US3645239A - Rotary piston machine - Google Patents

Rotary piston machine Download PDF

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US3645239A
US3645239A US3645239DA US3645239A US 3645239 A US3645239 A US 3645239A US 3645239D A US3645239D A US 3645239DA US 3645239 A US3645239 A US 3645239A
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pair
means
annular cylinder
shaft
chambers
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Arnulfo Q Cena
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ARNULFO Q CENA
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/02Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/07Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having crankshaft-and-connecting-rod type drive
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B57/00Internal-combustion aspects of rotary engines in which the combusted gases displace one or more reciprocating pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00Engines characterised by fuel-air mixture compression
    • F02B1/02Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00Other engines
    • F02B75/02Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2730/00Internal combustion engines with pistons rotating or oscillating with relation to the housing
    • F02B2730/03Internal combustion engines with pistons rotating or oscillating with relation to the housing with piston oscillating in a housing or in a space in the form of an annular sector
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02TCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00Road transport of goods or passengers
    • Y02T10/10Internal combustion engine [ICE] based vehicles
    • Y02T10/17Non-reciprocating piston engines, e.g. rotating motors

Abstract

My present invention relates to rotary machines and, more particularly, to a rotary internal-combustion engine having a rotating annular cylinder block within which are housed a pair of double-faced arcuate pistons rotating relatively therewith.

Description

United States Patent Qena 1 Feb 29, 1972 [54] ROTARY PISTON MACHINE [56] References Cited [72] Inventor: Arnulio Q. Cena, 108 Volta St., Makati, UNITED STATES PATENTS P 1,256,647 2/1918 Baudot ..4l8/34 x 1,353,205 9/1920 Woodward..... ....418/34 X Oct. Riesenecker X [21] Appl. No.: 869,075 Primary ExaminerAllan D. Herrmann Att0meyMichae1 S. Striker 52 us. c1 ..123/8.07,123/8.33,123/8.47, [57] ABSTRACT [51] Int. Cl ..F02b 53/08 My Present invention relates to mtary machines more [58] Field of Search ..123/8.27, 8.31, 8.33, 8.47, Particularly, a rotary internal-wmbusfim engine having I8; I 2/ m,

:2. n "g, I :11]-

E A 8 m rotating annular cylinder block within which are housed a pair of double-faced arcuate pistons rotating relatively therewith.

8 Claims, 17 Drawing Figures PAIENTEB FEB 29 I972 SHEH UIUF 12 PATENIEBFEBZS I972 3,645,239

SHEET 03 [1F 12 IIIVENTOR ARNULFO Q. CENA ATTORNEY PAIENTEI1EB29 e912 SHEET on HF 12 IN V'EN PAINT Emma 972 SHEET 050? 12 INVEHIOR ARN'ULFO Q. CENA ATTORNEY PATENTEDFEBZS 1972 3,645,239

SHEET 06 0F 12 INVENTOR ARNULPU Q.- CENA ATTORNEY ,PATENTEDFEB29 c972 SHEET 07BF 12 INVENTOR ARHULFO Q CENA PATENTEDFEBZB I972 1 3,645,239

SHEET 08m 12 INVENTOR ARNULFO Q. CENA I ATTORNEY PAIENTEBFEBZQ 1912 i 3 645 2 3 9 SHEET 09 [1F 12 INVENTOR ARNULPO Q. CENA PATENTEDFEB 29 I972 SHEET 10 0F 12 mvzmoa ARNULPO Q CENA ROTARY PISTON MACHINE Rotary internal-combustion engines are well known in the art, for example, the rotary vane-type engine wherein two sets of radial vanes rotate on the same axis but continuously change position relative to each other. This speeding up and slowing down of one set of vanes changes the volume of gas between the two sets needed for intake, compression, combustion and exhaust. These radial vane pistons are however rather disadvantageous in view of difficulty of sealing the sides thereof. Sealing the sides of a square or a rectangular-shape piston is really a very difficult job. Also in this type of rotary engine there is also the problem in the inertial force generated by the seals of the radial vanes which results in the fast and uneven wearing out of the cylinder. The uneven wear on the cylinder is one cause of loose compression.

It is, therefore, the principal object of the present invention to provide a rotary internal-combustion engine which will avoid the abovementioned disadvantages and this is achieved by the double-faced arcuate pistons with piston rings inside a rotating annular cylinder block.

A more specific feature of the invention is to provide a machine with a revolving annular cylinder block having a pair of cylinder heads, and a pair of double-faced arcuate pistons which move relatively to one another by means of scissor-action-type gear mechanism to effect intake of charge, compression, combustion and exhaust of the charge. It is also an object of this invention to provide a machine with a high efficiency and with an effective sealing means between said double-faced arcuate pistons and the cylinder.

The above objects are achieved, in accordance with the present invention by a machine characterized by a revolving annular cylinder block divided into two chambers by a pair of diametrically opposed cylinder heads. Each of said chambers has an intake port for fuel and air mixture, and an exhaust outlet for burned gases. Inside said annular cylinder are a pair of diametrically opposed double-faced arcuate cylindrical pistons which forms with the cylinder heads two combustion chambers. The relative angular movement or rotation of the arcuate pistons and the cylinder heads efiects intake, compression, combustion and exhaust. This relative rotations of the cylinder heads and the arcuate pistons are controlled by a scissor-action-type combination of cranks and gears. The scissor-action-type mechanism comprises of cranks journaled to opposed extending arms, which arms are rigidly connected to the shaft of the annular cylinder block. To each of said cranks is secured a planet gear which meshes with a sun gear secured to the engine housing. Rotation of the planet gears effects the cranking of a connecting rod pivotally connected to a pin at each end of an arm secured to the second shaft of the doubleface arcuate pistons. Upon rotation of the planet gears on the sun gear, the crank together with the connecting rod effects the relative movement of the cylinder heads and the doubleface arcuate pistons causing the drawing, compressing, expanding and expelling combustible fuel and air mixture in the combustion chambers.

Another feature of the invention resides in a revolving heavy annular cylinder block which also serves as a flywheel with a large momentum, while the lighter double-face arcuate pistons alternately catch up and fall behind the annular cylinder heads thereby performing the Otto cycle principle. The large momentum of the heavy annular cylinder block effects smooth rotation and uniform speed of the engine.

Still another feature of the present invention resides in the supercharging of the supply of fuel and air mixture by the pumping chambers into the combustion chambers wherein the said combustible mixture are drawn by said pumping chambars from the center of the partly hollow shaft of the engine and then charged into the annular cylinder combustion chambers.

Still another feature of the present invention is in the combination of a pair of parallel annular cylinder block wherein between the said annular cylinder blocks are located the scissor-action-type gear mechanism.

Another further feature of the present invention is the fourcycle rotary internal combustion engine wherein the cylinder head assembly of the annular cylinder block consist of intake port, exhaust port, intake valves and exhaust valves. This annular cylinder head assembly divides the annular cylinder block into two to form four combustion chambers. While the intake and exhaust valves of the said cylinder head assembly are actuated by valve plungers that slides around stationary cams.

Other objects, features and advantages of the present invention will be clearly understood from the following description, reference being made in the drawing of which:

FIG. 1 is a side view ofthe machine;

FIG. 2 is a longitudinal sectional view of the machine;

FIG. 3 is a sectional view taken through the annular cylinder block of the engine;

FIG. 4 is a front view of the machine;

FIG. 5 is a side view of the machine according to another embodiment of the invention;

FIG. 6 is a longitudinal sectional view of FIG. 5;

FIG. 7 is a sectional view taken through one of the annular cylinder block of FIG. 6;

FIG. 8 is a side view of another embodiment of the machine;

FIG. 9 is a longitudinal sectional view of the machine of FIG. 8;

FIG. 10 is a sectional view taken through the annular cylinder block according to an embodiment of FIG. 8;

FIGS. 11a, 11b, and are diagrammatical views of the operation of the two-cycle engine showing the stages of operation in one-half revolution of the engine;

FIGS. 12a, 12b, 12c and 12d are diagramatical views of the operation of the four-cycle engine showing the various stages of the cycle.

Referring now to FIGS. 1 to 4 of the drawings the rotary engine as embodied in this invention has support means comprising a cylindrical casing l with a central boss 31a and a flange 18a. Bolted to the flange 18a of the casing is the rear plate I8 which as a rearwardly extending central boss 18b coaxial with the central boss 31a of the casing.

At the front of the casing is a crossmember 13 with a central boss 8 coaxial with the bosses of the casing l and the rear plate 18. The crossmember 13 has integral rearwardly extending arms 13a of which are bolted to the front of the casing I.

Journaled in the bearings 14 in the boss of the rear plate I8, bearings 14a in the boss 31a of the backplate 31 and in the bearing 14b in the boss of the crossmember 13 is the main shaft 23 which has a pair of diametrically opposed spokes 4 integrally connected to the annular cylinder block 2. The annular cylinder block 2 is essentially a hollow torus having two equal opposed slit 47 at the inner side thereof; and a pair of opposed annular ribs 217 on both sides of the annular cylinder block 2 are bolted the sideplates 6 and 60 each of which has a central boss 12 joumaled on the bosses of the backplate 31 and the crossmember 13. Each of the central bosses 12 has a groove to receive a seal ring 12a to render the annular space 7 airtight.

The annular cylinder block 2 as shown clearly in FIG. 3 is divided into two identical compartments by the diametrically opposed walls 27 and 27a which serves as the cylinder heads. Substantially on the inner side of the annular cylinder block 2 are the diametrically opposed intake port 5 and 5a each of which is spaced substantially from the front the front side of the cylinder heads. Also on the inner side of the annular cylinder block are suction ports 33a and 33b which are each located close to the rear side of each cylinder head. The suction ports 33a and 33b lead to the pumping chambers E and F. The pumping chambers E and F are actually that part of the identical sections into which the annular cylinder block 2 is divided adjacent the rear sides of the cylinder heads 27 and 27a respectively. The part of the two identical chambers adjacent the front sides of the cylinder heads 27 and 27a are the combustion chambers C and D respectively.

On the annular cylinder block main shaft 23 is joumaled the hollow second shaft 24 at the front end of which are a pair of radial spokes 3. In the opposite end of the radial spokes 3 are pins 30 and 3b extending through the two opposite elongated slots 47 on the inner side of the annular cylinder block 2. To each end of pins 30 and 3b of said radial spokes 3 are the arcuate pistons A and B which oscillate within the hollow annular cylinder block 2. At both ends of the arcuate pistons are pistonheads la, lb, la and 1d with piston rings 25. Between the cylinder heads 27 and 27a and pistonheads la and lb respectively are formed combustion chambers C and D and between cylinder heads 27 and 27a and pistonheads 1c and 1d respectively are formed pumping chambers E and F in the annular cylinder block.

On the front side of the annular cylinder block are the threaded holes close to the front side of the cylinder heads which holes are adopted to receive the spark plugs 7a and 7b. While on the rear side of the annular cylinder block are the exhaust ports 21 and 21a. Said exhaust ports are oriented upwardly as shown in FIGS. 1 and 2.

On the front portion of the annular cylinder block main shaft 23 has an axial bore 10. The end of the said axial bore is threaded and sealed with plub bolt 30. The hollow front portion of the main shaft 23 has a pair of opposed front holes 110 which are adopted on rotation of said shaft to communicate in a predetermined time sequence with the carburetor 29. Longitudinally in line with each of the opposed front holes are the opposed rear holes 11 which communicates with the airtight annular space 7 which in turn communicates the combustion chambers C and D through the intake ports and 5a and the pumping chambers E and F through the suction ports 33a and 33b.

The carburetor 29 is secured to the end cover 28 and in turn secured to the crossmember 13. And on the vertical arms of the crossmember 13 are mounted the spark distributors 8a and 8b.

At the rear end of the main shaft 23 are a pair of radially extending arms and 20a at the end of which are joumaled the cranks l7 and 17a. To the pins of the crank 17 and 17a are secured the planet gears 16 and 16a which mesh with the sun gear 22 bolted to the rear side of the casing backplate 31.

At the rear end of the hollow shaft 24 are the opposed radial arms 26 and 26a. At the end of each of said arms are pins which are connected by link bars 19 and 19a to the pin of the corresponding crank. While fixed to the other end of said shaft 24 are radial arms 3. The extending arms of main shaft 23 and second shaft 24 moves in a reciprocating motion simultaneously with the annular cylinder block 2 in relation to pistons A and B caused by the crank 17 and 17a through link bars 19 and 190 that controls the length of the stroke.

The operation of the two-cycle engine as illustrated in FIGS. lla, llb and llc are as follows: The cylinder heads 27 and 27a are at 360 and l80 position respectively, and between the said cylinder heads 26, 27a and pistonheads la, lb and lc, ld are combustion chambers C and D and the pumping chambers E and F. In FIG. Ila the pumping chambers E and F has just finished the intake cycle and starting to compress the fuel and air mixture. While at the same instance combustion chambers C and D has finished the compression stroke so that the spark plug 7a and 7b are about to ignite the fuel and air mixture by spark distributor 8a and 8b thus expanding the burnt gases driving apart the cylinder heads 27, 27a and pistonheads la and lb (see FIG. 3) in the combustion chambers C and D. During the expansion of combustion chambers C and D the crank through planet gears in mesh with the sun gear causes the annular cylinder block 2 to rotate and at 90 rotation, FIG. llb the combustion chambers C and D have finished the expansion and at the same time are charged and with fuel and air mixture that comes from the pumping chambers E and F through port 3311 and 33b and intake port 5 and 5a driving away the burnt gases through exhaust ports 21 and 21a. Pumping chambers E and F start now drawing in fuel and air mixture again. As the annular cylinder block continues to rotate to half revolution or 180' as shown in FIG. llc the combustion chambers C and D are about to fire again repeating the cycle as in FIG. lla. After completing the 360 revolution the combustion chambers C and D has completed two power strokes each per shaft revolution so that there are four power stroke performed by the two combustion chambers C and D in one revolution.

Referring now to another embodiment of the two-cycle engine of this invention as shown in FIGS. 5, 6, and 7 are the two parallel annular cylinder block 2 and 2a fixed to a main shaft 23 through spokes 4 and are joined together by a cylinder 36. This annular cylinder blocks 2, 2a and the double-face arcuate pistons A, B, G and H are identical to two-cycle engine of FIGS. 1, 2, and 3 only it has four combustion chambers C, D, C, and D, and four pumping chambers E, F, E,, F, and that the controlling gear mechanism are placed between the said two parallel annular cylinder blocks 2 and 2a. Combustion chambers C,, D, and pumping chambers E,, F, of annular cylinder block 2a are not shown in the drawings since they are identical to annular cylinder block 2.

Annular cylinder block 2 and 2a are provided with intake manifold 35 and intake port 37 for the pumping chambers E, F, E,, F, and also intake transfer port not shown for the combustion chambers C, D, C, and D,. On .each combustion chambers C, D, C,, D, are provided with exhaust port 21, 21a, 21b, 21c and spark plugs 7a, 7b, 7c, 7d for exhausting and firing the said combustion chambers respectively.

Inside the parallel annular cylinder blocks 2 and 2b are two pairs of double-face arcuate pistons A, B, and G, H respectively. Pistons A and G are connected by pin 34 and pistons H and B are connected by pin 34a, FIG. 6. Connecting rod 19, 19a are pivotally connected to crank 17, 17a and to pins 34, 340 respectively so that pistons A, G and B, H reciprocate through the action of crank 17, and 17a in relation with the two parallel annular cylinder block 2 and 2b by the cooperation of the extending arms 26, 26a are joumaled to the main shaft 23 and at the end of said arms are rigidly connected the pins 34 and 34a. Spokes 4 and 4a which are fixed to the main shaft 23 has bossing 36a where the pins of crank 17 and 17a are joumaled and on both ends of said crank 17, 17a are planet gears 16, 16a, 16b and 16c meshing with sun gears 22 and 22a, FIG. 6. Sun gears 22 and 22a are bolted to the cross-frame l3 and plate 18. At its outer end of the main shaft 23 are bearings 14. 14a and said bearing are seated at the inner diameter of sun gears 22 and 22a.

It will be noted that the whole assembly as shown in FIGS. 5 and 6 are rotating except the sun gears 22, 22a, the crossedframe 13 and the plate 18. The only main parts exposed are the parallel cylinder blocks 2, 2a connecting cylinder 36 and cover plates 6 and 6a. Most of the moving parts are enclosed and that the internal moving parts are airtight and therefore lubrication is not a problem.

Describing the operation of the double-annular cylinder as shown in FIGS. 5, 6 and 7 are as follows. The working principle of this engine will not be repeated since it is the same as described previously in FIGS. lla, llb and llc. The only difference is in the gear and crank mechanism which is placed between the pair of annular cylinder blocks. No like in the first embodiment in FIGS. 1 and 2 where the gear and crank mechanism has its own fixed housing. In FIGS. 5 and 6 the gear and crank housing is rotating together with the assembly.

The engine assembly is rotating with the main shaft 23 axially journaled on both ends on bearings 14 and where the said bearing sits in the inside diameter of sun gears 22 and 22a. Fixed to the main shaft 23 are spokes 4 and 4a of cylinder blocks 2 and 2b. Journaled on the center of main shaft 23 are the extending arms 26 and 26a. From the partly hollow shaft 10 are opposed port holes 11, 11a and llb where the fuel and air mixture are drawn in from the carburetor 29 into the pumping chambers E, F, E, and F, passing through manifolds 35 and intake ports 37. As the gases are compresses in the pumping chambers E, F, E, and F, the gases are forced into the combustion chambers C, D, C, and D, through the transfer passage not shown in the drawings. The fuel and air mixture are compressed again in the combustion chambers and the spark plugs 7a, 7b, 7c and 7d ignites the charge through spark distributor 8a, 8b, 8c and 8d and does expand the combustion chambers driving apart the pistonheads and cylinder heads. During the separation, pressure is exerted between the cylinder heads and pistonheads and simultaneously turning the planet gears 16, 16a, 16b and 160 in mesh with the fixed sun gears 22 and 22a. Since the planet gears are fixed on both ends to the pin of crank 17 and 17a it forces the connecting rods 19, and 19a to reciprocate pins 34, 34a of the double-face arcuate pistons A, G and B, H in relation with the diametrically opposed cylinder head walls imparting torque to the main shaft 23.

Since there are four combustion chambers C, D, C, and D, and four pumping chambers E, F, E, and F, this two-cycle engine produces eight power expansion stroke from the four combustion chambers C, D, C, and D, per shaft revolution.

In cooling the engine, fins are prepared although water cooling system can be adopted. The cylinder 36, engine plate cover 6 and the annular cylinder blocks 2 and 2b are finned for cooling the engine and the oil in the assembly can be recirculated between the engine and radiator now shown. Oil is kept inside the engine because it is airtight in the bearings 14, 14a and oil seals 12a and 12b.

Another embodiment of the engine as shown in FIGS. 8, 9 and will now be described. the main difference of this engine over the engines described previously is that this is a fourcycle engine so that the annular cylinder block 2, the doubleface arcuate pistons A and B on the scissors-action-type gear mechanism are the same as discussed previously in the twocycle engines. The new feature ofthis engine over the first embodiment is that in the cylinder head assembly. This cylinder head assembly comprises the diametrically opposed walls which serves as cylinder head, the intake and exhaust port with corresponding intake and exhaust valves. The sets of valves of the cylinder head assembly are actuated by the plungers through stationary carns that are fixed to the bosses of the housing and the crossed frame. Further more all the four formed chambers C, D, E and F between pistonheads and cylinder head assembly are combustion chambers.

Referring to the drawings of FIGS. 8, 9 and 10 are shown the annular cylinder block 2 divided into halves by cylinder head block assembly 27 and 27a and fixed to the main shaft 23 through spokes 4. Inside the annular cylinder block 2 are two double-face arcuate pistons A and B are rigidly connected to the pins of spoke 3 and fixed to a second shaft 24. Slot 47 in the inner side of the annular cylinder block 2 is provided for the pins 3a and 3b of spokes 3 to travel according to the length of stroke of the double-face arcuate pistons.

The cylinder head block assembly 27 and 27a together with the intake port hole 44, exhaust port hole 45, valve seat and the valve guide assembly are in one piece so that the annular cylinder block flanges are bolted to the said cylinder head assembly to form the cylinder combustion chambers. On both sides of the cylinder head block assembly are bolted the plate cover 6 and 6a each of which has central boss 12 is journaled on the bosses of the backplate 31 and the crossmember 13. Each of the central bosses 12 has a groove to received the seal ring 12a. On said plate covers 6 and 6a has also the plunger guides 43 and 43a for the sets of plungers 40, and 40a. Said sets of plungers slide on fixed cams 41, 41a, 42 and 42a. The set of cams 41, 41a and 42, 42a are fixed on the bosses of the backplate 31 and the crossmember 13a. Cams 4] and 41a positioned on boss 31a located at the rear side of annular cylinder block assembly are used to open and close the'sets of exhaust valves 37 and 370. While cams 42 and 42a positioned on boss 8 located at the front of the annular cylinder block assembly are used to open and close the sets if intake valves 38 and 38a. All of the said valves are provided with springs not shown in the drawings.

The gear mechanism of the four-cycle engine in FIG. 9 is similar to the gear mechanism of the first embodiment of the two-cycle engine as shown in FIG. 2.

The operation of the four-cycle engine as illustrated in FIGS. 12a, 12b, 12c and 12d will now be described. All the four chambers in this engine are combustion chambers C, D, E and F as shown in FIG. 10. Each chambers are provided with intake valve and exhaust valve for opening and closing the port. The cylinder head 27 in FIG. 12a is at 360 position, while cylinder head 27a is at 180. As the engine starts to rotate, the pistonhead and cylinder heads reciprocate so that chamber D starts to draw in gas and air mixture from the open intake valve through the carburetor 29 passing the hollow 10 of main shaft 23, hole opening 11 of main shaft 23 into intake manifold 29 and intake port 44 and finally inside the chamber D. Chamber F starts to compress, and the intake and exhaust valve are closed. Spark plug 7a of chamber C starts to ignite the charge driving the cylinder heads and piston heads apart with the intake and exhaust valve closed. Chamber E start to contract the exhaust valve starts to open to discharge the burned gases through exhaust port 45. As the engine continues to move to 90 as shown in FIG. 12b the cylinder heads 27, 27a and the double-face arcuate pistons A and B are rotating as well as reciprocating relative to one another. At this instant the chambers has change there position. Chamber D in FIG. 12b has expanded and finished in drawing in fuel and air mixture and the corresponding intake and exhaust valves are now closed while chamber F compresses the charge so that both intake and exhaust valves are closed and ready for ignition at this position since the spark plug 7d is about to be fired by spark distributor 8b. Chamber C is contracting to expell the burned gases through the opened exhaust valve and chamber E is starting to expand to draw in fuel and air mixture from the opened exhaust intake valve. After one-half turn or l rotation the chambers has change again there position. Chamber D in FIG. 12c now is in the firing position where the intake and exhaust valve are still closed and the spark plug 7b is opposite the spark distributor 8a. Chamber F which has finished expansion and the exhaust valve opens to discharge the burned gases. Chamber C starts to draw in fresh change and chamber E compresses. At 270 turn the chambers changes there position again FIG. 12d so that chamber E is in the firing position. Chamber D exhausting, chamber F intakes the chamber C compressing. At one revolution or 360 turn the cycle is completed and appears now in the same position again as shown in FIG. 12a does each working chamber has accomplished the four-cycle stages of intake, compression, ignition and exhaust.

The firing order of this four-cycle rotary engine is at 360 and Spark distributor 8a is at 360 position and spark distributor 8b is at about 90. Combustion chambers C and D are always fired by spark distributor 8a at 360 and combustion chambers E and F are always fired by spark distributor 8b at 90 position. The firing order of the combustion chambers in one revolution as shown in FIGS. 12a to 12d are chambers C, F, D and E. Other firing order can be arranged according to there respective cams and valves in combination with there respective chambers.

Since the annular cylinder block 2 and the double-face arcuate pistons A and B serves as flywheel itself and are connected to a main shaft 23 and second shaft 24 respectively they rotate as a whole mass, so that through the action of the scissor-action-type gear mechanism the double-face arcuate pistons A and B reciprocate inside the annular cylinder while rotating imparting torque to the main shaft 23.

It will be understood that although the invention described are for two and four combustion chambers for the two-cycle and four-cycle rotary internal combustion engine, additional sets of annular cylinder blocks, cylinder heads and doubleface arcuate pistons are applicable to form more chambers. This engine is not also limited to be used as gasoline engine but can be also used as a diesel engine with minor modifications.

Having my invention described and illustrated, various modifications will be obvious to those skilled in the art without departing from the principle involved and as such be included within the scope ofthe invention as claimed.

Iclaim:

l. A rotary internal combustion engine comprising, in combination, support means; a first shaft rotatably mounted on said support means; an annular cylinder block coaxially surrounding said first shaft and connected thereto for rotation therewith, said annular cylinder block having a pair of diametrically opposite walls dividing the interior of said annular cylinder block into two compartments; a pair of double-faced arcuate pistons respectively located in said compartments and each forming between one face thereof and one of said dividing walls a first chamber and between the other face'thereof and the other dividing wall a second chamber; a hollow second shaft journaled on said first shaft, said second shaft being connected to said pistons for rotation therewith; inlet and outlet ports communicating with said chambers; means for supplying a metered fuel charge through said inlet ports into said chambers; means communicating at least with said first chamber for igniting a fuel charge compressed therein to thereby rotate said arcuate pistons relative to said annular cylinder block; and means controlling the relative rotation of said annular cylinder block and said arcuate pistons.

2. An engine as defined in claim 1, wherein each of said first chambers forms a combustion chamber and each of said second chambers forms a pumping chamber, and including an enclosed annular space coaxial with said annular cylinder block and rotary valve means forming part of said first shaft for connecting and disconnecting said means for supplying a metered fuel charge with said annular space, said inlet ports comprising a first port for each of said pumping chambers and providing communication between said annular spade and the respective pumping chamber, and a second port for each combustion chamber and providing communication between said annular space and the respective combustion chamber, and said outlet ports comprising an exhaust port for eachof said combustion chamber.

3. An engine as defined in claim 1, wherein each of said chambers constitutes a combustion chamber, one inlet port, one outlet port and a means for igniting a compressed fuel charge being provided for each of said chambers, and including passage means providing communication between said inlet ports and said means for supplying a metered fuel charge to said chambers, valve means in each of said ports, and stationary cam means for controlling said valve means.

4. An engine as defined in claim 3, wherein said inlet and outlet ports are located closely adjacent said dividing walls, each of said valve means comprising a valve seat at the respective port, a valve member reciprocable relative to said seat between an open and a closed position, a valve stem connected to said valve member, and a guided plunger between each valve stem and said cam means for reciprocating said valve member during rotation of said annular cylinder block relative to said stationary cam means.

5. An engine as defined in claim 1, wherein said controlling means comprise a sun gear coaxial with said first shaft and fixedly mounted on said support means, a pair of diametrically opposed planet gears meshing with said sun gear, a first pair of radial arms fixed to and projecting in opposite direction from said first shaft, a second pair of radial arms fixed to and projecting in opposite direction from said hollow second shaft, a crank pin journaled at the free end of each of said first pair of arms and each carrying one of said planet gears, a crank arm fixed to each crank pin, and a pair of connecting rods each connecting a respective crank arm with the free end of one of said second pair of arms.

6. An engine as defined in claim 1 and including a pair of said cylinder blocks arranged coaxially and axially spaced from each other and both connected to said first shaft for rotation therewith, each of said annular cylinder blocks having a pair of diametrically opposite walls dividing each of said annular cylinder blocks into two compartments, a pair of said double-faced arcuate pistons being respectively located in said compartments of each of said annular cylinder blocks, each of said pistons forming between one face thereof and one of said dividing walls a combustion chamber and between the other face thereof and the other dividing walla pumping chamber, said igniting means communicating with said combustion chambers, a pair of axially extending connecting pins respectively connecting the pair of arcuate pistons in one of said annular cylinder blocks with the pair of arcuate pistons in the other of said annular cylinder blocks, said hollow second shaft being connected to said pair of pins by a pair of axially spaced and radially extending arms, and said control means being in part located between said pair of annular cylinder blocks.

7. An engine as defined in claim 6, wherein said control means comprise a pair of coaxial and axially spaced sun gears fixedly mounted on said support means, a pair of diametrically opposite planet gears for each sun gear, two pairs of opposite extending radial connecting arms respectively connecting said pair of annular cylinder blocks with said first shaft, two cranks each having a pair of oppositely projecting first crank pins journaled in said connecting arms, a pair of crank arms fixed at one end thereof to the inner ends of said crank pins and connected to each other at the other ends thereof by a further crank pin, said planet gears being respectively fixed to the outer ends of said first crank pins, and a pair of connecting rods connecting the respective further crank pin with the respective connecting pins.

8. An engine as defined in claim 1, wherein said support means comprises a casing enclosing at least said control means.

Claims (8)

1. A rotary internal combustion engine comprising, in combination, support means; a first shaft rotatably mounted on said support means; an annular cylinder bloCk coaxially surrounding said first shaft and connected thereto for rotation therewith, said annular cylinder block having a pair of diametrically opposite walls dividing the interior of said annular cylinder block into two compartments; a pair of doublefaced arcuate pistons respectively located in said compartments and each forming between one face thereof and one of said dividing walls a first chamber and between the other face thereof and the other dividing wall a second chamber; a hollow second shaft journaled on said first shaft, said second shaft being connected to said pistons for rotation therewith; inlet and outlet ports communicating with said chambers; means for supplying a metered fuel charge through said inlet ports into said chambers; means communicating at least with said first chamber for igniting a fuel charge compressed therein to thereby rotate said arcuate pistons relative to said annular cylinder block; and means controlling the relative rotation of said annular cylinder block and said arcuate pistons.
2. An engine as defined in claim 1, wherein each of said first chambers forms a combustion chamber and each of said second chambers forms a pumping chamber, and including an enclosed annular space coaxial with said annular cylinder block and rotary valve means forming part of said first shaft for connecting and disconnecting said means for supplying a metered fuel charge with said annular space, said inlet ports comprising a first port for each of said pumping chambers and providing communication between said annular spade and the respective pumping chamber, and a second port for each combustion chamber and providing communication between said annular space and the respective combustion chamber, and said outlet ports comprising an exhaust port for each of said combustion chamber.
3. An engine as defined in claim 1, wherein each of said chambers constitutes a combustion chamber, one inlet port, one outlet port and a means for igniting a compressed fuel charge being provided for each of said chambers, and including passage means providing communication between said inlet ports and said means for supplying a metered fuel charge to said chambers, valve means in each of said ports, and stationary cam means for controlling said valve means.
4. An engine as defined in claim 3, wherein said inlet and outlet ports are located closely adjacent said dividing walls, each of said valve means comprising a valve seat at the respective port, a valve member reciprocable relative to said seat between an open and a closed position, a valve stem connected to said valve member, and a guided plunger between each valve stem and said cam means for reciprocating said valve member during rotation of said annular cylinder block relative to said stationary cam means.
5. An engine as defined in claim 1, wherein said controlling means comprise a sun gear coaxial with said first shaft and fixedly mounted on said support means, a pair of diametrically opposed planet gears meshing with said sun gear, a first pair of radial arms fixed to and projecting in opposite direction from said first shaft, a second pair of radial arms fixed to and projecting in opposite direction from said hollow second shaft, a crank pin journaled at the free end of each of said first pair of arms and each carrying one of said planet gears, a crank arm fixed to each crank pin, and a pair of connecting rods each connecting a respective crank arm with the free end of one of said second pair of arms.
6. An engine as defined in claim 1 and including a pair of said cylinder blocks arranged coaxially and axially spaced from each other and both connected to said first shaft for rotation therewith, each of said annular cylinder blocks having a pair of diametrically opposite walls dividing each of said annular cylinder blocks into two compartments, a pair of said double-faced arcuate pistons being respectively located in said compartments of each of said annular cylinder blocks, each of said pistons forming Between one face thereof and one of said dividing walls a combustion chamber and between the other face thereof and the other dividing wall a pumping chamber, said igniting means communicating with said combustion chambers, a pair of axially extending connecting pins respectively connecting the pair of arcuate pistons in one of said annular cylinder blocks with the pair of arcuate pistons in the other of said annular cylinder blocks, said hollow second shaft being connected to said pair of pins by a pair of axially spaced and radially extending arms, and said control means being in part located between said pair of annular cylinder blocks.
7. An engine as defined in claim 6, wherein said control means comprise a pair of coaxial and axially spaced sun gears fixedly mounted on said support means, a pair of diametrically opposite planet gears for each sun gear, two pairs of opposite extending radial connecting arms respectively connecting said pair of annular cylinder blocks with said first shaft, two cranks each having a pair of oppositely projecting first crank pins journaled in said connecting arms, a pair of crank arms fixed at one end thereof to the inner ends of said crank pins and connected to each other at the other ends thereof by a further crank pin, said planet gears being respectively fixed to the outer ends of said first crank pins, and a pair of connecting rods connecting the respective further crank pin with the respective connecting pins.
8. An engine as defined in claim 1, wherein said support means comprises a casing enclosing at least said control means.
US3645239D 1969-10-24 1969-10-24 Rotary piston machine Expired - Lifetime US3645239A (en)

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US3739755A (en) * 1970-11-13 1973-06-19 R Folstadt Rotary engine
US3909162A (en) * 1970-12-03 1975-09-30 Ata Nutku Toroidal chamber rotating piston machine
US3990405A (en) * 1975-01-16 1976-11-09 Joseph Kecik Rotary internal combustion engine
US4010716A (en) * 1974-07-12 1977-03-08 Karlis Minka Rotary engine
US4035111A (en) * 1975-08-06 1977-07-12 Cronen Sr Peter J Toroidal rotary engine
US4132078A (en) * 1976-07-27 1979-01-02 Enginor Ag Piston machine
US4679535A (en) * 1986-01-06 1987-07-14 Stadden Richard S Dual action geneva cam and rotary internal combustion engine and pump utilizing same
EP0345745A2 (en) * 1988-06-09 1989-12-13 Gil-Hwan Chun Rotary piston engine
US6071098A (en) * 1995-09-19 2000-06-06 Richards; Ronald Leslie Rotary internal combustion engines
US6158987A (en) * 1998-01-13 2000-12-12 Raikamo; Esko Power unit for use as a pressure-fluid operated motor and/or a pressure fluid pump
US6371743B1 (en) 1995-09-19 2002-04-16 Ronald Leslie Richards Rotary internal combustion engines
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US20050016494A1 (en) * 2003-02-04 2005-01-27 Udy Joseph Dale 4-Cycle, rotary, electromagnetic, internal combustion engines
US20060070602A1 (en) * 2004-10-04 2006-04-06 Georgescu Petrica L Rotary internal combustion engine
US20060225691A1 (en) * 2005-04-12 2006-10-12 Mccoin Dan K Differential with guided feedback control for rotary opposed-piston engine
US20060231062A1 (en) * 2004-05-27 2006-10-19 Wright Michael D Orbital engine
US20070137613A1 (en) * 2005-12-16 2007-06-21 Reisser Heinz-Gustav A Internal combustion engine
US20080050258A1 (en) * 2006-08-24 2008-02-28 Wright Michael D Orbital engine
US20080251043A1 (en) * 2007-04-13 2008-10-16 Yan Li Housing wheel engine
US20080314350A1 (en) * 2005-12-16 2008-12-25 Reisser Heinz-Gustav A Rotary piston internal combustion engine
US20100108021A1 (en) * 2007-03-28 2010-05-06 Waldemar Kurowski Rotary piston engine
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Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3739755A (en) * 1970-11-13 1973-06-19 R Folstadt Rotary engine
US3909162A (en) * 1970-12-03 1975-09-30 Ata Nutku Toroidal chamber rotating piston machine
US4010716A (en) * 1974-07-12 1977-03-08 Karlis Minka Rotary engine
US3990405A (en) * 1975-01-16 1976-11-09 Joseph Kecik Rotary internal combustion engine
US4035111A (en) * 1975-08-06 1977-07-12 Cronen Sr Peter J Toroidal rotary engine
US4132078A (en) * 1976-07-27 1979-01-02 Enginor Ag Piston machine
US4679535A (en) * 1986-01-06 1987-07-14 Stadden Richard S Dual action geneva cam and rotary internal combustion engine and pump utilizing same
EP0345745A2 (en) * 1988-06-09 1989-12-13 Gil-Hwan Chun Rotary piston engine
EP0345745A3 (en) * 1988-06-09 1990-03-28 Gil-Hwan Chun Rotary piston engine
US6371743B1 (en) 1995-09-19 2002-04-16 Ronald Leslie Richards Rotary internal combustion engines
US6071098A (en) * 1995-09-19 2000-06-06 Richards; Ronald Leslie Rotary internal combustion engines
US6158987A (en) * 1998-01-13 2000-12-12 Raikamo; Esko Power unit for use as a pressure-fluid operated motor and/or a pressure fluid pump
US6739307B2 (en) * 2002-03-26 2004-05-25 Ralph Gordon Morgado Internal combustion engine and method
US20040211387A1 (en) * 2002-03-26 2004-10-28 Morgado Ralph Gordon Internal combustion engine and method
US20070199537A1 (en) * 2002-03-26 2007-08-30 Morgado Ralph G Internal Combustion Engine and Method
US20040149252A1 (en) * 2003-02-04 2004-08-05 Udy Joseph D. Rotary, electromagnetic, internal combustion engines
US20040255899A1 (en) * 2003-02-04 2004-12-23 Udy Joseph D. Two-cycle rotary engines
US20050016494A1 (en) * 2003-02-04 2005-01-27 Udy Joseph Dale 4-Cycle, rotary, electromagnetic, internal combustion engines
US6948473B2 (en) 2003-02-04 2005-09-27 Joseph Dale Udy 4-cycle, rotary, electromagnetic, internal combustion engines
US6962137B2 (en) 2003-02-04 2005-11-08 Joseph Dale Udy Two-cycle rotary engines
US6880494B2 (en) * 2003-07-22 2005-04-19 Karl V. Hoose Toroidal internal combustion engine
US20050016493A1 (en) * 2003-07-22 2005-01-27 Hoose Karl V. Toroidal internal combustion Engine
US20060231062A1 (en) * 2004-05-27 2006-10-19 Wright Michael D Orbital engine
US20100095926A1 (en) * 2004-05-27 2010-04-22 Wright Innovations, Llc Orbital engine
US7182061B2 (en) * 2004-10-04 2007-02-27 Petrica Lucian Georgescu Rotary internal combustion engine
US20060070602A1 (en) * 2004-10-04 2006-04-06 Georgescu Petrica L Rotary internal combustion engine
US7472676B2 (en) * 2005-04-12 2009-01-06 Mccoin Dan K Differential with guided feedback control for rotary opposed-piston engine
US20060225691A1 (en) * 2005-04-12 2006-10-12 Mccoin Dan K Differential with guided feedback control for rotary opposed-piston engine
US8944025B2 (en) 2005-12-16 2015-02-03 Heinz-Gustav A. Reisser Rotary piston internal combustion engine
US7415962B2 (en) * 2005-12-16 2008-08-26 Reisser Heinz-Gustav A Internal combustion engine
US8033265B2 (en) 2005-12-16 2011-10-11 Reisser Heinz-Gustav A Rotary piston internal combustion engine
US20070137613A1 (en) * 2005-12-16 2007-06-21 Reisser Heinz-Gustav A Internal combustion engine
US20100307449A1 (en) * 2005-12-16 2010-12-09 Reisser Heinz-Gustav A Rotary piston internal combustion engine
US20080314350A1 (en) * 2005-12-16 2008-12-25 Reisser Heinz-Gustav A Rotary piston internal combustion engine
US8944015B2 (en) 2005-12-16 2015-02-03 Heinz-Gustav A. Reisser Rotary piston internal combustion engine
US8151759B2 (en) 2006-08-24 2012-04-10 Wright Innovations, Llc Orbital engine
US20080050258A1 (en) * 2006-08-24 2008-02-28 Wright Michael D Orbital engine
US20100108021A1 (en) * 2007-03-28 2010-05-06 Waldemar Kurowski Rotary piston engine
US8297253B2 (en) * 2007-03-28 2012-10-30 Waldemar Kurowski Rotary piston engine
US20080251043A1 (en) * 2007-04-13 2008-10-16 Yan Li Housing wheel engine
US7730869B2 (en) * 2007-04-13 2010-06-08 Yan Li Housing wheel engine

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