EP1658417B1 - Moteur polycylindre a barillet - Google Patents

Moteur polycylindre a barillet Download PDF

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Publication number
EP1658417B1
EP1658417B1 EP04766214A EP04766214A EP1658417B1 EP 1658417 B1 EP1658417 B1 EP 1658417B1 EP 04766214 A EP04766214 A EP 04766214A EP 04766214 A EP04766214 A EP 04766214A EP 1658417 B1 EP1658417 B1 EP 1658417B1
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Prior art keywords
engine
cylinders
transfer
cylinder
admission
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German (de)
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EP1658417A1 (fr
Inventor
Giulio Martinozzi
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Voglaire Helene
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Voglaire Helene
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    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/101—Control of working-fluid admission or discharge peculiar thereto for machines with stationary 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B75/021—Engines characterised by their cycles, e.g. six-stroke having six or more strokes per cycle
    • 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
    • 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
    • F02B2075/1828—Number of cylinders seven

Definitions

  • the invention relates to a multicylinder engine with the cylinders disposed in a circle and parallel to the centre line C/L, to assume the so-called barrel-type configuration, wherein the pistons are mounted and supported by a wobbling mechanism.
  • Said mechanism is conceived to reversibly convert the reciprocating movement of the multiplicity of pistons (disposed in a circular row), into the rotation of a crankshaft around the C/L, and for reversibly convert at the same time, the forces insisting on said pistons, into a corresponding couple insisting on the same central crankshaft.
  • the wobbling unit and abbreviated in WU, is essentially determined by two types of constraints:
  • said angular constraint can alternatively, but less efficiently, be obtained by means of a spherical coupling and a cardan joint between the wobbling element and the casing of the mechanism, as illustrated by the known mechanisms of D1 and D 5.
  • Another object of the invention is to select the value of certain geometrical parameters of the wobbling unity, in particular the tilt angle ⁇ ⁇ 10°, such as to minimise the lateral displacement of the piston, and optimise the space availability for the cylinders in the circular row, in relation to the piston's stroke.
  • Another object is to minimise the friction forces around the piston. This is achieved by fixedly mounting the pistons on the wobbling unit so as to form a single solid piston unit
  • Another object is to alleviate the torsional stresses on the crankshaft and the cyclic forces on the crankshaft bearings (against the wobble unit and against the casing) so as to allow an overall lighter structure and the lower level of vibrations.
  • This is achieved by providing a further couple of bevel gears having the vertex of their primitive cones coinciding with the centre point O of the mechanism.
  • Another object is to shape the internal rotating ducts of the distributor ring so as to generate a pre-compression of the operating fluid at the entrance of the cylinders. This can be achieved by giving the walls of the ducts the shape of centrifugal turbine blade.
  • Figures 1 to 5 show a first embodiment of the claimed internal combustion engine whose general layout is formed by a plurality of combustion chambers 11 or cylinders assembled together in a circular row over an essentially circular casing 12 with their axis generally parallel to the centre line (C/L) of the casing. i.e. of the engine.
  • a corresponding plurality of pistons 13 are able to move up and down in a sealed contact, so as to generate a displacement volume, the pistons being supported and connected, through their stems, to the peripheral edge 14 of a wobbling unit 15 (WU), which is in turn rotatably supported, through bearings (not shown), by a Z-shaped crankshaft 16.
  • This crankshaft is mounted on the casing, through other bearings (not shown), in order to rotate around said C/L.
  • the present engine comprises an uneven number of cylinders: this is a necessary condition in order to allow the synchronisation with a rotary distributor 23 which governs the admission and exhaust of the operative fluid into and from each combustion chamber, as later on further explained.
  • Said rotary distributor is formed by a solid ring composed by a number S of identical circular sectors, see figure 3 , each sectors comprising one admission opening (Aa, ..., Ea) and one exhaust opening (Ae, ..., Ee), as well as relevant ducts 24, 25 leading to corresponding admission and exhaust external openings which communicate with an admission collector and an exhaust collector respectively.
  • Said ring is rotatably mounted around and perpendicular to the C/L of the engine, directly over the heads of the cylinders in a sliding contact therewith so that the each of said openings is progressively brought into register with a single hole or port (P1, ... , P9) provided in the cylinder heads, thereby said ring functioning as admission and alternatively exhaust valves, contemporary over all the cylinder heads with a cyclic frequency equal to ⁇ M /2, as it is necessary for controlling the well known four-stroke thermodynamic cycle of the internal combustion engines.
  • FIG 13 another more detailed example of a single sector is given, as part of a four-sectors distributor ring adapted to govern a 4-stroke cycle on a 7 cylinder engine.
  • each phase e.g. the ignition
  • each phase of the 4-stroke cycle taking place through all 9 cylinders invests successively said cylinders with the following sequence: 1, 8, 6, 4, 2, 7, 5, 3, 1, and 1,8,6, ... again (according to the cylinder numbering given in figure 4 ), that is regularly jumping from one cylinder to the after-next.
  • the associated distributor ring in this example, is that partially (one sector only, spanning 90°) reproduced in figure 13 .
  • the combination of the two figures allows to visualise the synchronisation and succession of the 4 phases, guaranteed by the illustrated angular position of the admission (Aa, Ba, Ca, Da) and exhaust (Ae, Be, Ce, De) openings provided in the 4 sectors.
  • thermodynamic cycles characterised by a higher number of piston strokes, e.g. : a 6-stroke or in a 8-stroke or even in a 12-stroke cycle.
  • the ring is formed by two sectors, only the sector A being completely drawn with full lines, and sector B is drawn with dash lines. They are however identical and provided each with six ports, in specific angular positions, which allow the correct control of the gas flow in-and-out flow with a synchronic sequence, parallel to that explained in relation to figure 13 , but extended to the case of the 8-stroke cycle. Further aspects on this example will be discussed later on.
  • thermodynamic nature and associated advantages of a 6- or 8-or 12-stroke cycle is unknown in the state of the art, at least within the field of the volume-displacement engines, having the classic multi-cylinder V or in-line configuration, supposedly because considered too complex and impracticable to realize, so as to leave them unexplored.
  • the lines 1-2, 2-3 and 3-4 which indicate the adiabatic compression phase, the heat supply phase (combustion by spark ignition or by progressive injection) and the adiabatic expansion phase, respectively.
  • the line 4-1 conventionally represents the "heat extraction” phase which takes place externally of the engine, since notoriously the "open cycles” start with fresh gas (air) sucked from atmosphere (at the conditions of point 1) and terminates with expanded gas discharged into atmosphere (at the conditions of point 4).
  • the relevant chamber's openings are located in a determined order and angular positions, among the positions of the admission openings Aa, Ba and of the exhaust openings Ae, Be in such a way that said toroidal expansion chamber enters in communication with the various cylinders, as the ring slides over them, during predetermined time intervals coinciding with the appropriate time phases of the 6-phases thermodynamic cycle illustrated in figure 11 .
  • a second very interesting embodiment of the distribution ring which is defined by claims 6 and 9, is adapted to govern a 12-stroke cycle which offer the possibility of accomplishing another thermodynamic cycle composed by 8 phases , as represented in figure 12 .
  • IPCC intermediate pressure compression chamber
  • Said compression chamber is also provided with three extensions (24',24",24"'), for each sector, which open into said bottom circular surface 23' of the ring, at an appropriate angular position to allow the compressed gas flow to enter and leave the cylinders during the first six strokes of each piston, in phase with the following six strokes (total 12-stroke) which are then responsible for the double expansion phase, as already explained above, with the figure 13 , in the case of a 6 phase thermodynamic cycle.
  • this additional IPCC compression chamber is enabled to transfer the fluid, compressed to an intermediate pressure, from one cylinder to two cylinders which are diametrically opposed within the cylinders circular row of the barrel engine, whereby the compression chamber performs also the function of a buffer for the intermediately compressed fluid.
  • the resulting "double compression phase” is represented by the lines between the points 1 and 2' (first compression) and 2"-2 (second compression) in figure 12 .
  • said factor g/s decreases, at a constant radius, with the value of the tilt angle ⁇ .
  • a further preferable characteristic is formed by a second couple of bevel gears, the vertex of which is also placed at the centre O of the engine.
  • the duty of said bevel gears is that of taking the torque (thus the power) out of the wobbling unit and transmitting it to an output shaft co-axial, but distinct from the main engine shaft.
  • the cited torque is that generated by the cyclic succession of forces exerted by the pistons in their expansion strokes all around the periphery of the wobbling unit.
  • the first (28) of these bevel gear is an internal bevel gear mounted under the bottom of the wobbling unit and it meshes progressively over a second external bevel gear or conical pinion (29) which is rotatably supported by the casing (see figure 1 ) around the centreline C/L of the engine and coupled to the output shaft of the engine.
  • This first internal gear 28, fixedly and co-axially mounted to the WU (15), has a primitive cone with an angle ⁇ at its vertex, said vertex being placed on the centre point O, and the second (external) pinion gear (29), rotatably mounted around the C/L on the bottom part of casing (12), has a primitive cone with an angle ⁇ at its vertex which coincide with the vertex of the first gear (28) on the centre point O of the engine so that the are in an appropriate meshing condition, during the wobbling movement of the WU.
  • ⁇ P / ⁇ M sin ⁇ - sin ⁇ / sin ⁇ which are easily derived from the diagram of figure 2
  • ⁇ P / ⁇ M is a desired value of a reductive transmission ratio between the wobbling frequency, i.e. the main-shaft rotary speed: ⁇ M
  • the pinion's (29) i.e. the engine-output-shaft's, rotary speed: ⁇ P .
  • said second couple of bevel gears (28, 29) is adapted to extract the forces, generated by the pistons, out of the WU and to transform them into a couple on the axis of the pinion, i.e. onto the output-shaft (30) of the engine, advantageously discharging the engine's main crank-shaft (17+19+21) from all torque stresses.
  • the suggested engine configuration comprises the following major and essential components see figures 1 and 5 :

Claims (5)

  1. Moteur à cylindres multiples disposés en barillet ayant un axe central (C/L) et un point central (O), comprenant :
    - un bloc statique (12) sur le quel un nombre (N) de cylindres (11) sont disposés en cercle et en parallèle tout autour de l'axe central (C/L) ;
    - un nombre correspondant de pistons (13), chacun monté à l'intérieur de chacun des cylindres ;
    - un vilebrequin (16) comprenant deux portions d'extrémités (17,18) et une portion intermédiaire (19) dont l'axe (w-w) croise l'axe commun (C/L) des portions finales sur le point central (O) en formant un angle d'inclinaison α, ledit vilebrequin étant monté en rotation sur le bloc statique moyennant un premier couple de roulements à billes (20,20') qui opèrent entre le bloc statique et les deux portions d'extrémités, celles-ci étant solidement connectées à la portion centrale à travers au moins une manivelle (21).
    - un corps oscillant (15), essentiellement axial - symétrique, monté en rotation, moyennant un deuxième couple de roulements à billes (22,22') , sur la portion intermédiaire (19) du vilebrequin, de façon à ce que l'axe w-w de celle-ci coïncide avec l'axe central de symétrie dudit corps oscillant, lesdits pistons étant connectés à, et supportés par, la périphérie de ce même corps, si bien que lesdits pistons et ledit corps(15) forment ensemble une pièce unique nommée : Unité Oscillante (WU) ;
    - un premier couple d'engrenages coniques (26,27) ayant un cône primitif identique, avec un angle au vertex µ = π - α/2 , un de ces engrenages (26) étant solidement attaché au bloc statique (12) et l'autre (27) solidement monté sur l'Unité Oscillante (WU) en position opposée, et de façon à ce que les deux vertex desdits engrenages coïncident ensemble avec le point central O du moteur, que l'axe de l'un des engrenage (26) coïncide avec l'axe central du moteur et que l'axe de l'autre (27) coïncide avec l'axe de l'Unité Oscillante (WU), ledit premier couple d'engrenages formant, par leur interaction, une contrainte à la rotation de la WU autour du C/L ;
    - un distributeur rotatif synchronisé, ayant essentiellement la forme d'un anneau (23) monté en rotation autour du C/L du moteur, monté ainsi co-axialement au cercle des cylindres, de manière à pouvoir glisser en rotation au-dessus des têtes (H1, ....., Hn) des cylindres et étant adapté pour accomplir, simultanément, le contrôle du passage cyclique et intermittent du fluide opératif en entré et en ortie de tous lesdites N cylindres, à travers d'ouvertures correspondantes (P1, ....., Pn ) pratiquées dans lesdites têtes, sa vitesse de rotation (ωd) étant opportunément synchronisé avec la vitesse de rotation du moteur (Ω m );
    - ledit anneau distributeur (23) étant monté au dessus des têtes des cylindres, en contact glissant, sur un plan perpendiculaire à l'axe centrale C/L, si bien que, pendant sa rotation, certains conduits d'admission (24) et de décharge (25), présents dans l'anneau entrent en collimation avec les dites ouvertures (P1, ..,Pn), et, en glissant au delà, les referment alternativement, en assumant avec ceci la fonction, sur les cylindres,d'une double série de soupapes d'admission et des décharge.
    - un angle d'inclinaison α inférieur a 15°, et de préférence, inférieur à 8° ;
    - une seule et unique ouverture (P1, .. , Pn) dans chaque tête des cylindres, pour le passage en entrée et en sortie du fluide compressible (air ou gaz respectivement) ;
    - ledit anneau distributeur étant composé par un nombre S de secteurs circulaires identiques (A, B, C, ....), formant ensemble une pièce intégrale ,
    chacun des secteurs comprenant au moins une ouverture d'admission (Aa, Ba, Ca, ...), avec conduit relatif (24), et une ouverture de décharge (Ae, Be, Ce, ...), avec conduit relatif (24), pour la connexion avec, respectivement, un collecteur d'admission et un collecteur de décharge, ledit nombre S étant dépendant du nombre N des cylindres ;
    - la vitesse de rotation (ωd) de l'anneau étant synchronisée, moyennant un mécanisme d'engrenages réducteurs, avec la vitesse (Ω m) du moteur selon la relation : ωd = + Ωm/(N+1) si S=(N+1)/2 , ou bien : ωd = - Ωm/ (N-1) si S=(N-1)/2 ,
    ou N représente un nombre impair supérieur ou égal à 3,
    caractérisé en ce que ledit anneau distributeur (23) est formé par un nombre S de secteurs circulaires identiques qui est déterminé par la relation : S = N + 1 / C / 2
    Figure imgb0017
     pendant qu'il tourne toujours avec la même vitesse de rotation donnée par ω ⁢ d = + Ωm / N + 1 ,
    Figure imgb0018
     de façon à permettre l'évolution dans le cylindres du moteur d'un cycle thermodynamique à temps multiples, N étant toujours le nombres des cylindres, C étant le nombre de courses complètes des pistons nécessaires à l'accomplissement d'un cycle thermodynamique à temps multiples prédéterminé, où C = 8 (cycle à 8 temps) ou C = 12 (cycle à 12 temps) :
    - dans le cas de C = 8, un conduit d'expansion et de transfert est formé dans chaque secteur, ayant une forme identique dans tous les S secteurs, ladite forme étant telle que une chambre toroïdale d'expansion et transfert (IPTC) se forme à l'intérieur de l'anneau lors de l'assemblage des secteurs S, chacun d'eux étant pourvu aussi d'extensions dudit conduit qui s'ouvrent, en nombre de 3, sur la surface circulaire de base (23') de l'anneau, dans une position angulaire intermédiaire, entre lesdites ouvertures d'admission (Aa, Ba, ...) et de décharge (Ae, Be, ..), de manière à permettre au fluide à pression intermédiaire, de couler, à travers la dite chambre toroïdale, à partir d'un cylindre en phase de décharge vers deux cylindres adjacents, en phase d'aspiration, dans la partie diamétralement opposée du cercle des cylindres, ladite chambre toroïdale (IPTC) remplissant aussi une fonction d'accumulateur de gaz pour le fluide en expansion; et
    - dans le cas de C = 12 , un conduit additionnel de compression (IPCD) est formé dans chaque secteur, ayant une forme identique dans tous les S secteurs, ladite forme étant telle que une chambre toroïdale additionnelle de compression (IPCC) se forme à l'intérieur de l'anneau, lors de l'assemblage des secteurs S, chacun d'eux étant pourvu aussi d'extensions (25a', 25a", 25a"') dudit conduit s'ouvrant, en nombre de 3, sur la surface circulaire de base (23') de l'anneau, dans une position angulaire intermédiaire, entre lesdites ouvertures d'admission (Aa, Ba, ...) et de décharge (Ae, Be, ..), de manière à permettre au fluide à pression intermédiaire, de couler, à travers la dite chambre toroïdale de compression (IPCC), à partir de deux cylindres adjacents, en phase de décharge après l'aspiration, vers un cylindre, en phase de remplissage, dans la partie diamétralement opposée du cercle des cylindres, ladite chambre toroïdale (IPTC) remplissant aussi une fonction d'accumulateur de gaz pour le fluide en compression.
  2. Le moteur à cylindres multiples disposés en barillet selon la revendication 1 caractérisé en ce que l'anneau distributeur rotatif est formé par un nombre de secteurs identiques S = (N+1)/4, c'est-à-dire C=8, et que chacun des secteur S comprend 6 ouvertures : une ouverture (Aa, Ba, Ca, ...) pour l'admission à basse pression (LP), une ouverture (24') pour la décharge/transfert à pression intermédiaire (IP) , deux ouvertures (24",24"') pour l'admission à pression intermédiaire (IP), et deux ouvertures (Ae', Ae", ... , Be', Be", .. ) pour la décharge à basse pression (LP), ledit distributeur comprenant aussi, à l'intérieur tout autour de l'anneau, la chambre toroïdal d'expansion (ETC) qui est en communication avec l'ouverture de décharge/transfert (24') et avec les deux ouvertures de transfert/admission à pression intermédiaire (24", 24"'), de façon à permettre au moteur de fonctionner selon un cycle à 8-temps (4-temps classiques + 4-temps d'expansion supplémentaire et décharge).
  3. Le moteur à cylindres multiples disposés en barillet selon la revendication 1 caractérisé en ce que l'anneau distributeur rotatif est formé par un nombre de secteur identiques S = (N+1)/6, c'est-à-dire C=12, et que chacun des secteur S comprend 10 ouvertures : deux ouvertures (Aa', Aa") pour l'admission basse pression (LP), deux ouvertures pour la compression/transfert à pression intermédiaire (IP), une ouverture pour le transfert/admission à pression intermédiaire (IP), une ouverture pour la décharge/transfert à pression intermédiaire (IP), deux ouvertures pour le transfert/admission à pression intermédiaire (IP), et deux ouvertures (Ae', Ae", ... , Be', Be", .. ) pour la décharge à basse pression (LP), ledit distributeur comprenant aussi, à l'intérieur tout autour de l'anneau :
    - une chambre toroïdale de compression (IPCC) qui est en communication avec les deux ouvertures de compression/transfert et avec l'ouverture de transfert/admission à pression intermédiaires (IP), et
    - une chambre toroïdale d'expansion (IPTC) qui est en communication avec l'ouverture de décharge/transfert à basse pression (IP) et avec les deux ouvertures de transfert/expansion à pression intermédiaire (IP),
    de façon à permettre au moteur de fonctionner selon un cycle à 12-temps ( 4-temps d'aspiration et compression préliminaire + 4-temps classiques + 4-temps d'expansion supplémentaire et décharge).
  4. Le moteur à cylindres multiples disposés en barillet selon une quelconque des revendications 1 à 3, caractérisé en ce que il est pourvu d'un deuxième couple d'engrenages conique, formé par :
    - un engrenage conique interne (28) qui est co-axialement et solidement monté sur l'Unité Oscillante (WU) et possède un angle au vertex β , ce vertex étant en coïncidence avec le point central (O) du moteur, et
    - un engrenage conique externe (pignon 29) qui est monté en appui rotatif autour de l'axe central C/L sur la base du bloc statique (12) et possède un angle au vertex γ , ce vertex étant aussi en coïncidence avec ledit point central (O) du moteur,
    Les angles β et γ étant sélectionnés à l'aide des relations suivantes : β - γ = α et Ωp / Ωm = sin β - sin γ / sin γ
    Figure imgb0019
    où Ω p / Ωm est un rapport de transmission choisi entre la fréquence oscillante du WU, c'est-à-dire la vitesse de rotation du vilebrequin ( Ωm ), et la vitesse de rotation Ωm de l'arbre de sortie relié au pignon (29), ledit deuxième couple d'engrenages étant ainsi adapté, par leur prise, à extraire les forces générées par les pistons en dehors de l'unité oscillante, et de le transformer en un couple agissant sur l'axe du pignon, c'est-à-dire sur l'arbre de sortie du moteur.
  5. Le moteur à cylindres multiples disposés en barillet selon une quelconque des revendications 1 à 4, caractérisé en ce que le dessin et la position de l'unité oscillante, par rapport au bloc statique et aux cylindres, sont tels que chaque point sur la tête des pistons décrive, pendant un cycle de révolution du vilebrequin, une trajectoire qui traverse deux fois le plan équatorial statique (E) du moteur, habilitant ainsi la construction intégrée des pistons en une seule pièce avec l'unité oscillante (WU).
EP04766214A 2003-07-25 2004-07-14 Moteur polycylindre a barillet Not-in-force EP1658417B1 (fr)

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EP04766214A EP1658417B1 (fr) 2003-07-25 2004-07-14 Moteur polycylindre a barillet

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Application Number Priority Date Filing Date Title
EP03017057 2003-07-25
EP04766214A EP1658417B1 (fr) 2003-07-25 2004-07-14 Moteur polycylindre a barillet
PCT/EP2004/051484 WO2005012692A1 (fr) 2003-07-25 2004-07-14 Moteur a plusieurs cylindres

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EP1658417A1 EP1658417A1 (fr) 2006-05-24
EP1658417B1 true EP1658417B1 (fr) 2009-11-11

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EP (1) EP1658417B1 (fr)
AT (1) ATE448385T1 (fr)
DE (1) DE602004024082D1 (fr)
WO (1) WO2005012692A1 (fr)

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CN100485164C (zh) * 2006-12-29 2009-05-06 郭有祥 陀螺轮转式引擎
EP2108797A1 (fr) 2008-04-07 2009-10-14 Giulio Martinozzi Moteur à combustion interne à faible consommation, intégrant un système pour la super expansion des gaz d'échappement
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ATE448385T1 (de) 2009-11-15
EP1658417A1 (fr) 2006-05-24
WO2005012692A1 (fr) 2005-02-10
DE602004024082D1 (de) 2009-12-24

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