FR2925571A1 - Motor constituting device, has engine shaft adapted to carry out continuous rotational movement around rotational axis, where axis is parallel and equidistant to theoretical and individual rotational axis - Google Patents

Abstract

The device (1) has a movement conversion mechanism (E4) connecting alternate rotational movements of the piston (7A-7D) around a theoretical and individual rotational axis with continuous rotational movement of an engine shaft (30) along a rotational axis. The mechanism controls tapping of rotative pistons. An engine shaft (30) is adapted to carry out a continuous rotational movement around the rotational axis. The rotational axis is parallel and equidistant to the theoretical and individual rotational axis.

Description

1 machine with rotary pistons with controlled flapping

The invention relates to a device for constituting a motor capable of producing a mechanical work under the pressure of a fluid, or a pump capable of transferring or pressurizing a fluid. When the device constitutes a motor, the fluid under pressure can be obtained, in particular, by a liquid column, by a reserve of compressed air or by the combustion of a fuel. When the device constitutes a pump, it must provide a mechanical energy which is then communicated to the compressed fluid and / or decanted. An example of the state of the art is described in US-5,222,463 which discloses a version of this type of machine. The present invention differs markedly from this because of the following arrangements: - the engine block (6) is fixed and defines the internal volume (41) - at least one pair of pistons (7A, 7B, 7C, 7D) is arranged in the interior volume (41); said 20 pistons delimit at least one chamber (42A, 42B, 42C, 42D) and are adapted to perform an alternating rotational movement about their theoretical and individual axis of rotation (50A, 50B, 50C, 50D) relative to the engine block (6) in said interior volume (41) to vary the volume of each chamber (42A, 42B, 42C, 42D), - the yoke (E3) is fixed to enter and exit the fluid in each chamber, a The motion conversion mechanism (E4) connects the alternating rotation movements of the pistons (7A, 7B, 7C, 7D) about their theoretical and individual axis of rotation (50A, 50B, 50C, 50D) to the continuous rotational movement of the piston. the motor shaft (30) following its

2 own axis of rotation (40). This conversion mechanism makes it possible to control the individual beats of the pistons. A piston beat is defined by its complete movement between two identical and successive extremal angular positions around the axes (50A, 50B, 50C, 50D): it is also a single alternating rotation cycle of said piston. The mechanisms for controlling the beat of the rotary pistons can be, in particular, of the following two kinds: one based on the use of a deformable rhombus, the other on that of a complex rotary cam. a driving shaft (30) is adapted to perform a continuous rotational movement around a very particular axis (40), characterized in that this axis of rotation is parallel and equidistant from all the theoretical and individual axes of rotation of the pistons (50A, 50B, 50C, 50D), to which physical rotation axes (47A, 47B, 47C, 47D) are associated.

To synchronize the movements of the pistons and convert their alternating rotational movement into continuous rotational movement on the output shaft, the internal combustion engine described in US-5,222,463 uses two arms carried by two coaxial tubes integral with at least two non-consecutive pistons, said arms having lights in which slide the crank pins of a crankshaft. The power produced by the beats of the rotating p = istons passes through a single path with 2 mechanically different coaxial pieces, making the conversion on the two massive arms whose motion is not balanced difficult. On the contrary, the present invention consists in passing power through different mechanically identical paths within the machine in order to obtain:

3 - a lighter dimensioning of the parts, in particular those converting the alternating rotational movement of the pistons in continuous rotational movement of the output shaft, - an overall reduction of their cost by obtaining larger series of parts lighter, - a high power of the machine, perfectly and fully balanced from 2 pairs of pistons, allowing a sharp increase in its speed of rotation. Preferably, the axes of rotation of the pistons (50A, 50B, 50C, 50D) are equidistant from the axis of motor rotation. Their intersections with a plane orthogonal to the axis (40) form a regular polygon centered on the axis (40) whose number of vertices is the number of rotary pistons (7A, 7B, 7C, 7D) of the machine. According to a complementary feature according to the invention, the device furthermore preferably comprises external sculptures (43A, 43B, 43C, 43D) integral with the pistons (7A, 7B, 7C, 7D) and meshing with each other. Thus, on the one hand, the chambers (42A, 42B, 42C, 42D) are more sealed, and on the other hand, the synchronization of the pistons is favored since the distance between the axes of rotation of the pistons and their even number allow the sculptures mesh directly between them, without the need for additional intermediate element. According to another characteristic according to the invention, the device preferably comprises as many chambers as pistons. Thus, each of the rotary pistons constantly separates two consecutive chambers from all the other chambers (42A, 42B, 42C, 42D) and performs at each moment a double effect scan: a decrease in the volume of the first chamber, and simultaneously, a increasing the volume of the second chamber being consecutive.

This ensures a high compactness of the engine. According to yet another characteristic according to the invention, the deformable rhomboid-type motion conversion mechanism preferably comprises: slides (21, 22, 23, 24) translating radially relative to the axis of rotation of the motor. (40), connecting rods (25,26,27,28) connecting in pairs the slides, eccentric (9A, 9B, 9C, 9D) driven by the pistons (7A, 7B, 7C, 7D) and connected with the connecting rods, 15 - at least one crank pin secured to the drive shaft (30) and driven by the sliders. In particular, if the crank pins, connecting rods, sliders, eccentrics and pistons are mounted on bearings, a high efficiency of the mechanism can be achieved and increased reliability by reducing the wear of the parts. According to a complementary feature, this generic deformable diamond type device preferably requires an architecture composed of 4 pistons, 4 eccentric, 4 connecting rods, 4 slides and two crank pins having the following characteristics: - the connecting rods (25,26,27,28) are mounted rotatably, exactly in their middle on the eccentrics (9A, 9B, 9C, 9D), and their extension defines exactly one deformable rhombus, and two of the four slides (23, 24) are translatable in a first direction, opposite direction of one another, - the two other slides (21,22) are translated in a second direction perpendicular to the first direction, in opposite directions from each other, - the slides (23,24 ) are the farthest 5 when the sliders (21,22) are the closest together, and vice versa. - The crank pins are diametrically opposed and each constantly in contact with two consecutive and orthogonal supports among the 4 supports (31,32,33,34) guided by the 4 slides (21,22,23,24). The robustness and efficiency of the conversion mechanism are thus further improved because the perfect guidance of said sliders can be done in particular with bearings tangent to the grooves (36,37) of the plate (29). According to an alternative characteristic also in accordance with the invention, the second type of mechanism of conversion of movement called rotary central cam, comprises: - eccentrics, sliders, at least one slide, rollers and a cam, and relies on the following features: - each eccentric (9) is integral with one of the pistons (7) and carries one of the sliders (52), - the sliders slide in one of the slides (53) at least, - the rollers ( 54) are integral with the slides (53) and exert a force on the central cam (55) to drive it in rotation, and - the cam (55) is integral with the motor shaft (30). Whatever the number of pairs of pistons between one and infinity, this rotating central cam mechanism allows, depending on the shape of the cam, to generate

6 extremely varied kinematic laws to convert the alternating rotational movement of the pistons (7) in continuous rotational movement of the motor shaft (30). Preferably, the cam comprises a plurality of lobes and the number of lobes of the cam is equal to the number of pairs of pistons multiplied by a non-zero integer. This allows the central cam to also have a role of reducing the movement at high efficiency and reduced space. However, technical constraints on: - the fineness of the lobes - the transmission angles of the forces at the cam / roller contacts may require an increase in the average diameter of the rotating central cam for large numbers of lobes. According to another characteristic according to the invention, preferably the device comprises at least two pairs of pistons, each slide slides in two consecutive slides, and each slide is held by two of the slides. The use of bearings for slides, rollers and slides also ensures very good yields and excellent reliability of the mechanism. According to another characteristic according to the invention, the device preferably also has the following characteristics: the cylinder head comprises at least one intake port (61) for introducing the fluid into each chamber, at least one valve of intake for closing the intake port, at least one exhaust port (62) for exhausting fluid from each chamber and at least one exhaust valve for closing off the exhaust port, - each intake valve opens and closes by passage of an intake rotary shutter (14) having one or more openings at its periphery to selectively seal and release the intake port, and each exhaust valve opens and closes by the passage of an exhaust rotary shutter (14) having one or more openings at its periphery for selectively closing and releasing the exhaust port. The use of one or more rotary shutters makes it possible to simplify the control of the valves and to obtain closures or releases of the very fast lights with a large section of fluid passage, while keeping a compact mechanism. According to a complementary feature according to the invention, the rotary shutter system can be, from the simplest to the most sophisticated: - without variable setting: a single piece common to all the intake and exhaust valves and rotating around the axis (40), equipped with two families of lights (63A, 63B, 63C, 63D), one for admission, the other for the exhaust, the two families of lights being distributed at its periphery , regularly, circularly and on two distinct radii about the axis (40), - with variable timing at the intake and exhaust: two parts rotating about the axis (40), equipped with lights distributed at their center. peripherally circularly and regularly around the axis (40): the first part is common to all the intake ports (61), the second to all exhaust (62). The variable valve timing then becomes

8 independent between the intake and the exhaust, but is not independent from one room to another, - with variable timing completely independent for each valve: for each room, two rotating parts equipped with one or more lights (63) distributed at their periphery, the first part for the intake (61), the second for the exhaust (62), the variable valve timing then becomes independent between the intake and the exhaust, and also d one room to another. In all cases, for both the intake and the exhaust, the movement of the rotary shutter (s) is preferably controlled firstly by the rotation of the motor shaft (30) and secondly by a admission management (65) assisted by a mechanical member (64). Thus, the rotation of the motor shaft makes it possible to manage the nominal operation of the intake and exhaust valves, while the inlet and exhaust management device or devices (64, 65) make it possible to manage variations with respect to the aforementioned nominal operation. According to another complementary feature, when the device comprises at least two chambers, and for each of these chambers at least: an intake port and an intake gate, an exhaust port and an exhaust gate . The intake and exhaust management devices (65) acting on their respective mechanical members (64) are capable of holding closed or open, for any number of alternate rotations of the pistons, respectively each shutter

9 rotary intake and each rotary exhaust shutter of at least one of the chambers. Thus, some of the chambers may not be used under certain circumstances, to reduce compression and expansion losses of gas, and thus improve the efficiency of the engine. In general, the intake and exhaust management systems supervise rotations of the rotary shutter (14), the sun gear (15) and the planet carrier (17). This supervision of the rotary distributions allows, by the modification, or even the deactivation of the nominal operation of the rooms, to reach optimum efficiencies for the machine, according to the evolutions of its environment.

According to another characteristic according to the invention, the device preferably also has the following characteristics: the volume of each chamber (42) varies during a piston beat, between a compression volume (minimum) and a suction volume (maximum), the device further comprises at least one volume-modifying device (3) communicating with the chamber and movable between an advanced position and a retracted position. Thus, the compression ratio can be adapted to approach the optimum operating conditions: - high rate if the member (3) is in the advanced position - low rate if the member (3) is in the retracted position According to a complementary feature according to the invention, de preferably the volume modification member carries an injector and / or a spark plug (2). The compactness of the engine and the efficiency of the combustion in the chambers can thus be improved, especially in supercharged engines with variable speed. Preferably, the volume modification member is slidably mounted in a bore (4).

According to another characteristic according to the invention, the motor unit preferably has a tubular shape closed at each end by a substantially flat plate. This simple solution reduces the cost of the device, and improves its robustness and compactness. According to yet another characteristic according to the invention, one of the plates is preferably integrated in the cylinder head. Other features and advantages of the present invention will be apparent from the following detailed description, with reference to the accompanying drawings in which: - Figure 1 illustrates in exploded perspective a device according to the invention, in Figure 2 illustrates the device in perspective 20 without the floor marked E4 in Figure 1, in Figure 3 illustrates in exploded perspective, on an enlarged scale, the stage marked El in Figure 1, Figure 4 illustrates in exploded perspective, on an enlarged scale, the E 2 and E 3 shown in FIG. 25, FIG. 5 shows the device assembled and viewed in profile in relation to the exploded views of the stages labeled E1, E2, E3 and E4 in FIG. 1, FIG. in cross-section, the stage E2, FIG. 7 is an exploded perspective view, on an enlarged scale, of the deformable rhombus type stage E4,

FIGS. 8A, 8B, 8C and 8D diagrammatically represent the deformable rhombus type stage E4, in four successive positions, FIG. 9 schematically represents the stage marked E4 of rotating central cam type with rollers pointing towards the center. 2 of the machine and 2 pairs of pistons, FIG. 10 schematically shows the stage marked E4 of rotating central cam type with rollers pointing towards the periphery of the machine and 2 pairs of pistons, FIG. 11 schematically represents the variant of FIG. FIG. 9 in the case of a device with 3 pairs of pistons, FIG. 12 schematically represents the variant of FIGS. 9 or 10 in the case of a device with a single pair of pistons, FIG. 13 schematically represents a variant of Figure 10 in the case of a device with 2 pairs of pistons and a heptupled central cam (55), or having 2x7 = 14 lobes, Figure 14 shows schematic FIG. 11 shows a variant of FIG. 11 in the case of a device with 3 pairs of pistons and two central cams (55, 58) quadrupled each comprising 3 × 4 = 12 lobes, FIG. 15 schematically represents a variant of FIG. in the case of a single pair of pistons and a sextupled central cam (55) having 1x6 = 6 lobes, FIG. 16 shows a variant of FIG. 12 in the case of a single pair of pistons and two central cams (55,58), each of which is not duplicated, each having 1x9 = 9 lobes. FIG. 17 shows the valve rotary shutter mechanism labeled 10A, 10B, 10C, 10D, 10E, 10F, 10G, 10H in FIG. 2, with its management device (64, 65), FIG. adjustable rotary shutter common to 4 intake ports (61A, 61B, 61C, 61D) that can be generalized for any number of circular and regularly distributed lights, whether they be intake or exhaust. Figures 1 to 7 illustrate a device 1, forming in the illustrated application an internal combustion engine. The engine 1 is articulated around 4 stages E1, E2, E3, E4, represented more particularly in FIGS. 1 and 5, and succeeding one another along an axis 40 corresponding to the axis of rotation of the output shaft 30 of the engine.

Stage E1 is dedicated to fuel injection and compression ratio adjustment. Stage E2 is dedicated to energy conversion (combustion). Stage E3 is dedicated to the gas exchange of the engine with the outside and forms a cylinder head. The stage E4 is constituted by the conversion mechanism of an alternating rotary movement from the stage E2 into a continuous rotary movement for the output shaft of the motor. As illustrated in particular in Figures 4 and 6, the stage 2 consists essentially of a casing 6 of substantially tubular shape defining an interior volume 41 closed at its ends by plates 5, 8 containing 4 rotary pistons 7A, 7B 7C and 7D integral pivoting shafts 47A, 47B, 47C, 47D. The pistons are rotatably mounted about individual axes of rotation of pistons 50A, 50B, 50C, 50D parallel and equidistant to the axis of rotation 40 of the drive shaft 30. As illustrated in particular in FIGS. 2 and 6, the pistons 7A, 7B, 7C, 7D angularly delimit four

13 chambers 42A, 42B, 42C, 42D extending between the end plates 5, 8 and between two adjacent pistons. External treads 43A, 43B, 43C, 43D are integrated with the pistons 7A, 7B, 7C, 7D, and the external treads of two adjacent pistons mesh with each other, so that two adjacent pistons rotate in opposite directions about their axis of rotation. 50A, 50B, 50C, 50D respectively. The volume of each of the chambers 42A, 42B, 42C, 42D varies with the rotation of the pistons 7A, 7B, 7C, 7D between a compression volume (minimum) and a suction volume (maximum). The volume of two adjacent chambers 42A, 42B, 42C, 42D varies in opposite manner. Stage 2 is the heart of the engine, because it is the place of thermomechanical conversions. The 4 rotary pistons 7A, 7B, 7C, 7D are driven in a rotary and reciprocating motion with an amplitude of 90 °. When the rotary pistons are in a vertical or horizontal position, they become tangent with one of the shoulders 67A, 67B, 67C, 67D integral with the housing 6 and distributed at 90 °. This has the effect of creating a flushing effect inside the combustion chamber 42A, 42B, 42C, 42D and promotes combustion during fuel injection and / or on ignition. The reciprocating rotation of the 4 pistons 7A, 7B, 7C, 7D makes it possible to ensure in each combustion chamber the admission of the fresh gases, their compression, the explosion / expansion and the exhaust. The cooling of the engine can in particular be done by the integration of cooling fins over the entire periphery of the sealed housing 17, or by the circulation of a refrigerant in the thickness of this housing as suggested by the holes (P ) arrows in Figure 6 and their arrow connections R1 and R3 in Figure 2.

In order to perform the 4-stroke cycle in each chamber 42A, 42B, 42C, 42D, each rotary piston 7A, 7B, 7C, 7D must make 2 round trips, preferably with an amplitude of 900. The Otto and of Diesel are particularly perfectly compatible with the device. The lubrication of stage E2 is possible by injecting oil into the center of the engine. There is then an oil bath in contact with the rotary pistons 7A, 7B, 7C, 79. The groove arrangement in these pistons makes it possible to pass the oil under the effect of the centrifugal force to the periphery of the piston. 6. This lubrication is desirable to reduce friction and increase the longevity of parts. The engine 1 can also operate in pneumatic mode, by injecting fluid under pressure at the (minimum) compression volume of each chamber 42A, 42B, 42C, 42D, expansion up to the volume (maximum) suction and exhaust of the gas expanded when returning to the compression volume, then repeat this cycle. In this case, only the round-trip of the rotary pistons 7A, 7B, 7C, 7D is necessary to perform a cycle. The engine 1 can also operate in a 2-stroke engine, vigorously scavenging the flue gases with fresh gases at the end of the explosion / expansion. It then suffices for a single round trip of the rotary pistons 7A, 7B, 7C, 7D to perform a cycle. As illustrated in particular in FIG. 3, the stage E1 consists of the end plate 5, of 4 assemblies each comprising a volume modification member 3A, 3B, 3C, 3D sliding in the bore of FIG. a hollow body 4A, 4B, 4C, 4D integral with the end plate 5 and enclosing an injector 2A, 2B, 2C, 2D. The bore of each of the hollow bodies 4A, 4B, 4C, 4D communicates with a corresponding chamber 42A, 42B, 42C, 42D.

The volume modifying member 3A, 3B, 3C, 3D forms a piston and allows a rapid modification of the compression volume and / or the suction volume of the chambers by penetrating more or less in the chambers 42A, 42B, 42C , 42D. This control can be done in particular by injecting an incompressible fluid under pressure into the hollow body 4A, 413, 4C, 4D or by an electric motor equipped with a worm gear reducer pushing or withdrawing the piston formed by the volume modification member 3A, 3B, 3C, 3D. This control can be done independently for one or other of the 4 combustion chambers 42A, 42B, 42C, 42D. The amplitude of adjustment depends on the dimensions of the engine parts. To simplify the control, the adjustable pistons 3A, 3B, 3C, 3D could be secured and actuated by a common mechanism, but the adjustment is no longer independent of a room to another. At the end of compression in a chamber 42A, 42B, 42C, 42D, the injector 2A, 2B, 2C, 2D finely atomizes a fuel and the eventual candle creates a spark, in order to proceed to the explosion-expansion engine time. As a variant, the compression volume can be voluntarily fixed by fixing the assembly formed by the volume modification member 3A, 3B, 3C, 3D and the injector 2A, 2B, 2C, 2D on the end plate 5 In addition, any method of introducing fuel and ignition is possible: carburettor, spark plug, indirect injection mono or multipoint, direct injection mono or multipoint, thermo-ignition, photo-ignition. Finally, and naturally, when the engine 1 operates exclusively in pneumatic mode, any introduction of fuel and any ignition device are useless. As illustrated in particular in FIGS. 2, 4 and 5, the yoke defining the stage E3 essentially comprises the end plate 8, 4 pairs of valves 10A, 10B, 10C, 10D, 10E, 10F, 10G, 10H, a combustion gas inlet pipe 11, a flue gas exhaust pipe 12, a timing belt 13, eight rotary distribution systems (64, 65) for the management of admissions and exhausts as described in FIG. 17.

The plate 8 thus has eight openings, semicircular in the illustrated embodiment, ensuring the gas exchange between the combustion chambers 42A, 42B, 42C, 42D and the outside of the engine through the 8 rotary distributors. Four of these openings form intake ports 61A, 61B, 61C, 61D. The other four openings form exhaust ports 62A, 62B, 62C, 62D. The valves for closing the intake ports 61A, 61B, 61C, 61D form intake valves 10A, 10C, 10E, 10G. The valves for closing the exhaust ports 62A, 62B, 62C, 62D form exhaust valves 10B, 10D, 10F, 10H. The continuous rotation movement of the output shaft of the motor 30 is transmitted to the planet carrier 17 of each of the valves 10A, 10B, 10C, 10D, 10E, 10F, 10G, 10H through the timing belt 13. The rotation of the motor shaft 30 is advantageously mechanically transmitted (by means not shown) to the timing belt 13.

Alternatively, rotation of the output shaft of the motor 30 could be picked up by a sensor and transmitted to the timing belt 13 by an electric motor controlled according to the rotation of the motor shaft 30 picked up by the sensor.

In both cases, the timing belt 13 is received in a groove provided for this purpose on each of the rotary distribution systems, to synchronize their rotation. Such a belt can be smooth or notched provided to provide the groove with teeth. The path of the

Belt 13 may also be more elaborate to maximize the winding angles on each planet carrier 17. Using intake and exhaust management systems (64,65) to oversee the rotations of the vehicle. With the rotary shutter (14), the sun gear (15) and the planet carrier 17, it is possible, while the engine is running, to advance or to delay the passage of the opening 63 of the rotary shutter 14 above the light corresponding to the engine cycle and to extend or reduce the passage time of the opening 63 opposite the opening. Rotary distribution systems even have the possibility of deactivating 1, 2 or 3 of the 4 combustion chambers 42A, 42B, 42C, 42D at will to avoid gas exchange or unwanted compression, leaving the valves respectively constantly closed. or open. This gives great flexibility to the engine because its displacement becomes variable, in increments of 25% of its total power in the case of a four-piston engine 7A, 7B, 7C, 7D. Lubrication or lubrication of the valves is possible to reduce friction and simultaneously increase the longevity and tightness of the device. For the sake of simplification of the engine, the rotary distribution system could be removed for example by directly actuating the rotary shutter 14. In this case, the engine would have lower adjustment possibilities, both at the intake and at the exhaust. It is also possible to envisage a rotary distribution based on a single circular plate in rotation around the axis 40 whose bores would intermittently release the intake and / or exhaust ports 61 of each chamber 42 as illustrated in FIG. . 18. The use of another system by sliding drawers or electromagnetic valve control is

18 a serious alternative for the management of admissions and exhausts. As illustrated in particular in FIGS. 7 and 8, the motion conversion mechanism defining the stage E4 essentially comprises four eccentric members 9A, 9B, 9C, 913, two vertical sliders 21, 22, two horizontal sliders 23, 24, two upper rods 26, 27, two lower rods 25, 28, guide grooves 36, 37, two horizontal pushers 31, 32, two vertical pushers 33, 34, two crank pins 44, 45 integral with the output shaft 30 and a protection plate 38 having a hole 39 traversed by the output shaft 30. The eccentric 9A, 9B, 9C, 9D are carried by the shafts 47A, 47B, 47C, 47D traversing the end plates 5, 8 and pivoting around of their respective piston pins 50A, 50B, 50C, 50D. The vertical sliders 21 and 22 are received in the guide groove 36 extending in a vertical direction 48 while the horizontal sliders 23 and 24 are received in the guide groove 37 extending in a horizontal direction 49. The grooves of guide 36, 37 are made in a support plate 29. The slides 21,22,23,24 are rotatably mounted on the appropriate ends of the rods 25,26,27,28., more precisely, the upper rods 26,27 respectively connect the vertical slider 22 to the horizontal sliders 23, 24, while the lower links 25, 28 respectively connect the vertical slider 21 to the horizontal sliders 23, 24. The connecting rods 25, 26, 27, 28 are all of the same length and mounted symmetrically. relative to the directions 48 and 49 so the intersections of their extensions defines exactly a deformable rhombus. The vertical slides 21, 22 move in a direction opposite to each other in the vertical direction 48,

19 while the horizontal slides 23, 24 move in the opposite direction in the horizontal direction 49. Furthermore, the slides (21 and 22) are closest when the sliders (23 and 24) are furthest away, and vice versa. The center of each of the four rods 25, 26, 27, 28 is rotatably mounted on the eccentric 9A, 9B, 9C, 9D, so that it recovers the rotary 90 ° reciprocating movement of each end of the pivoting shafts 47A, 47B 47C, 47D. The horizontal pushers 31, 32 are fixed on the vertical slides 21, 22, while the vertical pushers 33, 34 are fixed on the horizontal slides 23, 24. Finally, each of the pushers 31, 32, 33, 34 is supported on the diametrically opposite pins 44, 45 of the output shaft 30, which allows to obtain a continuous rotational movement, as shown in Figures 8A, 8B, 8C, 8D. More specifically, each of the crank pins 44, 45 is pushed simultaneously by one of the horizontal pushers 31, 32 and one of the vertical pushers 33, 34. The kinematics generated by this device has the advantage of quickly crossing the dead point high. Thus, a reduction in the production of NOx-type pollutants at top dead center is achieved by reducing the dead-time of the top dead center, a reduction in the thermal leakage of the highly compressed gas, or even partially or totally burned, so a better conservation of its energy - a better restitution of the gas energy during a relaxation which lasts longer, - a better filling of the rooms during the admission which lasts longer, 20 - within the framework of a operation of the motor as a pump, the continuity of the pumped fluid flow. In order to ensure optimum lubrication of the motion conversion mechanism defining stage E4, it is possible to place it in an oil bath. The main objective of this engine is to have maximum compactness. It may be noted that the volume of fresh gas sucked by this engine is proportional to the square of its characteristic dimension, which can be defined by the double of the length of the rotary pistons, unlike the traditional piston / rod / crank which aspire only volumes proportional to their characteristic dimension, which can be defined by the stroke of the piston. Moreover, all the engine accessories, except the injectors, have a reduced volume to a minimum. This gives the motor object of the invention an exceptional compactness. At equal power, the compactness could be increased by a factor of 3 compared with a piston / crank / crank / casing motor, and even by a factor of 4 by eliminating the El stage, and even more by using a Rotating central cam on top. In the extension of this high compactness, the volumes and masses of material required for the construction of such an engine would be much lower than those required by current techniques. Sized for pressures of 100 bar, the machine object of the invention would use between 20 and 25 kg of steel of standard quality in the material per liter of displacement. Consequently, this engine authorizes: a very significant reduction in manufacturing costs; hybridization of the vehicles: the space released can be occupied by a second non-thermal engine as well as by its energy storage device; The braking of the vehicles by recuperation of their kinetic energy: the space savings are then occupied by the recovery device, an increased freedom of design: the gains in space make it possible to give ease of movement; cockpit, to obtain greater steering angles, or even to motorize a vehicle by several small motors dedicated to either an axle or each wheel (4x4 vehicle without AWD, 2x2 motorcycle ...). 10 - an increase in the power of the engines: • by a better filling on the intake, • by a combustion favored by the vortices created during the compression, • at equal volume, a power 3 to 4 times greater than that of a piston engine / connecting rod / crank. This engine also offers a number of environmental benefits, such as: - Reducing vehicle pollution by: • Implementing more powerful gas pollution control devices by saving space with this engine • Using a non-polluting hybrid propulsion mode whenever it is necessary, especially in the city, • by having a better combustion in the combustion chambers, • by having fewer losses in the gearbox: the engine object of the The invention produces slow but high torque torque at low revolutions, particularly if a highly multilobed central cam is used; it

22 makes it possible to limit the reduction gears, which is ideal for towing a load, • Compatibility with all types of fuel, in particular less polluting: biofuels (vegetable oils or alcohols), natural gas and especially hydrogen , -exploitation of the compression ratio setting and kinematics driven by the chosen cam profile that opens the way to new types of combustion: - Controlled thermo-ignition mode (CAI / HCCI). controlled auto ignition / homogeneous charge compression ignition), - the photo-ignition mode: combustion triggered by radiation resulting from very high sudden temperatures obtained by sudden compression and higher compression ratios. These two modes are currently almost inapplicable because of the kinematics imposed by the rod / crank system and the low thickness of the piston heads. On the contrary, the rotary pistons, thanks to their large thickness and their favorable kinematics of the top dead center, allow: • a combustion of fuel considered cleaner (NOx, particles) and more efficient (lower consumptions) • a better mechanical reliability FIGS. 9 to 12 illustrate the rotating central cam embodiment of the motion conversion mechanism defining the stage E4 of the engine 1 whose principle makes it possible to convert the alternating rotation movement of the pistons into a continuous rotation movement of the shaft output regardless of the number of pairs of pistons.

In FIG. 9, the motion conversion mechanism E4 essentially comprises four eccentrics 51A, 51B, 510, 51D, four slides 52A, 52B ,, 52C, 52D, two vertical rails 53A, 53C, two horizontal rails 53B, 53D, four rollers 54A, 54B, 54C, 54D rigidly connected to the slides by means of connecting bars 56A, 56B, 56C, 56D and a cam 55. Each of the slides 52A, 52B, 52C, 52D slides both in the one of the vertical rails 53A, 53C and in one of the horizontal rails 53B, 53D. The vertical slides 53A, 53C are thus translated horizontally in the opposite direction by the slides 52A, 52B, 52C, 52D during the rotation of the pistons 7A, 7B, 7C, 7D, while the horizontal slides 53B, 53D are moved vertically in the direction opposite. The slides 53A, 53B, 53C, 53D thus define a rectangle at each apex of which there is a slide 52A, 52B, 52C, 52D. The cam 55 has a guide groove 57 having two lobes 55A, 55B in which are received the rollers 54A, 54B, 54C, 54D. The rollers being integral with the slides 53A, 53B, 53C, 53D, during the rotation of the pistons 7A, 7B, 7C, 7D, the rollers 54A, 54B, 54C, 54D exert a pressure on the cam 55 causing the cam 55 to react by reaction. and the motor shaft 30 integral with the cam 55 in rotation. The profile of the groove 57 of the cam 55 has inflection points in which are the rollers 54A, 54B, 54C, 54D, when the pistons 7A, 7B, 7C, 7D simultaneously reach one end of their movement of rotation. The alternating rotational movement of the pistons 7A, 7B, 7C, 7D is thus converted into continuous rotational movement of the drive shaft 30. The embodiment of the motion conversion mechanism E4 illustrated in FIG.

24 of embodiment shown in Figure 9, in that the connecting bars 56A, 56B, 56C, 56D place the rollers 54A, 54B, 54C, 54D outside the rectangle defined by the centers of the slides 52A, 52B, 52C , 52D, while in the embodiment illustrated in FIG. 9, the connecting bars 56A, 56B, 56C, 56D place the rollers 54A, 54B, 54C, 54D within the rectangle defined by the centers of the sliders 52A , 52B, 52C, 52D. The cam 55 is enlarged, as is the radius of curvature of the lobes 55A, 55B. The embodiment of the motion conversion mechanism E4 illustrated in FIG. 11 consists of an adaptation of the embodiment illustrated in FIG. 9 in the case where the engine comprises six pistons 7A, 7B, 7C, 7D, 7E, 7F. The motion conversion mechanism E4 then essentially comprises six eccentrics 51A, 51B, 51C, 51D, 51E, 51F, six sliders 52A, 52B, 52C, 52D, 52E, 52F, three pairs of parallel sliders 53A, 53D; 53B, 53E; 53C, 53F; six rollers 54A, 54B, 54C, 54D, 54E, 54F rigidly connected to the slides via connecting rods 56A, 56B, 56C, 56D, 56E, 56F and a cam 55. Each of the slides 52A, 52B, 52C, 52D, 52E, 52F slides both in two adjacent slides. The slides are held by two sliders, so that they are translated in pairs during the rotation of the pistons 7A, 7B, 7C, 7D, 7E, 7F. The cam 55 has a guide groove 57 having three lobes 55A, 55B, 55C in which are received the rollers 54A, 54B, 54C, 54D, 54E, 54F. During the rotation of the pistons 7A, 7B, 7C, 7D, 7E, 7F, the rollers 54A, 54B, 54C, 54D, 54E, 54F exert a pressure on the cam 55 driving it by reaction in rotation. The profile of the groove 57 of the cam 55 has points of inflection in which the rollers are located.

54A, 54B, 54C, 54D, 54E, 54F when the pistons 7A, 7B, 7C 7D, 7E, 7F reach one end of their rotational movement. The embodiment of the motion conversion mechanism E4 illustrated in FIG. 12 consists of an adaptation of the embodiment illustrated in FIG. 9 in the case where the engine comprises two pistons 7A, 7B. The movement conversion mechanism E4 then essentially comprises two eccentrics 51A, 51B, two slides 52A, 52B, a slide 53, two rollers 54A, 54B, rigidly connected on either side of the slideway by means of rods link 56A, 56B and a cam 55. In view of the foregoing, the motion conversion mechanism E4 illustrated in FIGS. 9 to 12 can easily be extrapolated to convert the motion of any number of pairs of rotational pistons. alternated in a continuous rotation movement. In addition, as illustrated in Figures 12 to 16, the fact of overmultilober strongly cam, that is to say to multiply the minimum number of lobes it must include (ie the number of pairs of pistons) by a positive integer, allows the central cam, without making it more cumbersome or more fragile, to have two functions: - on the one hand, a very fine parameterization of the movement of the rotary pistons 7 according to the rotation of the shaft motor 30 - on the other hand, the reduction of the movement with a good efficiency (simplifying or even eliminating the gearbox).

Claims (20)

1. Device (1) intended to constitute a motor capable of producing mechanical work under the pressure of a fluid, or a pump capable of transferring or pressurizing a fluid, said device comprising: a fixed engine block (6) ) defining an interior volume (41), - at least one pair of pistons (7A, 7B, 7C, 7D) disposed in the interior volume (41); said pistons 10 delimit at least one chamber (42A, 42B, 42C, 42D) and are adapted to perform an alternating rotational movement about their theoretical and individual axis of rotation (50A, 50B, 50C, 50D) relative to the engine block (6) in said interior volume (41) to vary the volume of each chamber (42A, 42B, 42C, 42D), - a fixed yoke (E3) for entering and exiting the fluid in each chamber, - a a motion conversion mechanism (E4) connecting the alternating rotation movements of the pistons 20 (7A, 7B, 7C, 7D) about their theoretical and individual axis of rotation (50A, 50B, 50C, 50D) to the continuous rotational movement of the motor shaft (30) along its own axis of rotation (40). This conversion mechanism controls the beats of the rotary pistons (7A, 7B, 7C, 7D) and can be of two kinds: one based on the use of a deformable rhombus, the other on that of a cam complex rotary. - A drive shaft (30) adapted to perform a continuous rotational movement about a very particular axis (40), characterized in that this axis of rotation 30 is parallel and equidistant from all the theoretical and individual axes of rotation of the pistons (50A, 50B, 50C, 50D). 2. Device according to claim 1, wherein the theoretical and individual axes of rotation (50A, 50B, 27 50C, 50D) of piston are equidistant from the axis of engine rotation (40) and their intersections with a plane orthogonal to the axis (40) form a regular polygon centered on the axis (40) whose number of vertices is the number of rotary pistons (7A, 78,7C, 7D) of the machine. 3. Device according to claim 2, further comprising outer sculptures (43A, 43B, 43C, 43D) integral with the pistons (7A, 7B, 7C, 7D) and meshing with each other. 4. Device according to any one of the preceding claims comprising as many chambers (42A, 42B, 42C, 42D) as pistons (7A, 7B, 7C, 7D). 5. Device according to any one of the preceding claims, wherein the deformable diamond-shaped motion conversion mechanism (E4) comprises: - slides (21, 22, 23, 24) moving radially relative to the axis motor rotation (40), connecting rods (25,26,27,28) connecting in pairs the slides (21,22,23,24) to eccentrics (9A, 9B, 9C, 9D) driven by the pistons (7A, 7B, 7C, 7D) and connected to the connecting rods (25,26,27,28), and to at least one crank pin (44,45) integral with the driving shaft (30) and driven by the sliders ( 21,22,23,24). 6. Device according to claim 5, comprising 4 pistons (7A, 7B, 7C, 7D), 4 eccentric (9A, 9B, 9C, 9D), 4 connecting rods (25, 26, 27, 28), 4 slides (21, 22, 23, 24) and two crank pins (44, 45) in which: the rods (25, 26, 27, 28) are rotatably mounted, exactly in the middle, on the eccentrics (9A, 9B, 9C, 9D) . The extensions of the connecting rods (25, 26, 27, 28) define exactly one deformable rhombus, and two or two (21,22) of the four slides are translated in a first direction of sliding (48), in the opposite direction one of the further, the two other (23, 24) sliders are translated in a second sliding direction (49) perpendicular to the first sliding direction (48), in opposite directions from each other, to the sliders (23,24) are furthest apart when the sliders (21,22) are the closest together, and vice versa, the crank pins (44,45) are diametrically opposed and each simultaneously in contact with two orthogonal sliders. Apparatus according to any one of claims 1 to 4, wherein: the motion conversion mechanism (E2) referred to as the rotating central cam comprises eccentrics (51A, 51B, 51C, 51D, 51E, 51F), sliders (52A, 52B, 52C, 52D, 52E, 52F), at least one slider (53A, 53B, 53C, 53D, 53E, 53F), rollers (54A, 54B, 54C, 54D, 54E, 54F) and a cam (55), each eccentric (51A, 51B, 51C, 51D, 51E, 51F) is integral with one of the pistons (7A, 7B, 70,7D, 7E, 7F) and carries one of the slides (52A, 52B, 52C, 52D, 52E, 52F), where the sliders (52A, 52B, 52C, 52D, 52E, 52F) slide in one of the sliders (53A, 53B, 53C, 53D, 53E, 53F ), the rollers (54A, 54B, 54C, 54D, 54E, 54F) are integral with the slideways (53A, 53B, 53C, 53D, 53E, 53F) and exert a force on the cam (55) to drive it in rotation, and the cam (55) is integral with the drive shaft (30) 29 8. Device according to claim 7, wherein the cam (55) comprises a plurality of lobes (55A, 55B, 55C) e ~ the number of lobes (55A, 55B, 55C) of the cam is equal to the number of pairs of pistons (7A, 7B, 7C, 7D, 7E, 7F) multiplied by a non-zero integer. 9. Device according to any one of claims 7 or 8, wherein: - the device comprises at least two pairs of pistons (7A, 7B, 7C, 7D, 7E, 7F), - each slide (52A, 52B, 52C , 52D, 52E, 52F) slides in two slides (53A, 53B, 53C, 53D, 53E, 53F), and - each slide (53A, 53B, 53C, 53D, 53E, 53F) is held by two of the slides. (52A, 52B, 52C, 52D, 52E, 52F) 10. Device according to any one of the preceding claims, wherein: - the yoke (E3) comprises at least one intake port (61A, 61B, 61C, 61D) for introducing the fluid into each chamber (42A, 42B , 42C, 42D), an intake valve (10A, 10C, 10E, 10G) for closing the intake port (61A, 61B, 61C, 61D), an exhaust port (62A, 62B, 62C, 62D) ) for discharging the fluid from each chamber (42A, 42B, 42C, 42D) and at least one exhaust valve (10B, 10D, 10F, 10H) to close the exhaust port (62A, 62B, 62C, 62D) each intake valve (10A, 10C, 10E, 10G) comprises a rotary inlet valve (14) having an opening (63) for selectively closing and releasing the intake port (61A, 61B, 61C, 61D), and - each exhaust valve (10B, 10D, 10F, 10H) comprises an exhaust rotary shutter (14) having an opening (63) for selectively closing and releasing the exhaust port ( 62A, 62B, 62C, 62D). 11. Device according to claim 10 wherein the rotary shutter system can be, from the simplest to the most sophisticated: - without variable timing: a single piece common to all the intake and exhaust valves and in rotation around the axis (40), equipped with two families of lights (63A, 63B, 63C, 63D), one for admission, the other for the exhaust, the two families of lights being distributed at its periphery, lo regularly, circularly and on two distinct radii around the axis (40), - with variable timing at the inlet and the exhaust: two parts rotating about the axis (40), equipped with lights distributed at their circular periphery 15 and regularly about the axis (40): the first part is common to all the intake ports (61), the second to all exhaust (62), - with variable timing fully independent for each valve: for each chamber, two pieces in rotation equipped with one or more lights (63) distributed at their periphery, the first part for the admission (61), the second for the exhaust (62), with the possibility of obtaining these variable settings with the help of epicyclic gear trains comprising at least one sun gear (15) and at least one planet carrier (17). 12. Device according to claims 10 and 11, wherein the rotation of each rotary admission shutter (14) is controlled on the one hand by the rotation of the motor shaft (30) and on the other hand by a control system. Admission management (65) supervising rotations of the rotary shutter (14), the sun gear (15) and the planet carrier (17). 13. Device according to claims 10 and 11, wherein the rotation of each rotary shutter 35 (14) is controlled on the one hand by the rotation of the motor shaft (30) and on the other hand by a system of exhaust management (65) supervising rotations of the rotary shutter (14), the sun gear (15) and the planet carrier (17). 14. Device according to claims 12 or 13, said device comprising at least two chambers (42A, 42B, 42C, 42D) and for each of these chambers at least one intake port (61A, 61B, 610, 61D), a intake shutter (14), an exhaust port (62A, 62B, 62C, 62D) and an exhaust shutter (14), wherein the control unit (65), by means of each rotary distribution system, controls the various intake and exhaust rotary shutters (14) completely independently. 15. Device according to claim 14, wherein the rotary distribution system of the intake and the rotary distribution system of the exhaust, controlled by the management member (65), keep closed or open, for any number alternating rotations of the pistons, respectively each rotary admission shutter (14) and each rotary exhaust shutter (14) of at least one of the chambers (42A, 42B, 42C, 42D). Apparatus according to any one of the preceding claims, wherein: - the volume of each chamber (42A, 42B, 42C, 42D) varies during an alternating rotation cycle of piston (7A, 7B, 7C, 7D) between a compression volume and a suction volume, the device further comprises at least one volume modifying member (3A, 3B, 3C, 3D) communicating with the chamber (42A, 42B, 42C, 42D). ) and movable between an advanced position and a retracted position 17. Device according to claim 16, in which the volume modifying member (3A, 3B, 3C, 3D) carries an injector (2A, 2B, 2C, 2D) and / or a device for igniting the fuel mixture. . Apparatus according to claim 16 or claim 17, wherein the volume modifying member (3A, 3B, 3C, 3D) is mounted. sliding in a bore (4A, 4B, 4C, 4D). 19. Device according to any one of the preceding claims, wherein the motor unit (6) has a tubular shape closed at each end by a plate (5,8) substantially flat. 20. Device according to claim 19, wherein one of the plates (5,8) is integrated in the cylinder head (E3).