GB2384028A

GB2384028A - Rotary piston internal combustion engine

Info

Publication number: GB2384028A
Application number: GB0200410A
Authority: GB
Inventors: Chahe Kaloustian
Original assignee: Individual
Current assignee: Individual
Priority date: 2002-01-09
Filing date: 2002-01-09
Publication date: 2003-07-16
Also published as: WO2003058037A1; GB0200410D0; AU2002356337A1

Abstract

A rotary piston internal combustion engine, motor, pump or compressor comprising two sets of a plurality of pistons 2,3,4,5,6,7,8, & 9. The pistons rotate within a toroidal or annular chamber formed from two halves 10 & 12. The drive mechanism is an epicyclic gear train formed from at least two sets of two meshing equal non circular gears 38 (39) rotating about their geometric axis and two sets of unequal circular gears 28 (29). Each set is housed on either side of the toroidal chamber.

Description

ROTARY PISTON INTERNAL COMBUSTION ENGINE

This invention relates to a Rotary Internal Combustion Engine, motor, pump or compressor of the revolving block type in which two sets of a plurality of pistons mechanically coupled to discs move toward, then parallel to and away from each other.

In such engines different types of mechanisms translate reciprocating motion of the pistons into rotary output shaft motion by way of a combination of mechanical components such as cams, locks, gear-cams, planetary gear trains, non-circular gears, shaft-gears, elliptical eccentric gear arrangements. The pistons are generally vane type, arcuate type or a variation of these types. In the Wankel, the rotor replaces the piston. In the toroidal chamber design, the mechanisms generating the desired movement of the pistons are housed on one side or both sides of the toroid or the annular ring. The output shaft is connected to the mechanism.

In Rotary Internal Combustion Engines a major disadvantage arises from the complexity of the mechanisms that contain reciprocating elements with reversal of direction, complex and odd shapes and have not been fabricated on commercial scale. Experimentation on the Wankel engine too since 1957 has not resulted currently in production for automobiles and the automotive industry as a whole. In the Wankel engine rotor design the disadvantage is the low torque, high speed, high fuel consumption, special tooling, special sealing, gears exposed to the heat of combustion, large power wastage that all are inherent to the triangular rotor design.

Reference to US patent 3,822,971, the means used to perform the cycles in the four-stroke internal combustion engine do not provide repetitive cycles with the first order elliptic gears rotating around their foci due to the great precision required in fabrication in addition to the complications created by the requirement for dynamic balancing of the planetary system. Also the tolerances for normal wear and tear incorporated into the design is not achievable in practice with the gear arrangement disclosed resulting in piston reversal and irregular cycles. Thus it is found that the engine disclosed in US3,822,97 1 is not practical.

The object of this invention is to alleviate the complexities in the design of the mechanisms.

According to its broadest aspect, the present invention provides a fourstroke rotary piston internal combustion engine of the revolving block type operated with the sequence of suction, compression, power and exhaust strokes of a four-stroke internal combustion engine, in which the moving parts rotate generally unidirectionally and around their geometric centers and comprising a toroidal chamber split along a plane perpendicular to the toroidal axis in which two piston sets, each including at least two pistons, capable of orbiting within the toroidal chamber, each piston set having arms extending radially through the circumferential slot formed around the chamber and coupled to a power transmission and a manifold adapted to control the induction and discharge of compressible fluid to spaces between the pistons, whereby the combustion of the fluid or decompression of the fluid in one of the spaces causes the piston of one set to advance along its orbit relative to the piston of another set so rotating an output shaft coupled to the transmission with a total number of firing cycles in one revolution of the shaft output rotation in accordance with the general formula of n*m*(p+1)/4 wherein n is the number of pairs of pistons, m is the order of the non-circular gears and (p+1) is the denominator of the circular gear ratio p/(p+1) as obtained from the analysis of the meshing of gears in the epicyclic gear system wherein the central circular gear carries the set of pistons attached to the disc plate and orbiting in the toroidal cylinder and wherein other combinations of circular gear ratios and

geometries of non-circular gears provide many more possibilities of firing cycles preferably in multiples of three for every 360 degrees rotation of the shaft output as obtained from analysis of piston movement orbiting the toroidal cylinder wherein any type of fuel used in internal combustion engines and at different compression ratios varying between 2. 5 and 12 depending upon the type of fuel used would be applied. The non- circular contour of the gears of the second order and higher is achievable in practice and produce substantially parallel movement of consecutive pistons, as described by the mathematical relationship HE = 42/m) (N /N) [tan- (a/b)tan O] of the angular displacement between piston input and shaft output and associated graph, wherein combustion takes place at substantially constant volume. The term combustion in the present context is used to describe the burning of the fuel-

air mixture.

A further object of this invention is to provide a solution to the fundamental problem of tolerance margin both for fabrication and for normal wear and teat in operation without appreciably affecting engine performance.

A still further object ofthis invention is to make use of higher order of at least twin non-circular gears rotating about their geometric centers and the uniform polygonal contour of which defines the order of the gear. Thus a three-sided polygon will define a third order non-circular gear. A square will be termed as a fourth order non-circular gear, and so on. The contour of each of these polygons is a repetitive curve that produces a long dwell followed by a short dwell. One set is in mesh with another set with a phase difference.

According to the present invention there is provided an annular cylindrical toroidal chamber split along a plane perpendicular to the toroidal axis wherein one set of two arcuate pistons or more rotate unidirectionally by accelerating and decelerating out of phase with another equivalent set of two arcuate pistons or more. Each set contains an equal number of arcuate pistons. The arcuate pistons of one set are mechanically coupled to the arms of a disc at equal spacing over the circumference of the disc plate. The disc plate is located in a housing and the arms protrude from the housing into the annular chamber through a circumferential slot along its inner periphery and unto which the arcuate pistons are mounted. The sealing of the annular cylinder between consecutive arcuate pistons is effected by the spring effect of two arcuate piston rings of the one set acting as the piston crown and the spring effect of two arcuate pistons rings of the other set acting as the cylinder head. Sealing of the annular cylinder containing the arcuate pistons between the chamber and the rotating disc is effected by a circumferential mechanical seal which is spring loaded and provided with adjusting screw. Sealing between the two disc plates onto which are mounted the two sets of arcuate pistons is effected by annular circular seals. Sealing of the annular cylinder between the arcuate piston rings and the circumferential mechanical seal is effected by an obturator. To the disc plate, at its geometric center, a circular gear is mechanically fixed. The arcuate pistons of the set, the corresponding circular disc plate and the gear revolve as one assembly block around the central output shaft and independent from it by way of bearings. To the output shaft is keyed an arm that holds a small shaft mounted on bearings. On the one side of the arm is a circular gear that meshes with the circular gear of the disc plate. On the other side of the arm is a poncircular gear. The noncircular gear meshes with an identical noncircular gear that is held to the housing in a fixed position. The assembly thus formed is an epicyclic gear train. During the passage of the piston, portholes that are positioned at predetermined locations are alternately covered and uncovered and act as the inlet and exhaust ports. The number of 'cycles per revolution' listed in the matrix requires different methods of covering and uncovering the portholes. In the one category, as in the preferred embodiment, the movement of the pistons covers and uncovers the portholes. In a different category known but not made part of the preferred embodiment, two sets of portholes are required wherein external means are provided for one set to be uncovered during one at, ,

revolution of the output shaft and the second set of portholes to be uncovered during the next revolution thus alternating between one set for one rotation and the other set for the next rotation of the output shaft. This is repeated in a reciprocating manner over the continuous output rotation. This category obviously is more complicated and more expensive for fabrication and is not pursued in the present invention. According to this invention, several identical units can be coupled in tandem to generally produce power output or input in multiple, of one unit.

A specific embodiment of the invention will now be described by way of example, wherein four pairs of pistons in a Spark Ignition engine are used, four on each set, with fourth degree non-

circular gears, compression ratio of 6 and ratio of circular gears of 2:3, and twelve firmg cycles for each revolution of the output shaft, as highlighted in the attached matrix of cycles per revolution, and with reference to the accompanying drawings in which: Figure 1 shows an axial cutaway view of a water-cooled engine.

Figure 2 shows an axial cutaway view of an air-cooled engine.

Figure 3 shows the main components of the engine, motor, pump, compressor mechanism in plan view.

Figure 4 shows schematically the main components of the engine, motor, pump, compressor mechanism across the output shaft.

Figure 5 shows the instantaneous position of the two sets of piston pairs wherein firing occurs between the two consecutive pistons 2 & 6 at position zero and 4 & 8 at position IT.

Figure 6 shows the firing positions between pistons 6 & 3 at position C/3 and 5& 8 at position 47rl3. Figure 7 shows the firing positions between pistons 3 & 7 at position 2nd; and 5 & 9 at position 57 /3.

Figure 8 shows the firing positions between pistons 7 & 4 at position add 9 & 2 at position 2.

Figure 9 shows the flung positions between pistons 2 & 6 at position /3 and 4 & 8 at position 47 /3 Figure 10 shows the firing positions between pistons 6 & 3 at position 2'T/,3 and 5 & 8 at position 57 /3 Figure 11 shows the firing positions between pistons 3 & 7 at position and 5 & 9 at position 2 Figure 12 shows the firing positions between pistons 7 & 4 at position n/3 and 9 & 2 at position 4;cl3 Figure 13 shows the firing positions between pistons 2 & 6 at position 27 13 and 4 & 8 at position 5'T/3:

Figure 14 shows the firing positions between pistons 5 & 8 at position and 6 & 3 at position 2 Figure 15 shows the firing positions between pistons 5 & 9 at position /3 and 3 & 7 at position 47 13

Figure 16 shows the firing positions between pistons 9 & 2 at position 27 /3 and 7 & 4 at position 57 /3 Figure 17 shows schematically the annular cylinder with the spark plugs in position and the distribution of exhaust and intake portholes.

Figure 18 portrays the graph of the unidirectional motion of the four pistons with output shaft rotation and the firing positions. The pistons rotate through 120 degrees for one complete revolution of the output shaft.

Figure 19 shows a close-up view of the substantially constant spacing during the ignition and combustion phase.

Figure 20 represents the third order non-circular gear.

Figure 21 represents the fourth order non-circular gear.

Figure 22 represents the eighth order non-circular gear.

Figure 23 represents the engine assembly.

Figure 24 represents three engines coupled in tandem along a given axis.

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Referring to the drawings the engine construction comprises eight pistons 2, 3, 4 &: 5 rotating within an annular cylindrical toroidal chamber formed by two halves 10 and 12. A piston set is provided by a plurality of pistons 2, 3,4 & 5 coupled to a transmission via a plurality of arms extending radially from a circular plate 14 to which the pistons are mechanically held through Penn Dins 16 17.1X &;19 respectively. A circular Rear 26 is held onto the circular disc plate

position 81 is ready to be ignited by the two spark plugs 53 and 55. Piston 7 has advanced toward piston 4 and expelled burnt gases through porthole 104. At the same time the intake charge is drawn in through porthole 93, while piston 3 advances slightly to cover the exhaust port 103. Piston 8 has completed the power stroke, uncovered exhaust porthole 105 and ready to exhaust the burnt gases. At the same time piston 8 compresses the charge by moving toward

piston input/shaft output angular rotational relationship using the second order non-circular gears is given by the following relationship: 0i2 = go - (N3/N4) [tan- (a/b)tan O] For the third order non-circular gears shown in figure 19, the piston input/shaft output angular rotational relationship is given by the following relationship: 0i3= po- 2/3 (N3/N4) [tan-'(alb)tan(3/2)q'0] For the fourth order non-circular gears shown in figure 20, the piston inp utlshaft output angular rotational relationship is given by the following relationship: 0i4= po- 1/2 (N3/N4) [tan-l(a/b)tan2<pO] wherein 2, Di3, Gil are the piston input rotation in degrees using second, third and fourth order non-circular gears respectively, NO is the shaft output rotation associated with the corresponding order of gears, N3/N4 is the ratio or circular gears, a is half the major axis of the non-circular gear contour, b is half the minor axis of the non-circular gear contour. For the fifth and higher order noncircular gears, the following relationship between piston input/shaft output angular rotation applies to the repetitive sections of the associated non-circular contours: IF2VI + IF3VI = k wherein the arc between the two apexes of the non-circular gear is a sector of an ellipse. This sector along the perimeter of the non-circular gear repeats itself between each apex or pointed tip and k is a constant number defined by the geometry of the non-circular gear and provides an infinite number of options from which selections will need to be made for any preferred embodiment and given by the following generic relationship.

0illl = 2/m) (N3/N4) [tan-l(a/b)tanq)O] wherein m is the order of the noncircular gear and 0= is the generic piston input rotation in degrees using mu order non-circular gear. Other terms are as described above.

Figure 23 shows three identical and equally sized engines, motors, pumps or compressors 110, 112 and 114 wherein mechanical shaft coupling 116, between 110 and 112, and mechanical shaft coupling 118, between 112 and 114, are used to obtain three times the output power at the power takeoff shaR 120 of one, or requires three times the power input of one at the input shalt 120.

1 A rotary piston four-stroke internal combustion engine of the revolving block type operated with the sequence of suction, compression, power and exhaust strokes of a four-stroke internal combustion engine, in which the moving parts rotate genera-fly unidirectionally and around their geometric centers and comprising a toroidal chamber split along a plane perpendicular to the toroidal axis in which two piston sets, each including at least two pistons, capable of orbiting within the toroidal chamber, each piston set having anns extending radially through the circumferential slot formed around the chamber and coupled to a power transmission and a manifold adapted to control the induction and discharge of compressible fluid to spaces between the pistons, whereby the combustion of the fluid or decompression of the fluid in one of the spaces causes the piston of one set to advance along its orbit relative to the piston of another set so rotating an output shaft coupled to the transmission with a total number of firing cycles in one revolution of the shaft output rotation in accordance with the general formula of n*m*(p+1)/4 wherein n is the Rumba of pairs of pistons, m is the order of the nonsecular gears and (p+1) is the denominator of the circular gear ratio p/(p+1) as obtained from the analysis of the meshing of gears in the epicyclic gear system wherein the central circular gear carries the set of pistons attached to the disc plate and orbiting in the toroidal cylinder and wherein other combinations of circular gear ratios and geometries of non ircular gears provide many more possibilities of firing cycles preferably in multiples oftbree for every 360 degrees rotation ofthe shaft output as obtained from analysis of piston movement orbiting the toroidal cylinder wherein any type of fuel used in spark ignition internal combustion engines and at different compression ratios varying between 2.5 and 12 depending upon the type of fuel used and in compression ignition internal combustion engines at different compression ratios varying between 18 and 25 and depending upon the type of fuel used would be applied.

2. A rotary piston engine according to claim 1 wherein the total number of firing cycles per one complete revolution of the output shaft is a multiple of three and the total number of pistons is a multiple of four.

3.A rotary piston two-stroke internal combustion engine of the revolving block type operated with the sequence of power/exhaust/scavenging, compression strokes of a two-stroke internal combustion engine, in which the moving parts rotate generally unidirectionally and around their geometric centers as in claim 1 with a firing in accordance with the general formula of n*m*(p+l)/2 wherein notation is as in claim 1.

4 A rotary piston motor of the revolving block type in which the moving parts rotate generally unidirectionally and around their geometric centers and comprising a toroidal chamber split along a plane perpendicular to the toroidal axis, in which two piston sets, each including at least two pistons, capable of orbiting within the toroidal chamber, each piston set having arias extending radially through the circumferential slot formed around the chamber and coupled to a power transmission and a manifold adapted to control the induction and discharge of compressible or noncompressible fluid to the spaces between the pistons, whereby the pressure of the fluid in one of the spaces causes the piston of one set to advance along its orbit relative to the piston of another set so rotating an output shaft coupled to the transmission with fluid pulses in accordance with the general formula n*m*(p+l)/2 wherein the letters have the same notation as in claim 1.

5 A rotary piston pump of the revolving block type in which the moving parts rotate generally unidirectionally and around their geometric centers and comprising a toroidal chamber splitalong a plane perpendicular to the toroidal axis, in which two piston sets, each including at least two pistons, capable of orbiting within the toroidal chamber, each piston set having alms extending radially through the circumferential slot formed around the chamber and coupled to a

non-compressible fluid to the space between the pistons whereby the rotation of the one set of pistons advancing along its orbit relative to the pistons of another set causes the pressure of the fluid in one of the spaces to increase so supplying a non-compressible fluid at higher pressure to a manifold wherein the application of torque to a power transmission causes the pistons of one set to advance around the chamber towards the piston ofthe other set so compressing or causing intake of the fluid trapped between the pistons with pulses in accordance with the general fonnula n*m$(p+1)/2 as in claim 4 above.

6 A rotary piston compressor of the revolving block type according to claim 5 wherein the fluid is compressible.

7 A rotary piston four-stroke internal combustion engine according to claims 1 and 2, and configured in a preferred embodiment for a toroidal mean diameter of 1 80mm with two piston pairs, second order non ircular gears and circular gear ratio of 2/3 in particular, wherein non-

circular gears rotating about their geometric axes, the preferred embodiment having firing cycles for every 120 degrees rotation in particular, performing the sequence of the four-stroke engine cycles wherein the back side of a piston acting as a moving cylinder head to the piston behind it and providing a net rotating torque through the mechanism in which the reaction torque is transmitted through the static non-circular gear to the frame holding the engine in which the centerline distance between the non-circular gears and circular gears is obtained by trial and error for different number of gear teeth and gear tooth module combinations and in which the spark plug location and the positioning of the injector, exhaust and intake ports location are determined by analysis of the positions of the pistons orbiting within the toroidal chamber according to the formula = - - (N3/N4)[tan-l(a/b tan].

8 A rotary piston four-stroke internal combustion engine according to claim 7 wherein circular gears having a ratio different from one, determine the number of firing cycles for each complete revolution of the output shaft for a given set of pistons and non-circular gears as obtained from analysis of the piston motion along the toroidal orbit for each of the circular gear ratios of I/, 213, 3/d, 4/5, 5/6 and deducibly extrapolated for higher circular gear ratios p/(p+l) approaching but less than one to arrive at each of the numbers in the matrix included in the specifications,

other combinations of non-circular geometries and circular gear ratios providing many more poss b ht es.

9 An engine according to clanns 7 and 8 wherein the number of firing cycles for every 360 degrees rotation of the output shaft is less than or equal to six applied preferably to the automobile industry, bikes, leisure vehicles, motor boats and applications covering small power engines and others of similar nature for fractional up to 20 horsepower.

10 An engine according to claims 7 and 8 wherein the number of firing cycles for every 360 degrees rotation of the output shaft is greater than 6 and less than or equal to 18 and adapted preferably to large trucks, racing cars, medium size generators and engines greater than 20 horsepower up to and in the range of 1000 horsepower.

11 An engine according to claims 7 and 8 wherein the number of firing cycles for every 360 degrees rotation of the output shaft is greater than 18 and applicable preferably to greater than 1000 horsepower up to 50O, OOO horsepower or more such as in large stationary power generation plant and marine propulsion.

12 A rotary piston two stroke internal combustion engine according to claim 3 wherein circular gears having a ratio different from one, determine Me number of firing cycles for each complete revolution ofthe output shaft for a given set of pistons and non ircular gears as obtained from analysis of the piston motion along the to oidal orbit of the pistons for each of the circular gear

approaching but less than one to arrive at each of the numbers in the matrix included in the specifications, other combinations of non-circular geometries and circular gear ratios providing

many more possibilities the lower number of firing cycles for every 360degree shaft output rotation preferably 1 to 3 applied to small power engines and motorcycles.

13 A rotary piston four-stroke internal combustion engine according to claims 1, 2, 7 and 8, wherein combustion takes place both at substantially constant volume and constant pressure in both spark ignition and compression ignition engines.

14 A rotary piston two-stroke internal combustion engine according to claims 3 and 12, wherein combustion takes place at substantially constant volume and is cor gured in a preferred embodiment with two piston pairs with second order non-circular gears.

15 A rotary piston motor according to claim 4 wherein non-circular gears rotating about their geometric axes create constant pressure fluid pulses, of duration dependent on and determined by the geometry of the noncircular gears, and which for a preferred embodiment of two pairs of pistons, second order non-circular gears is 30 degrees rotation in particular performing the sequence of high pressure induction and driving the output shaft by pressing against the back side of a piston acting as a moving cylinder head to the piston behind it and providing a net rotating torque through the mechanism in which the reaction torque is transmitted through the static non-circular gear to the frame holding the engine in which the centerline distance between the non-circular gears and the circular gears is obtained by trial and error for different number of gear teeth and gear tooth module combinations and in which the induction and discharge ports locations are determined by analysis of the positions of the pistons orbiting within the toroid according to the formula 0a = NO (N3/N4) [tan-l(a/b)tanq o].

16 A rotary piston motor according to claims 4 and 15 wherein circular gears having a ratio different from one determine the number of high pressure pulses of the fluid for each complete revolution of the output shaft as obtained from the analysis of the piston motion along the toroidal orbit of the pistons for each of the circular gear ratios of l/, 2/3, 3/4, 415, 5/6 and deducibly extrapolated for higher circular gear ratios p/(p+l) approaching but less than one to arrive at each of the numbers in the matrLx included in the specifications, other combinations of

non-circular geometries and circular gear ratios providing many more possibilities, the higher number of pulses for every 360 degrees shaft output rotation, preferably 36 or more, being suited for large capacity hydroelectric power generation lOOMW or more.

17 A rotary piston pump according to claim 5 wherein pulses of noncompressible fluid for the preferred embodiment with two piston pairs, second order non-circular gears and circular gear ratio of 2/3 have pressure pulses every 30 degrees in particular performing the sequence of induction and pressurization wherein the back side of a piston acts as a moving cylinder head against which the piston behind it pressurizes the fluid imparting a reaction torque that is transmitted through the static non-circular gear to the frame holding the pump in which the centerline distance between the non-circular gears and circular gears are obtained by trial and error for different numbers of gear teeth and gear tooth module combinations and in which the induction and discharge ports are located based on the analysis of the positions of the pistons orbiting within the toroidal chamber accordingto the formula 0 = spa - (N /N) [tan-l(a/b)tan pO].

18 A rotary piston pump according to claims 5 and 17 wherein circular gears having a ratio different from one determine the number of discharge high pressure pulses of non-compressible fluid for each complete revolution of the input shaft as obtained from analysis of the pistonmotion along the toroidal orbit of the pistons for each of the circular gear ratios of A, 213, 3/4, 4/5, 5/6 and deducibly extrapolated for higher circular gear ratios p/(p+1) approaching but less than one to arrive at each of the numbers in the matrix included in the specifications, other

possibilities, the higher number of high pressure pulses of noncompressible fluid applied preferably in large capacity cross-country pumping through pipelines or in land irrigation pumping millions of gallons per day.

19 A rotary piston compressor according to claims 6, 17 and 18 applied to compressible fluid.

20 A rotary piston internal combustion engine, motor, pump or compressor as claimed in the preceding claims wherein an epicyclic gear train formed by two sets generates rotary motion from unidirectional circular oscillating motion and at 180-degree phase shift between the two sets. 21 A rotary piston four-stroke and two-stroke internal combustion engine, motor, pump or compressor according to the preceding claims wherein blocking and free passage through the intake/suction and exhaust/discharge ports is effected by the arcuate pistons covering and uncovering ports respectively on the toroidal cylinder as they advance along their toroidal orbit.

22 A rotary piston four-stroke and two-stroke internal combustion engine as claimed and described in any one of the preceding claims 1, 2, 3, 7, 8, 12, 13, 20 and 21 wherein two spark plugs are placed substantially facing each other at each flung position thereby reducing burn time. 23 A rotary piston four-stroke and two-stroke internal combustion engine according to the preceding claims 1, 2, 3, 7, 8, 12, 13, 20, 21 and 22 wherein rotation of an output shaft is reversed by changing the direction of the starter rotation and interchanging intake and exhaust manifolds. 24 A rotary piston motor according to claims 4, 15, 16, 20 and 21 wherein rotation of output shaft is reversed by reversing the direction of the fluid and interchanging induction and discharge manifolds.

25 A rotary piston pump according to claims 5, 17, 18, 20 and 21 wherein suction and discharge ports of the non-compressible fluid are reversed by reversing the direction of rotation of the input shaft and interchanging suction and discharge pipes or manifolds.

26 A rotary piston compressor according to claims 6, 19, 20 and 21 wherein suction and discharge ports of the compressible fluid are reversed by reversing the direction of rotation of the input shaft and interchanging suction and discharge pipes or manifolds.

27 A rotary piston four-stroke and two-stroke internal combustion engine according to claims 1, 2, 3, 7, 8, 9, 10, 11, 12, 13, 14, 20, 21, 22, 23, wherein intake and exhaust portholes are made to vary in size and shape while running and to thereby control engine performance.

28 A rotary piston motor, pump or compressor according to claims 4, 5, 6, 1 5,16,17,18, 19, 20, 21, 24, 25, 26, wherein suction and discharge portholes are made to vary in size and shape while running and to thereby control performance and output.

29 A rotary piston four-stroke and two-stroke internal combustion engine, motor, pump or compressor according to the preceding claims wherein identical or different size engines and motors are mounted in tandem by coupling Me shafts to produce double, triple or more multiple outputs of the same or different engines or motors along one single power takeoff shad and multiple pumps or multiple compressors are mounted in tandem along one single input shad to produce double, triple or more multiple outputs of the same or different pumps or compressors.

i

Claims

Amendments to the claims have been filed as follows Claims

1. A rotary piston four-stroke internal combustion engine of the revolving block type 5 operated with the sequence of suction, compression, power and exhaust strokes of a four-

stroke internal combustion engine, in which the moving parts rotate generally unidirectionally, and comprising a toroidal chamber split along a plane perpendicular to the toroidal axis in which two piston sets, each including at least two pistons, capable of orbiting within the toroidal chamber, each piston set having arms extending radially through the 10 circumferential slot formed around the chamber and coupled to a power transmission and a manifold adapted to control the induction and discharge of compressible fluid to spaces..

between the pistons, whereby À 5, the combustion of the fluid or decompression of the fluid in one of the spaces causes . the piston of one set to advance along its orbit relative to the piston of another set so rotating 6 e À;;. IS an output shaft, said output shaft being coupled to the transmission, said transmission comprising an epicyclic gear system having: '; a central circular gear coaxially coupled to a disc plate carrying the piston sets, ' a circular planetary gear meshed with the central circular gear, a non-circular planetary gear coaxially coupled with the circular planetary gear, and 20 said non-circular planetary gear meshing with a non-circular reaction gear, with a total number of firing cycles in one revolution of the shaft output rotation is equal to n m*(p+1 /4 where n is the number of pairs of pistons, m is the order of the non-circular gears and 2s the circular gear ratio = the ratio of the number of teeth of the circular planetary gear to the number of teeth of the central circular gear and p+ 1 = p / (the circular gear ratio) characterized in that the non-circular planetary gear is coupled to rotate around its

geometric axis.

2. An engine according to claim 1 wherein the non-circular planetary gear has a second or higher order geometry.

s

3. An engine according to claim 1 wherein the circular gear ratio and geometry of the non-circular gear is selected to provide an integer multiple of three firing cycles for every 360 degrees rotation of the output shaft.

10

4. An engine according to claim 2 wherein the total number of pistons is four or an integer multiple of four.

5. A rotary piston four-stroke internal combustion engine according to claims1 to 4 wherein the spark plug location and the positioning of the injector, exhaust and intake ports 15 location are determined according to the formula: Oi2 = (:po-(N31N4)[tan-1(a/b)tan po].

6. An engine, according to any one of claims 1 to 4 wherein the number of firing cycles for every 360 degrees rotation of the output shaft is less than or equal to six and has a power 20 output equal or less than 20HP.

7. An engine according to any one of the preceding claims in combination with one of: an automobile, bike, leisure vehicle or motor boat.

25

8. An engine, according to any one of claims 1 to 4 wherein the number of firing cycles for every 360 degrees rotation of the output shaft is from six to eighteen and has a power output in the range 20HP to 1000HP.

fly

9. An engine according to any one of the preceding claims in combination with one of: an automobile, large truck, racing car or medium size generator.

10. An engine according to any one of claims 1 to 4 wherein the number of firing cycles 5 for every 360 degrees rotation of the output shah is equal to or more than eighteen and has a power output of more than 1 OOOHP.

11. An engine according to claim 10 in combination with one of a large stationary power plant or marine vessel.

12. An engine according to one of claims 1 to 4 wherein combustion takes place both at substantially constant volume and constant pressure in both spark ignition and compression ignition engines.

13. An engine according to one of claims 1 to 4 wherein rotation of the output shaft is reversed by changing the direction of the starter rotation and interchanging intake and exhaust manifolds.

14. An engine according to claims 1 to 4 wherein intake and exhaust portholes are made 20 to vary in size and shape while running and to thereby control engine performance.

15. An engine according to claims 1 to 4 wherein engines are mounted in tandem by coupling the shafts to produce double, triple or more multiple outputs along one single power takeoff shaft.

16. A rotary piston two-stroke internal combustion engine of the revolving block type operated with the sequence of power/exhausVscavenging, compression strokes of a two-

stroke internal combustion engine, in which the moving parts rotate generally unidirectionally,