Internal combustion engine

Abstract

The internal combustion engine comprises a first rotor member (11) rotatably carried according to a first axis of rotation (21) and a second rotor member (12) rotatably carried according to a second axis of rotation (22) coaxial with said first axis of rotation (21 ). A first and a second pair of opposed cylinders (30) are associated with said first rotor member (11). Said opposed cylinders (30) have respective pistons (31) adapted to define within the same cylinders (30) relative combustion chambers (32) and connected, by means of connecting rod means (33), to said second rotor member (12).

Description

[0001] Description

[0002] INTERNAL COMBUSTION ENGINE

[0003] Technical field

[0004]

[0001] The present invention relates to an internal combustion engine.

[0005] Prior art

[0006]

[0002] The use of internal combustion engines to drive mechanical equipment, such as land or marine vehicles and the like, has long been known. The internal combustion engine converts the thermal energy of an air-fuel mixture into mechanical work, made available through an output shaft.

[0007]

[0003] A well-known type of internal combustion engine is the four-stroke reciprocating volumetric engine that provides mechanical energy to a large portion of road vehicles. Such an engine employs one or more cylinders equipped with a combustion chamber where the compression and firing of the air-fuel mixture cause the displacement of a respective piston; the pistons, by means of connecting rod transmission means, cause the output shaft to rotate. In practice, the operation of the engine provides, in succession for each of the cylinders, the phases of intake, compression, firing of the air-fuel mixture, followed by the exhaust of the burnt gases.

[0008]

[0004] The described type of internal combustion engine has undergone modifications and improvements over time to enhance its functional characteristics. However, it is still lamented that known internal combustion engines of the aforementioned type have a low efficiency, mainly due to the fact that the thrust of the pistons on the connecting rods is not fully exploited. Indeed, the engine exerts the maximum thrust on the piston when the lever arm is practically zero; while the arm progressively increases, the thrust continuously decreases. When the arm is at its maximum (90°), the thrust is greatly diminished, almost becoming zero when the arm returns to zero, at the bottom dead center.

[0009]

[0005] It is also known that an increase in the compression ratio corresponds, within certain limits, to an increase in engine efficiency and that varying the compression ratio would allow for optimal results in terms of efficiency. Some engines are equipped for this purpose with a complex linkage that allows intervention on the piston stroke, varying the volume of the combustion chamber and thus the compression.

[0010]

[0006] It is clear how the alternating movement of the connecting rod and piston masses, continuously accelerated and braked, negatively affects the efficiency and how the lateral swinging of the connecting rod causes the ovalization of the cylinder and anticipates the wear of the piston rings.

[0011]

[0007] There is therefore a felt need to provide a new type of internal combustion engine capable of overcoming the aforementioned drawbacks.

[0012] Disclosure

[0008] The task of the present invention is to solve the cited problems by devising an internal combustion engine that allows the aforementioned drawbacks to be overcome.

[0013]

[0009] Within the scope of this task, a further object of the invention is to provide an internal combustion engine with high efficiency.

[0014]

[0010] Another object of the invention is to provide an internal combustion engine that ensures high durability.

[0015]

[0011] A further object of the invention is to provide an internal combustion engine with a simple constructive and functional design, versatile use, as well as a relatively low cost.

[0016]

[0012] The cited objects are achieved, according to the present invention, by the internal combustion engine according to claim 1.

[0017]

[0013] The internal combustion engine comprises: a first rotor member rotatably carried according to a first axis of rotation; a second rotor member rotatably carried according to a second axis of rotation coaxial with said first axis of rotation; at least one pair of opposed cylinders mounted on said first rotor member, where said opposed cylinders have respective pistons adapted to define within the same cylinders respective combustion chambers and connected, by means of connecting rod means, to said second rotor member.

[0018]

[0014] Advantageously, the internal combustion engine comprises a first pair and a second pair of said opposed cylinders mounted on said first rotor member.

[0019]

[0015] According to the present invention, said first and second axes of rotation are mounted on an external casing, independently of each other, by means of unidirectional rolling members, so as to allow the rotation of said rotor members in a single direction.

[0020]

[0016] Suitably, said rotor members are rotatably carried, independently of each other, on parallel planes of arrangement.

[0021]

[0017] Suitably, said parallel planes of arrangement are orthogonal to said axes of rotation of the rotor members.

[0022]

[0018] Suitably, said combustion chambers of said opposed cylinders are in communication with respective ducts for fuel supply and for the exhaust of burnt gases.

[0023]

[0019] Preferably, said opposed cylinders have a single intake and exhaust valve located at the bottom of the relative combustion chamber.

[0024]

[0020] Advantageously, said opposed cylinders have an exhaust port formed on the edge of the cylinders themselves.

[0025]

[0021] Suitably, said exhaust port opens upon the descent of the piston inside the combustion chamber of said cylinders, allowing the entry from said intake valve of compressed air which exhausts the fumes.

[0026]

[0022] Preferably, said intake and exhaust valve is electrically controlled.

[0027]

[0023] Preferably, said axes of rotation are made of tubular shafts connected, by means of suitable transmission means, to the half-shafts of a differential member.

[0024] Preferably, said connecting rod means of each pair of said opposed cylinders are pivotally articulated to said second rotor member by means of a respective rotation pin.

[0028]

[0025] Preferably, said rotation pin is pivotally articulated to said second rotor member along an axis perpendicular to the same second rotor member.

[0029]

[0026] Preferably, said second rotor member forms air intake blades adapted to generate an air flow that passes through the internal combustion engine to perform the cooling of said opposed cylinders.

[0030]

[0027] Preferably, said opposed cylinders have cooling fins on their outer surface.

[0031]

[0028] According to a different embodiment of the invention, the internal combustion engine comprises: a first rotor member rotatably carried according to a first axis of rotation; a second rotor member rotatably carried according to a second axis of rotation coaxial with said first axis of rotation; a first pair of opposed cylinders associated with said first rotor member; a second pair of opposed cylinders associated with said second rotor member; where said opposed cylinders have respective pistons adapted to define within the same cylinders relative combustion chambers; said pistons being associated with connecting rod means hinged respectively to the opposite rotor member.

[0032]

[0029] Suitably, said connecting rod means are adapted to actuate a corresponding piston of the opposite rotor member.

[0033]

[0030] Suitably, said connecting rod means are connected directly to the opposite rotor.

[0034]

[0031] According to a further embodiment of the invention, the internal combustion engine comprises: a first rotor member rotatably carried according to a first axis of rotation; a second rotor member rotatably carried according to a second axis of rotation coaxial with said first axis of rotation; at least one pair of opposed cylinders associated with said first rotor member; where said pair of opposed cylinders is made in monolithic form and has within it a respective pair of pistons adapted to define within the same opposed cylinders relative combustion chambers; the pistons of said pair of pistons being rigidly associated with each other by means of connecting rod means hinged to said second rotor member by means of a rocker member.

[0035]

[0032] Advantageously, the internal combustion engine comprises: a first pair of said opposed cylinders associated with said first rotor member, and a second pair of said opposed cylinders associated with said first rotor member; where said first pair and said second pair of opposed cylinders are respectively made in monolithic form and each has within it a respective pair of said pistons adapted to define within the same opposed cylinders relative combustion chambers; said pistons of each said pair of pistons being rigidly associated with each other by means of connecting rod means hinged respectively to said second rotor member by means of said rocker member.

[0036]

[0033] In particular, said first axis of rotation defines the driveshaft of said cylinders and said second axis of rotation defines the driveshaft of said pistons.

[0037]

[0034] Preferably, said connecting rod means comprise a stem of substantially linear shape, integral at its opposite ends respectively with said pistons of said pair of pistons and hinged to said rocker member at a hinge member.

[0038]

[0035] Preferably, said hinge member comprises a pin projecting transversely from said stem in a substantially central position and configured to slidingly engage a guide slot made longitudinally on said rocker member.

[0039]

[0036] Preferably, said rocker member is adapted to be associated, in a substantially central position, in axis with the driveshaft of said opposed pistons and has on opposite sides with respect to said driveshaft first and second guide means configured to be slidingly engaged by respective pins projecting transversely from said connecting rod means.

[0040] Brief description of the drawings

[0041]

[0037] The details of the invention will become more evident from the detailed description of a preferred embodiment of the internal combustion engine, illustrated by way of example in the accompanying drawings, in which: figure 1 shows a schematic longitudinal sectional view of the internal combustion engine according to the present invention; figures 2 and 3 show respectively a longitudinal sectional view and a transverse sectional view of a first embodiment of the internal combustion engine in question, in the two-cylinder configuration; figures 4a, 4b, 4c, 4d and 4e show respectively a transverse sectional view of said two- cylinder internal combustion engine in successive operating phases; figures 5 and 6 show a longitudinal sectional view and a transverse sectional view of a second embodiment of the internal combustion engine according to the present invention, in the four-cylinder configuration; figures 7a to 7m show respectively a transverse sectional view of said four-cylinder internal combustion engine in successive operating phases; figures 8a and 8b show respectively a transverse sectional view of said four-cylinder internal combustion engine equipped with an anti-collision mechanism between the rotor members, in different working positions; figure 9 shows a transverse sectional view of a different embodiment of said four-cylinder internal combustion engine; figures 9a to 9e show respectively said transverse sectional view of the different embodiment of the four-cylinder internal combustion engine in successive operating phases; figure 10 shows a schematic longitudinal sectional view of a further embodiment of the internal combustion engine according to the present invention; figure 11 shows a corresponding transverse sectional view thereof; figures 12a to 12c show respectively said longitudinal sectional view of this further embodiment of the internal combustion engine in successive operating phases.

[0042] Description of embodiments of the invention

[0043]

[0038] With particular reference to these figures, the internal combustion engine according to the present invention is indicated as a whole by 1 . The internal combustion engine 1 comprises a first rotor member 11 , rotatably carried according to a first axis of rotation 21 , and a second rotor member 12 rotatably carried according to a second axis of rotation 22 coaxial with said first axis of rotation 21 .

[0044]

[0039] The axes of rotation 21 , 22 are preferably made of tubular shafts connected, by means of suitable gears or toothed belts, to the two half-shafts of a differential member, known per se.

[0045]

[0040] Said first and second axes of rotation 21 , 22 are rotatably mounted inside an external casing

[0046] 10, independently of each other, by means of unidirectional rolling members 23, so as to allow the rotation of the rotor members 11 , 12 only in one direction. The unidirectional rolling members 23 are constituted, for example, by suitable pawls.

[0047]

[0041] It should be noted that the axes of rotation 21 , 22 are suitably connected to each other by means of a bearing insert, not shown in the figures, adapted to ensure their coaxiality.

[0048]

[0042] To the first rotor member 11 is associated at least one pair of opposed cylinders 30, where said opposed cylinders 30 have respective pistons 31 adapted to define within the same cylinders 30 relative combustion chambers 32. The pistons 31 are connected, by means of respective connecting rod means 33, to the second rotor member 12. Hereinafter, for simplicity, the connecting rod means 33 are also referred to as connecting rods.

[0049]

[0043] In figures 2 and 3, a two-cylinder internal combustion engine according to the present invention is illustrated. It should be noted that the use of a single pair of opposed cylinders 30 can be provided in the case of two-stroke engines.

[0050]

[0044] In particular, the external casing 10 forms an enclosure within which the rotor members 11 , 12 are coaxially housed. The external casing 10 defines suitable seats for the unidirectional rolling members 23 which rotatably carry the axes of rotation 21 , 22 of the rotor members

[0051] 11 , 12.

[0052]

[0045] The external casing 10 also has, on opposite walls, openings 13, 14 for air intake and exhaust respectively (see fig. 5). The openings 13, 14 are closed by suitable grilles. The air flow through the internal combustion engine is adapted to cool the opposed cylinders 30. To this end, the second rotor member 12 forms suitable air intake blades 15. The cylinders 30 also have suitable cooling fins 16.

[0053]

[0046] Advantageously, the cylinders 30 have a single intake and exhaust valve 35 located at the bottom of the relative combustion chamber 32. Preferably, the intake and exhaust valve 35 is electrically controlled. It should be noted that the unidirectional air flow ensures that the outgoing fumes and the incoming air in the combustion chamber 32 do not interfere. It is however possible to provide suitable arrangements to direct and accelerate the flows on the head of the valve 35 or supercharging by means of known compressor means, such as an exhaust gas turbine and the like.

[0054]

[0047] In the combustion chamber 32 of the cylinders 30 opens a fuel injector member 36 (see figures 5 and 6). The injector member 36 is supplied through a duct 37 passing through the hollow axis of the rotor member 11 and connected to a distributor member 38. The distributor member 38 and the injector member 36 can be controlled mechanically by the approach of the rotor members 11 , 12 or electrically.

[0055]

[0048] On the first and second axes of rotation 21 , 22 are mounted respective pulleys for connection to the starter motors and to the differential.

[0056]

[0049] During the operation of the engine, the usual phases of intake, compression, firing and exhaust follow each other in a regular manner for each of the cylinders 30, one after the other (see figures 4a to 4e in sequence). For greater clarity, the cylinder 30 in the firing phase has been marked with an asterisk.

[0057]

[0050] It should be noted that in the embodiment illustrated in figures 4a to 4e, the cylinders 30 have an intake valve 35 located at the base of the cylinder 30 and an exhaust port 39 made on the edge of the cylinder itself. This solution is particularly advantageous in the case of a supercharged two-stroke engine, in which when the piston 31 reaches the bottom dead center it leaves open the exhaust port 39 made on the edge of the cylinder 30; from said exhaust port 39 to the opening of the valve 35 the fumes are pushed out and the cylinder 30 is filled with fresh air. In substance, this allows for all active phases. In fact, when the piston 31 , by descending, opens the exhaust port 39, compressed air enters from the intake valve 35, which exhausts the fumes, fills the cylinder and is then further compressed, mixed with the fuel and then ignited.

[0058]

[0051] According to a preferred embodiment, a first and a second pair of opposed cylinders 30 are associated with the first rotor member 11 , having respective pistons 31 adapted to define within the same cylinders 30 said combustion chambers 32. As mentioned, the pistons 31 are connected, by means of respective connecting rods 33, to the second rotor member 12.

[0059]

[0052] More particularly, as visible in fig. 6, the four-cylinder internal combustion engine has a first pair of opposed cylinders 30a, 30d and a second pair of opposed cylinders 30b, 30c arranged alongside the first pair of opposed cylinders 30a, 30d on the first rotor member 11 . The connecting rods 33 of each pair of opposed cylinders 30 are pivotally articulated to the second rotor member 12 by means of a respective rotation pin 34 along an axis perpendicular to said second rotor member 12.

[0060]

[0053] As visible in figures 8a, 8b, it is suitably possible to provide for the use of an anti-collision mechanism 40 consisting of an elastic element hinged on pins 41 , adapted to prevent interference between the rotor members 11 , 12. When the conflict limit with the first rotor member 11 is exceeded, the second rotor member 12 comes into contact with the elastic element 40 which deforms, preventing contact with the same first rotor member 11 .

[0061]

[0054] It is suitably possible to provide for the supply of the engine by injection, with the injectors mounted on the first rotor member 11 which carries the cylinders 30. In practice, however, it is possible to use any other supply system.

[0062]

[0055] During the operation of the engine, the usual phases of intake, compression, firing and exhaust follow each other in a regular manner for each of the cylinders 30, one after the other.

[0063]

[0056] In particular, assuming that the firing initially occurs in the combustion chamber of the first cylinder 30a, the second cylinder 30b is in the exhaust phase, the third cylinder 30c is in the intake phase and the fourth cylinder 30d is in the compression phase (see figures 7a, 7b and 7c in sequence, in which the firing phase, an intermediate expansion phase and the final expansion phase of the aforementioned first cylinder 3a are visible, as well as the rotation produced, with corresponding phases of the other three cylinders).

[0064]

[0057] The firing in the combustion chamber of the first cylinder 30a causes the sliding of the relative piston 31 which, through the connecting rod 33, causes the rotation of the second rotor member 12. Obviously, this rotation is followed by the connecting rods 33 of the subsequent cylinders 30b, 30c and 30d, each in the appropriate phase of its cycle, as indicated above.

[0065]

[0058] Subsequently, at the end of the first cycle of the first cylinder 30a, the firing occurs in the combustion chamber of the fourth cylinder 30d, where the compression phase has been completed. Simultaneously, the first cylinder 30a is in the exhaust phase, the second cylinder 30b is in the intake phase and the third cylinder 30c is in the compression phase (see figures 7d, 7e and 7f in sequence).

[0066]

[0059] The firing in the combustion chamber of the fourth cylinder 30d causes in this case the sliding of the same cylinder 30d with respect to its piston 31 , as its connecting rod 33 is prevented from rotating in the opposite direction to the previous rotation by the unidirectional rolling member 23 which engages the rotation pin 34, causing the rotation of the first rotor member 11 .

[0067]

[0060] Similarly, firing subsequently occurs in the combustion chamber of the third cylinder 30c, where the compression phase has been completed. Simultaneously, the fourth cylinder 30d is in the exhaust phase, the first cylinder 30a is in the intake phase and the second cylinder 30b is in the compression phase (see figures 7f, 7g and 7h in sequence).

[0068]

[0061] Again, subsequently, firing occurs in the combustion chamber of the second cylinder 30b, where the compression phase has been completed (see figures 7i, 7I, 7m in sequence).

[0062] In practice, the firing phase that alternately affects one of the cylinders of the first pair of opposed cylinders 30a, 30b and one of the cylinders of the second pair of opposed cylinders 30c, 30d causes the rotation alternately of the second rotor member 12 and the first rotor member 11 , in the same direction of rotation. A continuous rotary motion is thus produced which generates energy separately through the coaxial axes of rotation 21 , 22.

[0069]

[0063] The intake and exhaust valve 35 remains open for the entire duration of the two exhaust and intake cycles, given that on the head of the cylinders 30 the air flow generated by the rotors 11 , 12 is continuous and unidirectional, so when the valve 35 opens for the exhaust of the fumes, these are introduced into the air stream towards the outlet side while on the other side fresh air enters to fill the cylinder.

[0070]

[0064] It should be noted that the rotors 11 , 12 are mounted coaxially on the external casing 10, free to rotate independently of each other but in the same direction thanks to the unidirectional rolling members 23.

[0071]

[0065] Suitably, the connecting rods 33 of the first pair of opposed cylinders 30a, 30d and of the second pair of opposed cylinders 30b, 30c are respectively arranged on parallel, specially spaced planes, to allow their connection to a respective rotation pin 34. To this end, it is possible to provide that one of the cylinders 30 of each pair of said opposed cylinders is partially housed in a respective recess made in the first rotor member 11 .

[0072]

[0066] The described internal combustion engine thus achieves the object of overcoming the drawbacks lamented in traditional internal combustion engines. In particular, the internal combustion engine according to the invention is endowed with high efficiency.

[0073]

[0067] This result is obtained thanks to the inventive idea of transforming the alternating motion of the pistons into a circular motion.

[0074]

[0068] More specifically, it is observed that the lever arm of the connecting rods is much larger than in known engines and remains almost constant at its maximum throughout the descent phase of the connecting rod. The imperceptible lateral stresses of the connecting rod guarantee against the ovalization of the cylinder, reduce friction and increase the reliability and durability of the engine. Moreover, the masses are all in continuous rotation and have no alternating motion. Suitably, the rotors can be balanced in such a way as to cancel out any vibration. With no forced piston cycles in the cylinder, the ignition of the mixture can also occur before the point of minimum distance of the piston head from the cylinder head and therefore in conditions of variable compression at will with a further increase in efficiency.

[0075]

[0069] Another advantage of the internal combustion engine according to the present invention is that it is significantly lighter than traditional engines, thanks to having a smaller number of moving parts, and is more reliable due to the rotary motion.

[0076]

[0070] The single intake and exhaust valve, located at the bottom of the relative combustion chamber and of large diameter, improves the evacuation of fumes and the optimal filling of the combustion chamber. The fact that the valve remains always open during the two cycles further reduces movements and mechanisms.

[0077]

[0071] In fig. 9, a different embodiment of the internal combustion engine according to the present invention is illustrated, in which the first and second rotor members, for greater clarity indicated as 111 , 112, each carry a pair of opposed cylinders 130; the rotor members 111 , 112 each have hinged the connecting rod 133 which actuates a corresponding piston 131 of the opposite rotor member.

[0078]

[0072] As in the previous case, the rotor members 111 , 112 are rotatably carried according to coaxial and independent axes of rotation 121 , 122, by means of unidirectional rolling members 123, so as to allow the rotation of the same rotor members 111 , 112 only in one direction.

[0079]

[0073] The operation of the engine reproduces that described previously for the first embodiment (see figures 9a to 9e in sequence). Starting from the firing phase in a respective cylinder 130, for example associated with the first rotor member 111 , the expansion that occurs determines the rotation of the second engine rotor 112 in the permitted direction; simultaneously in the other cylinders the usual exhaust, intake and compression phases are orderly performed.

[0080]

[0074] In figures 10 and 11 , a further embodiment of the internal combustion engine according to the present invention is illustrated which, as seen previously, comprises a first rotor member

[0081] 211 rotatably carried according to a first axis of rotation 221 and a second rotor member

[0082] 212 rotatably carried according to a second axis of rotation 222 coaxial with said first axis of rotation 221. At least one pair of opposed cylinders 230 is associated with the first rotor member 211.

[0083]

[0075] Preferably, as in the illustrated case, the engine comprises a first and a second pair of opposed cylinders 230 arranged side by side on the first rotor member 211 .

[0084]

[0076] According to an aspect of the invention, each pair of opposed cylinders 230 is made in monolithic form and has within it a respective pair of pistons 231 adapted to define within the same opposed cylinders 230 relative combustion chambers 232. The combustion chambers 232 are closed at the opposite ends of the opposed cylinders 230 by respective heads 239, bearing the conventional intake and exhaust valves 241 , 242 and the fuel injector member 240.

[0085]

[0077] The pistons 231 of each pair of pistons 231 are rigidly associated with each other by means of connecting rod means 233 hinged to said second rotor member 212 by means of a rocker member 234.

[0086]

[0078] In substance, the first axis of rotation 221 of the first rotor member 211 defines the driveshaft of said opposed cylinders 230 and the second axis of rotation 222 of the second rotor member 212 defines the driveshaft of said pistons 231 .

[0087]

[0079] According to another aspect of the invention, said connecting rod means 233 comprise a stem 235 of substantially linear shape, integral at the opposite ends respectively with said pistons 231 of each pair of pistons 231 and hinged to the rocker member 234 at a hinge member 236.

[0088]

[0080] In particular, the rocker member 234 is adapted to be associated, in a substantially central position, in axis with the driveshaft 222 of said opposed pistons 231.

[0089]

[0081] The hinge member 236 comprises a pin 237 projecting transversely from said stem 235 in a substantially central position and configured to slidingly engage guide means 238 made longitudinally on said rocker member 234.

[0090]

[0082] In particular, the rocker member 234 has on opposite sides with respect to said driveshaft 222 first and second guide means 238 configured to be slidingly engaged by respective pins 237 projecting transversely from the stem 235 of corresponding connecting rod means

[0091] 233 of each pair of pistons 231 .

[0092]

[0083] Suitably, said guide means 238 are defined by a pair of slots made on the rocker member

[0093] 234 on opposite sides with respect to the driveshaft 222 and configured to be slidingly engaged by said respective transverse pins 237.

[0094]

[0084] It should be noted that the engine object of the invention is substantially composed of two autonomous coaxial groups, the first rotor 211 and the second rotor 212. The first rotor 211 or cylinder rotor is composed of the opposed cylinders 230, integral with each other on a rotating member 210, for example in the shape of a disc, rotatably carried by the respective driveshaft 221 ; the second rotor 212 or piston rotor is composed of the rocker member 234 rotatably carried by the respective driveshaft 222 and bearing hinged the first and second pair of opposed pistons 231 united by their respective stems 235 to form a monolithic group.

[0095]

[0085] The driveshaft of the cylinders 221 and the driveshaft of the pistons 222 are engaged with each other at a respective end by means of a suitable bearing 213 adapted to ensure their coaxiality and to allow a fluid relative rotation of the two shafts. The driveshaft of the cylinders 221 and the driveshaft of the pistons 222 are also mounted on respective rolling members 214, in particular free-wheel bearings, adapted to allow the same shafts to rotate in a single, common direction for both.

[0096]

[0086] The rolling members 214 are suitably supported by respective portions 215 of the engine frame.

[0097]

[0087] The operation of the engine substantially reproduces that described for the previous embodiments. During the operation of the engine, the usual phases of intake, compression, firing and exhaust follow each other in a regular manner for each of the cylinders 230, one after the other (see figures 12a to 12c in sequence). For greater clarity, in this case too, the cylinder in the firing phase has been marked with an asterisk. This refers in particular to the cylinder indicated with the reference 230a. The adjacent opposed cylinders, in a clockwise direction, respectively perform the exhaust, intake, and compression phases.

[0098]

[0088] The rotary engine thus configured has great constructive simplicity. In particular, the joints of the connecting rods, both at the big end and the small end, are eliminated, while the play is entirely transferred to the slot of the rocker. Furthermore, there is a simple and optimal lubrication of all moving parts. All movements occur in the central inner part common to the two cylinders, and a constant volume space is created, closed between the bottom of the alternating pistons and the outlets of the two driveshafts.

[0099]

[0089] In effect, the two monolithic piston-rod-piston groups move inside their respective cylinders, compensating for the volumes of the space, i.e. , when one is up, the other is down; while the front and rear faces of the space are closed by the seats of the two transmission shafts that engage within their respective free-wheel bearings. The lubricating fluid is thus enclosed in the constant volume rotating chamber so defined; the centrifugal force pushes it below the oil scraper ring which then returns it towards the center. It is eventually possible to provide simple flow deviator members to optimize the path of the lubricant.

[0100]

[0090] In the practical implementation of the invention, the materials used, as well as the shape and dimensions, can be any according to the requirements.

[0101]

[0091] Where the technical features mentioned in any claim are followed by reference signs, those reference signs have been included for the sole purpose of increasing the intelligibility of the claims and accordingly, such reference signs have no limiting effect on the scope of each element identified by way of example by such reference signs.

Claims

Claims1. An internal combustion engine comprising: a first rotor member (11 ) rotatably carried according to a first axis of rotation (21 ); a second rotor member (12) rotatably carried according to a second axis of rotation (22) coaxial with said first axis of rotation (21 ); a pair of opposed cylinders (30) associated with said first rotor member (11 ), where said opposed cylinders (30) have respective pistons (31 ) adapted to define within the same cylinders (30) relative combustion chambers (32) and connected, by means of connecting rod means (33), to said second rotor member (12).

2. The internal combustion engine of claim 1 , wherein it comprises a first and a second pair of said opposed cylinders (30) associated with said first rotor member (11 ).

3. The internal combustion engine of claim 1 or 2, wherein said first and second axes of rotation (21 , 22) are mounted on an external casing (10), independently of each other, by means of unidirectional rolling members (23), so as to allow the rotation of said rotor members (11 , 12) in a single direction.

4. The internal combustion engine of any one of the preceding claims, wherein said combustion chambers (32) of said opposed cylinders (30) are in communication with respective ducts for fuel supply and for the exhaust of burnt gases.

5. The internal combustion engine of claim 4, wherein said opposed cylinders (30) have a single intake and exhaust valve (35) located at the bottom of the relative combustion chamber (32).

6. The internal combustion engine of claim 4 or 5, wherein said opposed cylinders (30) have an exhaust port (39) made on the edge of the cylinders (30) themselves.

7. The internal combustion engine of any one of the preceding claims, wherein said opposed cylinders (30) operate in succession the phases of intake, compression, firing and exhaust of the combustible fluid.

8. The internal combustion engine of any one of the preceding claims, wherein said second rotor member (12) forms air intake blades (15) adapted to generate an air flow that passes through the internal combustion engine to perform the cooling of said opposed cylinders (30).

9. The internal combustion engine of claim 1 , wherein it comprises: a first rotor member (111 ) rotatably carried according to a first axis of rotation (121 ); a second rotor member (112) rotatably carried according to a second axis of rotation (122) coaxial with said first axis of rotation (121 ); a first pair of opposed cylinders (130) associated with said first rotor member (111 );a second pair of opposed cylinders (130) associated with said second rotor member (112); where said opposed cylinders (130) have respective pistons (131 ) adapted to define within the same cylinders (130) relative combustion chambers (132); said pistons (131 ) being associated with connecting rod means (133) hinged respectively to the opposite rotor member (111 , 112), to actuate a corresponding piston (131 ) of the opposite rotor member.

10. An internal combustion engine comprising: a first rotor member (211 ) rotatably carried according to a first axis of rotation (221 ); a second rotor member (212) rotatably carried according to a second axis of rotation (222) coaxial with said first axis of rotation (221 ); at least one pair of opposed cylinders (230) associated with said first rotor member (211 ); where said pair of opposed cylinders (230) is made in monolithic form and has within it a respective pair of pistons (231 ) adapted to define within the same opposed cylinders (230) relative combustion chambers (232); the pistons (231 ) of said pair of pistons (231 ) being rigidly associated with each other by means of connecting rod means (233) hinged to said second rotor member (212) by means of a rocker member (234).

11. The internal combustion engine of claim 10, wherein it comprises: a first pair of said opposed cylinders (230) associated with said first rotor member (211 ); and a second pair of said opposed cylinders (230) associated with said first rotor member (211 ); where said first pair and said second pair of opposed cylinders (230) are respectively made in monolithic form and each has within it a respective pair of said pistons (231 ) adapted to define within the same cylinders (230) relative combustion chambers (232); said pistons (231 ) of each said pair of pistons (231 ) being rigidly associated with each other by means of connecting rod means (233) hinged respectively to the second rotor member (212) by means of said rocker member (234).

12. The internal combustion engine of claim 10 or 11 , wherein said connecting rod means (233) respectively comprise a stem (235) of substantially linear shape, bearing integral at the opposite ends respectively the said pistons (231 ) of each pair of pistons (231 ) and hinged to said rocker member (234) at a hinge member (236).

13. The internal combustion engine of claim 12, wherein said hinge member (236) comprises a pin (237) projecting transversely from said stem (235) in a substantially central position and configured to slidingly engage a guide slot (238) made longitudinally on said rocker member (234).

4. The internal combustion engine of claim 13, wherein rocker member (234) is adapted to be associated, in a substantially central position, in axis with the driveshaft (222) of said opposed pistons (231 ) and has on opposite sides with respect to said driveshaft (222) first and second guide means (238) configured to be slidingly engaged by respective pins (237) projecting transversely from said connecting rod means (233).

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