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WO1988008483A1 - Moteur a combustion interne a piston rotatif - Google Patents

Moteur a combustion interne a piston rotatif Download PDF

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Publication number
WO1988008483A1
WO1988008483A1 PCT/EP1988/000363 EP8800363W WO8808483A1 WO 1988008483 A1 WO1988008483 A1 WO 1988008483A1 EP 8800363 W EP8800363 W EP 8800363W WO 8808483 A1 WO8808483 A1 WO 8808483A1
Authority
WO
WIPO (PCT)
Prior art keywords
internal combustion
combustion engine
cylinder
engine according
crankshaft
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.)
Ceased
Application number
PCT/EP1988/000363
Other languages
German (de)
English (en)
Inventor
Josef Gail
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 WO1988008483A1 publication Critical patent/WO1988008483A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F02B57/00—Internal-combustion aspects of rotary engines in which the combusted gases displace one or more reciprocating pistons
    • F02B57/08—Engines with star-shaped cylinder arrangements
    • 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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/068—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with an actuated or actuating element being at the inner ends of the cylinders
    • 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
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1824—Number of cylinders six

Definitions

  • the invention relates to a rotary piston internal combustion engine, with an engine block, with a crankshaft rotatably mounted in the engine block, with a cylinder rotor which is mounted coaxially to the crankshaft relative to the crankshaft and which has a plurality of cylinders offset with respect to one another, the cylinder axes of which intersect the axis of rotation perpendicularly, with reciprocating pistons working on the crankshaft in the cylinders and with mutually associated gas exchange openings in the engine block and in the cylinders.
  • a rotary piston internal combustion engine of this type is known from German Offenlegungsschrift 26 03 695.
  • the pistons are individually connected to the crankshaft via connecting rods.
  • the pistons over a comparatively large length must be guided in the cylinders and accordingly the diameter of the cylinder rotor is comparatively large.
  • the cylinder rotor thus has a high peripheral speed and accordingly the relative speed at which the sealing elements provided for sealing the gas exchange openings in the cylinder cups move relative to the engine block is high.
  • the cylinders are arranged in pairs offset by 180 degrees around the axis of rotation and the pistons of each pair are connected via a piston rod with a piston which is rotatably mounted on a crankshaft and which few common compensating crank of the same crank eccentricity are connected.
  • a cylinder rotor of this type has a comparatively small diameter, even when the internal combustion engine is performing well, and rotates at a reduced speed in relation to the speed of the crankshaft. In this way, a comparatively low peripheral speed is achieved in the area of the gas exchange openings and the stress on the sealing elements at the gas exchange openings is low. This applies in particular if the cylinder rotor is coupled to the crankshaft via a gear and rotates in the opposite direction to the direction of rotation of the crankshaft.
  • the cylinder rotor comprises a plurality of cylinder pairs, the cylinder axes of which lie in a common plane to simplify the gas flow.
  • Three pairs of cylinders have proven to be particularly suitable, since in this way particularly quiet, high-performance motors can be constructed.
  • the gear unit that couples the cylinder rotor to the crankshaft is expediently designed as a planetary gear unit, which further contributes to reducing the overall dimensions of the engine.
  • the gearbox reduces the speed of the cylinder rotor drew on the speed of the crankshaft with three pairs of cylinders, preferably in a ratio of 1: 3. This measure allows comparatively long gas change times, especially if in the
  • Engine block two sets of gas exchange channels arranged side by side in the direction of the axis of rotation are provided and each of these sets is assigned only one cylinder of each pair with its gas exchange opening.
  • the gas-exchange openings of the cylinders are seen in the cylinder roofs superiors 5 and are surrounded by ring seals which are resiliently pressed against the inner surface of the engine block.
  • the inner jacket of the engine block has the shape of a hollow spherical zone or spherical barrel, so that the circular ring seal just lies on the inner jacket of the engine block.
  • the ring seal preferably consists of a plurality of sealing rings arranged one inside the other, for example radially resilient, slotted sealing rings or a radially resilient spiral with a plurality of turns.
  • the sealing rings are in
  • a ring seal of this type can cause temperature-related material deformation without deterioration
  • the ring seal expediently sits in an annular groove which is separated from the gas exchange opening of the cylinder roof by a protective edge.
  • the protective edge protects the ring seal from direct contact with hot gases.
  • Particularly elastic ring seals consist of high-temperature-resistant plastic, to which ceramic material, for example in powder form, is added to increase the durability.
  • the elastic properties of such a ring seal are sufficient to be able to seal reliably against cylindrical, straight or conical outer surfaces.
  • the cylinder rotor has, on at least one of its sides, annular cooling fins coaxial with one another, between which complementary, annular cooling fins of the engine block projecting from the opposite side face of the engine block. Due to their enlarged surface, the cooling fins form a labyrinth that transfers the heat from the cylinder rotor to the engine block.
  • the labyrinth is expediently connected to the lubricating oil circuit of the engine in order to increase the cooling capacity.
  • the engine block can be air-cooled or water-cooled in the customary manner and can thus also take over the cooling of the oil flowing through the labyrinth.
  • a centrifugal disc suitably attached at the transition of the outer jacket of the cylinder rotor into the cooling fin labyrinth seals the cooling fin labyrinth to the gas exchange channels and conveys the oil flowing in the labyrinth seal into an essentially unpressurized peripheral chamber of the engine block, from which there is is returned to the engine oil circuit.
  • the oil flow flowing through the cooling fin labyrinth can also be used to lubricate the gearbox that couples the cylinder rotor to the crankshaft. This is especially true when a planetary gear integrated in the engine block is used.
  • FIG. 1 shows an axial cross section through a spark-ignition four-stroke internal combustion engine with six cylinders rotating in a cylinder rotor around the crankshaft;
  • FIG. 2 shows an axial longitudinal section through the internal combustion engine, seen along a line II-II in FIG. 1;
  • Figure 3 is a working diagram of the internal combustion engine;
  • FIG. 4 shows a partial sectional view through an annular seal that can be used in the internal combustion engine of FIGS. 1 and 2;
  • FIG. 5 shows a detailed view of the ring seal from FIG. 4 corresponding to a circle V in FIG. 4;
  • Figure 6 is a plan view of the ring seal of Figure 4;
  • FIG. 7 shows a detailed view similar to FIG. 5 through a variant of a ring seal;
  • FIG. 8 shows a plan view of the ring seal according to FIG. 7 and FIG. 9 shows a detailed view through a further variant of the ring seal similar to FIG. 5.
  • the spark-ignited four-stroke internal combustion engine shown in FIGS. 1 and 2 comprises an engine block 1, which encloses a cylinder rotor 7, which is rotatably mounted in a ball bearing 3 about an axis of rotation 5 on the engine block 1.
  • Six of the rotary cylinder 7 has at each equal angular distances of 60 degrees about the axis of rotation 5 mutually angularly offset cylinder 9, the Cylinde 'in hawking a common plane, indicated at 11 in FIG. 2, perpendicular to the axis of rotation 5 and intersect the axis of rotation 5 vertically at a common intersection.
  • pistons 13 are arranged so as to be displaceable in a sealed manner, of which the pistons opposite each other and offset by 180 degrees are connected to one another in pairs by a common piston rod 15.
  • the piston rods 15 have a bearing opening 17 in the center between the pistons 13, in each of which an eccentric disc 19 is rotatably mounted parallel to the axis of rotation 5 by means of a needle bearing 21 '.
  • the eccentric disc 19 is in turn with a
  • Eccentricity 23 rotatably mounted axially parallel to the axis of rotation 5 on a crank 25 of a crankshaft 27 by means of a needle bearing 29.
  • the crankshaft 27 is in turn supported in the engine block 1 via bearings 31, 33 rotatable about the axis of rotation 5.
  • the offset or crank eccentricity 35 of the crankshaft 27 is selected equal to the eccentricity 23 of the eccentric disks 23.
  • the eccentric disks 23 thus form compensating cranks, which ensure that the pistons 13 of each pair can move along the cylinder axis that intersects the "axis of rotation 5" when the cylinder rotor 7 rotates despite the piston rod 15 being firmly connected to the piston 13 Kraf machine thus requires no connecting rods each movably mounted on the crankshaft or the piston so that the axial and radial dimensions of the cylinder rotor 7 are relatively small despite the comparatively high cylinders.
  • the piston rods 15 engage symmetrically to the plane 11 in order to avoid tilting moments of the crankshaft 27, which would load the bearings 31, 33. While the piston rod 15 of a pair of pistons lies in the plane 11, the piston rods 15 of the other two piston pairs are forked symmetrically to the plane 11 and each take a half 41 and 43 in the bearing openings of their cranked fork parts 37 and 39, respectively of the eccentric disks also arranged symmetrically to plane 11.
  • the halves 41 are aligned at the same angle to one another, as are the halves 43.
  • the eccentric disks assigned to the 3 piston pairs are offset by 120 degrees with respect to the axis of the crank 25 shown at 45, as is indicated by the axes of rotation of the bearings indicated at 47 in FIG 21 is indicated.
  • the eccentric disks 19 and 41, 43 of the three piston pairs are connected to one another, which can be divided into planes parallel to plane 11 in order to be able to slide the bearing openings of the piston rods 15 onto the eccentric disks.
  • the bearings of the piston rods or their fork parts can be divided in the center, as is common with connecting rod bearings.
  • asymmetrically cranked piston rods can also be provided, it then being sufficient to make the eccentric disk unit axially divisible in plane 11.
  • the cylinder rotor is coupled to the crankshaft via a planetary gear 49 reducing its speed in a ratio of 1: 3.
  • the planetary gear 49 ensures that the cylinder rotor 7 and the crankshaft 27 rotate in the opposite direction of rotation, as indicated by directional arrows 51, 53 in FIG. 1.
  • the planetary gear 49 has a planet gear carrier 52 which is fixedly connected to the engine block 1 and on which the bearing 33 on the one hand, the crankshaft 27 and, on the other hand, a plurality of bearing journals 54 planet gears 55, which are offset with respect to one another in the circumferential direction.
  • the planet gears 55 mesh on the one hand with a sun gear 57 fixedly mounted on the crankshaft 27 and on the other hand with a ring gear 59 fixedly arranged on the cylindrical rotor 7.
  • the diameters of the gears 55, 57 and 59 are chosen so that the desired one direction of rotation reversing reduction of 1: 3 results.
  • the crankshaft 27 emerges axially on both sides from the engine block 1 and is usually sealed at both points by Simmer rings or the like.
  • flywheels 61, 63 are fastened on the crankshaft 27 outside the engine block, which at the same time carry balance weights 65, 67 for balancing an imbalance caused by the pistons and the crankshaft.
  • the flywheel 61 also carries a ring gear 69 for a starter (not shown in more detail) and forms a contact surface for the clutch disc of a motor vehicle friction clutch for use in a motor vehicle.
  • the other flywheel 63 has magnets 71 distributed around its circumference, to which a magnet switch 73 controlling the ignition responds.
  • At least one gas exchange opening 75 is provided in the roof of each cylinder 9 forming the outer jacket of the cylinder rotor 7, which has inlet channels 77 and outlet channels 79 that are open to the cylinder rotor 7 and offset with respect to one another on the inner circumference of the engine block 1 in the course of the rotation of the cylinder rotor 7 cooperate.
  • the gas exchange openings 75 are diametrically opposed cylinders 9 on top of one another opposite sides of the plane 11 arranged, as best shown in Figure 2. Accordingly, two sets of inlet ducts 77 and outlet ducts 79 are provided in the engine block 1 on opposite sides of the plane 11, of which a first sentence in FIG. 1 is shown with full lines and the second sentence with dashed lines. To distinguish them, the channels of the second set are designated 77 'and 79 ". Each of the two sets here comprises two inlet channels diametrically opposite one another with respect to the axis of rotation 5 and two outlet channels diametrically opposite one another. Furthermore, one of the Gas exchange openings associated with channel sets are provided with two diametrically opposed spark plugs 81 and 81 'which ignite the compressed fuel-air mixture through the gas exchange opening 75.
  • the internal combustion engine operates in a four-stroke cycle, which is carried out for each of the cylinders 9 during a 180 degree rotation of the cylinder rotor 7. Accordingly, a rotation angle of the cylinder rotor 7 of 45 degrees is available for the intake stroke, the compression stroke, the work stroke and the exhaust stroke. Accordingly, the spark plugs, exhaust ducts and inlet ducts also follow one another in multiples of 45 degrees, the two sets of ducts again being angularly offset from one another by 45 degrees.
  • FIG. 3 shows a timing diagram of the internal combustion engine, in which the cylinders are numbered in the direction of rotation 51 of the cylinder rotor 7 and the gas channels drawn with full lines in FIG. 1 are labeled A and the gas channels drawn with dashed lines are labeled B.
  • the 45-degree sectors of engine block 1 are shown in FIG. 1 and numbered using Roman numerals.
  • the angular origin is arbitrarily placed in the angular position of the first cylinder shown in FIG. 1. In this position, the piston of the first cylinder is in its top dead center position, in which the fuel-air mixture is ignited. According to the diagram of Fig.
  • the gas exchange openings 75 in the cylinder roofs are each radially resiliently sealed by ring seals 83 against the jacket of the engine block 1 surrounding the cylinder roofs.
  • the ring seal 83 encloses the gas exchange opening 75 and is seated in an annular groove 85 which is open to the inner casing of the engine block 1 and is shown in FIG. 4 for a preferred embodiment of the internal combustion engine.
  • the inner jacket of the engine block 1 shown at 87 has the shape of a spherical zone or spherical barrel, and the ring seal 83 has. Circular shape. It thus lies on the inner jacket 87 in one plane, which improves the sealing.
  • the ring seal 83 consists of two separate, radially arranged sealing rings 89, which are supported by a corrugated spring 91 also located in the ring groove 85 via an annular pressure disk 93 against the inner jacket 87 be pressed.
  • the sealing rings 89 have mutually rotated slots 95 and are radially resiliently inserted into the annular groove 85, so that they are pressed against each other and against the radially outer wall 97 of the annular groove 85 due to their own radial prestress.
  • At least one channel 99 led through the cylinder roof into the annular groove 85 exposes the surfaces of the ring seal 83 facing away from the casing 87 and the outer wall 97 to the gas pressure of the cylinder, as a result of which the contact pressure against these surfaces and thus the sealing effect is increased.
  • the annular groove 85 runs at an axial distance from the gas exchange opening 75, so that a protective edge 101 remains radially inside the sealing rings 89 and protects the sealing rings 89 from direct contact with the hot exhaust gases flowing through the gas exchange opening 75,
  • FIG. 4 shows details of the gas exchange ducts of the engine block 1 arranged on opposite sides of the plane 11, here for example the outlet duct 79 and the inlet duct 77 '.
  • the channels are divided by at least one web 103 or 105 running in the circumferential direction, on which the ring seal 83 can be supported in order to reduce the deformation caused by its resilient contact pressure.
  • ring seal 83 By dividing the ring seal 83 into a plurality of sealing rings 89 arranged one inside the other, a more elastic seal is achieved which can better adapt to a temperature-related material deformation.
  • FIG. 7 and 8 show a variant of such a Ab ⁇ seal, which only differs from the ring seal of Figuren4 to 6, that the annular seal 83 is formed a l s a multiple windings 107 spring-elastic spiral.
  • Identical parts are here with the reference numerals of FIG. 4 to 6, reference being made to the description of these figures for explanation.
  • the turns 107 of the spiral are radially resilient against each other and on the radially outer boundary wall 93 of the circumferential groove 85 and are in turn pressed by a corrugated spring 91 via a thrust washer 93 against the spherical zone-shaped inner jacket 87 of the engine block 1.
  • FIG. 9 shows a further variant, in which the ring seal 83 is constructed as an elastic plastic ring 109 made of a high-temperature-resistant plastic which contains powdered ceramic material in order to improve its wear resistance.
  • the plastic ring 109 has a plurality of sealing lips 111 arranged radially one inside the other and, together with the wave spring 91, is in turn seated in an annular groove 85 of the cylinder roof which surrounds the gas exchange opening 75. Parts having the same effect are again identified here with the reference numbers of FIGS. 4 to 5, to the description of which reference is made.
  • Figures 1 and 2 also show details of the cooling system of the internal combustion engine.
  • the cooling fins 113, 115 form axially on both sides of the cylinder rotor 7 labyrinths, which facilitate the heat transfer from the cylinder rotor 7 to the engine block 1 due to their enlarged surface.
  • the engine block 1 Adjacent to the cooling fins 115, the engine block 1 contains cooling water channels 117, which are connected to a cooling water circuit of the engine and dissipate the heat from the engine block 1.
  • the jacket of the engine block 1 also contains a plurality of axial cooling water channels 119, which improve the cooling effect.
  • An oil pump 120 shown at 12Q and driven by the crankshaft 27 conveys the lubricating oil via oil channels 121 into the area of the crankshaft bearings, the planetary gear 49 and into the area of the radially inner circumference of the labyrinths. Due to the centrifugal action of the rotating cylinder rotor 7, the lubricating oil is conveyed via the labyrinths to unpressurized collecting channels 123 of the engine block 1, which limit the labyrinths radially outward in the region of the outer circumference of the cylinder rotor 7.
  • part of the circumferential wall of the engine block 1, as indicated at 127 (FIG. 1), is designed as a removable cover part which closes an opening through which the ring seals 83 can be accessed - are on loan. This measure simplifies the maintenance of the internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Un moteur à combustion interne comprend un bloc-cylindres (1), un vilebrequin (27) rotativement monté dans le bloc-cylindres (1) et un rotor à cylindres (7) coaxial et rotatif par rapport au vilebrequin (27) dans le bloc-cylindres (1). Le rotor à cylindres (7) comprend plusieurs cylindres (9) angulairement décalés les uns par rapport aux autres et dont les axes interceptent orthogonalement l'axe de rotation (5). Les cylindres (9) sont décalés, par paires, de 180° autour de l'axe de rotation (5) et contiennent des pistons (9) reliés par paires au moyen d'une tige de piston (15) à une manivelle compensatrice (19) commune à la paire de pistons et de même excentricité rotativement montée sur une manivelle (25) du vilebrequin (27). Le rotor à cylindres (7) est couplé par un engrenage réducteur au vilebrequin (27) et est entraîné en sens opposé à ce dernier. De préférence, trois paires de pistons sont prévues. Ce moteur à combustion interne de dimensions relativement réduites a un rendement élevé et permet de régler aisément l'échange de gaz.
PCT/EP1988/000363 1987-04-30 1988-04-29 Moteur a combustion interne a piston rotatif Ceased WO1988008483A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3714566 1987-04-30
DEP3714566.5 1987-04-30

Publications (1)

Publication Number Publication Date
WO1988008483A1 true WO1988008483A1 (fr) 1988-11-03

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Family Applications (1)

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PCT/EP1988/000363 Ceased WO1988008483A1 (fr) 1987-04-30 1988-04-29 Moteur a combustion interne a piston rotatif

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WO (1) WO1988008483A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990015918A1 (fr) * 1989-06-12 1990-12-27 Josef Gail Machine a piston
WO1994005902A1 (fr) * 1992-08-28 1994-03-17 Josef Gail Moteur a cylindres rotatifs
WO1998057036A1 (fr) * 1997-06-12 1998-12-17 Clifford Colin A Moteur a pistons radiaux et a cylindres rotatifs
EP0918137A3 (fr) * 1992-03-16 1999-06-02 CLIFFORD, Colin, A. Machine rotative à combustion interne
WO2000019071A1 (fr) * 1998-09-28 2000-04-06 Jorma Lillbacka Moteur sans soupapes
DE102005033448A1 (de) * 2005-07-18 2007-01-25 Josef Gail Druckgas-Zylinderläufermotor
ITVI20100199A1 (it) * 2010-07-21 2012-01-22 Maurizio Morbin Motore a combustione interna
WO2012089621A1 (fr) * 2010-12-29 2012-07-05 Becker Otto Hermann Moteur à combustion interne pourvu de cylindres rotatifs

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB677101A (en) * 1949-06-18 1952-08-06 Eduard Woydt Radial-cylinder pumps and motors
US3167058A (en) * 1961-07-04 1965-01-26 Czike Sandor Rotary four-cycle internal combustion engine
DE2365050A1 (de) * 1973-01-10 1974-07-18 Cameron Johnson Alan Umlaufkolbenmaschine, insbesondere verbrennungskraftmaschine
US3946706A (en) * 1973-06-14 1976-03-30 Yves Pailler Rotary machines comprising four cylinders in a star

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB677101A (en) * 1949-06-18 1952-08-06 Eduard Woydt Radial-cylinder pumps and motors
US3167058A (en) * 1961-07-04 1965-01-26 Czike Sandor Rotary four-cycle internal combustion engine
DE2365050A1 (de) * 1973-01-10 1974-07-18 Cameron Johnson Alan Umlaufkolbenmaschine, insbesondere verbrennungskraftmaschine
US3946706A (en) * 1973-06-14 1976-03-30 Yves Pailler Rotary machines comprising four cylinders in a star

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990015918A1 (fr) * 1989-06-12 1990-12-27 Josef Gail Machine a piston
US5375564A (en) * 1989-06-12 1994-12-27 Gail; Josef Rotating cylinder internal combustion engine
EP0918137A3 (fr) * 1992-03-16 1999-06-02 CLIFFORD, Colin, A. Machine rotative à combustion interne
WO1994005902A1 (fr) * 1992-08-28 1994-03-17 Josef Gail Moteur a cylindres rotatifs
US5720241A (en) * 1992-08-28 1998-02-24 Gail; Josef Rotary cylinder engine
WO1998057036A1 (fr) * 1997-06-12 1998-12-17 Clifford Colin A Moteur a pistons radiaux et a cylindres rotatifs
WO2000019071A1 (fr) * 1998-09-28 2000-04-06 Jorma Lillbacka Moteur sans soupapes
US6240884B1 (en) 1998-09-28 2001-06-05 Lillbacka Jetair Oy Valveless rotating cylinder internal combustion engine
DE102005033448A1 (de) * 2005-07-18 2007-01-25 Josef Gail Druckgas-Zylinderläufermotor
ITVI20100199A1 (it) * 2010-07-21 2012-01-22 Maurizio Morbin Motore a combustione interna
WO2012089621A1 (fr) * 2010-12-29 2012-07-05 Becker Otto Hermann Moteur à combustion interne pourvu de cylindres rotatifs

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