EP0877154A2 - Moteur à combustion interne avec un système de contrÔle pour une soupape rotative - Google Patents

Moteur à combustion interne avec un système de contrÔle pour une soupape rotative Download PDF

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Publication number
EP0877154A2
EP0877154A2 EP98108051A EP98108051A EP0877154A2 EP 0877154 A2 EP0877154 A2 EP 0877154A2 EP 98108051 A EP98108051 A EP 98108051A EP 98108051 A EP98108051 A EP 98108051A EP 0877154 A2 EP0877154 A2 EP 0877154A2
Authority
EP
European Patent Office
Prior art keywords
sleeve
head
ceiling
engine according
ignition
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Withdrawn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
EP98108051A
Other languages
German (de)
English (en)
Other versions
EP0877154A3 (fr
Inventor
Giorgio Enrico Falck
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 EP0877154A2 publication Critical patent/EP0877154A2/fr
Publication of EP0877154A3 publication Critical patent/EP0877154A3/fr
Withdrawn legal-status Critical Current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
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • F01B15/007—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 having spinning cylinders, i.e. the cylinders rotating about their longitudinal axis
    • 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
    • F01L7/028—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves having the rotational axis coaxial with the cylinder axis and the valve surface not surrounding piston or cylinder
    • 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
    • F01L7/04—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
    • 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
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • 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
    • F02B75/34—Ultra-small engines, e.g. for driving models
    • 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

Definitions

  • the present invention relates to an endothermic alternative engine of the type utilising a timing system constituted by a jacket (or sleeve) that rotates co-axially with the cylinder and is provided with apertures or holes suitable to be brought in correspondence with channels obtained in the cylinder head to allow the thermal (otto or diesel) cycle to take place.
  • a timing system constituted by a jacket (or sleeve) that rotates co-axially with the cylinder and is provided with apertures or holes suitable to be brought in correspondence with channels obtained in the cylinder head to allow the thermal (otto or diesel) cycle to take place.
  • Object of this invention is to provide an endothermic engine utilising an improved rotary sleeve timing system, such as to solve the aforementioned problems, and to overcome the related drawbacks, and such as to be utilisable in a reliable manner in both otto and diesel cycle engines, even with very high compression ratios, with no danger of compression losses and oil and/or exhaust gas blow-by between the rotary sleeve and the cylinder internal surface.
  • said axial translation is suitable to distribute throughout the whole surface the lubricating fluid, with the well-known squish effect.
  • Both the external surface of said ceiling and the internal surface of said head have preferably a flat shape.
  • the external surface of said ceiling has a male cone or truncated-cone shape, while the internal surface of said head has a female cone or truncated-cone shape, or the external surface of said ceiling has a hemispheric convex shape while the internal surface of said head has a hemispheric concave shape.
  • said ignition means are constituted by at least a sparking plug provided with the usual devices for the synchronisation of the spark.
  • Said sparking plug is mounted integrally with the head in said hole located in the centre of the head, and provides to igniting the mixture in the explosion stage, through a corresponding central hole obtained in said ceiling.
  • said sparking plug is fixed-mounted in said central hole obtained in said ceiling through the central hole obtained in the head, and rotates integrally with said sleeve, receiving current by means of sliding contacts or a spark or the like.
  • the rotary sleeve rotates with a number of rotations equal to half the number of rotation of the driving shaft, and the ratio of the teeth of the bevel gear pair is 1:2.
  • multiple ratios are realisable, such as 1:4, 1:8, etc.
  • Lubrication may be realised either using a mixture constituted by oil and gasoline, or oil forced through a positive-displacement pump or the like through a network of channels associated to suitably positioned rabbles, oriented, in particular on the ceiling external surface, based on theoretical evaluations and/or indications obtained from experimental tests, or by effect of lubrication obtained directly from gasoline and the use of known materials with a very low friction coefficient or even self-lubricating.
  • said thrust-bearing and centering element is so positioned as to generate a clearance for the sleeve along its longitudinal axis, comprised between 0,01 and 0,10 mm.
  • Said thrust-bearing element for said sleeve is constituted, according to a first embodiment, by a ball bearing (or a roller bearing) which performs also a function of radial centering (with oblique races according to an ideal angle).
  • This ball bearing is preferably positioned in the sleeve lower part and is in an ideal situation as the low part is cold and extremely well oiled by the oil-beating in the sump.
  • said thrust-bearing element is constituted by an annular flange radially protruding from the top of said sleeve ceiling and forming an integral whole with the surface of said ceiling, suitable to slidingly adhere to the head internal surface, increasing in this way the tightness during the compression and explosion stages, and to stop the axial translation towards the lower part of the sleeve, striking against a special step provided in the cylinder body.
  • said hole obtained in the head and said ignition means inserted in said hole have an off-centre position with respect to the centre of the head and with respect to the centre of the sleeve ceiling.
  • the sleeve ceiling is provided with one only aperture or window which is sequentially positioned in correspondence of the feed duct, the hole bearing said off-centre ignition means and the exhaust duct obtained in the head and through which feeding, ignition and exhaust are realised.
  • This embodiment allows to employ ignition means constituted by a pigtail which is kept always incandescent.
  • the pigtail is insulated from the explosion chamber by the sleeve ceiling and gets in touch with the mixture only during the ignition stage, when the window obtained in the sleeve places itself in correspondence of the ignition means. In this ways the advantage is obtained of not having to use the expensive and complex device for the spark timing.
  • lubrication feeding takes place through suitable ducts in the centre of the head, in correspondence of the centre of the sleeve ceiling, realising in this way a better and more uniform distribution of the same lubricant.
  • said ignition means are constituted by a high turbulence precombustion chamber, such as a Comet/Riccardo precombustion chamber or the like, into which gas oil is introduced and atomised during the engine passive cycle, said atomised gas oil being then mixed in the same precombustion chamber with the highly compressed air coming from the sleeve through one only aperture or window obtained in the sleeve ceiling when said aperture places itself in communication with the inlet hole of said precombustion chamber obtained in said head, causing in this way the ignition of the formed mixture and realising a diesel cycle without injector.
  • a high turbulence precombustion chamber such as a Comet/Riccardo precombustion chamber or the like
  • one (or more) apertures are obtained in the sleeve "ceiling", while two (or more) apertures are obtained in the cylinder head, one being an exhaust aperture and another one being an intake aperture.
  • Apertures are angle positioned, so as to coincide at the time appropriate to open and close the same, in coincidence with the up and down movement of the piston, creating the classical stages of the four-stroke-cycle (either diesel or otto): intake, compression, explosion-expansion, exhaust.
  • the sleeve is connected with the engine axle by a gear system whose teeth number ratio is two to one (or multiples of two).
  • the simplest system is constituted by one only bevel gear pair, but many other connections may be realised. What matters is that the sleeve rotates at a one to two speed (or multiples of two) with respect to the engine axle. It is worth stressing the extreme mechanical simplicity and therefore the very low cost of realisation of the engine according to the present invention, which renders it particularly suitable for low-powered cars, wherein the mechanical complexity and the high cost of the valve timing system have prevented the diffusion in favour of the two-stroke-cycle engine, accepting the defects of the same, namely high acoustic and air pollution and the necessity of mixing fuel with oil.
  • a classic example of application is represented by engines for motorscooter 50, small auxiliary engines, etc.
  • Another advantage of the invention is the reduced height, only a little more than the height of a two-stroke-cycle engine.
  • Another advantage is due to the fact that in the engine according to the present invention, the rotation of the sleeve and therefore of the gas mixture-containing chamber facilitates and spurs an intimate mixing of the mixture ingredients, which allows to obtain a maximum yield and a low environment pollution.
  • a further advantage is represented by the absence of an alternate, spring-back movement, as is the case for conventional valves, which limit the rotation speed, on penalty of a surging of the same.
  • An engine according to the invention can rotate at 15,000/20,000 rpm, as proved by the tested prototypes. It should be taken into account that the sleeve can freely move upward, which allows to strongly press the sleeve "ceiling" against the head during the explosion, and to ensure a perfect gas-tightness.
  • This movement has also the double aim of facilitating lubrication, due to the well-known "squish” effect (i.e., lubrication by intense compression), which shows excellent friction coefficients.
  • This lubrication may be obtained with oil or the same fuel (for instance, gas oil in diesel engines).
  • the sparking plug is kept separated from the sleeve "ceiling" by the combustion chamber, communicating with the same only in a specific stage of the cycle, namely at the time of ignition/explosion.
  • the engine according to the present invention comprises two distinct “spaces” or “zones” or “volumes”, of which the first one is fixed and comprises ignition means, while the volume of the second one varies according to the piston position, said spaces being separate from one another during the passive stage of the cycle (exhaust, intake, compression start), while being in communication with one another during the active stage of the cycle (compression end, explosion, expansion).
  • the engine according to the invention comprises a cylinder 1 in whose inside the rotary sleeve 2, bell-like top-closed by a plate or ceiling 3, is rotary-mounted, moved by crankshaft 4 through a bevel gear pair 5.
  • the ratio of the teeth of the bevel gear pair is 1:2, to cause the sleeve to rotate with a number of rotations equal to half the number of rotations of the crankshaft.
  • the external surface of ceiling 3 which is flat in the embodiment shown in the figures, may be cone or truncated cone-shaped, or hemispheric or it may have any other shape suitable to allow it to mating-rotate against the corresponding lower surface of head 7.
  • An alternative piston 6 is mounted in the inside of sleeve 2; ceiling 3 of sleeve 2 is provided with a central hole 9 which is gone through by the end of sparking plug 10 for the ignition of the mixture, and with a window 8 that, during the rotation of the sleeve, places itself sequentially in correspondence of windows 11 and 12 provided in head 7 and in connection with intake duct 13 respectively exhaust duct 14 obtained in the head.
  • the size and the positions of the windows may be so selected as to achieve, for a minimum time fraction during the cycle stages, a connection between the feed duct and the exhaust duct, ensuring thereby the washing of the cylinder.
  • windows 11 and 12 are placed at 90° to each other.
  • head 7 there is centrally obtained hole 15, in whose inside the sparking plug 10 is fixedly housed.
  • the edge of hole 9 obtained in ceiling 3 of rotary sleeve 2 freely rotates around the end of the sparking plug.
  • the sparking plug 10 is integrally mounted with ceiling 3 of rotary sleeve 2 and rotates with the latter in the inside of hole 15 obtained in the head.
  • the sparking plug is rotary, it is possible to regulate the passage of the current to the sparking plug by providing the sleeve-sparking plug unit with a radial protrusion connected to the electrode of the sparking plug, causing such electrode, during the rotation of the sleeve, to come to sliding with a like non-rotary protrusion, connected with the high voltage circuit, and preferably housed on the cylinder.
  • sleeve 2 is mounted on thrust bearings 16 interposed between the cylinder and the sleeve, in such a number and position as to contrast radial stresses, so as to prevent sleeve from any slap, while allowing an axial translation movement (flotation) in the order of some tenths of millimetre: in this way, the thrust due to the explosion pushes the external surface of ceiling 3 against the internal surface of head 7, ensuring thereby a perfect sliding tightness. It has been observed that this is realised by mounting thrust bearing 16 in such a way as to ensure a clearance 17 in the order of 0.01-0.10 mm between the ceiling and the head.
  • the rotary sleeve timing system may be so structured as to be applicable to internal combustion engines of both the two- and the four-stroke-cycle types by changing the rotation speed of the sleeve according to the rotation speed of the driving shaft, i.e. by selecting the speed of the sleeve based on the stroke number of the engine, the number and position of the holes obtainable in the sleeve ceiling and the number and position of intake and exhaust ducts obtainable in the cylinder head.
  • ceiling 23 of rotary sleeve 22 is provided with the thrust-bearing element constituted by the annular flange 24 which prevents the axial translation toward the lower part of sleeve 22, striking against the step 25 obtained in cylinder 1.
  • the ignition means constituted by sparking plug 10 is off-centre with respect to the ceiling of sleeve 23 and is inserted in hole 26 obtained in head 27.
  • head 27 there are also obtained windows 11 and 12, in connection with intake duct 13 respectively exhaust duct 14.
  • window 28 In the ceiling of sleeve 23 there is instead obtained one only window 28 which places itself sequentially in correspondence of intake duct 13, hole 26 housing the ignition sparking plug 10 and exhaust duct 14.
  • FIG. 7 shows a further embodiment wherein the ignition means are off-centre with respect to the centre of the ceiling of sleeve 23 and the centre of head 32, and are constituted by a high-turbulence precombustion chamber 30 in which gas oil is continuously introduced through duct 31.
  • precombustion chamber 30 gas oil is atomised mixed with the highly compressed air coming from the sleeve through the one only window 28 obtained precisely in the ceiling of the sleeve when said window stands in correspondence of exhaust duct 33 of precombustion chamber 30 at the end of the compression.
  • An ignition incandescent net may be included in the precombustion chamber.

Landscapes

  • 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)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP98108051A 1997-05-07 1998-05-04 Moteur à combustion interne avec un système de contrÔle pour une soupape rotative Withdrawn EP0877154A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT97MI001056A IT1292223B1 (it) 1997-05-07 1997-05-07 Motore a combustione interna provvisto di distribuzione a fodero rotante
ITMI971056 1997-05-07

Publications (2)

Publication Number Publication Date
EP0877154A2 true EP0877154A2 (fr) 1998-11-11
EP0877154A3 EP0877154A3 (fr) 1999-05-19

Family

ID=11377083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98108051A Withdrawn EP0877154A3 (fr) 1997-05-07 1998-05-04 Moteur à combustion interne avec un système de contrÔle pour une soupape rotative

Country Status (2)

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EP (1) EP0877154A3 (fr)
IT (1) IT1292223B1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004029431A1 (fr) * 2002-09-28 2004-04-08 Dr. Schrick Gmbh Dispositif de couplage pour relier le vilebrequin d'un moteur a combustion interne a un generateur electrique
EP1500803A1 (fr) * 2003-07-22 2005-01-26 Cristian Dalla Riva Moteur à combustion carburé par une mixture d'essence notamment pour l'application dans un outil motorisé porté par un utilisateur

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1260757A (en) * 1968-03-09 1972-01-19 Enrico Lamperti A rotary valve member seated within the cylinder head for endothermic two-or four-stroke cycle or diesel engines
DE2714351A1 (de) * 1977-03-31 1978-10-05 Dylla Norbert Drehschiebergesteuerter viertakt- verbrennungsmotor
DE2910822C2 (de) * 1979-03-20 1982-12-09 Norbert 8000 München Dylla Luftgekühlter, drehschiebergesteuerter Viertakt-Verbrennungsmotor
FR2600718B1 (fr) * 1986-06-27 1990-06-29 Peugeot Canal de transfert pour prechambre de moteur diesel et son application a un moteur automobile
GB8708037D0 (en) * 1987-04-03 1987-05-07 Jaguar Cars Rotary valves
IT1264947B1 (it) * 1993-07-19 1996-10-17 Fin Gef Srl Motore a combustione interna a quattro tempi, di elevata semplicita' meccanica

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004029431A1 (fr) * 2002-09-28 2004-04-08 Dr. Schrick Gmbh Dispositif de couplage pour relier le vilebrequin d'un moteur a combustion interne a un generateur electrique
EP1500803A1 (fr) * 2003-07-22 2005-01-26 Cristian Dalla Riva Moteur à combustion carburé par une mixture d'essence notamment pour l'application dans un outil motorisé porté par un utilisateur

Also Published As

Publication number Publication date
ITMI971056A0 (fr) 1997-05-07
EP0877154A3 (fr) 1999-05-19
ITMI971056A1 (it) 1998-11-07
IT1292223B1 (it) 1999-01-29

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