EP0579903A1 - Sequentieller Drehschieber mit doppelt wirkender Steuerung - Google Patents

Sequentieller Drehschieber mit doppelt wirkender Steuerung Download PDF

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Publication number
EP0579903A1
EP0579903A1 EP93105632A EP93105632A EP0579903A1 EP 0579903 A1 EP0579903 A1 EP 0579903A1 EP 93105632 A EP93105632 A EP 93105632A EP 93105632 A EP93105632 A EP 93105632A EP 0579903 A1 EP0579903 A1 EP 0579903A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve shaft
jacket
cylindrical
hollow cylindrical
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP93105632A
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English (en)
French (fr)
Inventor
Miljenko Schiattino
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0579903A1 publication Critical patent/EP0579903A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/026—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with two or more rotary valves, their rotational axes being parallel, e.g. 4-stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/006—Camshaft or pushrod housings

Definitions

  • the present invention relates to a device to be used in any machine which uses a valve distribution system and especially for use in internal combustion engines of the type used in cars, trucks, and the like. More particularly, the present invention relates to a double effect distribution sequential valve shaft for use in place of a system of levers and valves of alternative motion which have been used in the past.
  • the present invention will be described by illustrating its operation in an internal combustion engine with spark ignition.
  • the valve in such a system is a rod with a small plate on one extreme which has a conical seat for shutting the opening to the cylinder head, due to the effect of a spring fixed to it.
  • valve slips inside a guide and the opening and closing of the cylinder is done by a rocker arm which pushes it to its extreme or, when the pressure of the rocker arm ceases, it closes the conduit by the effect of the spring.
  • the movement of the rocker arm is carried out by a camshaft which transmits the sequence of opening and closing of each one of the intake or exhaust valves.
  • the camshaft is moved by the crankshaft by means of a chain, cogwheels or a dented belt with a number of turns equivalent to 1/2 rpm of the crankshaft in a four stroke engine (Otto cycle).
  • the present invention relates to a double effect distribution sequential valve shaft for use in an internal combustion engine or in any valve-type distribution system using camshafts and valves.
  • the device of the present invention is an important variation over the prior art and acts with superior performance and substantially minor cost of manufacturing.
  • the improvements derived from the advantages of the present invention have not previously been achieved by the existing systems.
  • each valve shaft consists of a jacket and a holed shaft, i.e., a shaft formed with a plurality of spaced holes or openings.
  • Each shaft is housed in a cylinder head cover of appropriate design, different from any one related to valve systems in the prior art.
  • the cylinder head cover is water cooled, and has openings which coincide with the openings in the jacket.
  • Each lower perforation or opening coincides with a combustion chamber of each cylinder of the engine.
  • the upper perforation coincides with either the intake or the exhaust manifold.
  • Each longitudinal valve shaft is mounted inside the jacket with a very accurate tolerance and also has perforations or openings from side to side in the vertical plane.
  • Each valve shaft opening is separated from the other by the distance between cylinder centers and is placed at a predetermined angle in the vertical plane, depending on its function in the sequence of intake or exhaust.
  • valve shaft Since the openings of the shaft extend through the shaft, from side to side in the vertical plane, at every complete turn one of the holes communicates through an opening in the jacket with a hole in the head of one combustion chamber of a predetermined cylinder twice. For this reason, the valve shaft is named "double effect." Because of this double effect, one complete turn of the crankshaft need only correspond to 1/4 of the turn of the double effect distribution sequential valve shaft instead of 1/2 turn as in a conventional camshaft. The rotation is transmitted from a pulley on the crankshaft by means of pulleys and toothed belts, with a corresponding difference of diameters to reduce the number of turns to a 4:1 ratio.
  • One of the ends of the valve shaft has a seeger ring and a bolted cover to permit longitudinal expansion only in the direction opposite to the pulleys. (See Fig. 2A).
  • the device used in the present invention is described below and illustrated in Figs. 1A-3D.
  • the present invention includes two longitudinal shafts (a) and (b) on the cylinder head 5 aligned with the engine axis, comprising a jacket 1 and a shaft formed with holes, i.e., a holed shaft.
  • the engine includes motor block 7, piston 8, cylinder head 5, connecting rod 12, a distribution toothed belt 9, distribution and reduction toothed pulley 11, tension pulley 13, and motion distribution toothed pulley 14.
  • a housing for two jackets is provided in the cylinder head cover 5, with outer water chambers.
  • a jacket 1, with perforations or openings 20 from side to side in the vertical plane of the jacket, is inserted into the housing under pressure and with a sealer. Each opening 20 coincides with a combustion chamber of each cylinder of the engine.
  • a double effect distribution sequential valve shaft 2 is mounted inside the jacket 1 with a very accurate tolerance.
  • the shaft also has perforations or openings 22 extending from side to side in the vertical plane. Each opening 22 is separated from the other by the same distance between cylinders and is placed at a predetermined angle in the vertical plane, depending on the sequence of intake or exhaust and the type of engine.
  • the openings 22 of the shaft are side to side in the vertical plane, at every complete turn, one of the openings 22 communicates twice every turn through an opening 20 in the jacket 1 with a hole 24 in the head of one combustion chamber of a given cylinder 3, for which reason it is named "double effect.”
  • one complete turn of the crankshaft need only result in 1/4 of a turn of the double effect distribution sequential valve shaft 2.
  • the rotation of the valve shaft is transmitted from a pulley 14 on the crankshaft 25 by means of pulleys and toothed belts 11 and 9, with a corresponding difference of diameters to reduce the number of turns to 4:1.
  • the exhaust or intake exit is shown at 4 in Fig. 1B.
  • one of the ends of the valve shaft has a seeger ring 15 and a bolted cover 16 to limit the longitudinal expansion of the valve shaft in the direction opposite to the pulleys.
  • the cover 16 which limits the movement of the seeger ring 15 has a double tip rubber lock 17.
  • the closing efficiency of the system is achieved as follows. All the closing systems, as for example, the piston rings 8 or the present valves, already described, base their closing efficiency on use of pressurized gases, labyrinths or pressurized conical seats, with good efficiency.
  • this invention bases its closing efficiency on the fact that the valve shaft 2 is inserted into the jacket 1 with a high precision, i.e., very close tolerance.
  • the annular space 31 between the jacket and the shaft will be filled by a film of lubricant.
  • a zone or annular slot (e.g. in the exhaust) indicated as 30, without lubrication and without friction because of the openings in the jacket 1 and shaft 2. Because the annular space or slot 30 is equivalent to that of a lubrication film, the gases tend, at the moment of compression, to escape through that annular slot establishing a turbulent flow of exhaust.
  • Figs. 2A and 3D show oil chambers 32 and the oil grooves 33 through which lubrication oil enters and exits.
  • the oil is cooled on the jacket 1 by the water chambers of the cylinder head cover 5.
  • the shape of the openings in the valve shaft and the projections thereof may be polygons, arcs, open or closed or combinations thereof.
  • the concentric jacket 1 may be part of the cylinder head cover 5 or a separate replaceable part. Further, all the openings from side to side, corresponding to intake and exhaust, may be on the same shaft.
  • the double effect distribution sequential valve shaft may be made of any kind of material adequate to maintain its functioning, such as metal, carbonite, ceramic, KEVLARTM or their alloys or combinations.
  • the double effect distribution sequential valve shaft may be hollow, with internal or external lubrication, or no lubrication at all. Further, the valve shaft may be of different diameters along its body, and may be located anywhere on or over the cylinder head or the engine block.
  • the valve shaft may be transverse or longitudinal (as referred to the engine axis), in one or multiple parts.
  • the jacket of the double effect distribution sequential valve shaft may be external and may be divided into two or more parts, longitudinally or transversely, in relation to the engine axis.
  • the rotation of the double effect distribution sequential valve shaft 2 may be transmitted in a direct or an indirect way by a chain toothed belt, gearing, cable, belt or self-moved by an independent motor, in mechanical, electrical, hydraulic or pneumatic ways.
  • the valve shaft 2 may have labyrinths, rings, pressure seals or wrinkled surfaces to assure a high closing efficiency, in one zone or multiple zones. Further, the valve shaft 2 may be simple or multiple, longitudinal, transverse or at any angle in space.
  • the valve shaft openings 22 may also communicate laterally across the external surface of the shaft or internally.
  • the seats of the valve shaft may be cylindrical, conical, spherical or any combination thereof.
  • the valve shaft 2 may have separated sealing elements longitudinally or transversely in relation to the engine axis.
  • the present invention has the capacity to dissipate heat.
  • the prior art valves with plates provide frontal resistance to the exit of gases impelled by the piston on its way to exhaust and are immobile during combustion. A border of the valve periphery opposes the exit of gases and quickly absorbs heat from the gases, which is very difficult to dissipate. Because the valve of the present invention, however, is rotary, the area of the valve shaft exposed to heat is constantly changing and can, thus, transmit the heat to the rest of the valve body and cool it by means of the lubricating oil and water chambers. Consequently, it is much more difficult for the valve to become heated to dangerous temperatures.
  • the present invention achieves superior smoothness of performance due to the fact that the impact of the valves on their (a) seats; (b) rockers; (c) valve plates; and (d) springs and the camshaft have been eliminated.
  • the present invention also achieves a longer useful life span as a function of the number of cycles since the speed, i.e., number of turns, has been reduced to 50% of the prior art camshaft.
  • the present invention has no mobile or fixed parts to penetrate into the combustion chamber of the cylinder.
  • the present invention achieves a better flow of gases of exhaust and intake.
  • the present invention has a perforation or opening which communicates directly with the combustion chamber, and the gases can flow at elevated speed and without obstacles.
  • the present invention due to the possibility of direct entrance and exit of gases and lesser braking, provides a more efficient expulsion and, therefore, a cleaner filling of the mixture "air-fuel". As a result, more complete combustion; greater energy generation; less contaminating residuals (CO2 and CO) and economy in fuel at the same power delivery.
  • the present invention also provides better performance for the turbo-feeder.
  • the greater speed of the exhaust gases transmitted to the intake of "air-fuel” provides better performance in the turbo-feeder moved by the exhaust gases. Having generated a high energy, the engine needs an efficient and quick dissipation of heat, which the sequential valve shaft helps to provide.
  • the present invention consumes less lubricating oil as a direct result of a lesser amount of parts to be lubricated.
  • the present invention allows the use of a cooling system having less capacity than those in the prior art due to a greater dissipation of heat in exhaust gases and the possibility of adding cooling flaps in the cylinder cover in direct contact with the chambers of cooling water.
  • the distribution system of the present invention is free of maintenance due to the fact that it does not need regulations of any type and the typical pounding of valves or fusion of the exhaust valves are eliminated.
  • the present invention allows for more economical and easier changes of spare parts. To change the distribution system it is only necessary to dismount three pulleys and the frontal caps for the change of both "shafts" without having to take away the cylinder head cover.
  • Net power delivery of the engine is increased by the present invention because the torsion moments of the camshaft necessary to wind the springs are eliminated as well as the friction of its seats, the rocker arms and the guides of the present valves.
  • the present invention costs less to manufacture than prior art systems. Cylinder head covers of greater symmetry and smaller size with greater variety of design may be used, since this invention allows varied positions of longitudinal mounting of new "shafts".

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP93105632A 1992-07-20 1993-04-06 Sequentieller Drehschieber mit doppelt wirkender Steuerung Withdrawn EP0579903A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AR322785 1992-07-20
AR32278592 1992-07-20

Publications (1)

Publication Number Publication Date
EP0579903A1 true EP0579903A1 (de) 1994-01-26

Family

ID=3478846

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93105632A Withdrawn EP0579903A1 (de) 1992-07-20 1993-04-06 Sequentieller Drehschieber mit doppelt wirkender Steuerung

Country Status (2)

Country Link
EP (1) EP0579903A1 (de)
JP (1) JPH0674009A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997035098A1 (es) * 1996-03-15 1997-09-25 Los Rios Sanz Jose Manuel De Culata perfeccionada con valvula rotativa de flujo completamente rectilineo
EP1074693A3 (de) * 1999-08-04 2001-12-19 Elmer Schmidt Hubkolbenvorrichtung
JP2002532724A (ja) * 1998-08-11 2002-10-02 スナップトラック・インコーポレーテッド 衛星位置決めシステム信号を得る方法および装置
ITPR20120060A1 (it) * 2012-10-03 2014-04-04 Marcello Marchi Metodo e sistema di alimentazione e scarico di motori a combustione interna e motore cosi' ottenuto

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003013847A (ja) * 2001-03-26 2003-01-15 Okinawa General Bureau Cabinet Office 水力作動コンプレッサ
JP7220032B2 (ja) * 2018-08-06 2023-02-09 富士登 松下 レシプロ式内燃機関の吸排気装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR741463A (de) * 1900-01-01
FR1053298A (fr) * 1952-04-02 1954-02-01 Distribution rotative pour moteur à combustion
EP0099873A2 (de) * 1982-07-19 1984-02-01 Josef V. Illichmann Zylindrischer Drehschieber mit Abdichtung für Kolbenmotoren
FR2547867A1 (fr) * 1983-06-24 1984-12-28 Collin Gilbert Culasse perfectionnee, notamment pour moteurs a explosion, et son application a un compresseur de fluides
GB2190139A (en) * 1986-05-03 1987-11-11 Howard Brian Leitch Rotary spool valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR741463A (de) * 1900-01-01
FR1053298A (fr) * 1952-04-02 1954-02-01 Distribution rotative pour moteur à combustion
EP0099873A2 (de) * 1982-07-19 1984-02-01 Josef V. Illichmann Zylindrischer Drehschieber mit Abdichtung für Kolbenmotoren
FR2547867A1 (fr) * 1983-06-24 1984-12-28 Collin Gilbert Culasse perfectionnee, notamment pour moteurs a explosion, et son application a un compresseur de fluides
GB2190139A (en) * 1986-05-03 1987-11-11 Howard Brian Leitch Rotary spool valve

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997035098A1 (es) * 1996-03-15 1997-09-25 Los Rios Sanz Jose Manuel De Culata perfeccionada con valvula rotativa de flujo completamente rectilineo
JP2002532724A (ja) * 1998-08-11 2002-10-02 スナップトラック・インコーポレーテッド 衛星位置決めシステム信号を得る方法および装置
JP2015155908A (ja) * 1998-08-11 2015-08-27 スナップトラック・インコーポレーテッド 衛星位置決めシステム信号を得る方法および装置
EP1074693A3 (de) * 1999-08-04 2001-12-19 Elmer Schmidt Hubkolbenvorrichtung
ITPR20120060A1 (it) * 2012-10-03 2014-04-04 Marcello Marchi Metodo e sistema di alimentazione e scarico di motori a combustione interna e motore cosi' ottenuto

Also Published As

Publication number Publication date
JPH0674009A (ja) 1994-03-15

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