US3641988A - Valve-actuating mechanism for an internal combustion engine - Google Patents

Valve-actuating mechanism for an internal combustion engine Download PDF

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Publication number
US3641988A
US3641988A US7927A US3641988DA US3641988A US 3641988 A US3641988 A US 3641988A US 7927 A US7927 A US 7927A US 3641988D A US3641988D A US 3641988DA US 3641988 A US3641988 A US 3641988A
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Prior art keywords
valve
engine
mechanism according
shaft
speed
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Expired - Lifetime
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US7927A
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English (en)
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Glevared Torazza
Deate Giacesa
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FIAT SOC PER AZIEAI
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FIAT SOC PER AZIEAI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203—Variable control of intake and exhaust valves
    • F02D13/0207—Variable control of intake and exhaust valves changing valve lift or valve lift and timing
    • F02D13/0211—Variable control of intake and exhaust valves changing valve lift or valve lift and timing the change of valve timing is caused by the change in valve lift, i.e. both valve lift and timing are functionally related
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/035—Centrifugal forces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • a valve-actuating mechanism for an internal combustion en gine has a number of rocker arms for operating the respective valves, each rocker am having a profiled cam surface for engaging the respective valve, and means, preferably hydraulically operated, for varying the valve movement produced by the rocker arm in dependence upon the engine speed and load to vary the valve timing for optimum efficiency.
  • 16Claims 10Drawing Figures u 21 IL 17 15 23 25 2 18 ll 12 20 I l r'1 13 PAIENTEB FEB 15 I972 SHEET 5 [IF 9 1 1 3 1 8 w 1 Z w W m O 1 M 3 w w 5 1 1 8 5 6 2 5 u 2 2 s K g l I ⁇ 3 ll. 2 INK T T 3 2 I ⁇ i d 1 v?
  • the timing used in practice is usually a compromise, giving moderate engine powers at both low and high speeds; that is to say, the performance of the engine will only be good within a fairly limited speed range.
  • each cam has a variable lift law along its width so that by shifting the cam shaft axially, different valve timings are achieved. From this it necessarily arises that the tappets engaged by the cams must be spherical, and in consequence there is punctiform contact between each cam and tappet, with very high contact pressures, if the valve springs are so proportioned as to allow high valve operating speeds;
  • the present invention provides a valve actuating mechanism for an internal combustion reciprocating engine, including a rotary drive shaft, and characterized in that the mechanism includes means for converting the rotary movement of the drive shaft into rocking movement of a cam having a cam surface the contour of which includes a profiled valve operating portion, and means for varying the amplitude of the valve movement caused by said profiled cam portion in dependence upon the speed of and load upon the engine.
  • FIG. 1 is a sectional elevation of a first embodiment of a valve actuating mechanism according to the invention with induction and exhaust valves closed;
  • FIG. 2 is a part-sectional elevation of part of the mechanism illustrated in FIG. I, on a larger scale, with the valve open;
  • FIG. 3 is a diagrammatic illustration of an hydraulic device which is part of the mechanism illustrated in FIG. 1;
  • FIG. 4 consists of a number of diagrams illustrating graphically the variations of the lift, speed and acceleration of the valves plotted againstthe angular position of the rotating shaft of the mechanism illustrated in FIG. 1, for two different positions of the hydraulic device illustrated in FIG. 3;
  • FIG. 5 is a view in elevation of a variant of the embodiment illustrated in FIG. 1;
  • FIG. 6 is a diagrammatic representation of an hydraulic device forming part of the mechanism illustrated in FIG. 5;
  • FIG. 7 consists of a number of diagrams illustrating graphically the variations of the lift, speed and acceleration of the valves plotted against the angular position of the rotating shaft of the mechanism illustrated in FIG. 5 for two different positions of the device illustrated in FIG. 6;
  • FIG. 8 is a sectional elevation of a second embodiment of a valve actuating mechanism according to the invention.
  • FIG. 9 is a sectional elevation of part of a third embodiment of the invention.
  • FIG. 10 comprises a number of diagrams illustrating graphically the variations of the lift, speed and acceleration of the valves plotted against the angular position of the rotating shaft of the mechanism illustrated in FIG. 9 for two different positions of an hydraulic device similar to that illustrated in FIG. 6.
  • FIGS. 1 and 2 illustrate the valve gear of a four-stroke internal combustion engine of the kind having overhead induction and exhaust valves arranged in a V configuration and driven by two respective overhead camshafts driven by the engine.
  • FIG. 1 indicates part of the internal combustion engine, showing the upper part of a cylinder 2 housing a slidable piston 3 driven by a connecting rod 4.
  • the cylinder 2 has at its upper end two ports 5 for induction and exhaust respectively, said ports 5 cooperating respectively with an induction valve 6 and an exhaust valve 6a.
  • Each valve 6, 6a comprises a head 7 which is shaped in the conventional manner to make sealing contact with seats ground on the respective ports 5.
  • Each vale 6, 6a further has a stem 8 formed integrally with the head 7 and surmounted by a cotter 9.
  • each valve 6 between the cotter 9 and the port 5, and surrounding the stem 8 there are provided a number of springs 10 (two in the example illustrated) to urge the valves 6-6a towards their closed positions (FIG. 1
  • cam shafts 12 In order to effect opening of the valves 6, 6a against the biasing action of the springs 10, there are housed in the cylinder head 11 of the engine 1, above the valves, two cam shafts 12, shown in broken outline in FIG. 1, one for each valve 6-6a.
  • the cam shafts l2 rotate at a speed which is directly related to the speed of the engine. In this particular case, where the engine is of the four-stroke type, the shafts 12 rotate at a speed equal to half that of the engine shaft.
  • Each of the two cam shafts 12 supports, at axially spaced positions, a number of circular eccentrics 13 the number of which is equal to the number of valves on the shafts 12.
  • each eccentric 13 there is keyed or secured a connecting rod 15 having a small end 14 to which is pivotally connected, by means of a pin 16, a cam in the form of a rocker arm 17.
  • the rocker arms 17 associated with each cam shaft 12 are pivotally supported on a shaft 18.
  • each rocker arm 17 On the side of the shaft 18 opposite to the pivot pin 16 each rocker arm 17 has a shaped cam surface 19 having a first section 20 concentric with the axis of the shaft 18, and a second section, hereinafter referred to as the gauge portion 21, the shape of which determines the law of operation of the respective valves 6-6a.
  • Each rocker arm 17 acts with its cam surface 19 on the upper surface 22 of an oscillating lever 23 pivotally mounted at one end on a shaft 24. At its other end, on its lower surface, each oscillating lever 23 has a rounded surface 25, the profile of which is an arc of a circle, which rests upon the cotter 9 of the respective valve stem 8.
  • Each support 26 (FIG. 3) has an internal. cylindrical bore 27 in which a piston 28 is slidingly mounted.
  • the piston 28 has at its lower end an integral projection 29 which rests upon a bearing face 30 formed in the cylinder head 1 1.
  • the upper part of the cylindrical bore 27 communicates, through a port 31, with a duct 32a through which flows oil under pressure from the lubrication system of the engine, supplied by a pump 33.
  • the flow or the pressure of the oil, or both, are regulated by a valve 34 in dependence upon the speed of the engine and the load on the latter, that is, the torque delivered thereby.
  • a branch duct 35 including a flow restrictor 36 branches from the duct 32a, downstream of the pump 33.
  • the branch duct 35 supplies oil to a centrifugal governor 37 which in turn controls, in accordance with the speed of the engine, the oil pressure upstream of the restrictor 36, that is, the input oil pressure at the valve 34.
  • the oil pressure determined by the centrifugal governor 37, controls the opening of the valve 34.
  • the opening of the valve 34 is at the same time controlled by a vacuum-operated capsule 38, communicating with the induction manifold of the engine, shown diagrammatically at 39.
  • the capsule 38 controls the valve 34 in dependence on the load on the engine.
  • each rocker arm 17 is effected by means of a desmodromic drive system comprising an articulated quadrilateral linkage formed by the respective eccentric 13 which acts as a crank, the connecting rod 15 and the rocker arm 17.
  • the shaft 24 since the shaft 24 is carried by the movable supports 26, which in their turn are pivotable about the shaft 18, the shaft 24 can shift through a circular arc having a radius equal to the distance between the axes of the shafts l8 and 24, and it is precisely this shifting which achieves the required variation of the valve timing.
  • the oscillating lever 23 is shown as a continuous line in the position which gives the maximum timing, and in broken outline in the position which gives the minimum timing.
  • the operating play or tappet clearance is not influenced by the position of the axis of the shaft 24; conversely, it is possible to obtain an operating play or clearance which is linearly variable with the valve timing by suitably displacing the center of curvature of the rounded surface 25 from the axis of the shaft 18. This can be useful if, for example, the engine is subject to thermal expansions of the kinematic fall of the valve 6 bringing about variations in the play which are proportional to the engine speed and load.
  • the oil under pressure which enters the bore 27 is the same as is used to lubricatethe engine.-ln fact the oil supply duct 320 connected to the bore 27 is branched from a duct 32 which supplies the lubricating oil to the engine; the quantity and the pressure of the oil, or both, are governed by the valve 34, comprising a governor, which is attached to the device and which senses the speed and the load of the engine, as hereinbefore described.
  • variation of the timing is achieved, as has been seen, by means of an hydraulic drive actuator. It will be appreciated, however, that the variation of the timing can be effected by means of mechanical, pneumatic or electrical actuators responsive to the speed and the load of the engine.
  • FIG. 4 show clearly the effect of the relationship which exists between the length of the connecting rod and the aforesaid crank arm in the device illustrated in FIGS. 1 and 2.
  • the graphs showing the variations of the lift, velocity and acceleration of the valve are asymmetrical. Specifically, the absolute values of the velocity and the acceleration are greater when the value is open, with the advantage of obtaining, when the valve closes, low noise and efficient working of the cooperating members.
  • the continuous curves refer to a wide timing position, whereas the dashed curves refer to a position corresponding to a narrower timing.
  • a single rotating cam shaft 12 drives both the valves 6; this cam shaft 12 is housed in the engine cylinder block on one side of the row ofcylinders 2.
  • Each rocker arm 17 is mounted on a shaft 18 which is arranged to rotate within a number of supports fixed to a bearing face 30 in the head 11, by means of screws 46 (see FIG. 6).
  • the rocker arm 17, in contrast with that shown in FIGS. 1 and 2, has its shaped cam surface on the same side of the shaft 18 as the pin 16.
  • a support arm 47 is rotatably supported on the shaft 18 and in turn supports a shaft 24 which acts as a fulcrum for an oscillating lever 23.
  • the support arm 47 is formed on the opposite side of the shaft 24 from the shaft 18 with a nose 48 which bears upon a trapezium-shaped upper surface 49 of a piston 50 of an hydraulic actuator device 51 illustrated in FIG. 6.
  • the piston 50 is mounted slidingly in a cylindrical bore 52 in the device 51, the bore 52 being closed at its lower end by the bearing face 30.
  • Oil under pressure is supplied to the lower part of the bore 52 through an aperture 53.
  • This oil is supplied, as in the embodiment illustrated in FIG. 3, from the lubrication system via a duct 32a.
  • the pressurized oil is circulated by a pump 33, and a valve 34 governs the delivery and the pressure of the oil in accordance with the speed of the engine and the load to which the engine is subjected, that is, the torque delivered by the engine.
  • the upper surface 49 of the piston 50 has, on diametrically opposite sides with respect to the axis of the piston 50, two inclined plane surfaces, shown as 54 and 55, on which the noses 48 associated with the induction valve 6 and the exhaust valve 6a bear respectively.
  • connecting rods 15 work as tie rods; this can be done as illustrated in FIG. 5, by making each rocker arm 17 operative to lift its respective valve when the crank gear consisting of the eccentric l3 and of the connecting rod 15 is situated around the bottom dead center.
  • FIG. 8 relates to a fourstroke internal combustion engine which has induction valves 6 and exhaust valves 6a arranged in a V formation.
  • a single rotating cam shaft 12 is housed in the cylinder block to one side of the row of cylinders 2, and governs the opening and the closing of said valves 6 and 6a.
  • each connecting rod 15 remote from the eccentric 13 is joined by means of a pin 56 to one end of one arm 57 of a small bellcrank lever 58 acting as'a rocker.
  • the levers 58, associated with the two connecting rods 15, are mounted on a common shaft 59 which acts as a fulcrum.
  • each lever 58 there is pivotally joined, by means of a pin 61, one end of a link 62 which is pivotally connected at its other end, by means of a pin 63, to the rocker arm 17.
  • the rocker arm 17 has a cam surface 19 which acts on an oscillating lever 23 which in turn acts upon the cotter 9 of the respective valve 6.
  • rocker arm 17 and the oscillating lever 23 are carried by supports 45 attached to the cylinder head 11 of the engine 1 by means of screws, not shown.
  • the shaft 59 acting as a fulcrum for the rocker levers 58 is supported by a support 64 mounted rotatably upon one of the shafts 18, which relates to the cam 17 driving one of the two valves, for example, that carrying the rocker arms 17 associated with the exhaust valves 6a.
  • the shaft 59 is supported by the pistonof an hydraulic actuator device of the type illustrated in FIGS. 3 and 6; by means of this device the shaft 59 can be displaced in dependence upon the speed of and load on the engine 1.
  • the result of the displacement of the shaft 59 is a variation of the effective length of the connecting rod 15 and the link 62 and, therefore, a different profile of the cam surface 19 of the rocker arm 17.
  • a disadvantage of this arrangement is that is comprises more moving parts than the embodiment described previously. Moreover the embodiment just described has a single actuator device, and from this it follows that, while the drive is achieved with greater case, there is the disadvantage that the same variation of stroke for both the induction and exhaust valves. It is clear that to avoid this disadvantage it would be necessary to have the rocker levers 58 rotatable about fulcra on two separate shafts and to displace their axes of oscillation with independent actuators.
  • the oscillating lever 23, the pivotal axis of the shaft of which remains fixed is not strictly indispensible and could be replaced by a flat or cylindrical cotter, but its use makes it possible to reduce the dimensions of the rocker arm 17.
  • FIG. 9 relates to a' fourstroke internal combustion engine .1 with induction and exhaust valves 6, 6a in line.
  • the single rotating shaft 12 arranged in the cylinder block on one side of the cylinder 2 drives the opening and closing of the valves referred to above. 7 I
  • the shaft 12 carries, for each valve, the integral circular eccentric 13 on which the lower end of the connecting rod 15 is rotatably mounted.
  • the rocker arm 17 is pivotably connected to the upper end of the connecting rod 15 by means of a pivot pin 65, the cam 17 being mounted for rocking movement on a shaft 18.
  • the cam 17 has a cam surface 19 which acts on a contoured surface 66 made on a face of one arm 67 of a rocker 68 pivotally mounted on a shaft 24.
  • the other arm of the rocker 68 consists of the lever 23 which acts upon the cotter 9 of the respective valve 6.
  • the shaft 18 on which the rocker arms 17 are rotatably mounted is supported by an oscillating arm 69 rotatably mounted upon ashaft 70.
  • the shaft 70 and the shaft 24 are in turn rotatably supported upon'the support 45 which is fixed to the-cylinder head 11 of the engine 1 by means by screws (not shown).
  • the shaft 18 on which the rocker arms 17 are mounted bears upon an hydraulic actuator device of the same type as those illustrated in FIGS. 3 and 6 and is thus displaceable in accordance with the speed of and load on the engine 1.
  • FIG. 9 is illustrated the position of the shaft 18 corresponding to the maximum cam lift; for a displacement of the shaft 18 downwardlya reduction in timing results, so that the said displacement causes a rotation of the. rocker arm 17 around the pivot pin 65 and hence a given portion of the cam surface 19 comes into operation with a delay angle equal to the angle through which the rocker arm 17 has rotated around the pin 65.
  • the contoured surface 66 made upon the face of the arm 67 of the rocker 68 must have its centerof curvature coincident, when the respective valve 6 is closed, with the axis of the shaft 70, if the valve operating clearance or play is to be constant with variations in the timing.
  • a displacement of the center of curvature of the contoured surface 66 of the axis of the shaft 70 causes the valve operating play to vary linearly with valve timing.
  • FIG. show the laws of movement of the valve in two different positions of the shaft 18. In view of the length of the connecting rod it is evident that the diagrams are practically symmetrical.
  • a valve-actuating mechanism for an internal combustion engine having a rotary drive shaft, a plugal governor controlling the operation of said valve in depen-- rality of rocker arms, means converting rotary movement of the shaft into rocking movement of the rocker arms, and respective valves operable by the rocker arms
  • the improvement comprising the rocker arm having a cam surface the contour of which includes a profiled valve operating portion, means varying the amplitude of the valve movement caused by said profiled valve operating portion, means varying the amplitude of the valve movement caused by said profile d cam portion in dependence upon the speed of and load upon the engine including an oscillating lever interposed between the cam surface and the valve effective to amplify the valve displacement caused by the valve operating portion of the said cam surface, and means effecting a relative rotation between the rocker arm and the oscillating lever, said rotation having a magnitude determined by the speed of and load on the engine, wherein the means effecting the relative rotation between the rocker arm and the oscillating lever displace the ful
  • Mechanism according to claim 2 including an hydraulic actuator device arranged to cause rotation of the support in dependence upon the speed of and load on the engine.
  • the; hydraulic actuator device comprises meansdefining a bore in the movable support, a piston slidably mounted in the bore, a fixed reaction surface engaging the piston, and means supplying said bore with oil the pressure of which is dependent upon the speed of and load on the engine.
  • Mechanism according to claim 4 including a valve regulating the pressure of the oil supplied to said bore, a centrifudence on the engine speed and a vacuum-opcrated capsule, connected to the induction system of the engine, controlling the operation of said valve in dependence on the engine load;
  • Mechanism according to claim 1 including respective shafts mounted in the cylinder head of the engine, and respective crank means, for example an eccentric and a connecting rod connecting the induction and exhaust valves to the'respective shafts, opening of the respective valves being effected when the crank means are in top dead center positions.
  • Mechanism according to claim 2 including a cam shaft on which the rocker arms are rotatably mounted, the movable support comprising an oscillating arm mounted for rotation about the cam shaft, and further including a shaft carried by the oscillating arm and acting as a fulcrum for the oscillating lever, means being provided for rotating said arm in dependence upon the speed of and load on the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US7927A 1969-02-13 1970-02-02 Valve-actuating mechanism for an internal combustion engine Expired - Lifetime US3641988A (en)

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IT5058169 1969-02-13

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US3641988A true US3641988A (en) 1972-02-15

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US (1) US3641988A (enExample)
DE (2) DE2006618A1 (enExample)
ES (1) ES376448A1 (enExample)
FR (1) FR2032705A5 (enExample)
GB (1) GB1299673A (enExample)

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US3786792A (en) * 1971-05-28 1974-01-22 Mack Trucks Variable valve timing system
US3911879A (en) * 1973-07-13 1975-10-14 Daimler Benz Ag Valve adjustment mechanism for internal combustion engine
US4151817A (en) * 1976-12-15 1979-05-01 Eaton Corporation Engine valve control mechanism
WO1980000094A1 (en) * 1978-06-14 1980-01-24 Eaton Corp Improved engine valve control mechanism
US4200081A (en) * 1975-12-15 1980-04-29 Eaton Corporation Valve selector
US4224906A (en) * 1977-03-09 1980-09-30 Daimler-Benz Aktiengesellschaft Combustion engine with internal combustion
US4336775A (en) * 1975-12-12 1982-06-29 Eaton Corporation Valve selector
US4388897A (en) * 1980-09-22 1983-06-21 Bernard Rosa Variable camshaft assembly
US4438737A (en) * 1981-10-13 1984-03-27 Investment Rarities, Incorporated Apparatus and method for controlling the valve operation of an internal combustion engine
US4442806A (en) * 1981-12-03 1984-04-17 Honda Giken Kogyo Kabushiki Kaisha Valve driving control apparatus in an internal combustion engine
US4457268A (en) * 1982-01-25 1984-07-03 Jones Darrell L Valve position control device
US4503818A (en) * 1981-05-18 1985-03-12 Nissan Motor Company, Limited Variable valve timing arrangement for an internal combustion engine or the like
US4515121A (en) * 1981-12-03 1985-05-07 Honda Giken Kogyo Kabushiki Kaisha Valve driving control apparatus in an internal combusiton engine
US4556025A (en) * 1983-11-18 1985-12-03 Mazda Motor Corporation Engine valve mechanism having valve disabling device
US4558667A (en) * 1982-07-23 1985-12-17 Honda Giken Kogyo Kabushiki Kaisha Valve driving apparatus for an internal combustion engine
US4643141A (en) * 1986-01-26 1987-02-17 Bledsoe Phillip G Internal combustion engine valve lift and cam duration control system
US4911124A (en) * 1986-05-21 1990-03-27 Bennett Automotive Technology Pty., Ltd. Engines for use with gaseous fuels
WO1990003497A1 (de) * 1988-10-01 1990-04-05 Peter Kuhn Vorrichtung zur betätigung der ventile an verbrennungsmotoren mit veränderlicher ventilerhebungskurve
US5018487A (en) * 1989-06-30 1991-05-28 Suzuki Jidosha Kogyo Kabushiki Kaisha Valve timing mechanism with eccentric bushing on rocker shaft
US5078102A (en) * 1989-12-21 1992-01-07 Takuya Matsumoto Engine valve driving device
US5197447A (en) * 1992-04-14 1993-03-30 Dick Leon B Engine having valve stroke adjuster and fuel preheater
US5213073A (en) * 1990-11-05 1993-05-25 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Cylinder head of an internal combustion engine
US6360971B1 (en) 1998-11-25 2002-03-26 Alstom Method and appliance for atomizing liquid fuel for a firing installation
US6619250B2 (en) 2001-03-16 2003-09-16 Frank A. Folino Desmodromic valve actuation system
FR2838769A1 (fr) * 2002-04-22 2003-10-24 Mdi Motor Dev Internat Detendeur a debit variable et distribution par soupape a commande progressive pour moteur a injection d'air comprime fonctionnant en mono et pluri energie et autres moteurs ou compresseurs
US20040055552A1 (en) * 2001-03-16 2004-03-25 Folino Frank A. Thermal compensating desmodromic valve actuation system
US20040074460A1 (en) * 2002-10-18 2004-04-22 Dhruva Mandal Valve lifter body
US20050000314A1 (en) * 2002-10-18 2005-01-06 Dhruva Mandal Roller follower body
US6871622B2 (en) 2002-10-18 2005-03-29 Maclean-Fogg Company Leakdown plunger
US20060000436A1 (en) * 2001-03-16 2006-01-05 Folino Frank A System and method for controlling engine valve lift and valve opening percentage
US7028654B2 (en) 2002-10-18 2006-04-18 The Maclean-Fogg Company Metering socket
FR2877991A1 (fr) * 2004-11-16 2006-05-19 Renault Sas Dispositif ameliore de commande de soupape de moteur a combustion interne, a levee variable
US7191745B2 (en) 2002-10-18 2007-03-20 Maclean-Fogg Company Valve operating assembly
US20090241875A1 (en) * 2008-03-26 2009-10-01 Labere Rikki Scott Apparatus and methods for continuous variable valve timing
US20090241881A1 (en) * 2008-03-12 2009-10-01 Kawasaki Jukogyo Kabushiki Kaisha Valve Operating System
US20110209679A1 (en) * 2010-02-26 2011-09-01 Honda Motor Co., Ltd. Rocker arm structure
US8033261B1 (en) 2008-11-03 2011-10-11 Robbins Warren H Valve actuation system and related methods
US10316709B2 (en) 2015-09-21 2019-06-11 Eaton Intelligent Power Limited Electromechanical valve lash adjuster
US11187118B2 (en) 2019-05-06 2021-11-30 Caterpillar Motoren Gmbh & Co. Kg Charge changing control device, reciprocating engine and method for operating a charge changing control device

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FR2472078A1 (fr) * 1979-12-21 1981-06-26 Baguena Michel Distribution variable pour moteur a quatre temps
GB2133465A (en) * 1982-12-24 1984-07-25 Ford Motor Co I.c. engine camshaft drive mechanism
AU593665B2 (en) * 1986-05-21 1990-02-15 Bennett Automotive Technology Pty. Ltd. Engines for use with gaseous fuels
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US5988125A (en) * 1997-08-07 1999-11-23 Unisia Jecs Corporation Variable valve actuation apparatus for engine
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AT411090B (de) 2000-12-12 2003-09-25 Jenbacher Ag Vollvariabler hydraulischer ventilantrieb
EP1712747A1 (de) * 2005-04-17 2006-10-18 Uwe Eisenbeis Ventiltrieb mit variablem Ventilhub und Steuerzeiten für hochdrehende Verbrennungsmotoren

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US4224906A (en) * 1977-03-09 1980-09-30 Daimler-Benz Aktiengesellschaft Combustion engine with internal combustion
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US4503818A (en) * 1981-05-18 1985-03-12 Nissan Motor Company, Limited Variable valve timing arrangement for an internal combustion engine or the like
US4438737A (en) * 1981-10-13 1984-03-27 Investment Rarities, Incorporated Apparatus and method for controlling the valve operation of an internal combustion engine
US4515121A (en) * 1981-12-03 1985-05-07 Honda Giken Kogyo Kabushiki Kaisha Valve driving control apparatus in an internal combusiton engine
US4442806A (en) * 1981-12-03 1984-04-17 Honda Giken Kogyo Kabushiki Kaisha Valve driving control apparatus in an internal combustion engine
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US4556025A (en) * 1983-11-18 1985-12-03 Mazda Motor Corporation Engine valve mechanism having valve disabling device
US4643141A (en) * 1986-01-26 1987-02-17 Bledsoe Phillip G Internal combustion engine valve lift and cam duration control system
US4911124A (en) * 1986-05-21 1990-03-27 Bennett Automotive Technology Pty., Ltd. Engines for use with gaseous fuels
WO1990003497A1 (de) * 1988-10-01 1990-04-05 Peter Kuhn Vorrichtung zur betätigung der ventile an verbrennungsmotoren mit veränderlicher ventilerhebungskurve
US5018487A (en) * 1989-06-30 1991-05-28 Suzuki Jidosha Kogyo Kabushiki Kaisha Valve timing mechanism with eccentric bushing on rocker shaft
US5078102A (en) * 1989-12-21 1992-01-07 Takuya Matsumoto Engine valve driving device
US5213073A (en) * 1990-11-05 1993-05-25 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Cylinder head of an internal combustion engine
US5197447A (en) * 1992-04-14 1993-03-30 Dick Leon B Engine having valve stroke adjuster and fuel preheater
WO1993021437A1 (en) * 1992-04-14 1993-10-28 Dick Leon B Engine having valve stroke adjuster and fuel preheater
US5280776A (en) * 1992-04-14 1994-01-25 Dick Leon B Engine having fuel preheater
US6360971B1 (en) 1998-11-25 2002-03-26 Alstom Method and appliance for atomizing liquid fuel for a firing installation
US6619250B2 (en) 2001-03-16 2003-09-16 Frank A. Folino Desmodromic valve actuation system
US20060000436A1 (en) * 2001-03-16 2006-01-05 Folino Frank A System and method for controlling engine valve lift and valve opening percentage
US20040055552A1 (en) * 2001-03-16 2004-03-25 Folino Frank A. Thermal compensating desmodromic valve actuation system
US7082912B2 (en) 2001-03-16 2006-08-01 Folino Frank A System and method for controlling engine valve lift and valve opening percentage
US6953014B2 (en) 2001-03-16 2005-10-11 Folino Frank A Thermal compensating desmodromic valve actuation system
WO2003089764A1 (fr) * 2002-04-22 2003-10-30 Mdi Motor Developement International S.A. Detendeur a debit variable et distribution par soupape a commande progressive pour moteur a injection d'air comprime fonctionnant en mono et pluri energie et autres moteurs ou compresseurs
US7296405B2 (en) 2002-04-22 2007-11-20 Mdi Motor Development International S.A. Variable flow reducing valve and gradual control valve distribution system for a compressed air injection engine operating on mono or multi energy and other engines or compressors
FR2838769A1 (fr) * 2002-04-22 2003-10-24 Mdi Motor Dev Internat Detendeur a debit variable et distribution par soupape a commande progressive pour moteur a injection d'air comprime fonctionnant en mono et pluri energie et autres moteurs ou compresseurs
US20050224059A1 (en) * 2002-04-22 2005-10-13 Mdi Motor Development International S.A. Variable flow reducing valve and gradual control valve distribution system for a compressed air injection engine operating on mono or multi energy and other engines or compressors
US7273026B2 (en) 2002-10-18 2007-09-25 Maclean-Fogg Company Roller follower body
US20040074460A1 (en) * 2002-10-18 2004-04-22 Dhruva Mandal Valve lifter body
US7028654B2 (en) 2002-10-18 2006-04-18 The Maclean-Fogg Company Metering socket
US6871622B2 (en) 2002-10-18 2005-03-29 Maclean-Fogg Company Leakdown plunger
US7128034B2 (en) 2002-10-18 2006-10-31 Maclean-Fogg Company Valve lifter body
US7191745B2 (en) 2002-10-18 2007-03-20 Maclean-Fogg Company Valve operating assembly
US20050000314A1 (en) * 2002-10-18 2005-01-06 Dhruva Mandal Roller follower body
US7281329B2 (en) 2002-10-18 2007-10-16 Maclean-Fogg Company Method for fabricating a roller follower assembly
US7284520B2 (en) 2002-10-18 2007-10-23 Maclean-Fogg Company Valve lifter body and method of manufacture
FR2877991A1 (fr) * 2004-11-16 2006-05-19 Renault Sas Dispositif ameliore de commande de soupape de moteur a combustion interne, a levee variable
US20090241881A1 (en) * 2008-03-12 2009-10-01 Kawasaki Jukogyo Kabushiki Kaisha Valve Operating System
EP2101045A3 (en) * 2008-03-12 2010-06-09 Kawasaki Jukogyo Kabushiki Kaisha Valve operating system
US8118003B2 (en) 2008-03-12 2012-02-21 Kawasaki Jukogyo Kabushiki Kaisha Valve operating system
US20090241875A1 (en) * 2008-03-26 2009-10-01 Labere Rikki Scott Apparatus and methods for continuous variable valve timing
US7866292B2 (en) 2008-03-26 2011-01-11 AES Industries Inc Apparatus and methods for continuous variable valve timing
US8033261B1 (en) 2008-11-03 2011-10-11 Robbins Warren H Valve actuation system and related methods
US20110209679A1 (en) * 2010-02-26 2011-09-01 Honda Motor Co., Ltd. Rocker arm structure
US8689751B2 (en) * 2010-02-26 2014-04-08 Honda Motor Co., Ltd Rocker arm structure
US10316709B2 (en) 2015-09-21 2019-06-11 Eaton Intelligent Power Limited Electromechanical valve lash adjuster
US11187118B2 (en) 2019-05-06 2021-11-30 Caterpillar Motoren Gmbh & Co. Kg Charge changing control device, reciprocating engine and method for operating a charge changing control device

Also Published As

Publication number Publication date
ES376448A1 (es) 1972-04-16
DE2006618A1 (de) 1971-02-18
FR2032705A5 (enExample) 1970-11-27
DE7005077U (de) 1971-05-27
GB1299673A (en) 1972-12-13

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