper 26, thevalve 12, andspring keeper 192, while the disablespring 30 becomes isolated from the assembly (FIG. 43 ). - When the valve assembly approaches the end of travel, e.g. such as toward an
open position 20 b, thevalve 12,clapper 26, andspring keeper 192 decelerate, as the kinetic energy of the valve assembly is transformed to stored potential energy in thevalve spring 28. Near the limit of travel, the applied flux from theelectromagnets valve 12 in theopen position 20 b. - As described above, the attractive force from between the
permanent magnet 34 and theelectromagnets electromagnets - When the
spring keeper 192 compresses thevalve spring 28 to the bottom limit of movement, i.e. wherein theclapper 26 approaches thearmature 453 of theelectromagnets clapper 26 contacts and latches to the electromagnet assembly core because the magnet force increases as theclapper 26 approaches theelectromagnets valve 12 latches in theopen position 20 b. In the invention, thecore 453 may be made of solid or laminated materials. Where a laminated material is used for the core, the clapper may also be made of a laminate, preferably a continuous spiral to match the flux of the core. A laminated structure is less expensive to build and lighter in weight, and resists the generation of eddy currents, which distort the flux distribution and lose energy. In this embodiment, the preferred permanent magnet has dimensions of 3/16″×1½″×1½″. - In the
electromagnetic valve system 10 i shown inFIG. 43 andFIG. 44 , thevalve 12 latches in either theclosed position 20 a or in theopen position 20 b, with the application of minimal energy. In somepreferred system embodiments 10 i, the latching is provided entirely by magnetic energy provided by thepermanent magnet 34, such that no external energy is required to be applied to any of theelectromagnets - Release from either latch condition is controllable through applied energy signal, such as from an external control 302 (
FIG. 40 ,FIG. 41 ). As seen inFIG. 41 , anexternal controller 302 sends a signal, i.e. energy pulse, to theelectromagnets clapper 26. The applied pulse overcomes the permanent magnet attraction force, such that the compressed spring, e.g. thevalve spring 28, acts upon the assembly, which moves toward the opposite position. - Mechanical Valve Disabler System.
FIG. 45 is a detailed partial cross-sectional view of avalve disabler system 610 a. Avalve 612 is moveable in relation to ahead 616 having avalve port 617. The valve comprises avalve face 613 at afirst end 611 a, which is sealable in relation to avalve seat 615. Thevalve 612 also includes avalve stem 614 which extends from thefirst end 611 a to asecond end 611 b. Avalve cap 616 is located at thesecond end 611 b, such as avalve cap assembly 616, e.g. comprising a cap & retainers. - A
valve spring 618 provides a compressive force between thevalve 612 and aspring landing 620, which may be an integral portion of thehead 616. Thevalve spring 618 retains thevalve 612 in a normally closedposition 21 a (FIG. 46 ) in relation to thehead 616. When thevalve 612 extends toward anopen position 21 b (FIG. 49 ), the compression of thevalve spring 618 provides a bias force against thevalve cap 616. - A disable
spring 622 is also affixed to thevalve cap 616, and provides tension to controllably open thevalve 612. The disablespring 622 is also affixed to aring holder 624, such as by afirst holder landing 626. Acam spring 630 is located between thering holder 624, such as by a second holder landing 628, and controllably provides a compressive force between thering holder 624 and amovable cam cap 632. Arotatable camshaft 634, having acam lobe 636, controllably acts upon thecam cap 632, to compress thecam spring 630. - The
valve disabler system 610 a includes adisabler latch 640, which is movable between an unlatched, i.e. valve enabled,position 652 a, and a latched, i.e. valve disabled,position 652 b. InFIG. 45 , thedisabler latch 640 is in a latched position, such that rotation of thecamshaft 634 does not result in movement of thevalve 612 toward anopen position 21 b (FIG. 49 ). -
FIG. 46 is a partialcutaway view 660 of avalve disabler system 610 a in an uncompressed,disabled state 662.FIG. 47 is a partialcutaway view 670 of avalve disabler system 610 a in a compressed,disabled state 672. As seen inFIG. 46 andFIG. 47 , when thering holder 624 is confined by the latchedposition 652 b by the disablelatch 640, rotation of thecamshaft 634 does not result in the opening of thevalve 612. - As seen in
FIG. 47 , thecam lobe profile 636 acts to push thecam cap 632 from atop position 650 a toward alower position 650 b, which compresses thecam spring 630. However, thering holder 624 is prevented from vertical movement, by the disablelatch 640 being located in the lockedposition 652 b. Duringdisablement 652 b, thevalve 612 remains closed 21 a. -
FIG. 48 is a partialcutaway view 680 of avalve disabler system 610 a in an uncompressed, enabled state 682.FIG. 49 is a partialcutaway view 690 of avalve disabler system 610 a in a compressed, enabled state 692. As seen inFIG. 48 andFIG. 46 , when thering holder 624 is not confined, due to theenabled position 652 a of the disablelatch 640, rotation of thecamshaft 634 results in theopening 21 b of thevalve 612. - As seen in
FIG. 49 , thecam lobe profile 636 acts to push thecam cap 632 from atop position 650 a toward alower position 650 b, which compresses thecam spring 630. When the disablelatch 640 is in the enableposition 652 a, thering holder 624 is allowed to move vertically. - As seen in
FIG. 46 , as thecamshaft 634 rotates, theextended lobe region 636 of thecamshaft 634 acts upon thecam spring cap 632 andcam spring 630, to compress thecam spring 630. Thering holder 624, which is in contact with the second lower end of thecam spring 630, moves downward in reaction to the compressive force from thecam spring 630, since the disablelatch 640 is in the open “valve enabled”position 652 a. The lower end of the disablespring 622 is also connected to thering holder 624, such that the reactive downward movement of the ring holder creates tension in the disablespring 622. Thevalve 612 is vertically affixed to the upper second end of the disablespring 622, such that the valve opens 21 b in reaction to tension in the disablespring 622, whereby thevalve face 613 extends from thevalve seat 615. - Alternate Mechanical Valve Disabler System.
FIG. 50 is a detailed partialcross-sectional view 700 of an alternate mechanicalvalve disabler system 610 b in a first position with a disabler set.FIG. 51 is a detailed partialcross-sectional view 710 of an alternate mechanicalvalve disabler system 610 b in a second disabled position with a disabler set.FIG. 52 is a detailed partialcross-sectional view 720 of an alternate mechanicalvalve disabler system 610 b in a first enabled and closed position.FIG. 53 is a detailed partialcross-sectional view 730 of an alternate mechanicalvalve disabler system 610 b in a second enabled and opened position. - Disabler Details.
FIG. 54 is a detailed partialcross-sectional view 740 of a spring disabler mechanism 742 in contact with a valve cap 744 located between avalve spring 28 and a disablespring 30.FIG. 55 is aschematic profile 770 of a disabler cam lobe 772. - The lobe 772 is preferably designed to accelerate the disable
spring 30 and disable spring holder down with just enough forced delivered during approximately one sixth turn of acamshaft 34, so as to reach a fully compressed position with zero speed (as is done with the conventional camshaft/poppet valve system). In some embodiments, ¼ revolution is sufficient, since no deceleration is required. - The disabler solenoid 742 is released as soon as the disabler spring holder 744 begins to move downward, allowing the clapper to move along the outer surface of the holder. When the disabler spring holder reaches the lower zero speed point, the rebound spring pushes the clapper along the outer surface of the holder, locking it in place.
-
FIG. 54 shows the angled locking surface for both the valve cap and disabler spring holder. The angle theta of the surface determines the proportion of the disabler spring force, where Fx=Fz sine theta, which the solenoid spring must exert, to prevent the disabler spring from pushing up the holder. - The solenoid, when energized, overcomes the solenoid spring force, and allows the disabler spring holder to move up. The disabler spring is restrained from moving up to hold the spring compressed. The lobe surface restrains the holder in the up position.
- Although the valve disabler system and its methods of use are described herein in connection with an engine, such as an internal combustion engine, the apparatus and techniques can be implemented for a wide variety of alternate internal combustion and/or hybrid engines, or any combination thereof, as desired. Furthermore, the apparatus and techniques can be implemented for a wide variety of valves and/or actuators, or any combination thereof, as desired.
- Accordingly, although the invention has been described in detail with reference to a particular preferred embodiment, persons possessing ordinary skill in the art to which this invention pertains will appreciate that various modifications and enhancements may be made without departing from the spirit and scope of the claims that follow.
Claims (50)
1. A valve system, comprising:
a valve assembly linearly movable between a first closed position and a second open position;
a spring assembly in communication with the valve assembly having a first spring assembly position when the valve assembly is in the first closed position and a second spring assembly position when the valve assembly is in the second open position;
at least one first electromagnet; and
at least one permanent magnet;
wherein the magnetic field from at least one of the permanent magnets provides an attractive latching force to valve assembly when the valve assembly is in any of the first closed position and the second open position.
2. The valve system of claim 1 , wherein the permanent magnet comprises a permanent magnet clapper fixedly attached to the valve assembly.
3. The valve system of claim 1 , wherein the valve assembly further comprises a magnetically conductive clapper fixedly attached to the valve assembly.
4. The valve system of claim 3 , further comprising:
magnetically conductive material in contact with the permanent magnet, whereby the magnetically conductive clapper latches to the magnetically conductive material when the valve assembly is in any of the first closed position and the second open position.
5. The valve system of claim 1 , wherein the a spring assembly comprises a first spring and a second spring,
wherein the first spring is compressed by the valve assembly when the valve assembly is located in the second position, and is uncompressed when the valve assembly is located in the first position; and
wherein the second spring is compressed by the valve assembly when the valve assembly is located in the first position, and is uncompressed when the valve assembly is located in the second position.
6. The valve system of claim 5 , wherein said first spring is isolated from the valve assembly at the first closed position, and wherein said second spring is isolated from the valve assembly at the second open position.
7. The valve system of claim 5 , wherein the first spring and the second spring each have a different rate of compression.
8. The valve system of claim 5 , wherein the first spring and the second spring have different lengths.
9. The valve system of claim 5 , wherein the first spring and the second spring have different masses.
10. The valve system of claim 1 , further comprising:
means for providing energy to at least one of the electromagnets to increase a local magnetic field.
11. The valve system of claim 1 , further comprising:
means for providing energy to at least one of the electromagnets to decrease a local magnetic field.
12. The valve system of claim 1 , further comprising:
means for providing energy to at least one of the electromagnets to attract the valve assembly.
13. The valve system of claim 1 , further comprising:
means for providing energy to at least one of the electromagnets to repel the valve assembly.
14. The valve system of claim 1 , further comprising:
means for repelling and attracting the valve assembly to allow the valve assembly to be opened and/or closed more quickly than a natural frequency of the spring assembly would perform while still obtaining a soft landing.
15. The valve system of claim 1 , further comprising:
means for feedback control of valve assembly motion.
16. The valve system of claim 15 , wherein the feedback control compensates for any of friction forces and pressure forces.
17. The valve system of claim 1 , further comprising:
means for energy recovery during deceleration of said valve assembly.
18. The valve system of claim 1 , wherein the attractive latching force is sufficient to hold the valve assembly in any of the first closed position and the second open position, such that no external power is required to hold the valve assembly in any of the first closed position and the second open position.
19. The valve system of claim 1 , further comprising:
means for storing energy recovered from at least one of the electromagnets.
20. The valve system of claim 1 , wherein at least one of the permanent magnets comprises any of neodymium and samarium cobalt.
21. The valve system of claim 1 , wherein both a north pole and a south pole of at least one of the permanent magnets are used to attract or repel the valve assembly.
22. The valve system of claim 1 , further comprising:
an electromagnetic assembly core which extends from the electromagnet.
23. The valve system of claim 22 , wherein the electromagnetic assembly core comprises any of a solid material and a laminated material.
24. The valve system of claim 22 , wherein the electromagnetic assembly core comprises a laminated material, and wherein the valve assembly comprises a clapper fixedly attached to the valve assembly, the clapper comprising a laminated material.
25. A valve system, comprising:
a valve assembly linearly movable between a closed position and an open position;
a spring assembly associated with the valve assembly having a fist spring assembly position when the valve is in the first closed position and a second spring assembly position when the valve is in the second open position;
at least one electromagnet;
a clapper affixed to the valve assembly and movable in relation to the electromagnet; and
at least one permanent magnetic latch having a magnetic field, wherein the magnetic field from the permanent magnetic latches provides an attractive latching force to the clapper when the valve assembly is in any of the closed position and the open position.
26. The valve system of claim 25 , further comprising:
means for providing energy to at least one of the electromagnets to increase a local magnetic field.
27. The valve system of claim 25 , further comprising:
means for providing energy to at least one of the electromagnets to decrease a local magnetic field.
28. The valve system of claim 25 , further comprising:
means for providing energy to at least one of the electromagnets to attract the clapper.
29. The valve system of claim 25 , further comprising:
means for providing energy to at least one of the electromagnets to repel the clapper.
30. The valve system of claim 25 , wherein the clapper comprises a permanent magnet.
31. The valve system of claim 25 , further comprising:
means for repelling and attracting the valve assembly to allow the valve assembly to be opened and/or closed more quickly than a natural frequency of the spring assembly would perform while still obtaining a soft landing.
32. The valve system of claim 25 , further comprising:
means for feedback control of valve assembly motion.
33. The valve system of claim 32 , wherein the feedback control compensates for any of friction forces and pressure forces.
34. The valve system of claim 25 , further comprising:
means for energy recovery during deceleration of said valve assembly.
35. The valve system of claim 25 , wherein the attractive latching force is sufficient to hold the valve assembly in any of the first closed position and the second open position, such that no external power is required to hold the valve assembly in any of the first closed position and the second open position.
36. The valve system of claim 25 , further comprising:
means for storing energy recovered from at least one of the electromagnets.
37. The valve system of claim 25 , wherein the permanent magnet latches comprises any of neodymium and samarium cobalt.
38. The valve system of claim 25 , wherein the a spring assembly comprises a first spring and a second spring,
wherein the first spring is compressed by the valve assembly when the valve assembly is located in the second position, and is uncompressed when the valve assembly is located in the first position; and
wherein the second spring is compressed by the valve assembly when the valve assembly is located in the first position, and is uncompressed when the valve assembly is located in the second position.
39. The valve system of claim 38 , wherein the first spring is isolated from the valve assembly at the closed position, and wherein the second spring is isolated from the valve assembly at the open position.
40. The valve system of claim 38 , wherein the first spring and the second spring each have a different rate of compression.
41. The valve system of claim 38 , wherein the first spring and the second spring have different lengths.
42. The valve system of claim 38 , wherein the first spring and the second spring have different masses.
43. The valve system of claim 25 , wherein energy is returned to a power source by use of regenerative breaking of the clapper.
44. The valve system of claim 25 , wherein both a north pole and a south pole of at least one of the permanent magnet latches are used to attract or repel the clapper.
45. The valve system of claim 25 , further comprising:
a software module for at least partially controlling a soft landing and optionally for reducing power consumption.
46. The valve system of claim 25 , further comprising:
means to open the valve partially and close the valve again.
47. The valve system of claim 25 , further comprising:
an electromagnetic core.
48. The valve system of claim 47 , wherein the electromagnetic core is formed as a laminated structure.
49. The valve system of claim 25 , wherein the clapper is formed as a spiral laminate structure.
50. The valve system of claim 25 , wherein the clapper comprises at least one permanent magnet which provides at least a portion of the magnetic field for the permanent magnetic latches.
Priority Applications (2)
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US10/897,875 US20050046531A1 (en) | 2002-10-09 | 2004-07-22 | Electromagnetic valve system |
PCT/US2004/023685 WO2005012697A2 (en) | 2003-07-25 | 2004-07-23 | Electromagnetic valve system |
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US41726402P | 2002-10-09 | 2002-10-09 | |
US49019503P | 2003-07-25 | 2003-07-25 | |
US10/674,743 US20040113731A1 (en) | 2002-10-09 | 2003-09-29 | Electromagnetic valve system |
US10/897,875 US20050046531A1 (en) | 2002-10-09 | 2004-07-22 | Electromagnetic valve system |
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US10/674,743 Continuation-In-Part US20040113731A1 (en) | 2002-10-09 | 2003-09-29 | Electromagnetic valve system |
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US20050046531A1 true US20050046531A1 (en) | 2005-03-03 |
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US10/897,875 Abandoned US20050046531A1 (en) | 2002-10-09 | 2004-07-22 | Electromagnetic valve system |
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US (1) | US20050046531A1 (en) |
WO (1) | WO2005012697A2 (en) |
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US20060139135A1 (en) * | 2003-02-26 | 2006-06-29 | Siemens Aktiengesellscaft | Linear magnetic drive |
US20090238700A1 (en) * | 2006-06-28 | 2009-09-24 | Dott.Ing.Mario Cozzani S.R.L. | Equipment for continuous regulation of the flow rate of reciprocating compressors |
US20100214044A1 (en) * | 2009-02-23 | 2010-08-26 | Jun Shen | Electromechanical relay and method of operating same |
US20110001591A1 (en) * | 2008-03-06 | 2011-01-06 | Zf Friedrichshafen Ag | Electromagnetic actuating mechanism |
US20110070113A1 (en) * | 2008-06-27 | 2011-03-24 | Cameron International Corporation | System and devices including valves coupled to electric devices and methods of making, using, and operating the same |
US8212640B1 (en) * | 2011-07-26 | 2012-07-03 | Lockheed Martin Corporation | Tool having buffered electromagnet drive for depth control |
US20120204853A1 (en) * | 2011-02-14 | 2012-08-16 | Bsh Home Appliances Corporation | Household gas appliance with a magnetically controlled gas supply system |
US20120240474A1 (en) * | 2009-05-08 | 2012-09-27 | Fireco Limited | Apparatus for controlling the movement of a closure |
US20120261499A1 (en) * | 2009-11-10 | 2012-10-18 | Andrew Dames | Solenoid actuator |
US20130001030A1 (en) * | 2009-11-23 | 2013-01-03 | Beijingwest Industries Co., Ltd | Bi-stable shock absorber assembly |
US20140015596A1 (en) * | 2012-04-20 | 2014-01-16 | Bryan A. Martin | Magnetic field switches |
US20160169403A1 (en) * | 2014-12-15 | 2016-06-16 | Continental Automotive Gmbh | Coil assembly and fluid injection valve |
US20160239025A1 (en) * | 2013-07-09 | 2016-08-18 | Deka Products Limited Partnership | Modular Valve Apparatus and System |
US9435462B2 (en) * | 2013-05-22 | 2016-09-06 | Precision Engine Control Corporation | Valve with latching return spring |
US9518677B2 (en) | 2013-11-06 | 2016-12-13 | Ford Global Technologies, Llc | Method and system for adjusting a fuel tank isolation valve |
US9709006B2 (en) | 2015-04-08 | 2017-07-18 | Ford Global Technologies, Llc | Systems and methods for depressurizing a fuel tank |
US20170241379A1 (en) * | 2016-02-22 | 2017-08-24 | Donald Joseph Stoddard | High Velocity Vapor Injector for Liquid Fuel Based Engine |
US20170241562A1 (en) * | 2016-02-23 | 2017-08-24 | Rausch & Pausch Gmbh | Pole tube for electromagnets and magnetic valves, and method as well as apparatus for its manufacture |
US9777678B2 (en) | 2015-02-02 | 2017-10-03 | Ford Global Technologies, Llc | Latchable valve and method for operation of the latchable valve |
CN108374926A (en) * | 2018-03-30 | 2018-08-07 | 浙江三泉智能科技有限公司 | Impulse electromagnetic valve valve head and bathroom flushometer |
US10578066B2 (en) * | 2012-08-23 | 2020-03-03 | Continental Automotive Gmbh | Valve assembly for an injection valve and injection valve |
US20200119619A1 (en) * | 2018-10-16 | 2020-04-16 | Thomas Nikita Krupenkin | Method and Apparatus For Mechanical Energy Harvesting Using Variable Inductance Magnetic Flux Switch |
US11041440B2 (en) * | 2018-02-02 | 2021-06-22 | Rolls-Royce Plc | Fuel flow valve |
EP3830398A4 (en) * | 2018-07-31 | 2022-04-27 | Hedman Ericsson Patent AB | Electrically activated valve actuator for an internal combustion engine |
TWI764116B (en) * | 2019-03-25 | 2022-05-11 | 日商Smc股份有限公司 | Remote control device for solenoid valve |
US20230127691A1 (en) * | 2021-10-21 | 2023-04-27 | Kenneth Schulz | Electronic Valve Train Assembly |
RU2799408C2 (en) * | 2018-07-31 | 2023-07-05 | Хедман Эрикссон Патент Аб | Electrical valve actuator for internal combustion engine |
US11835018B2 (en) * | 2020-09-07 | 2023-12-05 | Dayco Ip Holdings, Llc | Magnetically latching valve for fuel vapor management systems and systems incorporating same |
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WO2011032724A2 (en) * | 2009-09-18 | 2011-03-24 | Fluid Automation Systems S.A. | Multiple coil solenoid valve |
DE102018008410A1 (en) * | 2018-10-25 | 2020-04-30 | Andreas Stihl Ag & Co. Kg | Electromagnetic valve, method for operating an electromagnetic valve |
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US6681728B2 (en) * | 2001-11-05 | 2004-01-27 | Ford Global Technologies, Llc | Method for controlling an electromechanical actuator for a fuel air charge valve |
US6763789B1 (en) * | 2003-04-01 | 2004-07-20 | Ford Global Technologies, Llc | Electromagnetic actuator with permanent magnet |
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US4690371A (en) * | 1985-10-22 | 1987-09-01 | Innovus | Electromagnetic valve with permanent magnet armature |
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US6003481A (en) * | 1996-09-04 | 1999-12-21 | Fev Motorentechnik Gmbh & Co. Kommanditgesellschaft | Electromagnetic actuator with impact damping |
US6049264A (en) * | 1997-12-09 | 2000-04-11 | Siemens Automotive Corporation | Electromagnetic actuator with composite core assembly |
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US6681728B2 (en) * | 2001-11-05 | 2004-01-27 | Ford Global Technologies, Llc | Method for controlling an electromechanical actuator for a fuel air charge valve |
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Cited By (42)
Publication number | Priority date | Publication date | Assignee | Title |
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US7482902B2 (en) * | 2003-02-26 | 2009-01-27 | Siemens Aktiengesellschaft | Linear magnetic drive |
US20060139135A1 (en) * | 2003-02-26 | 2006-06-29 | Siemens Aktiengesellscaft | Linear magnetic drive |
US20090238700A1 (en) * | 2006-06-28 | 2009-09-24 | Dott.Ing.Mario Cozzani S.R.L. | Equipment for continuous regulation of the flow rate of reciprocating compressors |
US9611845B2 (en) * | 2006-06-28 | 2017-04-04 | Dott.Ing. Mario Cozzani S.R.L. | Equipment for continuous regulation of the flow rate of reciprocating compressors |
US8228149B2 (en) * | 2008-03-06 | 2012-07-24 | Zf Friedrichshafen Ag | Electromagnetic actuating mechanism |
US20110001591A1 (en) * | 2008-03-06 | 2011-01-06 | Zf Friedrichshafen Ag | Electromagnetic actuating mechanism |
US9103335B2 (en) * | 2008-06-27 | 2015-08-11 | Ge Oil & Gas Compression Systems, Llc | System and devices including valves coupled to electric devices and methods of making, using, and operating the same |
US9567991B2 (en) * | 2008-06-27 | 2017-02-14 | Zahroof Valves, Inc. | Systems and devices including valves coupled to electric devices and methods of making, using, and operating the same |
US20110070113A1 (en) * | 2008-06-27 | 2011-03-24 | Cameron International Corporation | System and devices including valves coupled to electric devices and methods of making, using, and operating the same |
US20150308424A1 (en) * | 2008-06-27 | 2015-10-29 | Ge Oil & Gas Compression Systems, Llc | Systems and devices including valves coupled to electric devices and methods of making, using, and operating the same |
US8143978B2 (en) * | 2009-02-23 | 2012-03-27 | Magvention (Suzhou), Ltd. | Electromechanical relay and method of operating same |
US20100214044A1 (en) * | 2009-02-23 | 2010-08-26 | Jun Shen | Electromechanical relay and method of operating same |
US20120240474A1 (en) * | 2009-05-08 | 2012-09-27 | Fireco Limited | Apparatus for controlling the movement of a closure |
US9530551B2 (en) * | 2009-11-10 | 2016-12-27 | Sentec Ltd | Solenoid actuator |
US20120261499A1 (en) * | 2009-11-10 | 2012-10-18 | Andrew Dames | Solenoid actuator |
US9163694B2 (en) * | 2009-11-23 | 2015-10-20 | Beijingwest Industries Co., Ltd. | Bi-stable shock absorber assembly |
US20130001030A1 (en) * | 2009-11-23 | 2013-01-03 | Beijingwest Industries Co., Ltd | Bi-stable shock absorber assembly |
US8662071B2 (en) * | 2011-02-14 | 2014-03-04 | Bsh Home Appliances Corporation | Household gas appliance with a magnetically controlled gas supply system |
US20120204853A1 (en) * | 2011-02-14 | 2012-08-16 | Bsh Home Appliances Corporation | Household gas appliance with a magnetically controlled gas supply system |
US8212640B1 (en) * | 2011-07-26 | 2012-07-03 | Lockheed Martin Corporation | Tool having buffered electromagnet drive for depth control |
US20140015596A1 (en) * | 2012-04-20 | 2014-01-16 | Bryan A. Martin | Magnetic field switches |
US10578066B2 (en) * | 2012-08-23 | 2020-03-03 | Continental Automotive Gmbh | Valve assembly for an injection valve and injection valve |
US9435462B2 (en) * | 2013-05-22 | 2016-09-06 | Precision Engine Control Corporation | Valve with latching return spring |
US20160239025A1 (en) * | 2013-07-09 | 2016-08-18 | Deka Products Limited Partnership | Modular Valve Apparatus and System |
US10613553B2 (en) * | 2013-07-09 | 2020-04-07 | Deka Products Limited Partnership | Modular valve apparatus and system |
US9518677B2 (en) | 2013-11-06 | 2016-12-13 | Ford Global Technologies, Llc | Method and system for adjusting a fuel tank isolation valve |
US20160169403A1 (en) * | 2014-12-15 | 2016-06-16 | Continental Automotive Gmbh | Coil assembly and fluid injection valve |
US9777678B2 (en) | 2015-02-02 | 2017-10-03 | Ford Global Technologies, Llc | Latchable valve and method for operation of the latchable valve |
US9709006B2 (en) | 2015-04-08 | 2017-07-18 | Ford Global Technologies, Llc | Systems and methods for depressurizing a fuel tank |
US20170241379A1 (en) * | 2016-02-22 | 2017-08-24 | Donald Joseph Stoddard | High Velocity Vapor Injector for Liquid Fuel Based Engine |
US20170241380A1 (en) * | 2016-02-22 | 2017-08-24 | Donald Joseph Stoddard | Liquid fuel based engine system using high velocity fuel vapor injectors |
US10125890B2 (en) * | 2016-02-23 | 2018-11-13 | Rausch & Pausch Gmbh | Pole tube for electromagnets and magnetic valves, and method as well as apparatus for its manufacture |
US20170241562A1 (en) * | 2016-02-23 | 2017-08-24 | Rausch & Pausch Gmbh | Pole tube for electromagnets and magnetic valves, and method as well as apparatus for its manufacture |
US11041440B2 (en) * | 2018-02-02 | 2021-06-22 | Rolls-Royce Plc | Fuel flow valve |
CN108374926A (en) * | 2018-03-30 | 2018-08-07 | 浙江三泉智能科技有限公司 | Impulse electromagnetic valve valve head and bathroom flushometer |
EP3830398A4 (en) * | 2018-07-31 | 2022-04-27 | Hedman Ericsson Patent AB | Electrically activated valve actuator for an internal combustion engine |
RU2799408C2 (en) * | 2018-07-31 | 2023-07-05 | Хедман Эрикссон Патент Аб | Electrical valve actuator for internal combustion engine |
US20200119619A1 (en) * | 2018-10-16 | 2020-04-16 | Thomas Nikita Krupenkin | Method and Apparatus For Mechanical Energy Harvesting Using Variable Inductance Magnetic Flux Switch |
US10938276B2 (en) * | 2018-10-16 | 2021-03-02 | Thomas Nikita Krupenkin | Method and apparatus for mechanical energy harvesting using variable inductance magnetic flux switch |
TWI764116B (en) * | 2019-03-25 | 2022-05-11 | 日商Smc股份有限公司 | Remote control device for solenoid valve |
US11835018B2 (en) * | 2020-09-07 | 2023-12-05 | Dayco Ip Holdings, Llc | Magnetically latching valve for fuel vapor management systems and systems incorporating same |
US20230127691A1 (en) * | 2021-10-21 | 2023-04-27 | Kenneth Schulz | Electronic Valve Train Assembly |
Also Published As
Publication number | Publication date |
---|---|
WO2005012697A2 (en) | 2005-02-10 |
WO2005012697B1 (en) | 2005-06-02 |
WO2005012697A3 (en) | 2005-04-07 |
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