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WO2014191781A1 - Moteur à combustion interne à piston rotatif - Google Patents

Moteur à combustion interne à piston rotatif Download PDF

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Publication number
WO2014191781A1
WO2014191781A1 PCT/GE2013/000004 GE2013000004W WO2014191781A1 WO 2014191781 A1 WO2014191781 A1 WO 2014191781A1 GE 2013000004 W GE2013000004 W GE 2013000004W WO 2014191781 A1 WO2014191781 A1 WO 2014191781A1
Authority
WO
WIPO (PCT)
Prior art keywords
engine
core
block group
air
cylinder block
Prior art date
Application number
PCT/GE2013/000004
Other languages
English (en)
Inventor
Ramzan GOYTEMIROV
Original Assignee
Goytemirov Ramzan
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 Goytemirov Ramzan filed Critical Goytemirov Ramzan
Priority to PCT/GE2013/000004 priority Critical patent/WO2014191781A1/fr
Publication of WO2014191781A1 publication Critical patent/WO2014191781A1/fr

Links

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
    • 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
    • F01B13/045—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder with cylinder axes arranged substantially tangentially to a circle centred on main shaft axis
    • 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
    • F02B57/10—Engines with star-shaped cylinder arrangements with combustion space in centre of star

Definitions

  • the present invention pertains to engine technology and can be used in developing four- stroke non-poppet valve rotary internal combustion engines operating by gasoline fuel or natural gas, and particularly, by diesel or hydrogen fuel.
  • Wankel engine has found real application. Some attempts have been made to implement engines that are titled as orbital ones according to the US patent 3,787,150 of Sarich. Main advantage of the Wankel engine is small sizes at preset power. As compared with piston engines, the engine comprises twice as less movable parts, and, accordingly, it is potentially more reliable and is lower in cost.
  • the engine is characterized by use of planet motion of a rotor (piston) disposed within a housing, surface of which is made in the shape of epitrochoid.
  • Such structural solution enables to implement 4-stroke cycle of operation without the need in special gas distribution mechanism to be used. Chambers are sealed by radial and end sealing plates pressed against the housing by centrifugal forces, gas pressure, and band springs.
  • the Wankel engine that can hardly be overcome, or this is associated with heavy spending.
  • the first disadvantage is that the lengthened combustion chamber does not allow combusting the air-fuel mixture in effective way which leads to excessive fuel consumption.
  • the second disadvantage is that vibrations of plates of radial seal created in motion of the rotor leads to wearing of epitrochoidal inner surface of the housing and forms wavelike distortion thereof.
  • the third disadvantage is non-uniform heating of the housing associated with displacement of the combustion chamber with respect to the housing produces heat stresses leading to the epitrochoid distortion.
  • the orbital engine patented by Sarich (US3,787,150) has also a substantial structural drawback in that motion of blades that partition the operating volume of the engine into isolated chambers is translational with respect to the housing. At the same time, the blade ends fastened in the rotor perform motion similar to a sliding member in a sine mechanism. Such motion of the blade allowed Sarich to provide sealing of the blade in the housing in the simplest way. However, the method of fastening and sealing the blades in the rotor appeared to be very complicated, and, importantly, non-reliable.
  • the patent US3,703,344 discloses a structure of a non-poppet valve engine wherein admission and exhausting is performed via channels and cut-outs through a drive cam of a power shaft, pivot joints mounted in the rotor, blade plates, pivot joints mounted in the housing, and a housing.
  • the disclosed system has limitation in gas distribution possibilities and in mounting sealing elements to prevent effluxes.
  • Another orbital non-poppet valve engine is disclosed in patent RU2285127, wherein a rotor is mounted off-center on a power shaft.
  • a spool-type disk plays a role of a gas distribution mechanism that is coaxially disposed relative to the power shaft and has end recesses made along arcs of different radial circles. The disk rotates contrary to the power shaft rotation direction with twice as less speed and creates a cyclogram of operation of an engine having the odd number of combustion chambers.
  • the engine according to US3,828,740 comprises a rotary cylinder block group with four radially arranged cylinder-piston group having combustion chambers facing the center; a housing with a rim having a curvilinear, closed running track that is symmetrical with respect to the rotational center and having contact with pressure-bearing running rollers mounted directly on each piston; a spool-type gas distribution core having ports on outer periphery for supplying air-fuel mixture or air and ignition spark or for injecting the fuel into two oppositely disposed combustion chambers at once fastened on the housing in the central opening of the cylinder block group with clearance and with means for sealing the junction.
  • Each combustion chamber is provided with one inlet opening facing the rotational center opposite to the core ports for receiving air-fuel mixture, air, ignition spark or injectable fuel.
  • the engine is provided with a passageway for exhaust gasses to be exhausted successively from each combustion chamber in lower "dead point" after completing the working stroke, i.e. a piston remains fixed in a cylinder during turning of the block group by 90° degrees and new mixture or air is blown to push out exhaust gasses partially mixed therewith.
  • the combustion products like in well-known "two-stroke” principle, are partially remained in the cylinder and present in the process of power/expansion during the working stroke.
  • the present invention has for its objective to simplify the construction and ensure reliable and smooth operation in a four-stroke and non-poppet valve engine having any number of cylinders that can operate by different types of fuel (petroleum, gas, diesel, hydrogen).
  • the rotary-piston internal combustion engine comprising a cylinder block group on rotation supports mounted in the engine housing, the group having radially arranged cylinder-piston groups with a combustion chambers facing a rotational center; a rim mounted in the housing with a curvilinear, closed inner running track being symmetrical relative to the rotational center and being in contact with a pressure-bearing running rollers mounted on each piston directly or by means of a connecting rod supported by a lever mounted on a pivotal support on the cylinders block group; a gas distribution spool-type core having circular cross-section that is fixed on the housing to prevent its rotation and mounted in the central opening of the cylinder block group with running clearance and means for sealing a junction and having a port on its outer periphery for supplying the air-fuel mixture or air and a port for supplying ignition spark and/or injecting the fuel into the combustion chambers; each combustion chamber being provided with one inlet opening facing the rotational center for receiving the air-fuel mixture
  • a one single common passageway made on the same outer periphery of the core in the form of one more port through the same inlet matching opening is provided, and said two ports for supplying the fuel mixture or air and for exhausting together occupy an angular sector of no more than 180° on the outer periphery of the core and are spaced apart with the interval equaling to the central angle not less than that occupied by the inlet opening, the same exhaust opening, relative the rotational center, of each combustion chamber; and, at the same time, the sector which is not less than said angle on the outer surface of the core occupies said port for supplying the ignition spark and/or fuel injection and it is disposed in the sector of 180° diametrically opposed to the location of said two ports; said gas distribution spool-type core fixed on the housing to prevent its rotation is positioned in the central opening in freely suspended state;
  • said gas distribution spool-type core is of conical shape, spring loaded in axial direction and is mounted in a central opening having conical shape in the cylinder block group; channels for admission and diverting of cooling liquid is made in the spool-type gas distribution core;
  • said spool-type gas distribution core is made of a heat-resisting alloy or ceramics and/or the central opening of the cylinder block group is provided with a sleeve made of a heat- resisting alloy or ceramics;
  • the means for sealing the junction between the spool-type gas distribution core surface and the central opening of the cylinder block group is made as sealing rings, e.g. zigzag in shape, disposed in non-pivotable manner in annular channels of the core, and are made of heat-resisting materials;
  • the pistons are mounted in the cylinders arranged with an axis offset relative to the axis of rotation of the cylinder block group by a value exceeding the sum of radiuses of the cylinder and the spool-type gas distribution core in case the number of cylinders in the engine is no more than four;
  • the pivotal support of the floating lever supporting each connecting rod is disposed in the cylinder block group at the side opposite to the offset of the cylinders axis from the rotational center and is spaced apart from it to the extent that upon positioning the piston in the upper "dead point" of the cylinder, the floating lever together with the connecting rod create an obtuse angle towards the rotational center;
  • finnings are made at the ends and/or in the periphery of the cylinder block group, and blow down ports for cooling the engine by air are made in the housing;
  • One single spool-type core disposed in the cylinder block group center in freely suspended state can serve to supply air-fuel mixture or air through one single port to the combustion chambers; one single fuel injector or ignition spark and one single port in the same core for exhausting the exhaust gasses are sufficient; the spool-type core has not to be pressed to the cylindrical contact surfaces for sealing because its free disposition in the cylinder block group opening allows to make the surfaces and the junction with minimum operational clearance; the ports for fuel supply, ignition and exhausting are arranged along the angular sectors such that four-stroke cycle is accomplished in each cylinder successively, and thereby any number of cylinders that can be disposed within the predetermined sizes of the engine can be employed.
  • the spool-type core is of conical shape for ensuring the required sealing of the junction and enhanced compression in the combustion chambers.
  • the offset cylinders relative to the rotation axis enable, on the one hand, to better utilize the internal volume and reduce the sizes of the engine.
  • pressure-bearing rollers can be mounted and pivot axes of the levers can be arranged in a manner as to create auspicious interaction between the rollers and inclined surfaces of the rim. Due to the extra tilt back action of the pressure-bearing rollers onto the rim, the upper "dead point" can be passed and the force application arm can be increased faster, that creates a torque, to compare with conventional engines with a crankshaft. This is important in view of reducing the influence of blowing loads on the smoothness of operation of Diesel engines, and particularly, engines that operate by hydrogen fuel.
  • Fig.l shows front section of the four-cylinder engine according to the present invention
  • Fig.2 shows front section of the eight-cylinder engine according to the present invention
  • Fig.3 shows longitudinal cross section of the engine according to the present invention
  • Fig.4 shows front section of the four-cylinder engine according to the present invention and passage of each combustion chamber beside the ports of the gas distribution core in four-stroke cycle;
  • Fig.5 shows comparative diagram of upper "dead point” passage speed of the pressure- bearing rollers mounted on the pistons arranged offset with respect to rotational center after explosion.
  • the engine comprises a cylinder block group 3 mounted within a housing 1 on rotation supports 2.
  • Pistons 4 are accommodated in radially arranged cylinders 5 forming combustion chambers 6 facing a rotational center 7 of the cylinder block group 3.
  • Pivotally connected to the pistons 4 are connecting rods at another ends of which pressure-bearing running rollers 9 are mounted.
  • the connecting rods 8 are supported by floating levers 10, pivotal supports of which are positioned in the cylinder block group 3. Another end of each floating lever 10 is pivotally connected to the intermediate part of the respective connecting rod 8.
  • the pivotal support of the floating levers 10 which are arranged in the cylinder block group 3 is disposed at a ' distance from the rotational center 7 so that when positioning the piston 4 in the upper "dead point" (i.e. closest to the rotational center 7) the floating lever 10 creates an obtuse angle a with the connecting rod 8 at the rotational center 7 side opposite to the block group 3 rotation direction.
  • a rim 11 having a curvilinear, closed, symmetrical relative to the rotational center 7 inner operational running track 12 is mounted in the housing 1 (or is directly constructed therein).
  • the shape of the closed running track 12 is determined by four-stroke operation cycle which must conditionally be divisible by two.
  • a spool-type gas distribution core 14 is positioned in the central cylindrical opening 13 of the block group 3.
  • the core 14 is fixed to prevent its rotation in the housing 1; however, it is not fastened and is disposed within the opening in free-suspended state to ensure minimal running clearance in the junction, that is necessary for sealing and ensuring the required compression in the combustion chambers 6.
  • Rings 15 that seal the junction are mounted such that they are not capable of turning on the core 15.
  • All ports and channels needed for ensuring the four-stroke operation cycle as well as for liquid cooling of the engine are made on the outer cylindrical surface 14 of the core.
  • the supply port 16 is made in the angular sector not exceeding 90°, destined for the suction stroke or for blowing the air-fuel mixture or air.
  • Exhaust port 17 is made in the angular sector not exceeding 90°, destined for exhausting the exhaust gasses. Both of the ports 15 and 17, jointly, including the angular distance ⁇ between them, occupy not more than 180° of the angular sector.
  • a port 18 destined for spark supply and/or fuel injection is disposed on the outer surface of the core 15 in a remaining 180° sector destined for the compression and expansion strokes, approximately in the middle thereof, and can be provided with a spark plug 19 and/or fuel injector 20.
  • Each combustion chamber 6 is provided with an opening 21 that occupies the angular sector y, destined for receiving the air-fuel mixture, air, ignition spark and/or injectable fuel as well as for exhausting the exhaust gasses.
  • the angular interval ⁇ between them is made greater than the angular sector ⁇ which occupies an opening 21 of the combustion chamber 6.
  • the cylinders 5 with the pistons 4 can be offset relative to the rotational center 7 in the direction of the rotation of the block group 3 with value of A which is greater than the sum of the cylinder 5 diameter d and the diameter D of the outer surface of the spool-type gas distribution core 14 so as to reduce the sizes and ensure enhanced smoothness of the engine operation.
  • the outer surface of the spool- type gas distribution . core 14 can be made conical and can be positioned within the opening 13 of the block group 3 and can be spring-loaded in axial direction (this embodiment not shown in the figures). In the core 14, channels 22 for admission, circulation 23 and diverting of the cooling liquid are made.
  • the core 14 must be made of heat-resisting material, for example of heat-resisting ceramics, and the inner opening of the block group 3 is provided with a sleeve 24 made of heat- resisting material.
  • the engine can be provided with air cooling means made as finnings 25 in the cylinder block group 3, at the ends and/or in the periphery, and blow down ports 26 are made in the housing.
  • a toothed ring 27 can be made on the rim 11, and on the axes of the pressure-bearing running rollers 9, gear-wheels 28 can be mounted to allow the rollers 9 to run in the running track 12 without slipping.
  • the engine can be provided with a air-oil cooling means for the purposes of which oil is doped in the housing 1, upper the running track 12 of the rim 11, and channels for running-off the air-oil mixture for cooling the oil and channels for forcibly returning the oil and accessing the fresh air to the housing interior (this embodiment not shown in the figures) are made therein.
  • a air-oil cooling means for the purposes of which oil is doped in the housing 1, upper the running track 12 of the rim 11, and channels for running-off the air-oil mixture for cooling the oil and channels for forcibly returning the oil and accessing the fresh air to the housing interior (this embodiment not shown in the figures) are made therein.
  • the engine operates in the following manner.
  • the pistons 4 are performing forcible reciprocal motion within the rim 11 in the manner defined by the running track 12 shape.
  • the combustion chambers 6 of each cylinder 5 successively pass in circle beside ports 16, 18 and 17 of the core 14.
  • the air-fuel mixture or air is sucked or blown through the opening 21 into the combustion chamber 6 and the piston 4 moves in radial direction from the rotational center 7 (first stroke).
  • the piston 4 moves in radial direction towards the rotational center 7, the air-fuel mixture or air is compressed (second stroke) and, at the end of the compression (in the upper "dead point" of the piston 4), a spark is supplied by the spark plug 19 through the port 18, or fuel is initially injected by the injector 20 and then spark is supplied, or diesel fuel is injected without supplying the spark.
  • a spark is supplied by the spark plug 19 through the port 18, or fuel is initially injected by the injector 20 and then spark is supplied, or diesel fuel is injected without supplying the spark.
  • detonation, explosion or combustion of the fuel and expansion of gasses i.e. working stroke of the piston 4 from the center (third stroke) occurs.
  • the pressure-bearing roller 9 acts on the curvilinear running track 12, creates a torque and brings about further forcible rotation of the cylinder block group 3.
  • the piston 4 performs radial motion towards the rotational center 7 and the exhaust gasses exhaust successively from each combustion chamber 6 through the port 17 (fourth stroke).
  • one revolution of the cylinder block group corresponds to one working stroke and forcible rotation by 90°. Therefore, while the present engine can have any number of cylinders, at least four cylinders are necessary for continuous forcible rotation. In case of four cylinders contained in the present engine, four working strokes are performed in one revolution and the engine in this case can be considered more high-speed than a conventional four cylinder four-stroke engine with a crankshaft wherein two working strokes are performed per one revolution of the shaft. Due to this peculiarity, the engine is well suited to hydrogen fuel having the property of faster propagation of explosion to compare with petrol.
  • the obtuse angle a created between the floating lever 10 and the connecting rod 8 in the beginning of the working stroke causes additional roll-over action of the pressure-bearing roller 9 onto the running track 12 of the rim 11, creating this greater "arm” at this moment. It means that the applied force arm which cereals torque increases more rapidly than, for example, in an engine with a crankshaft.
  • the present invention allows to resolve the following technical tasks in a complex manner: in a non-poppet valve mechanical system of gas distribution four stroke cycle, any number of cylinders, use of conventional groups of . cylinders and pistons are combined in a single device that allows the most perfect combustion, smoothing impact load in the upper "dead point" (which is particularly important for diesel engines and those operating by hydrogen).

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

Abstract

La présente invention se rapporte à des moteurs quatre-temps à combustion interne, rotatifs et à soupapes qui ne sont pas des soupapes champignons qui fonctionnent à l'essence, au gaz naturel, au carburant diesel ou à l'hydrogène, et peut être utilisée pour permettre une simplification de la structure, ce qui assure un fonctionnement fiable et sans à-coups de moteurs comportant un nombre quelconque de cylindres. Le moteur comprend un bloc-cylindres monté dans un carter sur des supports de rotation, les chambres de combustion étant orientées vers le centre de rotation ; une bride ayant une voie de roulement interne fermée et curviligne étant en contact avec des galets de roulement de support de pression montés sur des pistons ; un noyau de type bobine de distribution de gaz à rotation bloquée dans une ouverture centrale du bloc-cylindres et qui comporte des orifices sur sa périphérie externe destinés à fournir le mélange air/carburant ou l'air, l'étincelle d'allumage et/ou à injecter le carburant dans les chambres de combustion ; l'invention comprend également un orifice commun destiné à évacuer avec succès les gaz d'échappement des chambres de combustion. Les orifices pour permettre en combinaison l'alimentation et l'évacuation occupent un espace inférieur ou égal à 180° ± 10 degrés sur le secteur angulaire du noyau, et l'orifice destiné à l'étincelle d'allumage et/ou à l'injection du carburant est disposé dans un secteur diamétralement opposé de 180° ± 10 degrés. Le noyau de type bobine est monté dans un état librement suspendu et peut avoir une forme conique, être à ressort de rappel et être composé d'une céramique thermorésistante.
PCT/GE2013/000004 2013-05-28 2013-05-28 Moteur à combustion interne à piston rotatif WO2014191781A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/GE2013/000004 WO2014191781A1 (fr) 2013-05-28 2013-05-28 Moteur à combustion interne à piston rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/GE2013/000004 WO2014191781A1 (fr) 2013-05-28 2013-05-28 Moteur à combustion interne à piston rotatif

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WO2014191781A1 true WO2014191781A1 (fr) 2014-12-04

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020112131A (ja) * 2019-01-16 2020-07-27 株式会社加地テック ガス圧縮機及びガス圧縮機の製造方法
ES2926750A1 (es) * 2021-04-19 2022-10-27 Civiac Gimenez Jose Ramon Motor de explosion de cuatro tiempos

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1456479A (en) * 1920-04-15 1923-05-22 Atkinson Dale Sydney Combined internal-combustion and turbine engine
GB235262A (en) * 1924-02-28 1925-05-28 Samuel Maddick Rotary engine
US1990660A (en) * 1931-12-14 1935-02-12 George B Mccann Radial internal combustion engine
DE812978C (de) * 1949-03-26 1951-09-06 Erich Immel Zweitakt-Brennkraftmaschine mit umlaufenden Zylindern
FR2050073A5 (fr) * 1970-06-08 1971-03-26 Recco Rene
FR2114501A5 (fr) * 1971-10-21 1972-06-30 Thomas Francis
DE2111607A1 (de) * 1971-03-11 1972-09-14 Manfred Schmid Brennkraftmaschine
WO2007090248A1 (fr) * 2006-07-07 2007-08-16 Ramzan Usmanovich Goytemirov Moteur a combustion interne

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1456479A (en) * 1920-04-15 1923-05-22 Atkinson Dale Sydney Combined internal-combustion and turbine engine
GB235262A (en) * 1924-02-28 1925-05-28 Samuel Maddick Rotary engine
US1990660A (en) * 1931-12-14 1935-02-12 George B Mccann Radial internal combustion engine
DE812978C (de) * 1949-03-26 1951-09-06 Erich Immel Zweitakt-Brennkraftmaschine mit umlaufenden Zylindern
FR2050073A5 (fr) * 1970-06-08 1971-03-26 Recco Rene
DE2111607A1 (de) * 1971-03-11 1972-09-14 Manfred Schmid Brennkraftmaschine
FR2114501A5 (fr) * 1971-10-21 1972-06-30 Thomas Francis
WO2007090248A1 (fr) * 2006-07-07 2007-08-16 Ramzan Usmanovich Goytemirov Moteur a combustion interne

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020112131A (ja) * 2019-01-16 2020-07-27 株式会社加地テック ガス圧縮機及びガス圧縮機の製造方法
AU2020208981B2 (en) * 2019-01-16 2022-12-15 Kaji Technology Corporation Gas compressor and production method for gas compressor
ES2926750A1 (es) * 2021-04-19 2022-10-27 Civiac Gimenez Jose Ramon Motor de explosion de cuatro tiempos

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