US3896772A

US3896772A - Overlapping swinging plate internal combustion engine

Info

Publication number: US3896772A
Application number: US391138A
Authority: US
Inventors: Samuel P Lyle
Original assignee: Individual
Current assignee: Individual
Priority date: 1973-08-24
Filing date: 1973-08-24
Publication date: 1975-07-29
Anticipated expiration: 1992-07-29

Abstract

An engine including a stationary cylindrical case member provided with a circular chamber, an intake manifold for delivering fuel and air mixture to the chamber, a shaft disposed concentrically of the chamber and being journaled to the case member, and a hub attached to the shaft. Also included are a plurality of overlappingly arranged plates for separating the chamber into a plurality of variable volume combustion cells. The plates are individually swingably attached to the case member establishing free swinging ends thereto. Guide structure is included for coupling each of the free swinging ends of the plates to the hub and for guidingly constraining the free ends of the plates. The plurality of plates are caused to oscillate about their respective swinging axes by internal combustion cycles of the combustion cells occurring in rotational sequence at predetermined periods respectively to collectively impart a constant rotary force to the shaft. The principal embodiment includes an elliptical shaped hub while an alternate embodiment discloses a cylindrical shaped hub.

Description

1 July 29, 1975 United States Patent [191 Lyle 1 1 ABSTRACT An engine including a stationary cylindrical case member provided with a circular chamber, an intake OVERLAPPING SWINGING PLATE INTERNAL COMBUSTION ENGINE [76] lnventor: Samuel P. Lyle, 218 Spring St.,

Huntingdon, Tenn. 38344 manifold for delivering fuel and air mixture to the Aug. 24, 1973 Appl. No.: 391,138

chamber, a shaft disposed concentrically of the cham- [22] Filed:

ber and being journaled to the case member, and a hub attached to the shaft. Also included are a plurality of overlappingly arranged plates for separating the chamber into a plurality of variable volume combus- [52] U.S. 123/847; 418/61 R; 418/62; 418/245 F02b 53/00 [51] Int.

[58] Field of Search................ 123/845 each of the free swinging ends of the plates to the hub and for guidingly constraining the free ends of the References Cited plates. The plurality of plates are caused to oscillate UNITED STATES PATENTS about their respective swinging axes by internal combustion cycles of the combustion cells occurring in rotational sequence at predetermined periods respectively to collectively impart a constant rotary force to the shaft. The principal embodiment includes an ellip- 123/845 XXX 272 M 8H8 1. 1 4 4 S N muw WQ m mm "M MWH Mam M a NR mwm S S JMT T A P N m E R O F 1,305,451 6/1919 Evans....... 1,841,841 1/1932 tical shaped hub while an alternate embodiment discloses a cylindrical shaped hub.

Primary ExaminerC. J. l-lusar Assistant ExaminerMichael Koczo, Jr. 17 Claims, 18 Drawing Figures Attorney, Agent, or Firm-John R. Walker, 111

SHEET FIG. I

PATENTED JUL 2 9 I975 PATENTED JUL 2 9 I975 SHEET PATENTEUJULZQISYS 3, 896.772

SHEET 3 Fig. 6

FIG. 7 FIG FIG. 9

ssss x rs a w g 77 l\ 75 PATENTED JUL 2 9 I975 nr-- L. Sum

SHEET OVERLAPPING SWINGING PLATE INTERNAL COMBUSTION ENGINE BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to the field of internal combustion engines, particularly engines having overlapping swinging plates.

SUMMARY OF THE INVENTION The concept of the present invention is to provide an internal combustion engine which includes a stationary cylindrical case member provided with a circular, chamber, an intake manifold for delivering fuel to the chamber, a shaft disposed concentrically of the chamber and being journaled to the case member, and a hub attached to the shaft for imparting rotary motion thereto. The engine herein disclosed includes a plurality of overlappingly arranged plates for separating the chamber into a plurality of variable combustion cells. Each of the plates are swingably attached to the case member thus establishing a free swinging end thereof. The free swinging ends of the plates are coupled to the hub and are guidignly constrained so they oscillate towards and away from the shaft as it rotates. Structure is also included for providing internal combustion cycles of the combustion cells in rotational sequence to cause oscillation of the plurality of plates about their respective swinging axes to collectively impart a continuous rotary force to the shaft. The principal embodiment includes an elliptical shaped hub which is keyed to a straight shaft while an alternate embodiment discloses a cylindrical shaped hub which is rotatably attached to an offset crank portion of the shaft.

DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of the assembled engine of the present invention with the view being taken as on a vertical plane through the center line of the engine, the rotating shaft and upper and lower oscillating plates being nonsectioned for purposes of clarity.

FIG. 2 is a front elevational view of one of the several oscillating plates, the plate being removed from the engme.

FIG. 3 is a side elevational veiw of the plate depicted in FIG. 2 showing the geometry of the layout to disclose the spiral construction of the concave face thereof.

FIG. 4 is a sectional view taken as on the line IV-IV of FIG. 1.

FIG. 5 is an enlarged partial view of the upper portion of FIG. 4.

FIG. 6 is a side elevational view of the hub assembly as it would appear when removed from the engine looking along the rotating axis thereof, a portion thereof being broken away to better illustrate another portion thereof.

FIG. 7 is a sectional view taken as on the line VII- VII of FIG. 6.

FIG. 8 is a sectional view taken as on the line VIII- VIII of FIG. 6.

FIG. 9 is a view similar to FIG. 3 showing the preferred geometry of the layout for an alternate length of the oscillating plate.

FIG. 10 is a view similar to FIG. 1 but showing an alternate embodiment of the engine herein disclosed.

FIG. 11 diagrammatically depicts the engine as shown in FIG. 10 in conjunction with air compressor structure plus a fuel distribution system with the view being taken at a first instant of time.

FIG. 12 is a view very similar to FIG. 11 with the view being taken at a second instant of time.

FIG. 13 is a sectional view taken as on the line XIII- -XIII of FIG. 10.

FIG. 14 is a side elevational view of the alternate embodiment of the intake disc.

FIG. 15 is a side elevational view of the alternate embodiment of the exhaust disc.

FIG. 16 is a side elevational view of both of the discs as shown in FIGS. l4, 15 looking along the rotation axes thereof to depict the preferred timing relationship of one disc with the other end of both discs with respect to the offset crank portion of the shaft.

FIG. 17 shows another embodiment of a shaft for the engine depicted in FIG. 10-16 with the view being taken on the vertical centerline and showing an eccentric mid-portion of the shaft engaging a circular hub.

FIG. 18 is a sectional view taken as on the line XVIII- -XVIII of FIG. 17 more clearly showing the eccentric mid portion of the shaft engaging the circular hub.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The internal combustion engine 11 of the present invention generally includes a stationary cylindrical case member 13 (FIGS. 1,4) provided with a circular chamber 15 (FIG. 4), intake manifold means 17 (FIG. 1) for delivering fuel to the chamber 15, a shaft 19 disposed concentrically of the chamber 15 and being journaled to the case member 13, and a rotor or hub means 21 attached to the shaft 19, as by key 20, for imparting rotary motion to the shaft 19. Also included are a plurality of overlappingly arranged plate means 23 which are individually designated as 23a, 23b, 230, etc., for separating the chamber 15 into a plurality of variable volume combustion cells 25 which are individually designated as 25a, 25b, 250, etc. A plurality of hinge means 27 which are individually designated 27a, 27b, 27c, etc., are included for swingably attaching one end of each of the plate means 23 to the case member 13 establishing a free swinging end, as at 29 (FIG. 5), for each of the plate means 23. Also included are guide means 31 (FIG. 5) for coupling each of the plate means 23 to the hub means 21 and for guidingly constraining the free ends 29 of each of the plate means 23 as the hub means 21 rotates. Means are also included, e.g., ignition means shown in FIG. 4 by a sparkplug 33, for providing internal combustion cycles of the combustion cells 25 in rotational succession, i.e., in the direction of rotation of the hub 21 as shown by the arrow 35, to cause oscillation of the plurality of plate means 23 about their respective hinge means 27 to collectively impart a continuous rotary force to the hub means 21 of the shaft 19.

The engine 11 preferably includes an exhaust manifold means 37 as shown in FIG. 1 of the drawings. More specifically, the intake manifold and exhaust manifold means 17, 37 of the principal embodiment respectively include

annular cavities

39, 41 which are communicated with the circular chamber 15. The intake manifold 17 is coupled to a suitable carburetion system designated as at 43 (only a portion of which is shown) and may be of any well-known construction. It should be sufficient to simply state that the craburetor 43 delivers fuel and air mixture to the annular cavity 39 for introduction into the plurality of combustion cells 25 in a manner yet to be disclosed. The annular cavity 41 collects the exhaust gases, in a manner to be described, from the combustion cells 25 and these gases are preferably channeled through suitable conduit structure as at 45 to a convenient dumping point.

From FIGS. 3, 4, 5, 9, and 13 of the drawings it may be seen that each of the plurality of the plate means 23 is spirally curved in cross section to facilitate an optimum overlapping compact relationship one with the other. In other words, the cross-section of the plate means 23 is not simply a segment of a circle but is preferably a segment of a spiral or an Archimedes curve and which will be more fully disclosed later in the specification.

From FIGS. 1 and 6 of the drawings it may be seen that intake disc means 47 is included for isolating the intake manifold means 17 from the variable combustion cells 25 is a manner which will be more apparent as the specification proceeds. From FIG. 6 of the drawings it may be seen that one quadrant of the intake disc means 47 is provided with at least one intake opening, as at 49, for sequentially communicating the plurality of combustion cells 25 with the intake manifold 17 in rotational succession at first predetermined periods as the hub means 21 or shaft 19 rotates, i.e., the first periods alluded to will be more fully disclosed later in the specification. It should be pointed out that the intake opening 49 is a rather large opening preferably emcp, substantially 90 of the intake disc 47 and may optionally be divided into a plurality of openings with structure yet to be disclosed.

Also included is exhaust disc means 51 for isolating the exhaust manifold 37 from the variagle combustion cells 25 at predetermined events. One quadrant of the exhaust disc means 51 is provided with at least one exhaust opening 53 which is similar and adjacent to the above-described intake opening 49 but is staggered or angularly displaced therefrom for successively communicating the plurality of combustion cells 25 with the exhaust manifold means 37 at predetermined period, e.e., subsequent to the first periods alluded to above, as the hub means 21 rotates. The predetermined periods and/or events will be more apparent as the specification proceeds.

Referring now to FIGS. 4 and of the drawings wherein it may be seen that the coupling means, cam or guide means 31 includes a plurality of arcuate cam follower means 55 which respectively are attached to the free ends 29 of the plurality of plate means 23. The coupling or guide means 31 also includes an elliptical track means 57 which is attached to the hub means 21 for slidably receiving and guildingly constraining the cam follower means 55 to cause each of the plate means 23 to swingably oscillate in sequence towards and away from the shaft 19 as the hub 21 or shaft 19 rotates.

Referring now to FIGS. 1 and 2 of the drawings wherein it may be seen that each of the plurality of hinge means 27 includes a shaft 59 which is freely received intermediate thereof in an elongated aperture 61 provided in the case member 13 and a pair of aligned

apertures

63,65 respectively provided in a pair of

lugs

67, 69 of the plate means 23. From FIGS. 1, 5 it may be seen that the track means 57 includes a first track means 57 attached to the intake disc 47 adjacent the hub 21 and a second confrontingly arranged tracks means designated as 57a and attached to the exhaust disc 51 adjacent the hub 21 with a pair of arcuate cam follower means 55, 55a attached to the free swinging ends 29 of each of the plate means 23 for respectively engaging the first and second track means 57, 57a

From the above disclosure it can now be readily determined that 180 rotation of the hub means 21 in the direction of the arrow 35 causes each of the plate means 23 to swing about the hinge means 27 from a position substantially as depicted for the plate 232 to a position depicted by the plate 23g, i.e., each plate 23 swings through its limits of travel twice for each revolution of the hub 21. It should be understood that the overlapping plates 23 sealingly separate the combustion cells 25 during the swinging movement through an arc of approximately 45. Therefore, the oscillating plates 23 develop a bellowslike action as the volume in each combustion cell 25 varies.

The engine 11 is a four-cycle engine with each cell 25 experiencing the four cycles for each revolution of the hub 21. More specifically, each combustion cell 25 is first introduced or communicated with the annular cavity 39 of the intake manifold 17 during the first predetermined period comprising substantially rotation of the hub 21, then each cell 25 is isolated from both intake and

exhaust manifolds

17, 37 during second and third substantially equal periods jointly comprising substantially rotation of the hub 21, and finally each cell 25 is introduced or comminicated with the annular cavity 41 of the exhaust manifold 37 during the fourth predetermined period comprising substantially 90 ro tation of the hub 21. It should be pointed out that the first period may hereinafter be conveniently referred to as the intake period, the second period may be referred to as the compression period, the third period may conveniently be referred to as the power period, and the fourth period may conveniently be referred to as the exhaust period.

It should also be pointed out that the hub 21 includes a smooth endless surface or elliptical shaped portion 71 (FIGS. 1,4) which is interposed between the intake and

exhaust discs

47, 51 to vary the volume of each combustion cell 25 as the hub 21 rotates, i.e., the free ends 29 of the plate means 23 each sealingly engaging the elliptical surface 71 and the

discs

47, 51 as the shaft 19 rotates like the

plates

23a, 23m depicted in FIG. 1. Additionally, the coupling or guide means 31 guidingly constrains the plate means 23 to cause the free ends 29 thereof to maintain contiguous engagement with the elliptical shaped portion 71 to swing the plurality of plate means about their respective swinging axes which further varies the volume of the combustion cells 25 as the hub 21 rotates.

The preferred instant for the previously mentioned ignition means, e.g., the sparkplug 33, to be activated is late in the compression period for each combustion cell 25. Therefore, the previously mentioned means for providing internal combustion cycles of the combusiton cells 25 includes ignition means, e.g., the sparkplug 33 or the like, for igniting the fuel within the plurality of combustion cells 25 at predetermined moments respectively, the fuel having first been subjected to pressure, i.e., during the compression period, by the swinging movements of the plate means 23 and the rotation of the hub means 21.

The ignition means includes at least the one sparkplug 33 which is attached to the case member 13 and projects into one of the combustion cells, e.g., the combustion cell 252, and a plurality of flame bypass passageways 73 which are individually designated as 73a. 73b, 730, etc. More specifically, the case member 13 is provided with the plurality of passageways 73 which are respectively disposed between the plurality of combustion cells 25, e.g., as shown for the passageway 732 disposed between the cells 25v, 252 in FIG. 5, for momentarily communicating adjacent ones of the combustion cells 25 one with theother in rotational succession as the plurality of oscillating plate means 23 resppectively swing to a predetermined position as the hub 21 rotates, i.e., late in the compression period. From FIG. 4 of the drawings it may also be seen that the passageways 73 also momentarily commjnicate adjacent ones of the combustion cells 25 one with the other late in the exhaust period, e.g., as shown by the passageway 73m communicating the

combustion cells

251, 25m. However, it should be understood that this is of no significance, i.e., serving no benefit or aggravation to the operation of the engine 11. From FIG. 1 of the drawings it may also be seen that a pair of passageways 73 are confrontingly arranged for each combustion cell 25, e.g., like that shown for the first passageway 732 adjacent the intake disc 47 and another passageway 732 adjacent the exhaust disc 51.

Also included are intake louver vane means 75 and exhaust louver vane means 77 (FIGS. 7 and 8) respectively interposed within the intake and

exhaust openings

49, 53 for accelerating the axial flow respectively of the fuel and the exhaust gases. Additionally, the

louver vanes

75, 77 provide reinforcement for the disc structure and facilitate the lapping action of the ends of the plates 23 as the openings 497 53 are passed thereby.

It should be understood that the cam follower means 55 may optionally consist of roller means 55r as shown in FIGS. 2 and 3 of the drawings. Accordingly, the rollers 55r are axially attached, as by axles 79, to the plate means 23 for runningly and ridingly engaging the elliptical track means 57 as the hub 21 rotates.

Particular attention is now directed toward FIG. 3 of the drawings wherein the end view of one of the spirally curved plates 23 is depicted. Each of the spirally curved plates 23 preferably includes a concave face 81 having a true are portion 83 adjacent the free end 29 thereof and a straight portion 85 adjacent the hinge means 27. The straight portion 85 is tangentially disposed with respect to the arc portion 83 and is fixably or integrally attached thereto. The length of each of the preferred configured plates 23 as measured along a first straight line 87, which extends from the dead center of the arcuate cam means or the axle 79 and terminates at the terminus of the straight portion 85 of the concave face 81, is precisely equal to a second straight line 89 which extends from the center point 91 of the true are portion 83 of the concave face 81 to the dead center of the cam means or the axle 79. Additionally, the first straight line 87 is also precisely equal to a third straight line 93 which extends from the terminus of the straight portion 85 of-the concave face 81 to the center point 91 of the true are portion 83 whereby the first, second and third

straight lines

87, 89, 93 define an equiliateral triangle 95.

Particular attention is now directed toward FIG. 9 of the drawings wherein an alternate length of the plate is shown and is character referenced therein by the numeral 23alt. Each of the alternate spirally curved plates 23alt. also includes a concave face 810 having a true arc portion 830 adjacent the free end 29 thereof and a straight portion a adjacent the hinge means 27. The straight portion 85a is tangentially disposed with respect to the true are portion 83a and is fixedly or integrally attached thereto. The length of each of the alternate plate means 23alt. as measured along a first straight line 870, which extends from the dead center of the arcuate cam means or the axle 79 and terminates at the terminus of the straight portion 85a of the concave face 81a, is unequal to a second straight line 890 which extends from the center point 910 of the true are portion 83a of the concave face 85a to the dead center of the cam means or the axle 79. The second straight line 89a is equal to a third straight line 930 which extends from the terminus of the straight portion 85a of the concave face 81a to the center point of the true arc portion 83a whereby the first, second and third straight lines 87a, 89a, 93a define an isoseceles triangle 95a. It should be understood that while the alternate length depicted in FIG. 9 is shorter than that depicted in FIG. 3, i.e., with respect to the length of the geometrical lines just described, it may optionally be greater than are the lengths of the geometrical construction lines without departing from the spirit of the present invention.

The operation of the engine 11 is very similar in theory to a conventional piston type four-cycle internal combustion engine. More specifically, commencing with the intake period and referring to FIG. 4 of the drawings, the combustion cell 251 is just beginning to be introduced (through the opening 49 in the intake disc 47) to the annular cavity 39 as the hub 21 is caused to rotate in the direction of the arrow 35 by any conventional starting means. The guide means 31 causes the plates 23], 23m, which define in part the combustion cell 251, to swing toward the shaft 19. Accordingly, subsequent to rotation the combustion cell 251 has reached its maximum volume and would appear substantially like the combustion cell 25f. At this time, the intake disc 47 has moved so as to lappingly close the combustion cell 251. During the second period or compression period the plates 23!, 23m swing away from the shaft 19 so that after another 90 of rotation the volume of the cell 231 would be varied to the minimun volume or appear somewhat like the cell 252, i.e., having received a charge of fuel and air mixture which has been suitably compressed. Accordingly, at some predetermined instant late in the compression period the sparkplug 33 is energized which starts the burning action of the fuel and air mixture within the combustion cell 251. This causes rapid expansion of the gases in the combustion cell 251 during the third or power period so that after another 90 of rotation the combustion cell 251 would again reach its maximum volume or would appear somewhat like that shown for the combustion cell 251. Accordingly, at this time the exhaust disc 51 has rotated so as to present the exhuast opening 53 to the combustion cell 251. Further rotation causes the

plates

231, 23m to start swinging away from the shaft 19 to decrease the volume of the combustion cell 251. Accordingly, during the fourth period or the exhaust period the exhaust gases are squeezed out of the combustion cell 25! so that after a complete 360 rotation the combustion cell has again reached its minimum volume or would appear somewhat like the cell 25m, i.e., it

would be substantially void of exhaust gases ready for the above-described cycle to be repeated.

From the above disclosure it should be apparent to those skilled in the art that only one sparkplug 33 is needed since the flame bypass passageways 73 ignite the fuel from adjacent cell to adjacent cell, i.e., commencing with the cell 25z, at the optimum time depending upon the positioning of the passageways 73 but always late in the compression period. Therefore, the sparkplug 33 only needs to be energized to start the above-described cycle. However, if desirable, the sparkplug 33 may be energized at a precise angular position of the shaft 19 in order to maintain optimum timing for cyclically initiating the burning sequence. The engine 11 may be shut down by mechanically blocking the flame bypass passageway 73z in any suitable wellknown manner. Accordingly, interrupting electrical flow to the sparkplug introduced to the combustion cell 25z would break the chain of flame bypass passageways, thus the engine would cease operation.

It should be pointed out that each combustion cell 25 experiences the above-described cycle in succession. In other words, having 24 plates as shown, the combustion cell 25m would be only 15 behind the combustion cell 25l for each of the described events, etc., for succeeding cells. In this regard, the number of plates 23 is optional, however, at least l6 plates 23 are desirable.

It should now be apparent that the pressure differential between adjacent combustion cells 25 at any given time is relatively low which simplifies the sealing of each combustion cell. In other words, in referring to FIG. 4 of the drawings, it should be evident that the pressure in the combustion cell 25e is just starting to build while the pressure in combustion cell 25d is a little greater; also, the pressure in combustion cell 25c is greater yet; further, the pressure in the combustion cell 25d is a lttle bit greater; further, the pressure in the combustion cell 25a is just a little bit greater, the pressure in the combustion cell 25z just a little greater (at which time the ignition starts the combustion cycles). This causes the pressure in the combustion cell 25y to be greater than that in 25z and the pressure in cell 25x is greater than that in cell 25y, etc. The pressure differential between the adjacent cells 25fthrough 25s is also very slight due to the same gradual change in volume thereof. Accordingly, the plates 23 are cushioned against any tendency to slap, i.e., the pressure on opposite sides of the plates 23 being only slightly different irrespective of the period or gas cycle event.

Each quadrant of the hub means 21 performs continuously its specific gas cycle event in one-fourth of the combustion cells 25 concurrently. For example, combustion expansion force is exerted uniformly and continuously upon the power quadrant of the hub 21, character referenced in FIG. 6 of the drawings by the capital letter P, by one-fourth of the combustion cells. This continuous power output in the power quadrant propels the hub 21 with a constant vector of torque being applied to the main shaft 19. This application of power is inherently uniform and constant subject only to variations imposed by exterior demand, i.e., the carburetor structure would preferably include a throttle (not shown) for permitting more fuel to enter the intake manifold to compensate for an increased load on the main shaft 19.

In FIG. 6 of the drawings each quadrant of the hub 21 is identified for convenient reference by the conventional symbols I, C, P, and E indicating respectively the intake, compression, power, and exhaust functions which that specific quadrant performs exclusively and continuously in sequence in arcuate groups of combustion cells 25. It should be understood that each cell 25 is stationary with respect to the case member 13 but an oscillation of approximately 45 in the hinged plate 23 acts like a bellows to draw charges into each combustion cell 25 in rotational sequence through the continuously open intake port or opening 49 in the intake quadrant I and concurrently to expel consumed exhaust gases through the continuously open exhaust port or exhaust opening 53 in the exhaust quadrant E.

Gas pressure is continuously applied to positive rotation of the hub 21 in three ways: First, by pressure normal to the surface in the power quadrant P. Second, by inward differential pressures upon each oscillating plate 23 during the power event of each combustion cell 25. Third, by outward differential pressures upon each oscillating plate 23 during the compression event in each cell 25. These outward differential pressures upon the plates 23 are transferred to the hub 21, during compression in each cell 25, through the elliptical track means 57 attached thereto and consequently contribute positive torque to the hub 21 or shaft 19. The plate pressures are normal to the surface of the elliptical shaped portion 71 and are carried by the sealingly fitted tight groove followers or cam follower means 55. The directions of the differential pressures upon the oscillating plates 23 are clearly evident from the fact that compressing pressures increase gradiently from one combustion cell 25 to the adjacent combustion cell 25 and the power pressures decrease gradiently from cell to cell.

This disclosure identified three positive torque forces which are inherent in the use of the spirally overlapping plates 23 and the combustion cells 25 of this invention. However, a relation to efficiency is also evident in the fact that if the direction of the spiral arrangement of the overlapping plates 23 were to be reversed the differential pressures would also be reversed and hence would be opposed to the power pressures applied to the surface of the elliptical shaped portion 71. Other factors favorable to efficiency in this engine are: First, each quadrant of the hub performs a single event of the gas cycle continuously. Second, the intake and exhaust ports or

openings

49, 53 are open continuously. Third, sealing pressures are reduced to the differential pressures between adjacent combustion cells 25. Fourth, the engine operation is void of valves, cam shafts, timing chains. and gears. Fifth, mechanical balance is inherent in the hub 21 and in the symmetrically opposed oscillation of the plates 23. Sixth, the moving parts consist only of a smooth surfaced hub 21 and a selective number of identical oscillating plates 23.

The overlapping swinging plate internal combustion engine of the present invention includes an alternate embodiment clearly shown in FIGS. 10 through 16 and is character referenced in the drawings by the numberal 11'. In order to simplify the disclosure of the engine 11, identical reference numerals will be used to identify the identical same parts previously disclosed for the principal embodiment. Additionally, parts of the engine 11' which are similar to those parts of the principal embodiment will be identified by the same reference numeral but will be differentiated therefrom by conventional prime marks. Therefore, it is believed that sufficient disclosure will be achieved by simply pointing out and elaborating on those features which distinguish the engine 11 from the previously fully disclosed engine 11.

The shaft 19' of the engine 11' includes an offset crank portion, as at 97, which is interposed between remote

straight end portions

99, 101 with the

remote portions

99, 101 being journalled to the case member 13, as with bearings 103. The hub means 21' includes a circular shaped portion or a sleeve 105 which engages the plate means 23'. The circular shaped portion or sleeve 105 may be split and further designated 105L, 105R. The sleeve 105 is rotatably attached to the offset crank portion 99 of the shaft 19 for movement in an eccentric path relative to the circular chamber 15 in a manner and for reasons yet to be disclosed. The guide means 31 is circular in shape and is fixedly attached to the sleeve 105 whereby the rotation of the shaft 19' is effective to cause the guide means 31 to sequentially swing the plurality of plate means 23' or cause each of the plate means 23' to oscillate in substantially the same manner as disclosed for the principle embodiment.

The manner in which the circular shaped portion of the hub 21 or the sleeve 105 is attached to the offset crank portion 97 is as follows: a split bearing assembly including first and

second members

107, 109 jointly define a circular aperture 111 which receives the offset crank portion 97. The

split bearings

107, 109 are fixedly attached one to the other by a plurality of bolt and nut means as at 113. The split bearing member 107 includes a pair of semicircular web-like extensions 115, l 17 and the split bearing member 108 includes a pair of semi-circular web-

like extensions

119, 121 as clearly shown in FIGS. 10 and 13 of the drawings. It should be pointed out that the radii of the web-

like extensions

115, 117, 119 and 121 are sufficiently large engough so that the perimeters thereof may engage the inside diameter of the sleeve 105 as clearly shown in FIG. 13 of the drawings. Additionally, the inside diameter of the sleeve 105 is sufficiently large enough to be freely passed over the crankshaft 19' to facilitate assembly and disassembly.

The sleeve 105 may optionally be of one piece construction, however, I prefer that it be constructed as above suggested or in two sections, i.e., a left hand member or section designated 105L and a right hand member or section designated 105R in FIG. 10 of the drawings. Additionally, the

sections

105L, 105R respectively include offset portions, as at 123, 125 for overlappingly engaging one another.

The offset

portions

123, 125 sealably engage one another in any well known manner about the circumferences thereof and terminate a predetermined distance short of full overlapping engagement to establish expansion and contraction spaces, as at 127, 129, to compensate for temperature changes of the engine 11'.

The sleeve member 105L is keyed to the web-like extension 115 in a conventional manner, e.g., as with the half-moon key 131. Additionally, the sleeve member 105R is keyed to the web-like extention member 117 in the smae manner, as with the half-moon key 133.

From the structure just described, it should now be apparent to those skilled in the art that the

sleeve members

105L and 105R may freely be rotated about the offset portion 97. However, it will become apparent as the specification proceeds that the hub means 21 travels along an eccentric path and does not rotate with the shaft 19', i.e., the offset crank portion 97 rotates within the

split bearings

107, 109 which support the sleeve 105.

The guide means 31' includes a left hand circular track and a right hand circular track 137. The track 135 may optionally be integrally formed with the sleeve member 105L and the track 137 may integrally be formed with the sleeve member 105R if desired. In any event, the

tracks

135, 137 are stationary with respect to the rotor means 21'.

A plurality of block means 139 are slidably mounted in the guide means 31' and the free-swinging ends 29 of the plate means 23 are pivotally attached to the respective block means 139. In other words, the block means 139 is synonomous with the previously cam follower means or is in lieu of the roller means described with the principle embodiment. In this regard, the previously described roller means 55 may optionally be used to guidingly constrain the free ends 29 of the plate means 23' in the engine 11.

It should now be apparent to those skilled in the art that a 360 rotation of the crankshaft 19 causes each of the plate means 23 to oscillate through only one cycle. This is a totally different concept than that of the principle embodiment which caused each of the plates 23 to oscillate through two cycles by rotating the shaft 19 through 360, i.e., achieving the four conventional events: intake, compression, explosion, and exhaust during 360 rotation of the shaft 19.

The engine 11 achieves the four conventional events but in a totally unconventional manner. From FIGS. 11 and 12 of the drawings it may be seen that the engine 11 includes air compressor means 141 disposed remote from the circular chamber 15 which is communicated therewith by intake manifold means 17' The in take manifold means 17 includes a fresh air section 143 and a combustible mixture section 145. The section 143 preferably is larger in volume than the section 145. Carburator means 43 is interposed within the combustible mixture section 145 in a manner obvious to those skilled in the art and the fuel and air output from the Carburator means 43' is controlled by a throttle valve 147.

Particular attention is now directed towards FIGS. 14 through 16 of the drawings which depict the distinguishing features of the intake disc 47' and the exhaust disc 51'. It should first be understood that the intake disc 47 is disposed concentrically of the circular chamber 15 and is keyed to the straight portion 101 of the shaft 19, as by a key 149. The exhaust disc means 51' is disposed concentrically of the circular chamber 15 and is keyed to the straight end portion 99 of the shaft 19, as with a key 151. Both discs 47' and 51' rotate concentrically with respect to the circular chamber 15.

One segment of the intake disc means 47', FIG. 14, is provided with a fresh air intake opening 153 and a combustible mixture intake opening 155 to sequentially communicate the plurality of combustion cells 25' with the intake manifold means 17' at predetermined periods as the shaft 19' rotates, i.e., in a specific manner to be fully disclosed as the specification proceeds.

One segment of the exhaust disc means 51', FIG. 15, is provided with an exhaust opening 157 to sequentially communicate the plurality of combustion cells 25' with the ambient air at a predetermined period as the shaft 1 1 19' rotates, i.e., also to be fully disclosed as the specification preceeds.

The fresh air opening 153 is defined in part by leading and trailing

edges

159, 161 and the combustible mixture opening 155 is defined in part by leading and trailing

edges

163, 165. Further, the exhaust opening 157 is defined in part by leading and trailing edges 167, I69, i.e., the leading and trailing reference being with respect to the direction of rotation as indicated by the arrow 35.

The fresh air intake opening 153 and the combustible mixture intake opening 155 are defined by an offset or raised shoulder portion, as at 171, which wipingly and sealably engages appropriate surfaces of the plurality of plates 23' as the shaft 19 rotates. In other words, the shoulder portion 171 engages the plates 23 to sealably deliver the fresh air and combustible mixture only to those combustion chambers 25' presented to the

openings

153, 155.

The opening 157 in the exhaust disc 51' is also defined by and offset or raised shoulder portion 173 which wipingly and sealably engages the appropriate portions of the plurality of plates 23' in the same manner as just described for the shoulder portion 171, i.e., to communicate ambient air with only those combustion cells 25 which are presented to the opening 157. The

shoulders

171, 173 are confrontingly arranged and in essence reach over the

respective tracks

135, 137 as shown in FIG. by the shoulder 171.

From FIG. 16 of the drawings it may be seen that the

openings

153 and 157 in the respective intake and exhaust discs 47', 51' are angularly displaced with respect to one another in such a manner that the respective leading

edges

159, 167 are angularly aligned one with the other. Additionally, the trailing edge 169 of the opening 157 is angularly aligned with the leading edge 163 of the opening 155. Further, the trailing

edges

161, 165 respectively of the

openings

153, 155 are angularly aligned one with the other.

From FIG. 16 of the drawings it may also be seen that the trailing edge 169 of the exhaust opening 157 and the leading edge 163 of the combustible mixture opening 155 are angularly displaced substantially 180 from the offset crank portion 97 of the shaft 19.

From FIG. 14 of the drawings it may be seen that the combustible mixture intake opening 155 in the intake disc 47' is angularly aligned with at least a portion of the fresh air intake opening 153. Further, the combustible mixture intake opening 155 is disposed inwardly towards the rotating axis of the intake disc means 47 from the fresh air intake opening 153.

FIG. 13 of the drawings would normally show only the exhaust disc 51 and the exhaust opening 157, however, phantom lines are added thereto to conveniently depict at least the

opening

153, 155 in the intake disc 47 and the above-described angular relationship between the intake disc 47 and the exhaust disc 51' in conjunction with the combustion cells 25 in order to simplify the understanding of the engine 11.

Particular attention is again directed towards FIGS. 11 and 12 of the drawings with reference first being to FIG. 11. Since the plates 23 oscillate only one cycle with each revolution of the shaft 19, it is desirable to rapidly expel the exhaust gases from the combustion cells 25 and immediately subsequent thereto the cells 25 should be charged with a combustible mixture which can then be compressed and ignited in a manner substantially identical to that previously described for the principle embodiment. These events are accomplished in a unique manner and in a short time period. More specifically, FIG. 11 shows the engine 11 stopped at a first position and FIG. 12 shows the engine 11' stopped at a second and subsequent position. The first position alluded to (FIG. 11) would correspond to either the cell 25a or 251 in FIG. 13 of the drawings. In other words, the

plates

23a and 25t' have swung substantially their maximum or the volume of the cells 25a, 25: are substantially at their maximum volume. Additionally, a portion of the fresh air intake opening 153 plus the exhaust opening 157 is presented simultaneously to the cells 25a, 25!. Also, it should be noted that a portion of the intake disc 47', as at 175 in FIG. 14, is interposed between the combustible mixture section and the

cells

250, 25t'. Accordingly, the air compressor 141 blows fresh air into the combustion cells 25a, 25t which rapidly moves the exhaust gases outwardly through the exhaust opening 157. Subsequent to the cells 25a, 25t' being evacuated of the exhaust gases, they will simultaneously be presented with the fresh air opening 153 and combustible mixture opening of the intake disc 47, i.e., the disc 47', 51 being rotated slightly or in essence will now have a relationship therewith substantially as depicted in FIG. 13 for the cell 25a.

More specifically, a portion of the exhaust disc 51', as at 177, is interposed between the combustion cell 25s and the annular cavity 41 of the exhaust manifold means 37. Additionally, it should be noted that the combustible mixture intake opening 155 plus a portion of the fresh air intake opening 153 are presented to the combustible cell 25s, thus the combustible cell 25s is charged with a combustible mixture. The combustible mixture is subsequently compressed and exploded in substantially the same manner as disclosed for the principle embodiment which, of course, causes an oscillating movement of the plurality of plate means 23' to collectively impart a rotaryforce to the shaft 19'.

Stated another way, the fresh air intake opening 153 of the intake disc means 47' has at least a portion thereof angularly aligned with the exhaust opening 157 of the exhaust disc means 51' whereby each of the combustion cells 25a through 251" is sequentially communicated on the one side thereof with the fresh air section 143 of the intake manifold means 17 and simultaneously on the opposite side thereof with ambient air, or the exhaust manifold 37, to enable the air compressor means 141 to force fresh air through the opening 153 which expels the exhaust gases outwardly through the exhaust opening 157 as the shaft 19' rotates. Additionally, the combustion cells 25a through 25t subsequently are communicated in rotational sequence with the carburetor means 43 via the combustible mixture opening 155 of the intake disc means 47' to forceably charge each of the combustion cells 25a through 251 with the combustible mixture, the exhaust opening 157 is simultaneously angularly displaced from the combustion cells 25a through 25t' as they are being charged with the combustible mixture, i.e., by the portion 177.

From FIG. 13 of the drawings it may be seen that the block means 139 are shown with irregular spacing therebetween. This irregular spacing depicts the limits of movement of the individual block means 138 within the

appropriate track

135 or 137, i.e., the block means 139 being free to slide to and fro within the

appropriate track

135, 137.

It should be pointed out that the fresh air section 143 includes an isolated annular portion so that the fresh air from the air compressor means 141 is communicated with each of the combustion cells 25' as the shaft 19' rotates. Additionally, the combustible mixture section 145 includes an isolated annular portion which communicates the carburetor 43' or delivers the combustible mixture to each combustion cell 25' as the shaft 19' rotates. The annular combustion mixture section 145 is preferably circumscribed by the annular fresh air section, thus the volume of the fresh air annular portion exceeds that of the combustible section.

Particular attention is now directed towards FIGS. 17 and 18 of the drawings wherein it may be seen that an alternate embodiment of the shaft for the engine 11 depicted in FIGS. through 16 of the drawings is disclosed. The shaft depicted in FIGS. 17 and 18 of the drawings is character referenced herein by the numeral 19" and while it may be used with various size engines 11' it will be appreciated by those skilled in the art that the shaft 19 is particularly advantageous for smaller engines 11. The shaft 19" eliminates considerable structure above disclosed as being included with the hub means 21. Therefore, a third embodiment of the hub means is herein disclosed and is character referenced by the numeral 21".

The shaft 19" includes an eccentric portion 191 interposed between remote axially alinged

straight end portions

99, 101 with the remote portions 99, 101' being journaled to the case member 13 in the same manner as above described. The hub means 21" includes a smooth endless surface or first circular shaped portion 71" disposed exterior of the hub 21" and which sealably engages the free swinging ends 29 of each of the plate means 23', in the same manner as above described for the engine 11'. The hub means 21 also includes a smooth endless surface or a second circular shaped portion 111' which corresponds to the circular aperture 111 depicted in FIG. 13 of the drawings. In other words, the second circular shaped portion 111 is disposed interior of the hub means 21" and rotatably engages the eccentric portion 191 of the shaft 19" for movement of the hub means 21" in an eccentric path relative to the circular chamber in the same manner as above described for the engine 11. Accordingly, the previously described guide means 31', being circular in shape, is fixedly attached to the hub means 21" whereby the rotation of the shaft 19" is effective to cause the guide means 31' to sequentially swing the plurality of plate means 23' or cause each of the plate means 23' to oscillate in the same manner as previously disclosed for the engine 11.

It will be appreciated by those skilled in the art that the hub means 21" eliminates the sleeve 105; the first and

second members

107, 109 or split bearing assembly; the bolt and nut means 113; and the web-

like extensions

115, 117, 119 and 121. The offset

portions

123, 125 as previously described, may optionally be deleted from the hub means 21 More specifically, in the event it is desirable to compensate for temperature changes the offset

portions

127, 129 which define the expansion and contraction spaces 127, 219 may be included with the hub means 21".

It should now be apparent to those skilled in the art that the hub means 21 is free to rotate about the eccentric portion 191 of the shaft 19", however, the hub means 21 travels along an eccentric path and does not rotate about the shaft 19", i.e., the eccentric portion 191 rotates within the hub means 21" in somewhat the same manner as above described in the disclosure for the engine 11.

Although the invention has been described and illustrated with respect to preferred embodiments thereof, it is to be understood that it is not to be so limited since changes and modifications may be made therein which are within the full intended scope of the invention.

1 claim:

1. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, intake manifold means for delivering fuel and air to said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft, a plurality of overlappingly arranged plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, said plate means each being swingably attached to said case member establishing a free swinging end thereof; guide means for coupling each of said plate means to said hub means, for guidingly constraining said free swinging ends of said plate means, and for sequentially swinging said plate means as said shaft rotates; and means for providing internal combustion cycles of said combustion cells in rotational succession and for causing forces to be exerted respectively on said plurality of plate means to impart a continuous rotary force to said shaft; said shaft being straight, said hub means including an elliptical shaped portion which engages said plurality of plate means, said guide means being elliptical in shape, and said hub means being keyed to said straight shaft whereby rotation of said shaft is effective to cause said guide means to sequentially swing said plurality of plate means.

2. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, intake manifold means for delivering fuel and air to said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft, a plurality of overlappingly arranged plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, said plate means each being swingably attached to said case member establishing a free swinging end thereof; guide means for coupling each of said plate means to said hub means, for guidingly constraining said free swinging ends of said plate means, and for sequentially swinging said plate means as said shaft rotates; and means for providing internal combustion cycles of said combustion cells in rotational succession and for causing forces to be exerted respectively on said plurality of plate means to impart a continuous rotary force to said shaft; said means for providing internal combustion cycles of said combustion cells including ignition means for igniting the fuel within said plurality of combustion cells at predetermined moments respectively, said fuel having first been subject to pressure by said swinging movement of said plate means; said ignition means including at least one spark plug attached to said case member and projecting into one of said plurality of combustion cells, and said case member being provided with a plurality of flame bypass passageways respectively disposed between said plurality of combustion cells for momentarily communicating adjacent ones of said combustion cells one with the other in rotational succession to propagate flame ignition from combustion cell to adjacent combustion cell, as said plurality of oscillating plate means respectively swing to predetermined positions.

3. ln an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, intake manifold means for delivering fuel and air to said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft, a plurality of symmetrically arranged overlapping plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, a plurality of hinge means for swingably attaching one end of each of said plate means to said case member establishing a free swinging end thereto, means for providing internal combustion cycles of said combustion cells in rotational sequence to cause oscillation of said plurality of plate means about their respective hinge means to collectively impart a continuous rotary force to said shaft, said hub means including intake disc means for isolating said intake manifold means from said combustion cells, said intake disc means being provided with at least one intake opening for sequentially communicating said plurality of combustion cells with said intake manifold means in rotational succession at first predetermined periods as said hub rotates, said hub means additionally including exhaust disc means for sequentially isolating said combustion cells from without, said exhaust disc means being provided with at least one exhaust opening which is staggered from at least a portion of said intake opening for successively communicating said plurality of combustion cells with the ambient air at subsequent predetermined periods as said shaft rotates, and guide means for coupling each of said free ends of said plurality of plate means to said hub means and for guidingly constraining said free ends to cause said plate means to oscillate in sequence towards and away from said shaft as it rotates.

4. The improvement of claim 3 in which each of said plurality of plate means is spirally curved in cross section to facilitate an optimum overlapping compact relationship of one with the other.

5. The improvement of claim 3 in which is included louvre vane means interposed within said intake and exhaust openings for accelerating the axial flow respectively of the fuel and the exhaust gases.

6. The improvement of claim 3 in which said guide means includes a plurality of cam follower means respectively attached to said free ends of each of said plurality plate means, and track means attached to said hub means and conforming to the exterior thereof for receiving and guidingly constraining said cam follower means to cause each of said plate means to oscillate in sequence towards and away from said shaft as said shaft rotates.

7. The improvement of claim 6 in which said cam follower means consists of roller means axially attached to said plate means for runningly and ridingly engaging said track means as said shaft rotates.

8. The improvement of claim 6 in which said cam follower means includes block means slidably mounted in said guide means.

9. The improvement of claim 6 in which each of said spirally curved plate means includes a concave face having a true are portion adjacent said free end thereof and a straight portion adjacent said hinge means, said straight portion being tangentially disposed with re spect to said are portion and being fixedly attached thereto in a spiral form.

10. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, intake manifold means for delivering fuel and air to said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft, a plurality of overlappingly arranged plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, said plate means each being swingably attached to said case member establishing a free swinging end thereof; guide means for coupling each of said plate means to said hub means, for guidingly constraining said free swinging ends of said plate means, and for sequentially swinging said plate means as said shaft rotates; and means for providing internal combustion cycles of said combustion cells in rotational succession and for causing forces to be exerted respectively on said plurality of plate means to impart a continuous rotary force to said shaft; said shaft including an eccentric portion interposed between remote axially aligned straight end portions with said remote portions being journaled to said case member; said hub means including a first circular shaped portion disposed exterior thereof which sealably engages said plate means and a second circular shaped portion disposed interior thereof which rotatably engages said eccentric portion of said shaft for movement of said hub means in an eccentric path relative to said circular chamber, said guide means being circular in shape and attached to said hub means whereby rotation of said shaft is effective to cause said guide means to sequentially swing said plurality of plate means.

11. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, annular intake manifold means for delivering fuel and air to said chamber, annular manifold means for collecting exhaust gases from said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft for rotation therewith, a plurality of spirally curved symmetrically arranged overlapping plate means slidably engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, a plurality of hinge means for swingably attaching one end of each of said plate means to said case member establishing a free swinging end thereof, said hub means including intake disc means interposed between said combustion cells and said annular intake manifold for isolating said intake manifold means from said combustion cells, one quadrant of said intake disc means including a first plurality of louvre vane means defining intake openings for sequentially communicating said plurality of combustion cells with said intake manifold means at respective first predetermined periods as said hub rotates, said hub means additionally including exhaust disc means attached to said shaft and being interposed between said combustion cells and said annular exhaust manifold isolating said exhaust manifold means from said combustion cells, one quadrant of said exhaust disc means including a second plurality of louvre vane means defining exhaust openings for sequentially communicating said plurality of combustion cells with said exhaust manifold means at respective fourth predetermined periods as said hub rotates; said quadrant of said intake disc means provided with said intake openings being adjacent to but staggered from said quadrant of said exhaust disc means provided with said exhaust openings whereby each of said combustion cells is first communicated with said intake manifold means during said first predetermined period comprising substantially 90 rotation of said hub means, then is isolated from both intake and exhaust manifold means during second and third substantially equal periods both comprising substantially 180 rotation of said hub means, and is finally communicated with said exhaust manifold means during said fourth predetermined period comprising substantially 90 rotation of said hub means; said hub means further including an elliptical shaped portion interposed between said intake and exhaust discs for slidably engaging the free swinging end at said plate means to vary the volume of each of said combustion cells as said hub means rotates; guide means for coupling each of said free ends of said plurality of plate means to said hub means, for guidingly constraining said plate means to cause said free ends of said plate means to maintain close engagement with said elliptical drum means, and for swinging the plurality of plate means about their swinging axes to further vary the volume of said combustion cells as said hub means rotates; and ignition means for providing internal combustion cycles of said combustion cells in rotational sequence to cause oscillation of said plurality of plate means to collectively impart a continuous rotary force to said shaft.

12. An internal combustion engine comprising a stationary cylindrical case member provided with a circular chamber, annular intake manifold means including a fresh air section and a combustible mixture section both sections being communicated with said chamber, carburetor means interposed within said combustible mixture section, air compressor means remote from said chamber and being communicated therewith by said intake manifold means, a shaft including an offset crank portion interposed between remote straight end portions, said shaft being disposed concentrically of said circular chamber with said end portions being journaled to said case member, hub means rotatably attached to said offset crank portion of said shaft for movement in an eccentric path relative to said circular chamber, a plurality of spirally curved symmetrically arranged overlapping plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, a plurality of hinge means for swingably attaching one end of each of said plate means to said case member establishing a free swinging end thereof, circular guide means circumferentially engaging said hub means and being attached thereto for coupling the free swinging ends of said plate means to said hub means, intake disc means disposed concentrically of said circular chamber and being keyed to one of said remote straight end portions of said shaft for concentric rotation with said circular chamber, one segment of said intake disc means being provided with fresh air and combustible mixture intake openings to sequentially communicate said plurality of combustion cells with said intake manifold means at predetermined periods as said shaft rotates, exhaust disc means disposed concentrically of said circular chamber and being keyed to the other one of said remote straight end portions of said shaft for rotation therewith, one segment of said exhaust disc means being provided with an exhaust opening to sequentially communicate said plurality of combustion cells with the ambient air at a predetermined period as said shaft rotates, said fresh air intake opening of said intake disc means having at least a portion thereof angularly aligned with said exhaust opening of said exhaust disc means whereby each of said combustion cells is simultaneously communicated on the one side thereof with said fresh air section of said intake manifold means and on the opposite side thereof with ambient air to enable said air compressor means to force exhaust gases outwardly through said exhaust opening as said shaft rotates, each of said combustion cells subsequently being communicated with said carburetor means via said combustible mixture opening of said intake disc means to forcibly charge each of said combustion cells with the combustible mixture, said exhaust opening being angularly displaced from said combustion cells as they are being charged with said combustible mixture, and ignition means for providing internal combustion cycles of said combustion cells in rotational sequence to cause an oscillating movement of said plurality of plate means to collectively impart a rotary force to said shaft.

13. The engine of claim 12 in which said ignition means includes at least one spark plug attached to said case member and projecting into one of said plurality of combustion cells, said case member being provided with a plurality of flame bypass passageways respectively disposed between said plurality of combustion cells for momentarily communicating adjacent ones of said combustion cells one with the other in rotational succession to propagate flame ignition from combustion cell to adjacent combustion cell in succession as said plurality of oscillating plate means respectively swing to predetermined positions, and means for closing said bypass passageways of at least one of said combustion cells to stop the flame propagation.

14. The engine of claim 12 in which said fresh air and combustible mixture openings in said intake disc means respectively are defined in part by leading and trailing edges, said exhaust opening in said exhaust disc means being defined in part by leading and trailing edges; and said intake and exhaust discs being angularly displaced with respect to one another in such a manner that said leading edges defining in part said fresh air and said exhaust openings are angularly aligned one with the other, said trailing edge defining in part said exhaust opening being angularly aligned with said leading edge defining in part said combustible mixture opening, and said trailing edges defining in part said fresh air and combustible mixture openings are angularly aligned one with the other.

15. The engine of claim 14 in which said trailing edge defining in part said exhaust opening of said exhaust disc means and said leading edge defining in part said combustible mixture opening of said intake disc means 19 are angularly displaced substantially 180 from said offset crank portion of said shaft.

16. The engine of claim 12 in which said combustible mixture opening in said intake disc means is angularly aligned with at least a portion of said fresh air opening, said combustible mixture opening being disposed inwardly towards the rotating axis of said intake disc means from said fresh air opening.

17. A method of operating an internal combustion rotary engine having a plurality of adjacent overlapping combustion cells surrounding a rotor rotating relative to said cells; adjacent ones of said cells being grouped into four sequential groups including an intake group, a compression group, a power group, and an exhaust group; and means for providing an intake event of a combustible mixture into said cells in said intake group, for providing a compression event in said cells in said compression group, for providing an ignition power event in said cells in said power group, and for providing an exhaust event of gases from said cells in said exhaust group; said method comprising progressively establishing said four groups out of different ones of adjacent said cells during rotation of said rotor so that said intake, compression, ignition and exhaust events are established sequentially in said cells with said events progressively moving around said engine; and causing said power events during the movement thereof around said engine to act on said rotor for the driving thereof.

Claims

1. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, intake manifold means for delivering fuel and air to said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft, a plurality of overlappingly arranged plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, said plate means each being swingably attached to said case member establishing a free swinging end thereof; guide means for coupling each of said plate means to said hub means, for guidingly constraining said free swinging ends of said plate means, and for sequentially swinging said plate means as said shaft rotates; and means for providing internal combustion cycles of said combustion cells in rotational succession and for causing forces to be exerted respectively on said plurality of plate means to impart a continuous rotary force to said shaft; said shaft being straight, said hub means including an elliptical shaped portion which engages said plurality of plate means, said guide means bein elliptical in shape, and said hub means being keyed to said straight shaft whereby rotation of said shaft is effective to cause said guide means to sequentially swing said plurality of plate means.

3. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, intake manifold means for delivering fuel and air to said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft, a plurality of symmetrically arranged overlapping plate means engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, a plurality of hinge means for swingably attaching one end of each of said plate means to said case member establishing a free swinging end thereto, means for providing internal combustion cycles of said combustion cells in rotational sequence to cause oscillation of said plurality of plate means about their respective hinge means to collectively impart a continuous rotary force to said shaft, said hub means including intake disc means for isolating said intake manifold means from said combustion cells, said intake disc means being provided with at least one intake opening for sequentially communicating said plurality of combustion cells with said intake manifold means in rotational succession at first predetermined periods as said hub rotates, said hub means additionally including exhaust disc means for sequentially isolating said combustion cells from without, said exhaust disc means being provided with at least one exhaust opening which is staggered from at least a portion of said intake opening for successively communicating said plurality of combustion cells with the ambient air at subsequent predetermined periods as said shaft rotates, and guide means for coupling each of said free ends of said plurality of plate means to said hub means and for guidingly constraining said free ends to cause said plate means to oscillate in sequence towards and away from said shaft as it rotates.

9. The improvement of claim 6 in which each of said spirally curved plate means includes a concave face having a true arc portion adjacent said free end thereof and a straight portion adjacent said hinge means, said straight portion being tangentially disposed with respect to said arc portion and being fixedly attached thereto in a spiral form.

11. In an internal combustion engine of the type having a stationary cylindrical case member provided with a circular chamber, annular intake manifold means for delivering fuel and air to said chamber, annular manifold means for collecting exhaust gases from said chamber, and a shaft disposed concentrically of said chamber and being journaled to said case member; the improvement which comprises hub means attached to said shaft for rotation therewith, a plurality of spirally curved symmetrically arranged overlapping plate means slidably engaging said hub means and said case member for separating said chamber into a plurality of variable volume combustion cells, a plurality of hinge means for swingably attaching one end of each of said plate means to said case member establishing a free swinging end thereof, said hub means including intake disc means interposed between said combustion cells and said annular intake manifold for isolating said intake manifold means from said combustion cells, one quadrant of said intake disc means including a first plurality of louvre vane means defining intake openings for sequentially communicating said plurality of combustion cells with said intake manifold means at respective first predetermined periods as said hub rotates, said hub means additionally including exhaust disc means attached to said shaft and being interposed between said combustion cells and said annular exhaust manifold isolating said exhaust manifold means from said combustion cells, one quadrant of said exhaust disc means including a second plurality of louvre vane means defining exhaust openings for sequentially communicating said plurality of combustion cells with said exhaust manifold means at respective fourth predetermined periods as said hub rotates; said quadrant of said intake disc means provided with said intake openings being adjacent to but staggered from said quadrant of said exhaust disc means provided with said exhaust openings whereby each of said combustion cells is first communicated with said intake manifold means during said first predetermined period comprising substantially 90* rotation of said hub means, then is isolated from both intake and exhaust manifold means during second and third substantially equal periods both comprising substantially 180* rotation of said hub means, and is finally communicated with said exhaust manifold means during said fourth predetermined period comprising substantially 90* rotation of said hub means; said hub means further including an elliptical shaped portion interposed between said intake and exhaust discs for sLidably engaging the free swinging end at said plate means to vary the volume of each of said combustion cells as said hub means rotates; guide means for coupling each of said free ends of said plurality of plate means to said hub means, for guidingly constraining said plate means to cause said free ends of said plate means to maintain close engagement with said elliptical drum means, and for swinging the plurality of plate means about their swinging axes to further vary the volume of said combustion cells as said hub means rotates; and ignition means for providing internal combustion cycles of said combustion cells in rotational sequence to cause oscillation of said plurality of plate means to collectively impart a continuous rotary force to said shaft.

15. The engine of claim 14 in which said trailing edge defining in part said exhaust opening of said exhaust disc means and said leading edge defining in part said combustible mixture opening of said intake disc means are angularly displaced substantially 180* from said offset crank portion of said shaft.