CZ151596A3 - Rotary engine with axial pistons - Google Patents

Abstract

The pistons include two sets, each having at least two pistons. The pistons of each set are at opposite sides of the axis of rotation of the rotor assembly, and output shaft and interconnected by piston-connection means so that the pistons of each set move in unison. The parts are so made and arranged that the piston cam follower means coact with the cam track in a manner ensuring that movement of either set of pistons in their cylinders is in the direction opposite to the direction of movement of the other set of pistons. The pistons of each set have their piston-connection in the form of a piston mounting plate having an aperture through which the output shaft extends. A number is provided where the piston mounting plate may be drivably connected to the output shaft as part of the rotor assembly while being permitted guided sliding movement in the direction along the axis and output shaft to permit movement of its pistons in their cylinders.

Description

The present invention relates to rotary internal combustion engines and in particular relates to an engine having different basic principles compared to many rotary engines that have been developed to date.

BACKGROUND OF THE INVENTION

The most known types of rotary motors that have been invented over the past few years utilize a rotating block having radially mounted piston cylinders, the outer ends of which are movable relative to the guideways, as shown, for example, in German Patent Specification No. 619,955 by Bodd U.S. Patent Nos. 4,023,536 and 4,974,553. Highly sophisticated design solutions include appropriate auxiliary mechanisms that substantially affect the operation of these engines, such as means that allow periodic introduction of air and fuel into the combustion chamber for each cylinder and piston.

We have recently developed a rotary engine with radial pistons, ύ

that comes out. of this general concept, which is described in ΐ our Australian Provisional Patent Application No. PN6474, and which we believe has a number of advantages over prior art solutions in the art of designing rotary motors having radial pistons.

However, our development in this field of technology, which is currently popular, has led us to explore another type of rotary engine in which the cylinders are equidistant from each other about a central axis and the pistons are guided parallel to each other and to said axis. Examples of this basic type of parallel-cylindrical rotary engine can be found in U.S. Patent Specification Nos. 4,287,858 (Anzalone), 4,250,283 (Chang) and 4,022,167 (Kristiansen). However, all these examples of rotary motors have very complicated design solutions, the pistons require complex assembly and guidance, so the assemblies are too long. When separate pistons are used, each being assembled independently of the others, the engine assemblies are heavy, expensive and complicated.

SUMMARY OF THE INVENTION The present invention has been developed to overcome or avoid the problems currently encountered by known motor types in which the piston axes are parallel to one another and are disposed about a central axis, the main object will develop new propulsion means to ensure maximum performance when using cylinders and pistons of relatively short length.

It is a further object of the present invention to provide such an engine that will be lightweight, small in size, and will consist of a minimum number of components, particularly worn components. '' '

Yet another object of the present invention is to provide such an engine having the ability to burn gasoline or other combustible fuel and which is an improved rotary engine of the above type wherein all fuel is burned at maximum fuel efficiency and where the emission of harmful exhaust emissions is reduced. Other objects and advantages of the present invention will be set forth below.

In view of the foregoing and other objects, the present invention, in a broad sense, relates to a rotary internal combustion engine of the type whose pistons are designed to reciprocate in respective cylinders that are spaced regularly and equidistantly about the longitudinal axis of rotation, said axis being the axis of rotation of a power transmission shaft extending rotatably and sealed through a bore in the first and second end plates of the engine housing in which the pistons and cylinders move as part of a rotary rotor assembly mounted to said power transmission shaft; the cam follower means are associated with each piston and are adapted to cooperate with the undulating cam track guided around the block, the fuel supply means supplying fuel for combustion, wherein the engine is characterized in that the pistons are assembled in two sets having at least two pistons, the pistons of each set being disposed on opposite sides of the rotor assembly rotation axis and the power transmission shaft, and interconnected by means of interconnecting pistons so that the pistons of one set move in the same and simultaneous manner and configured so that the piston cam follower means cooperate with the cam track means in such a way as to move the first set of pistons in their cylinders in one direction and the second set of pistons in the opposite direction.

In certain configurations, the means by which each piston stroke plate is coupled for propulsion to a power transmission shaft may include longitudinal splines formed on the power transmission shaft, wherein the sliding sliding but with the ability to provide rotation engages dp

- corresponding circumferential grooving of the opening of said piston lift plate.

* - - - - - -

The engine may have a varying number of cylinders, but each piston stroke plate typically has three, four, or more arms that are guided radially relative to the engine power transmission shaft, and mounted at the outer end of each arm piston. In a preferred embodiment, the first end plate has two diametrically opposed spark plugs which are said spark plugs or other suitable means, two diametrically opposed fuel injector sets, said fuel injector means, and two diametrically opposed exhaust outlets, said exhaust outlet means.

For engine cooling purposes, the end of the power transmission shaft at the intake and exhaust ends of the engine is hollow. to form coolant inlet means, said shaft being attached to the rotor assembly and said rotor assembly having coolant collecting means provided with sealing means so that the coolant used can be returned from the rotor assembly to a second end plate in which means for coolant outlet.

In most embodiments, the motor housing preferably comprises a substantially cylindrical housing body that is sealed between two end plates of the housing that are substantially circular as viewed in the direction of the axis of rotation.

Overview of the drawings

In order to facilitate an understanding of the invention and its practical application, reference will now be made to the accompanying drawings, in which FIG. 1 shows a schematic cross-section of the basic components of one embodiment of the present invention.

Giant. 2 is similar to FIG. 1, but shows a modified engine having a spaced cam track means at a certain distance from each other end of the engine as opposed to only one end.

Fig. 3 shows a detail of the design where a groove center or groove shaft transmitting the engine power is used.

Giant. 4 schematically illustrates the operation of strokes in connection with rotation, the direction of rotation being coincident with the clockwise direction of the block as shown.

Giant. 5 illustrates prior art torque comparative waveforms of the prior art and cam drive arrangement of our invention.

Giant. 6 is a cross-section similar to FIG. 1, but in this case the piston lift plate is shown in more detail.

Giant. 7, 8 and 9 show a view of the piston end and, respectively, a front view of the lower piston plate and a front view of the upper piston plate.

Giant. 10 is a partial cut-away design of an alternative design of the present invention showing the location of the upper and lower pistons.

Giant. 11 shows a cross-section of a preferred embodiment of the engine of the present invention.

Giant. 12 shows the intake and exhaust ends of the engine as seen in the direction of rotation of the axis of rotation.

Giant. 13 and 14 show, respectively, an axial view of a shaft and a cross section of a motor power transmission shaft.

Giant. 15 shows an axial view of an engine housing having pistons on the opposite side (not shown).

Giant. 16 shows a cross-section of a cylindrical lift plate.

Giant. 17 is an axial bottom view of the plate shown in FIG. 16.

Giant. 18 and 19 show, respectively, a cross-section of the upper piston lift plate and an axial view of the upper piston lift plate.

Giant. 20 shows a cross-section of a lower piston lift plate.

Giant. 21 corresponds to FIG. 20 in an axial view

Giant. 22 and 23 are, respectively, an axial view and a cross-section of the end plate and the drive end of the motor.

Giant. 24 is an axial view of the through-sealing member used in the embodiment shown in FIG. 11.

Giant. 25 is an enlarged view of the location of the sealing member applied to the embodiment shown in FIG. 11

Giant. 26 is a view corresponding to FIG. 25, but in this case an alternative method of sealing is shown.

Giant. 27 and 28 show, respectively, a cross section of the intake / exhaust end plate of the engine shown in Figs. 1 to 25 and an axial view of the intake / exhaust end plate.

DETAILED DESCRIPTION OF THE INVENTION

Giant. 1 to 10 are simplified illustrations to allow easy understanding of the broader principles of the present invention, while the further description with reference to FIGS. 11 to 26 is directed to a more specific design. As shown in FIG. 1, the engine of the present invention comprises a housing 10 having a cylindrical " skirt portion " which is sealed connected to the circular end plates, to the first or drive end plate 12 and to the second or intake / exhaust shown) lighter with end plate 13, wherein plate 13 has inlet openings (not shown) for fuel supply and exhaust openings are not for exhaust gas, and is equipped with suitable spark plugs or glow plugs. This drawing shows two cylinders 14 on the cylinder block 15 of the rotor assembly 16 rotating in the housing 10 by operative attachment to the power transmission shaft 17 rotatably mounted in the bearing 18 of the second end plate 13 and in the bearing. 19 první.k back plate 12

In this embodiment, the grooved portion of the power transmission shaft 17 is inserted into a groove hole in the piston lift plate 21 of the lifting cylinder through which the shaft 17 passes, so that the plate 21 can be driven by this shaft 17 and can slide axially thereon.

In this sense, Figure 1 illustrates the basic operation of a system in which the pistons 20 can move parallel to the axis of the power transmission shaft 17, and after the cam track 23 pushes the pistons 20 into the compression stroke, ignition occurs with the pistons in sight 20 are moved back to the lower position, but remain in their cylinders 14, the rollers continuously maintaining contact with the surface of the undulating cam track 23, as well as the other pistons being displaced down with them. to perform the suction lift the cam track 23 then pushes the pistons up in their cylinders again, two pistons exerting an exhaust stroke and the other two exerting a compression stroke, and this operation is repeated by rotating the pistons and cylinders in a predetermined direction to rotate the shaft 17 transmitting engine power. A second pair of pistons (not shown) belonging to the four-cylinder embodiment of FIG. 1 is similarly connected to the lift plate (not shown) to move uniformly.

Giant. 2 shows a modified embodiment in which the same components are used, but excluding. that the end plate 13 is, unlike FIG. 1, replaced by an end plate 24 equipped with a cam track, the cam track 25 being in contact with the rollers 26 of the cylinder-bearing block 27, thereby distinguishing the block 27 from the block 15 of FIG. This embodiment of the roller bearing block 27 also allows for sliding movement on the respective grooved portion of the power transmission shaft 17 so that the cam and the two sets of rollers 22 and 26 can cooperate with each other.

The advantages of this general system having parallel mounted cylinders are that. that no centrifugal force is required to return the pistons, no springs are required, and no duplication of the path required to push the rollers in and out is required, as is the case with the prior art. Two pistons move uniformly on the power stroke and the other two simultaneously and uniformly on the suction stroke, so that the driving force acting on the cam surfaces produces a rotational force that returns both piston-compressed pistons back to the exhaust stroke

Although there are a number of variants to achieve these results, the essential feature is that the pistons of each set can be integral with the lift plate and not with any moving parts. Dual ignition at each turn equals eight fires per turn at triple effect of 350-CI-V8 engines. In other words, this gives us a torque of 2-1. This is also achieved at a speed of a quarter of a minute per minute. This means that we have twice the torque of 350 V8 and also fuel consumption can be calculated as a third than that of a comparable unit.

It will be appreciated that no oil pressure is required and no coolant pump is required as this unit sucks the coolant centrifugally. It is envisaged that the preferred embodiments of this engine will comprise eight cylinders, two sets of four cylinders, and will achieve excellent results even in the small unit shown schematically in Figure 10 where the piston plate designated as the lower plate 28 has four radial arms 29 on which the pistons 30 are mounted, and wherein the top plate 31 is drawn with a cut-out so that only two pistons 32 are visible, with two gaps 33 visible on one side between adjacent lower pistons. 10 will have grooved parts to allow for sliding movement of said plates 28 and 31.

The essential requirements for the pistons 20 are shown in Figures G to 9, which show details of the upper piston plates 35 and the lower piston plates 36, each piston 20 having a cylindrical operative end 30 at which the piston rings (not shown) can be fitted. the non-operative end has pins 38 and rollers 22 on one axis perpendicular to the axis of the power transmission shaft 17.

Another advantage is that the cylinders are made to have a minimum length, only the length required for the piston stroke and the sealing ring and the space requirements of the seal are required.

The preferred operable embodiment of the present invention, which is shown in Figures 11 to 26, has been designed to incorporate all of the above advantages. As can be seen in these drawings, the housing 50 has a circular intake / exhaust plate 51 attached to a cylindrical housing 52 which is secured by screws 53 to the drive end plate 54. The power transmission rotary shaft 55 has a hollow tubular end 56 that is provided for the passage of coolant, and the shaft 55 has a central annular mounting plate 57 and a full diameter smaller portion 58 at its second or drive end, wherein the complete end indicated by reference numeral 59 has a further reduced diameter and is threaded for a pin nut.

The end 59 of the shaft 55 is, after insertion, fixed in the shrink tube 60 by said thrust nut connection, said tube 60 rotating in a bearing 61 housed in the bore 62 of the drive end plate 54 using an oil seal designated with reference 63. they are integral with the drive plate 64 rotating in the space within the circular undulating cam track 65, which is secured by screws 47 to the inner side of the end plate 54. The drive plate 64 protrudes longitudinal drive pins 49 which are adapted to slide through the longitudinal bores 48 in the openings 66 of the lower piston plate 67, so that the lower piston plate 67 is forced to rotate together with the drive plate 64 and can slide axially relative to the drive plate 64. Spring guide rods 68 protrude inwardly from the drive plate, at the upper ends of which are located compression springs 46 forcing the piston plate 67 away from the engine block 77, which aids the initial start-up of the engine.

The annular cam track 65 ripples between raised and lowered sections having the same height on opposite sides, the pistons 70 being fixed at equal distances from the cam track sections with which their cam followers 72 are in contact, each cam follower 72 being rotatably mounted on a cam pin 72 having its axis directed perpendicularly to the axis of the power transmission shaft 55, and piston rings 73 fitted with piston rings 73 sealing the bore 74 of the respective cylinders 75 given the dimensions of the removable bushings.76 of the cylinders mounted in the hem portions 69 of block 77 The upper piston plate 79 also reciprocates along the power transmission shaft 55 in the space toward the inner side of the lower piston plate 67 as is 11, wherein the spatial arrangement of the pistons is the same on both plate 67 and plate 79, each plate having four pistons 70 equidistant at the ends of the radial arms 80 and wherein the pistons of one set are Each piston has a crown 81 which is sealed at the working end and which is adapted to be exposed to the combustion gases during operation.

The exhaust / intake plate 51 (said top plate ") allows the mounting of external components as shown in Fig. 12, these components being arranged in a circle of cylindrical holes or inlets 82 (see Fig. 11 et seq.) And containing oppositely located spark plugs 83, the conduits of which are connected to the coils, oppositely located fuel injectors 84, oppositely located exhaust outlets and conduits 85, inlet conduit 87 for supplying coolant to inlet 87 of power transmission shaft 55, and coolant outlet with associated conduit 88. denotes an electronic ignition sensor and reference numeral 90 denotes a vacuum tube routed to the fuel injector via a PCV valve (positive crankcase ventilation); 28 shows the suction and exhaust ports 91 and 92 of the suction end plate 51, while FIG. 27 shows a hard seal of its face 93 and a recessed portion 94 for a coolant collector 45 that is fixed therewith. It is provided that it adjoins the rotary engine block 77 and has openings for the use of coolant through the passages 95 connecting the chambers 96 to allow coolant to circulate around the cylinder housings 76 as coolant flows into said chambers 96 through radial openings 97 through the block. 77 of the engine from the hollow end portion 56 of the power transmission shaft 55. Two oil seals are designated by reference numerals 98 and 99 to prevent coolant from entering the cylinder inlets 82.

Said suction end plate 51 has a threaded central bore 100 into which a threaded block adjusting sleeve 101 is screwed, comprising an axial bearing 102 for a power transmission shaft 55, the annular plate of said shaft 55 being fixed by pins 103 to the engine block 77. An upper cap component 104 is screwed to the adjusting sleeve 101, which closes the oil seal 105 and the pressure nut 106 screwed onto the power transmission shaft 55.

The manner in which the sealing of the cylindrical inlets 82 is maintained as the engine block is rotated will be apparent from the drawings where the components shown in Fig. 11 are shown to an enlarged scale in Figs. a sealing ring 107 which is non-rotatable and which has a pressure recess 109 and an upper sealing surface 110 to seal evenly against the fixed face 111 of the top plate 51. The edge of the inlet 82 is selected so that the O-ring 112 of the VITON type has been compressed by the inner rim of the sealing ring 107 in such a way that the surface of the pressure recess 109 is aligned with the same bottom surface 113. This seal is designed to minimize pressure on the sealing surface regardless of the presence of gas pressure, the result of which is a long service life with minimum friction and temperature.

An alternative method of sealing is shown in Fig. 26, where the thrust ring 114 is held in the recess 115 and movable outwardly against the annular edge at the inlet, which thrust ring acts as a gas leakage seal and is adapted to the desired inclination or angle so. to ensure irreversible activity. Other features of the seal ring 116 in this embodiment are the same as the seal ring 107 described with reference to FIGS. 24 and 25.

The design using the top cap nut 104 will be found to be very effective in adjusting the sealing clearances as desired, but, as already mentioned, the spring conductors on the rods 68 and springs 46 are not essential to engine operation, but assist in starting by pushing the piston the cam for the first ignition. If so decided, the springs can be replaced by hydraulic or pneumatic means

The described engines can operate as two-stroke engines with respective holes and can be combined with turbo systems or not. The engine can operate as a four-stroke or two-stroke diesel or turbo engine, etc. The engine has no components that require oil pressure support and, since no pressure is required, the engine can distribute oil to its moving parts by alternating pressures without any pumps or moving with part.

All modifications of the invention presented herein will confirm that embodiments of the invention are presented solely by way of explanation, by way of example, of a number of other variations to those skilled in the art, within the scope and scope of the invention, of the appended claims.

and may be a basis for as will be apparent to those skilled in the art without deviating as defined in

Claims (13)

A rotary internal combustion engine of the type whose pistons (20, 70) are designed for reciprocating motion in respective cylinders (14, 75), which are spaced regularly and equidistant about the longitudinal axis of rotation, said axis being the axis of rotation the transmission shaft ¢ 17,34,55) guided rotatably and sealed by a hole in the first end plate ¢ 12,54) and a hole in the second end plate ¢ 13,51) of the housing skříně 10,50), in which the pistons ¢ 20,70) and the cylinders ¢ 14.75) rotate as parts of the rotary assembly of the rotor (78) attached to said power transmission shaft (17,34,55), wherein the pistons ¢ 20,70) can simultaneously reciprocate in the cylinders ¢ 14,75), the cam follower means (22,26,71) are associated with each piston ¢ 20, .70) and are adapted to cooperate with the cam follower means ¢ 23,65) guided around the housing ¢ 10.50), the fuel supply means ¢ 84,90 ) supply fuel for sleeping The exhaust and exhaust means (85) remove the exhaust gases from the working ends of the cylinder bore (14,75) so that cyclic combustion of said fuel in said cylinder bores (14,75) causes a reciprocating movement of the pistons (,70 20.70) followed by pressing on the cam means. of the track (23), resulting in rotation of the power transmission rotor assembly (78) and power transmission shaft (17,34.55), characterized in that the pistons (20,70) are assembled in two sets, both sets having at least two pistons ( 20, 70), said pistons (20, 70) of each set being disposed on opposite sides of the rotational axis of the rotor assembly (16.78) and the engine power transmitting shaft (17,34.55) and interconnected by pistons connecting means (21) so that the pistons ¢ 20.70) of one set move simultaneously and in the same way, the components used are constructed and assembled so that the cam follower ¢ 22,26,71) of the pistons ¢ 20,70) together operate with cam track means ¢ 23,65) in such a way as to move the first set of pistons ¢ 20,70) in the respective cylinders ¢ 14,75) in one direction and move the second set of pistons ¢ 20,70) in the opposite direction13 Rotary internal combustion engine according to claim 1, characterized in that the pistons (20, 70) of each set have their pistons connecting means (21) in the form of a piston stroke plate (28, 67) having a bore through which a power transmission shaft (17) passes. 34.55), using means that allow drive connection of said piston lift plate (28, 67) as part of the rotor assembly (16, 78) to the engine power transmitting shaft (17, 34, 55). A rotary internal combustion engine according to claim 2, characterized in that said means by which the piston stroke plate (28, 67) can be coupled to the power transmission shaft (17,34,55) in a drive manner comprises longitudinal splines on said power transmission transmission. a shaft (17,34,55) such that the sliding but with the capability of sliding fits into the corresponding grooving of said opening in said piston lift plate (28,67). r A rotary internal combustion engine according to claim 2, characterized in that said means by which the piston stroke plate (28, 67) can be coupled to the power transmission shaft (17,34,55) in a drive manner comprises guide holes (66) in the shaft. a piston lift plate (28.67) at its diametrically opposed ends, wherein said guide holes (66) are adapted to slidably enter the free ends of the guide pins (49), which are located parallel to the axis of the power transmission shaft (17,34,55) and having second ends attached to the piston stroke plate means (28.67) forming part of the rotor assembly (16,78) and connected to the engine power transmitting shaft (17,34,55). Rotary internal combustion engine according to any one of the preceding claims 1 to 4, characterized in that each piston stroke plate (28, 67) has three, four or more arms (29, 80) which are guided radially in relation to the power a transmission shaft (17,34,551) and each having a piston (20,70) attached at its outer end, the pistons (20,70) of each set being spaced regularly and equidistant from each other, so that each set of said pistons (20, 70) enters the appropriately spaced cylinders (14, 75), all cylinders having their working ends to which fuel is supplied in a longitudinal position relative to said axis of rotation. í I. * A rotary internal combustion engine according to claim 5, characterized in that each cylinder (14.75) comprises a cylinder liner (76) which is detachably mounted in the engine block portion (15.77) of the rotor assembly (16,78), the power transmission shaft (16,78). 17,34,55) has fastening means by which it can be pushed or otherwise attached to said engine block portion (15,75) of the rotor assembly (78). A rotary internal combustion engine according to any one of claims 1 to 6, characterized in that the cam follower means (22, 26, 71) comprise a roller which is rotatably mounted on the respective piston (20, 70) of the cylinder. the lower end of the bore of the respective cylinder (14,75) and whose axis of rotation is perpendicular to said rotation axis of the power transmission shaft (17.34,55), wherein the rollers (22,26,71) of all the pistons (20,70) are located in equal distances from said axis of rotation of the power transmission shaft (17,34,55), the cam track means (23,65) being circular and mounted on the inside of the first end plate (12,54) of the housing (10,50) Rotary internal combustion engine according to claim 7, characterized in that openings (83,84,85) are formed externally in the second end plate (13,51) for attaching input means, said openings (83,84,85) are adapted to follow at a given moment the corresponding moving holes (91) of the rotor assembly (16, 78) in order to inject fuel into the working ends of the cylinder bore (.75 14.75), said second end plate ,5 13,51 ) is lubricated at the engine intake and exhaust ends, creating conditions for the placement of fuel injectors prostředků 84), spark plugs ¢ 83), or other similar means, and exhaust exhaust výfuk 85). Rotary internal combustion engine according to claim 8, characterized in that the second end plate (13,51) comprises a diametrically opposed pair of spark plugs (83) which are spark plugs or other suitable means, a pair of diametrically opposed fuel injector assemblies ) 84), which are fuel injection means and a pair of diametrically opposed exhaust outlets ¢ 85), which are exhaust exhaust means. A rotary internal combustion engine according to claims 8 and 9. characterized in that the end of the engine power transmission shaft (17,34,55) located at the engine intake and exhaust ends is hollow in order to form coolant supply means (87), wherein said shaft ¢ 17,34,55 ) is rigidly connected to the rotor assembly ¢ 78) and has inlet passages ¢ 95) extending from its hollow interior to the outer surroundings of each cylinder ¢ 14,75) for cooling, said rotor assembly ¢ 16,78) comprising a collector means ¢ 45 ) having sealing means ¢ 98.99), so that the coolant can be removed from the rotor assembly ¢ 78) to the second end plate desky 13.51), in which the coolant outlet means ¢ 88) is located. Rotary internal combustion engine according to any one of the preceding claims 1 to 7, characterized in that each cylinder (14,75) is adapted to receive fuel doses through each respective inlet port (82). which rotates together with the rotor assembly ,7 16,78) in such a mode that it connects to the corresponding hole in the fixed housing ¢ 10,50) by slidingly touching the surface (110) with the surface (111) in a plane perpendicular to a power transmission shaft (17,34,55) axis, wherein sealing between the surfaces (110, 111) is achieved by applying a circular sealing ring (107) which is adapted to compress the resilient, high temperature resistant ring (112) which is located between the underside of said sealing ring (107) and the recess in the cylindrical inlet (82) at a distance from the inner surface of said inlet (82). The rotary internal combustion engine of any one of claims 1 to 7, wherein each cylinder (14, 75) is adapted to receive fuel doses through each respective inlet port (82) that rotates with the rotor assembly. (16,78) in such a mode that the corresponding hole in the fixed housing (10,50) is caused by sliding contact of the surface (110) with the surface (111) in a plane perpendicular to the axis of the power transmission shaft (17), 34,55), wherein sealing between the surfaces (110, 111) is achieved by applying a circular sealing ring (116) having an inner recess (Ϊ15) containing a suitable steel or other pressure sealing ring (114) that is adapted to under pressure sealed the edge of the recess in the inlet (82) and maximized the sealing effect of the sealing ring (HJJ). The rotary internal combustion engine of claim 1, wherein the housing (10) has a central The first and second cam tracks (23, 25) are connected to respective first and second end plates (12, 24), and the rotor assembly (16) has first cam follower means (22) which cooperate with the first end plate (12) in the cam. and has second cam follower means (26) which cooperate with the second end plate (24) in relation to the reciprocating motion of the rollers (14). A rotary internal combustion engine according to claim 13, characterized in that. The first and second cam follower means (22, 26) are in the form of rollers that rotate on axes that are perpendicular to the axis of rotation of the shaft (17) transmitting engine power. Rotary internal combustion engine according to any one of the preceding claims, characterized in that the housing (10.50) comprises a substantially cylindrical housing (11,52) which is sealed to the two end plates (12, 12). 13.54.51) cabinets (10.50), wherein said end plates ¢ 12.13, 54.51) are substantially circular as viewed in the direction of the axis of rotation 16 - The rotary internal combustion engine as described overall with reference to any drawing of the accompanying drawing.