US3760777A - Rotary-piston engine - Google Patents

Rotary-piston engine Download PDF

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Publication number
US3760777A
US3760777A US00271393A US3760777DA US3760777A US 3760777 A US3760777 A US 3760777A US 00271393 A US00271393 A US 00271393A US 3760777D A US3760777D A US 3760777DA US 3760777 A US3760777 A US 3760777A
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Prior art keywords
rotor
stator
eccentric
track
center
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Expired - Lifetime
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US00271393A
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English (en)
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M Leroy
A Thiebaut
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    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/104—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger

Definitions

  • ABSTRACT Primary ExaminerCarlton R. Croyle Assistant Examiner-Louis T. Casaregoh Attorney--Camer0n, Kerkam, Sutton, Stowell and Stowell [5 7] ABSTRACT
  • the engine comprises a four-lobe cavity and a rotor having three heads which are each maintained in contact with the stator so as to define three variablevolumc chambers between the internal surface of the stator and the external surface of the rotor.
  • An oval-shaped eccentric is rigidly fixed to an output shaft havingan axis which coincides with the center of the stator and is continuously applied at three points in tangential contact with a closed track having theshape of a curvilinear triangle.
  • This invention relates to the technique of rotarypiston engines and more specifically engines of the type comprising a stator having a four-lobe cavity and a rotor with three heads which is capable of moving within said'cavity in such a manner as to define three variable-volume work chambers which are delimited by the internal surface of the stator and the external surface of the rotor.
  • An engine of this type is naturally provided in addition with conventional means for admitting a gas into these chambers, for initiating the combustion process and discharging gases after combustion and expansion.
  • the essential aim of the present invention is to overcome these disadvantages while retaining the advantages of rotary-piston engines of the typehereinabove defined.
  • the invention proposes a rotary-piston engine comprising a stator which defines a cavity having four identical lobes and a rotor which is capable of motion within said cavity and has three identical heads such that each head remains in contact with the stator so as to define three chambers having a variable volume between the internal surface of the stator and the external surface of the rotor, characterized in that the rotor has a closed track in the shape of a curvilinear triangle which contains the center of the rotor and the sides of which are parallel to those of the curve described by the trace of the stator on the rotor.
  • said engine comprises aneccentric rigidly fixed to an output shaft having an axis which coincides with said center of the stator and driven by said rotor track, said eccentric being of oval shape in order that it should always remain in tangential contact with said track at three points.
  • the eccentric comprises two symmetrical rollers which bear on said track and the axis of one roller coincides with the center of the stator.
  • at least one first curvilinear square roller rotates about the crank-pin of the eccentric with an external surface which slides continuously over a central zone of the rotor track
  • at least one second curvilinear square roller' is stationary and concentric with the stator with an external surface which continuously slides over a peripheral zone of the rotor track, said peripheral zone being adjacent to said central zone.
  • the displacements of the rotor are controlled by means of the eccentric which is in cooperating relation with the rotor track. It is thus possible to ensure uniform trans mission of rotational motion to the output shaft and to prevent abrupt impacts of the rotor against the stator. At zero velocity, the heads of the rotor reach their center of rotation.
  • a further advantage lies in the fact that the track can be formed by a hollowed portion having a cross-section in the shape of a curvilinear triangle and formed through the rotor, said hollowed portion being intended to provide a passageway for the output shaft or for an element associated with said shaft.
  • the engine comprises two similar stator and rotor assemblies, the rotors being connected by means of a common shaft which passes through these latter and is rigidly fixed to the corresponding eccentrics.
  • Transfer ducts are advantageously provided for connecting the intake ports for the admission of gas into the stator cavityof a first assembly to exhaust ports for discharging gas from the stator cavity of the second assembly so that this latter accordingly constitutes a gassuction unit for supplying the first assembly which constitutes the driving unit.
  • FIG. 1 illustrates diagrammatically a rotary-piston engine in accordance with the invention and as designed for operation in a four-stroke cycle and shows in particular different positions of the eccentric with respect to the rotor;
  • FIGS. 2 to 7 show diagrammatically different successive positions of the rotor within the stator in order to illustrate the operation of the engine
  • FIG. 8 is a partial transverse sectional view of an alternative embodiment of the engine in accordance with the invention, in which provision is made for two stator and rotor assemblies;
  • FIG. 9 is a transverse sectional view of the three essential elements of the engine according to FIG. 8 together with the system of connections between the two assemblies;
  • FIG. 10 shows the outline of the eccentric of the engine of FIG. 1;
  • FIGS. 11 and 12 are diagrammatic views of an alternative embodiment of the invention.
  • FIG. 13 is a view in sectional elevation showing a preferred embodiment of the rotary-piston engine in accordance with the invention.
  • the rotary-piston engine which is illustrated in FIG. 1 is essentially made up of a fixed stator l and a rotor 2 which is capable of motion inside a cavity-formed within the stator.
  • the stator 1 possesses symmetry of revolution of quaternary order about the fixed center C, the stator cavity being designed to form four identical lobes such as the lobe la.
  • the rotor 2 possesses symmetry of revolution of ternary order and forms three identical heads such as the head 2a which are adapted to come into position successively within each lobe of the stator.
  • the internal outline of the stator and the external outline of the rotor are so determined that at least two heads remain continuously in contact with the stator wall.
  • Three chambers, the volume of which varies during the displacements of the rotor, are thus defined between the internal surface of the stator and the external surface of the rotor.
  • the shapes adopted respectively for the lobes 1a of the stator 1 and for the heads 2a of the rotor 2 determine within the stator four lobe centers 11, 12, 13 and 14 each corresponding to an instantaneous center of rotation for the rotor head 2a which is present therein.
  • the outline of the lateral faces of the stator lobes corresponds to circular arcs which are centered at these points.
  • the rotor heads are each limited by two circular arcs centered at a point such as 21 which, when the head is located at the bottom of a lobe, coincides with the center 11, 12, 13 or 14 of said lobe these two circular arcs meet at a point which is fitted with packing seals and maintains a contact with the stator wall at the level of the cusp between the faces of two adjacent lobes.
  • FIGS. 2 to 7 illustrate the successive positions of the rotor.
  • FIG. 2 there begins the admission of gas into one of the chambers (on the right-hand side of the figure) up to the position illustrated in FIG. 3.
  • the gas is then transferred to the top portion of the stator cavity up to the position illustrated in FIG. 4, whereupon the compression of this gas begins to take place.
  • FIG. 5 the compression has been completed and ignition takes place. Expansion of the gases forces the rotor to the position illustrated in FIG. 6. Discharge of the burned gases begins in the position of FIG. 6 and continues in the position of FIG. 7 until the rotor returns to the position which was already illustrated in FIG. 3.
  • FIGS. 2 to 7 shows how the displacements of the rotor consist of a series of successive pivotal movements in which the centers of rotation employed are the centers of the stator lobes 14 (FIG. 2), 13 (FIG. 3), 12 (FIG. 4), and 11 (FIG.
  • the centers of rotation employed are the centers of the stator lobes 14 (FIG. 2), 13 (FIG. 3), 12 (FIG. 4), and 11 (FIG.
  • the work chamber which is limited by a predetermined face of the rotor therefore makes use in alternate succession of the ignition produced by each spark plug 31 and 32.
  • Each of the three work chambers is subjected to the one chamber to the other.
  • the admission or induction takes place on the right-hand side in FIG. 2 on a first face of the rotor, on the left-hand side in FIG. 4 on a second face and on the right-hand side in FIG. 6 on the third face.
  • the eccentric 40 is located within the interior of a hollowed portion at the center of the rotor 2 limited by a track 41 having the shape of a curvilinear triangle.
  • the eccentric 40 (shown in FIG. 1) has an oval shape in order that three points 44a, 44b and 44c of said eccentric should be continuously maintained in tangential contact with the track 41.
  • the eccentric 40 is partially limited at the two opposite extremities by two symmetrical rollers 42 and 43, the roller 42 having its axis at the center C and the roller 43 having its axis at a center M.
  • the sides of the eccentric can also be fitted with elements such as roller-bearings or ball-bearings.
  • the stator is provided, for example, with two reaction wheels 44 and 45 which are placed opposite to the two spark plugs.
  • the outline of the track 41 is defined on the basis of a parent track 46 formed by three equal circular arcs having as centers the three rotor-head centers such as 21 and representing the curve described on the rotor by the center C of the stator during the different movements of the rotor.
  • the sides of the curvilinear triangle which define the track 41 are parallel to these three circular arcs and located externally of the parent track 46 at a distance which is equal to the radius of the roller 42.
  • the shape of the eccentric 40 is determined by the shape of the track 41.
  • the distance be tween the centers of the two identical rollers 42 and 43 is equal to the height of the curvilinear triangles which form the parent track 46.
  • the sides of the eccentric are of convex shape in order that this latter may be perm itted to relay the rollers 42 and 43 in providing a bearing point on the track 41.
  • the eccentric unit as a whole is always in tangential contact with said track at three points.
  • the outline of the oval-shaped envelope of the eccentric 40 is determined by two sets of concave curves 65-66 and 67-68 which are symmetrical and opposite in pairs and joined tangentially to each other.
  • the two curves 65 and 66 correspond to the circumference of each roller 42 and 43 with respective centers C and M and a radius equal to the distance between each side of the parent track 46 which is parallel to the track 41 (shown in FIG. 1).
  • the second set of curves 67 and 68 represents the loci of the successive points of contact (44a to 44b, as shown in FIG. 1) between the track 41 of the rotor 2 and the envelope of the eccentric 40 at the time of their respective displacements.
  • FIG. 1 shows in chain-dottedlines three successive positions of the rotor heads, of the track 41 and of the eccentric 40 as these latter rotate about the center C during a pivotal movement of the rotor about the cen-
  • the engine comprises two stator and rotor assemblies 50 and'51 which are similar to the assembly the assembly 51 and in the assembly 50 for a gas-intake port and an exhaust port on each of the four faces of the stator. I g
  • the different exhaust ports of the assembly51 are connected respectively to the different intake ports of the assembly 50 by means of transfer ducts 54 in the manner which is illustrated in FIG. 9.
  • the assembly 50 constitutes a driving unit for effecting the rotation of the output shaft and, at the same time, the assembly 51 which is driven by the output shaft can serve as a gas-suction unit for supplying the driving unit.
  • each phase of reduction in volume .of a work chamber of the assembly 51 no longer produces compression but causes transfer of gas towards one of the chambers of the assembly 50, whereupon the gas subsequently undergoes the different phases of compression, ignition, expansion and exhaust within the assembly 50.
  • valves such as the valves 55 and 56 in the driving assembly 50 serve to open or close re- (shown in FIG. 13) in the'case just mentioned, the eccentric 40 of FIG. 1 is double (40a and 40b) and arranged on each sideof the rotor 2.
  • the axis of revolution of the shaft 3 of the crankshaft unit 142 coincides with the center C of the stator 1 (FIG. 1).
  • the journals 3a and 3b of the shaft 3 are joined to the crank-pin 143 by means of two crankarms which form eccentrics 40a, 40b.
  • the journals 3a and 3b are rotatably mounted in bearings 4a and 4b and the crank-pin 143 serves as a spindle for a square roller 5 having curvilinear faces or sides.
  • the periphery of spectively the gas-intake ports and the gas-exhaust ports are controlled by a system of tappets and rockerarms which are displaced by a distributor 57 rigidly fixed to the output shaft 53 during the rotation of this latter.
  • a gas distributor 58 is mounted against the stator 51b of the assembly 51. Said distributor is provided with ducts 59 which are located opposite to the ducts 60 for admitting gas into the assembly 51 and, on the other hand, with an annular passageway 61 which is continuously supplied with gas and is provided with openings opposite to the ducts 59. However, said openingsare closed-off by a rotary disc 62.
  • Said disc has a slot 63 which periodically establishes a communication between the ducts 59 and the passageway 61 during the time which is necessary for the admission each eccentric 40, 40a retains three points of contact with the track 41 of the rotor 2.
  • the roller 5 is in contact with the internal track 41 either by means of one side 5a (as shownin FIG.'11) or by means of two sides 5a and 5b (as shown in FIG. 12), depending on the relative positions of the crankshaft unit and of the track just mentioned.
  • the curvilinear square profile of a roller of the type designated by the reference 5 has the advantage of distributing the radial loads over a surface, namely the surfaces of one or two sides of the roller whereas, in the case of a roller 42 or 43 of circular shape, the radial load was applied at single points.
  • At least one square roller 6 (shown in FIG. 1 l) or 6a (shown in FIG. 13) having curvilinear sides is fixed-concentrically with the axis C on one radial face 7a of the stator (as shown in FIGS. 11 and 13), thediagonal axes of said roller 6 being displaced by 45 with respect to'the diagonal axes of the roller 5. Since the crankshaft unit 142 is symmetrical, it is an advantage to fix a second roller 6b which is identical with the first on the other radial face 7b of the stator.
  • the two rollers 5 and 6 have the same orientation with respect to the axis C and bear on the peripheral zones of the rotor 2, namely the zones adjacent to the central zone against which the roller 5 is applied.
  • the eccentric or eccentrics 40a and 40b continue to guide the movements of the rotor 2 and the radial loads are transferred and distributed over the curvilinear sides of. the rollers 5 and 6a, 6b.
  • a rotary-piston engine comprising a stator which defines a cavity having four identical lobes and a rotor which is capable of motion within said cavity and has three identical heads such as each head remains in contact with the stator so as to define three chambers having a variable volume between the internal surface of the stator and the external surface of the rotor, wherein the rotor has a closed track in the shape of a curvilinear triangle which contains the center of the rotor and the sides of which are parallel to those of the curve described by the center of thestator on the rotor during the displacements of said rotor, and wherein said engine comprises an eccentric rigidly fixed to an output shaft having an axis which coincides with said center of the stator and driven by said rotor track, said eccentric being of oval shape in order that it should always remain in tangential contact with said track at three points.
  • said eccentric comprises at least one curvilinear square roller which is rotatably mounted on the crank-pin of the eccentric and the external surface of which slides continuously over a central zone of the rotor track, at least one second curvilinear square roller which is stationary and concentric with the center of the stator and the external surface of which slides continuously over a peripheral zone of the rotor track, said peripheral zone being adjacent to said central zone.
  • curvilinear square rollers are oriented with respect to the rotor track in such manner that the respective diagonal axes thereof are relatively displaced by an angle of 45.
  • An engine according to claim l wherein said engine comprises two similar stator and rotor assemblies, the rotors being connected by means of a common shaft which passes therethrough and is rigidly fixed to the corresponding eccentrics.
  • engine according to claim 1 wherein said engine comprises transfer ducts which connect the intake ports for the admission of gas into the stator cavity of a first assembly aforesaid to exhaust ports for discharging gas from the stator cavity of the second assembly aforesaid so that said second assembly constitutes a gas-suction unit for supplying said first assembly which constitutes the driving unit.
  • An eccentric provided in particular for an engine according to claim 1, wherein said eccentric has an oval-shaped envelopedelimited by the junction of two sets of two concave curves which are symmetrical and opposite in pairs, the first set of curves having two centers, namely a center C of rotation of the eccentric and a center M of the crank-pin, the second set of curves being such as to represent the loci of the successive points of contact between the rotor track and said envelope.
US00271393A 1971-07-16 1972-07-13 Rotary-piston engine Expired - Lifetime US3760777A (en)

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FR7126132A FR2146526A5 (cs) 1971-07-16 1971-07-16

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US (1) US3760777A (cs)
AT (1) ATA609072A (cs)
BE (1) BE786347A (cs)
CA (1) CA963810A (cs)
CH (1) CH560319A5 (cs)
CS (1) CS158731B2 (cs)
DD (1) DD98336A5 (cs)
DE (1) DE2234781A1 (cs)
ES (1) ES404934A1 (cs)
FR (1) FR2146526A5 (cs)
GB (1) GB1394095A (cs)
IT (1) IT964686B (cs)
NL (1) NL7209878A (cs)
PL (1) PL84796B1 (cs)
SE (1) SE386478B (cs)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3922120A (en) * 1973-07-30 1975-11-25 Charles M Mccullough Rotary engines
US3967594A (en) * 1975-01-27 1976-07-06 Campbell Donald K Rotary power unit
US5373819A (en) * 1992-03-05 1994-12-20 Linder; Rene Rotary piston machine and method of manufacturing piston
WO2004007965A1 (en) * 2002-07-17 2004-01-22 Elthom Enterprises Limited Rotary screw machine end method of transforming a motion in such a machine
US20060032475A1 (en) * 2003-02-27 2006-02-16 Boris Schapiro Rotary piston machine with an oval rotary piston guided in an oval chamber
EP2322760A1 (en) * 2008-08-01 2011-05-18 Da Vinci Co., Ltd. Wankel rotary engine
US8667950B1 (en) * 2013-02-11 2014-03-11 Thomas Lee Fillios, Sr. Oil-less rotary engine
US20140209056A1 (en) * 2013-01-25 2014-07-31 Liquidpiston, Inc. Air-Cooled Rotary Engine
US9523310B2 (en) 2004-01-12 2016-12-20 Liquidpiston, Inc. Hybrid cycle combustion engine and methods
DE102013017359B4 (de) * 2013-10-18 2020-10-15 Peter Gehrke Drehscheibenkraftmaschine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51140010A (en) * 1975-05-28 1976-12-02 Fukumatsu Okada Rotor and side board of rotary engine
FR2567572B1 (fr) * 1984-07-13 1988-09-09 Chouffot Claude Moteur rotatif a piston triangulaire et cylindre a 4 faces
KR102282775B1 (ko) * 2017-05-22 2021-07-28 엘지전자 주식회사 로터리 엔진

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE103413C (cs) *
US3221715A (en) * 1961-03-09 1965-12-07 Romoli Mario Rotary internal combustion engine
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3426525A (en) * 1967-08-10 1969-02-11 Gotthard G Rubin Rotary piston external combustion engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE103413C (cs) *
US3221715A (en) * 1961-03-09 1965-12-07 Romoli Mario Rotary internal combustion engine
US3364907A (en) * 1965-04-27 1968-01-23 Ronald J St Onge Rotary piston mechanism
US3426525A (en) * 1967-08-10 1969-02-11 Gotthard G Rubin Rotary piston external combustion engine

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3922120A (en) * 1973-07-30 1975-11-25 Charles M Mccullough Rotary engines
US3967594A (en) * 1975-01-27 1976-07-06 Campbell Donald K Rotary power unit
US5373819A (en) * 1992-03-05 1994-12-20 Linder; Rene Rotary piston machine and method of manufacturing piston
WO2004007965A1 (en) * 2002-07-17 2004-01-22 Elthom Enterprises Limited Rotary screw machine end method of transforming a motion in such a machine
US20060018779A1 (en) * 2002-07-17 2006-01-26 Alexander Gorban Method of transforming a motion in a volume screw machine of rotary type and rotary screw machine
US7540728B2 (en) 2002-07-17 2009-06-02 Elthom Enterprises Limited Method of transforming a motion in a volume screw machine of rotary type and rotary screw machine
US20060032475A1 (en) * 2003-02-27 2006-02-16 Boris Schapiro Rotary piston machine with an oval rotary piston guided in an oval chamber
US7117840B2 (en) * 2003-02-27 2006-10-10 Boris Schapiro Rotary piston machine with an oval rotary piston guided in an oval chamber
US20070089701A1 (en) * 2003-02-27 2007-04-26 Boris Schapiro Rotary piston machine with an oval rotary piston
US7866296B2 (en) 2003-02-27 2011-01-11 Rkm-Rotationskolbenmaschinen Gbr Rotary piston machine with an oval rotary piston
US9523310B2 (en) 2004-01-12 2016-12-20 Liquidpiston, Inc. Hybrid cycle combustion engine and methods
EP2322760A1 (en) * 2008-08-01 2011-05-18 Da Vinci Co., Ltd. Wankel rotary engine
EP2322760A4 (en) * 2008-08-01 2012-03-21 Da Vinci Co Ltd WANKEL MOTOR
US20110126794A1 (en) * 2008-08-01 2011-06-02 Da Vinci Co., Ltd. Wankel rotary engine
US20140209056A1 (en) * 2013-01-25 2014-07-31 Liquidpiston, Inc. Air-Cooled Rotary Engine
CN105008666A (zh) * 2013-01-25 2015-10-28 液体活塞公司 空气冷却式转子发动机
US9528435B2 (en) * 2013-01-25 2016-12-27 Liquidpiston, Inc. Air-cooled rotary engine
RU2662031C2 (ru) * 2013-01-25 2018-07-23 Ликвидпистон, Инк. Роторный двигатель с воздушным охлаждением
US10125675B2 (en) 2013-01-25 2018-11-13 Liquidpiston, Inc. Internal combustion engine
US8667950B1 (en) * 2013-02-11 2014-03-11 Thomas Lee Fillios, Sr. Oil-less rotary engine
DE102013017359B4 (de) * 2013-10-18 2020-10-15 Peter Gehrke Drehscheibenkraftmaschine

Also Published As

Publication number Publication date
DE2234781A1 (de) 1973-02-08
CS158731B2 (cs) 1974-11-25
CH560319A5 (cs) 1975-03-27
IT964686B (it) 1974-01-31
SE386478B (sv) 1976-08-09
NL7209878A (cs) 1973-01-18
DD98336A5 (cs) 1973-06-12
BE786347A (fr) 1972-11-16
PL84796B1 (cs) 1976-04-30
GB1394095A (en) 1975-05-14
FR2146526A5 (cs) 1973-03-02
CA963810A (en) 1975-03-04
ATA609072A (de) 1980-01-15
ES404934A1 (es) 1975-06-16

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