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WO1998058167A1 - Moteur rotatif - Google Patents

Moteur rotatif Download PDF

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Publication number
WO1998058167A1
WO1998058167A1 PCT/PL1998/000028 PL9800028W WO9858167A1 WO 1998058167 A1 WO1998058167 A1 WO 1998058167A1 PL 9800028 W PL9800028 W PL 9800028W WO 9858167 A1 WO9858167 A1 WO 9858167A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
cylinder
shaft
axis
hole
Prior art date
Application number
PCT/PL1998/000028
Other languages
English (en)
Inventor
Stanislaw Kulka
Original Assignee
Stanislaw Kulka
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 Stanislaw Kulka filed Critical Stanislaw Kulka
Priority to AU76791/98A priority Critical patent/AU7679198A/en
Publication of WO1998058167A1 publication Critical patent/WO1998058167A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston 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
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F02B2053/005—Wankel 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
    • F02B75/02—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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to a rotary internal-combustion engine for driving machines and vehicles.
  • most known designs are piston engines and Wankel engine.
  • the effective efficiency for various types of engine according to the invention ranges between 48% up to 64%, that results from the geometry of the engine design.
  • the work cycle of the single-cylinder rotary engine is similar to that of a two-cylinder four-stroke piston engine.
  • the rotary engine consists of the following units:
  • the cylinder unit consists of the cylinder itself and two identical heads closing tightly, at both sides, the cylinder hole with two parallel flat surfaces vertical to the cylinder hole axis.
  • the r(f) closed plane curve defines the contour of the cylinder internal wall.
  • the cylinder height, H should be not bigger than dimension 2R j of the cylinder hole: 0 ⁇ H ⁇ 2R j .
  • Each head has a round port coaxial with the axis of the cylinder hole of diameter D equal to: 2aR j ⁇ D ⁇ 2R j (l - a).
  • the engine shaft is mounted in said ports. Besides that, at least two openings, closed with valves and serving as the supply and exhaust system ducts, are made in the heads or in the cylinder body.
  • the working mechanism of the engine consists of the shaft and the rotor.
  • the cubicoidal part of the shaft is used to connect the shaft itself with the rotor.
  • Three ports are made in the shaft for the rotor driving mechanism.
  • One of the ports, in the form of longitudinal slot, is located symmetrically along the shaft axis. This slot intersects symmetrically the middle part of the shaft, i.e.
  • the remaining two ports in the shaft are identical having a circular cross-section, and their axes are parallel each other, whereby crossing vertically the shaft axis. They are located symmetrically at both sides, outside the cylinder, and they protrude crosswise through the along-axis-opening and parallel to the shorter sides of the rectangular cross-section of the shaft. The distance between these hole axes depends on cylinder height, H, thickness of the heads, and technical parameters of the rotor driving mechanism.
  • the rotor seated on the shaft inside the cylinder, is made in the form of an arm dividing the cylinder into two tightly separated chambers.
  • the rotor has got two parallel flat bases co-operating with two flat surfaces of the heads and makes a solid body of cylindrical and prismatic features, wherein all generating lines and side edges constitute sections of straight lines being parallel each other and vertical to both bases.
  • the rotor height is equal to the cylinder height H.
  • the rotor axis is verdical to its flat bases and parallel to the cylinder axis, and it is the axis of symmetry for the rotor solid.
  • the ends of the rotor arm are determined by two points: r j (0) and r j ( ⁇ ) and its length is: (2R j - b).
  • the rotor has got a hole, coaxial with the rotor axis, of a rectangular cross-section, situated in such a manner that longer sides of the rectangle are parallel to the rotor length.
  • the rotor is mounted on the engine shaft in such a manner that the cubicoidal member of the shaft is located in the rectangular hole of the rotor; where the hole width is equal to the rectangle width and the length of the hole is longer by at least 2aRr j than the shaft cubicoid length.
  • the cubicoidal member of the shaft serves as a guide, along which the rotor moves radially with a reciprocating motion in relation to the shaft axis whereby rotating together with the shaft around its axis.
  • Rotor controlling mechanism controls the reciprocating radial motion of the rotor in relation to the shaft axis, shifting the rotor upon the cubicoidal member of the shaft.
  • the control mechanism consists of the following components: slide (lpc), connecting-rod (1 pc), guiding shaft (2 pcs), bevel gear (2 pcs), toothed ring (2 pcs).
  • the cubicoidal slide length is equal to the length of the rectangular hole in the rotor, and its width is equal to that of the along-axis-opening in the shaft; it is rigidly mounted in the rectangular port of the rotor and protrudes through along- axis-opening in the engine shaft.
  • the port of a circular section with its centre at the point O j is made in the slide.
  • the distance between the ports for crank-pins in the connecting-rod (i.e. theoretical length of the connecting-rod) is equal to that between the axes of the guiding shafts.
  • the cranks of both guiding shafts coincident in phase, move the connecting-rod in such a way that its axis is always parallel to the axis of the engine shaft and always in line with the rotor axis.
  • the diameter of the connecting-rod bar is equal to that of the port in the slide, and the connecting-rod moving with a reciprocating motion in the port of the slide forces a radial reciprocating motion of the rotor on its shaft by means of the slide.
  • the design of the controlling mechanism provides a mechanical feedback of the radial motion of the rotor, in relation to the shaft axis, with the rotary motion of the rotor (together with its shaft) around the shaft axis. It means that each position of the rotor, in its rotary motion, corresponds with specific position of the rotor in its radial motion on the shaft cubicoid, and vice versa.
  • the ends of the rotor arm move along the internal wall of the cylinder but do not exert a pressure on the wall (from inertia of the rotor mass); a contact of the rotor with the internal wall of the cylinder hole is needed to achieve compression in both chambers of the cylinder (at both sides of the rotor), and it is tealized by sealing-lubricating members.
  • the supply system feeds both chambers of the cylinder with fuel and air at appropriate phase of engine operation.
  • Widely known schemes generally employed in piston engines can be adapted to the supply system, taking into consideration kind of fuel and type of engine (compression ratio, supercharging, carburettor, injection, etc.).
  • the supply system comprises channels made in the cylinder body and/or heads, these channels being closed with valves.
  • Valve drive can be transmitted mechanically from the engine shaft, or electronically- controlled electromagnetic drive may be designed for the valves.
  • the exhaust system is used to remove exhaust gas from the chamber of the engine; similarly to the supply system, the exhaust system comprises channels closed with valves.
  • One supply system and one exhaust system serve for both chambers of the single cylinder.
  • the ignition system depending on the engine type, various types can be used, based on known systems used in four-stroke piston engines.
  • the lubrication system provides continuous lubrication for friction parts in the engine.
  • the way in which the rotor co-operates with the shaft allows to use the working mechanism as a pump to force oil circulation in the lubrication system.
  • the rotor sealing is effected by means of sealing members joined with the rotor to separate and seal both chambers of the cylinder closed with heads.
  • the sealing members constituting sealing/lubricating components and connected with forced oil circulation system, provide lubrication to the internal surfaces of the cylinder and heads.
  • the cooling system well known designs are used, such as air flow and/or closed liquid circulation; however; required cooling intensity is much smaller compared with piston engines because the course of the thermodynamic process allows to achieve much higher efficiency at a cost of smaller heat losses.
  • a cyclic change of volume takes place in both cylinder chambers, and the work cycle of a single-cylinder engine is similar to the work cycle of a double-cylinder four-stroke piston engine during the rotor-shaft rotary motion.
  • the work phase ignition is effected with advance to the angle f 2 , and the work phase commences when the rotor is in the position corresponding with the angle f 2 , just before reaching the V min .
  • the pressure of the gas (exhaust gas), p(f) acts against the arm of the rotor and, starting from the position for the angle f 2 , the rotor acts with the moment of a positive force against the shaft, according to the engine geometry.
  • the volume of the cylinder chamber changes from V f2 to V, ⁇ (i.e.
  • valves open and close the holes of the suction and exhaust channels according to the phase of the given chamber of the cylinder.
  • the engine according to the invention as compared with engines in common use, has many essential advantages, such as: one cylinder has two chambers; the rotor turns the shaft directly and the main working motion of the rotor is the rotary motion; the rotor-shaft unit can be used as a pump to force an oil flow in the lubrication system; the rotor does not exert pressure onto the wall of the cylinder hole and no excessive friction occurs; and the most important advantage is high overall (effective) efficiency of the engine.
  • Effective (total) efficiencv of the engine according to the invention varies from 48% to 64%, i.e. it is nearly twice as high as efficiency of engines currently in use, and it depends on the thermodynamic process resulting from the geometry of -_ t -_
  • the most important factor determining the level of efficiency is the course of the curve of the exhaust gas pressure force moment, M(f), acting against the shaft axis during the work phase.
  • M(f) 2p(f) RRx 2 a sin f for fe ⁇ - ⁇ /6; ⁇ >, where: p(f) is an equation of the gas pressure for fe ( - ⁇ /6; ⁇ ).
  • the coefficient: (1.6 ⁇ 2.0), for engines of a high compression ratio with a pressure ignition is to be assumed from the lower limit 1,6, and greater values up to 2.0 are to be taken for engines of a low pressure ratio with spark ignition.
  • toothed ring (bevel crown gear) (2 pcs)
  • Fig. l assembly drawing: the engine according to the invention is shown in
  • Fig.2 the section in the plane perpendicular to the engine shaft axis shows the closed plane curve r(f), this curve forming the contour of the cylinder hole wall,
  • Fig.3 the section in the plane perpendicular to the engine shaft axis ( marked BB in the Fig.1) shows the guiding shaft.
  • Sheet 3/4 the section in the plane perpendicular to the engine shaft axis ( marked BB in the Fig.1) shows the guiding shaft.
  • Fig.4 rotor - the view: projection on the plane perpendicular to the shaft axis shows the rotor in the cylinder, where point O ⁇ coincides with point O; besides, the contour of the rotor side wall is shown as curve r ⁇ (f).
  • the invention is shown in the Figure 1, Figure 2 and Figure 3, as an exemplary design of a single-cylinder two-chamber rotary engine.
  • the cylinder 1, having the cylinder hole of a shape determined by the r(f) curve, is rigidly connected with two heads 2.
  • the shaft 3 is journalled in the holes of both heads 2, and its axis is in line with the axis of the cylinder 1.
  • the rotor 4 is seated on the cubicoidal member of said shaft 3, inside the cylinder 1, and divides said cylinder 1 into two chambers tightly separated.
  • the slide 5 is rigidly mounted in the rectangular port of said rotor 4, and protrudes through the along-axis-opening of said shaft 3.
  • two guiding shafts 7 In both transverse openings of the shaft 3 (at its both ends) there are supported two guiding shafts 7 (their axes are parallel each other), being a type of crankshafts.
  • cranks of said shafts 7 are connected with the connecting-rod 6 protruding through the opening of said slide 5, and its axis is always parallel to the axis of the shaft 3.
  • At the opposite ends of the shafts 7, there are installed rigidly two bevel gears 8 operating with two toothed rings 9 installed rigidly on both heads 2 whereby constituting two rectangular bevel gear transmissions of a transmission ratio i 1 each.
  • the supply and exhaust systems in the exemplary design (as one of the most optimal designs) have two suction and two exhaust channels made in the body of said cylinder 1, these channels being closed with suction valve 10 and exhaust valve 11. These valves are the slidable, and they open and/or close the channels at appropriate phases of the cycle to supply both chambers of the cylinder 1 and/or remove exhaust gas.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Supercharger (AREA)

Abstract

Le moteur rotatif de la présente invention fonctionne selon un cycle de travail à quatre phases et, de par sa géométrie, atteint un rendement se situant, suivant le type, dans une plage variant entre 48 % et 64 %. Le cylindre a un trou de forme cylindrique, ce trou étant solidement fermé en ses deux extrémités par deux têtes plates (2). La section du trou du cylindre (1) est une courbe plane fermée se définissant par l'équation à coordonnées polaires selon laquelle on a (r, f): r(f) = R1 + aR1sin f pour: f⊂∫0; 2Π⊃ avec R1 > 0 et 0 < a ≤ 0,5. L'arbre (3), qui croise le trou du cylindre (1), est supporté dans les trous des deux têtes (2), et son axe est aligné sur l'axe du trou de cylindre (1) considéré. La section de l'arbre (3) entre les têtes (2), c'est-à-dire à l'intérieur du cylindre considéré (1), est de section rectangulaire et de forme cubicoïde. Le rotor (4) installé dans le cylindre considéré (1), se présentant sous la forme d'un bras, divise intérieurement le cylindre (1) en deux chambres hermétiques l'une par rapport à l'autre. La forme de la paroi intérieure du rotor considéré (4) est définie dans sa section par la ligne brisée plane définie par la fonction (r1, f): en coordonnées polaires. Ce moteur permet d'atteindre un rendement bien plus élevé que les moteurs à piston en raison de la course du moment de force de la pression des gaz s'exerçant contre l'arbre (3) pendant la phase de travail, et ce, en raison de la géométrie et du processus thermodynamique du moteur.
PCT/PL1998/000028 1997-06-16 1998-06-16 Moteur rotatif WO1998058167A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU76791/98A AU7679198A (en) 1997-06-16 1998-06-16 Rotary engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PL320581A PL191001B1 (pl) 1997-06-16 1997-06-16 Silnik spalinowy, obrotowy
PLP.320581 1997-06-16

Publications (1)

Publication Number Publication Date
WO1998058167A1 true WO1998058167A1 (fr) 1998-12-23

Family

ID=20070101

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/PL1998/000028 WO1998058167A1 (fr) 1997-06-16 1998-06-16 Moteur rotatif

Country Status (3)

Country Link
AU (1) AU7679198A (fr)
PL (1) PL191001B1 (fr)
WO (1) WO1998058167A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GR1005163B (el) * 2005-04-12 2006-03-21 Ιωαννης Κανελλοπουλος Περιστροφικος μηχανισμος θετικης εκτοπισης ρευστων
RU2689659C1 (ru) * 2018-01-16 2019-05-28 Михаил Сергеевич Кудряшов Роторный двигатель

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU740129B2 (en) * 1994-12-23 2001-11-01 Anton H. Clemens Catheter placement system providing retraction of the sharp upon disengagement of the catheter from the handle

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3690791A (en) * 1970-02-10 1972-09-12 Robert L Dieter Rotary engine with radially shiftable rotor
US4300874A (en) * 1978-06-12 1981-11-17 Capella Inc. Rotary machine with lenticular rotor and a circular guide member therefor
US4967707A (en) * 1988-07-14 1990-11-06 Rogant H R Rotary engine
DE19514531A1 (de) * 1995-04-20 1996-10-24 Hassan Mohamed Soliman Drehkolbenmaschine
DE19628867A1 (de) * 1996-07-17 1998-01-22 Manfred Buesselmann Rotationsläufer-Motor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3690791A (en) * 1970-02-10 1972-09-12 Robert L Dieter Rotary engine with radially shiftable rotor
US4300874A (en) * 1978-06-12 1981-11-17 Capella Inc. Rotary machine with lenticular rotor and a circular guide member therefor
US4967707A (en) * 1988-07-14 1990-11-06 Rogant H R Rotary engine
DE19514531A1 (de) * 1995-04-20 1996-10-24 Hassan Mohamed Soliman Drehkolbenmaschine
DE19628867A1 (de) * 1996-07-17 1998-01-22 Manfred Buesselmann Rotationsläufer-Motor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GR1005163B (el) * 2005-04-12 2006-03-21 Ιωαννης Κανελλοπουλος Περιστροφικος μηχανισμος θετικης εκτοπισης ρευστων
RU2689659C1 (ru) * 2018-01-16 2019-05-28 Михаил Сергеевич Кудряшов Роторный двигатель

Also Published As

Publication number Publication date
PL320581A1 (en) 1998-12-21
PL191001B1 (pl) 2006-02-28
AU7679198A (en) 1999-01-04

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