EP0750719A1

EP0750719A1 - Internal combustion engine having rotary distribution valves

Info

Publication number: EP0750719A1
Application number: EP95914408A
Authority: EP
Inventors: Maurice Huwarts
Original assignee: Individual
Current assignee: Individual
Priority date: 1994-03-25
Filing date: 1995-03-23
Publication date: 1997-01-02
Anticipated expiration: 2015-03-23
Also published as: FR2717857A1; JPH09510765A; FR2717857B1; DE69503042T2; US5690069A; AU2141795A; DE69503042D1; EP0750719B1; WO1995026460A1

Abstract

A multi-cylinder internal combustion engine comprising a cylinder assembly with intake ports and exhaust ports arranged in register, wherein the distribution system for opening and closing said intake and exhaust ports includes two rotary pipes (T-8, T-9) each consisting of a plurality of mutually communicating aligned hollow valves (8a, 8b, 8c, 8d or 9a, 9b, 9c, 9d) with a side wall provided with as many apertures (10a, 10b, 10c, 10d; 11a, 11b, 11c, 11d) as there are cylinders. The rotary intake pipe (T-8) and the rotary exhaust pipe (T-9) are housed in an intake manifold (31) and an exhaust manifold (32) respectively, each defining a chamber surrounding said intake pipe (T-8) and said exhaust pipe (T-9) respectively over a large part of the periphery thereof, said chambers (31, 32) being sealed off from one another and arranged so that gaseous fluids can flow freely outside and along said rotary distribution pipes (T-8, T-9).

Description

Internal combustion engine, with rotary distribution shutters.

The present invention relates to an internal combustion engine with rotary distribution shutters.

We already have . sought to overcome the drawbacks of conventional valve distribution systems, by proposing distribution devices with rotary shutters i fs. We know, for example, by the document

US-A-2,730,088, an ult ic li ndre internal combustion engine comprising a group of in-line cylinders, the combustion chambers of which each communicate with an intake orifice and with an exhaust orifice, the orifices of inlet, on the one hand, and the exhaust ports, on the other hand, of said group of cylinders being arranged in alignments, the distribution means allowing the opening and closing of said intake and exhaust ports comprising two rotary nozzles, of circular section, each comprising a plurality of aligned hollow shutters, rigidly connected to one another and communicating with each other, and the side wall of which is provided with a plurality of spaced apart lights, angularly offset , and the number of which corresponds to that of the cylinders to be served, one of these rotary nozzles allowing the opening and closing of the alignment of intake orifices of the group of cylinders, while the second allows the opening and closing of the alignment of exhaust orifices of said group of cylinders.

Each rotary nozzle is made up of alternating cylindrical portions of different diameters, the gas passage openings being provided in the portions of reduced diameter. Each rotary nozzle of distribution is housed in a fixed sheath and its larger diameter portions are dimensioned to have a well-adjusted rotation and sliding clearance inside said fixed sheath, these larger portions being provided, near their ends, with sealing rings allowing a tight seal to be established for the passage of gases.

The device described in document US-A-.730.088 has a significant drawback which results from the fact that the circulation of gases takes place exclusively inside the rotary inlet and exhaust distributor rods.

It follows, in the case of admission, that the first cylinder is fed prefer i e lement, then the second, then the third, etc.

These cylinders are therefore supplied successively, in a very uneven manner, both in volume and in quality as a gas mixture, so that there is a poor balance of the engine. In the same way, the evacuation of the burnt gases is done only through the interior of the rotary exhaust rod, successively for each of the cylinders, so that the exhaust of the gases also operates very irregularly depending on whether the cylinders are more or less distant from the outlet of said rod.

Another drawback of the device described in the aforementioned document lies in the fact that one is obliged to place the carburetor or the exhaust at one of the ends of the rotary distributing tubular rods, which constitutes a constraint when the engine must register in a reduced volume.

An object of the present invention is to remedy the drawbacks outlined above of mu It i cy li ndre internal combustion engines, with a - 3 -

rotary distribution, of the kind described above.

According to the invention, this objective is achieved thanks to an engine of this kind, more particularly remarkable by the fact that the rotary intake nozzle and the rotary exhaust nozzle are housed, the first, in an intake manifold and , the second, in an exhaust manifold each forming a chamber or space surrounding, respectively, said intake nozzle and said exhaust nozzle, over a large portion of their periphery, these chambers being so separated sealed and arranged so as to allow gas circulation outside and along said rotary nozzles.

Thanks to the above characteristic arrangements, the circulation of gases takes place both inside and outside of the rotary distribution nozzles, in the space formed between the latter and the internal surface of said manifolds, in which turns the gas stream (fuel and / or oxidizer), so that, in the case of supply, all the cylinders are supplied in substantially the same conditions, both in volume and in quality of the gas mixture, if although you get better combustion and better engine balance.

Likewise, the evacuation of gases which takes place both from the inside and from the outside of the rotary exhaust nozzle is greatly improved. In addition, thanks to these characteristic features, it is possible to place the carburetor (s), or other supply devices (injectors, etc.) and the exhaust, in different locations of the cylinder head, which is a very advantageous appreciable when the engines have to be housed in reduced volumes.

According to another characteristic arrangement of the invention, each intake and exhaust port is equipped with at least one movable seat making it possible to modify the cross section of the fluids, as well as the moment or instant of closure or of L opening of said orifice, and adjustment means make it possible to adjust the position of these movable seats, these means comprising a cylinder installed, in a sealed manner, through the sealed wall separating the intake and exhaust manifolds, and in which is housed a piston subjected to the action of a compression spring tending to push it in the direction of the exhaust manifold, at least one of the faces of this piston being connected, by means of a ^* articulation, to a control rod itself connected to a connecting rod wedged on a shaft on which are also wedged connecting rods, each connected by means of a transmission linkage to at least one of the mobile seats. At least one of the rotary shutters.

The aims, characteristics and advantages above, and others still, will emerge more clearly from the description which follows and from the appended drawings in which:

Figure 1 is a longitudinal sectional view of the upper part of a cylinder equipped with a dispensing device according to the invention.

Figure 2 is a perspective view of an embodiment of a rotary distributor nozzle consisting of two shutters arranged in the extension of one another.

FIG. 2a represents, by two axial half-sections, two other examples of the configuration of a rotary distributing nozzle consisting of two obturators assembled in the extension of each other.

Figure 3 is an axial sectional view of the drive nozzle of a rotary nozzle.

Figure 3bis is a front view of the end of this tip.

Figure 4 is an axial sectional view of an embodiment of the opposite nozzle of the nozzle.

Figure 5 is a plan view in section of a dispensing assembly according to the invention. Figures 6 to 9a i llustrate the operation of the distribution system according to the invention.

Figure 10 is a schematic view, in plan and in section, of an embodiment of rotary intake and exhaust nozzles fitted to the upper part of a four-cylinder engine.

FIG. 10 bis is a diagrammatic view on a larger scale on line 10-10 in FIG. 10.

Figure 11 is a perspective view in section i llustrant a control device of the seat adjustment system mobi the rotary shutters.

Figure 12 is a cross-sectional view of a rotary shutter and its movable seats.

Figure 13 is a perspective view of one of these movable seats.

Figure 14 is a front view of a lateral flange for guiding movable seats.

Reference is made to said drawings to describe an advantageous, although in no way limiting, embodiment of the internal combustion engine according to the invention and, more particularly of the distribution device equipping this engine.

FIG. 1 shows the upper part of a cylinder 1 and a cylinder head 2 fixed to the upper part of this cylinder and delimiting the combustion or explosion chamber 3. In the cylinder head 2, by example made of special aluminum and with an appropriate conformation, the intake 4 and exhaust 5 ports are themselves provided with seats 6, 7, respectively, shutters. The shutters consist of rotary elements 8, 9, hollow, of circular section, in the side wall of which is provided a light 10, 11, respectively, for each cylinder of the engine to be served or served. These shutters can have a cylindrical, or conical, or ovoid, or even spherical shape. Depending on the number of cylinders to be served or served, two or more of two rotary shutters 8, 9 are assembled in succession and in alignment, for example by screwing or otherwise. FIG. 2 illustrates two cylindrical rotary shutters 8a, 8b assembled one after the other and intended to equip a twin-cylinder engine. The assemblies T thus produced will be designated under the name of "rotary nozzles" in the description which follows, in order to facilitate the description.

FIG. 2bis shows two other examples of conformation of the rotary distributor nozzle T consisting of two shutters 8 or 8 ′ assembled in the extension of one another, with a sliding capacity of amplitude limited relative to the Another, by means of simple grooves 61, which makes it possible to solve the problems which could arise from the effects of expansion or from a slight misalignment. In addition, in this figure, the shutters 8 of the lower half-cut have a concave conformation, while the shutters 8 'of the upper half-cut have a bulged shape in their central part, such a shape increasing the capacity of introduction of fresh gases into the cylinders.

As stated earlier, the number shutters 8 or 9 constituting each intake nozzle T-8 and each exhaust nozzle T-9 is a function of the number of cylinders of the engine. Thus, FIG. 10 shows rotary nozzles for intake T-8 and exhaust T-9 each consisting of an alignment of four shutters 8a, 8b, 8c, 8d, or 9a, 9b, 9c, 9d, respectively , whose lights 10a, 10b, 10c, 10d or 11a, 11b, 11c, 11d are offset by 90 degrees. The shutters such as 8a, 8b, 8c, 8d, ...., thus aligned and integral with one another in rotation, constitute a tubular assembly according to which said shutters are in permanent communication by their bore. It is understood that the rotary nozzles T-8 and T-9 can be arranged and di mens i onnées to serve r or serve a variable number of cylinders whose axes may or may not be parallel.

Each nozzle T is, for example, made up of tubular pieces of machined steel and the exterior and, if necessary, interior surfaces, can be provided, over all or part of their length, with a coating of ceramic or other material capable of withstand thermal and other shocks, during the phases: explosion, expansion and exhaust, in particular in the case of an internal combustion engine.

One of the ends of the nozzles T-8 and T-9 is provided with a drive and guide nozzle designated as a whole by the reference 12 (FIG. 3), while the opposite end of the said nozzle can be provided with a closing end piece 13 (FIG. 5) which may consist of a simple plate fixed in a leaktight manner, by screwing, on said end, or with a end piece 14 comprising a tubular axial extension 14a (FIG. 4) allowing , depending on the case> its connection, for example by means of a seal rotary, to a fuel mixture rear pipe or to an exhaust pipe.

Each rotary nozzle T-8 and T-9 thus produced and equipped, comprises, according to the embodiment of Figures 2 and 5, at a distance from its portions provided with the lights 10 or 11, parts of smaller diameter 15a, 15b , 15c (FIG. 2) on which the inner rings of the bearings 16a, 16b, 16c are fixed ensuring the guiding in rotation and the positioning in translation of said nozzles. The outer rings of these bearings are fixed to the housing wall described in the rest of this description and formed in the cylinder head 2. The aforementioned bearings could be replaced by rings. Each bearing 16a, 16b, 16c or outer friction ring is surrounded by two eccentric and concentric rings 17, 18 of which at least one can be driven in rotation, with however the possibility of limited angular movement. This assembly, bearing and rings, is maintained and guided, at the bearings, between two pairs of half-shells The 19. One of the half-shells The of each of these pairs of half-shells 19 is provided of a lug 19a. These lugs 19a penetrate into one of the faces of one and the other of the two eccentric rings, so that a movement movement is obtained which tends to move away or bring the rotary nozzle T-8, T- 9 of the seats 6, 7 (which are described in more detail in the remainder of the present description), by a simple rotation of these half-shells, the method of fixing on the cylinder head makes it possible to multiply the angular positions.

As a result, an ease of adjustment appears; The screws 20 fixing these half-coqui ls On the bearings being directly accessible after removal of the elements 29 and 30 closing the openings not used in the cylinder head for the entry or exit of the fluids. The axial positioning of the rotating ducts T-8, T-9 in their bearings 16a, 16b, 16c, is provided by a machined shoulder 22 on which abuts one of the side faces of ^the cage has said roύle.ments whose 'other face is blocked by the end of the following rotary cage, or by a fixed ring 23 with regard to the end bearing 16c. The role of this ring, with regard to the front bearing 16a, is held by a shoulder 24 facing inwards, which has the end piece 12. This end piece 12 has a smooth bearing surface 25 on which the inner ring of the roule¬ ment 16a and a shaft 26 on which is fixed, for example by keying, a toothed pulley 27 driven by toothed belt or a pinion driven by chain. The outer end 26a of this steel end piece can be machined or shaped (Figure 3bis) so as to be able to drive an igniter, for example of the Delco type (Registered Trademark) or another device necessary for the operation of the engine. Any engine necessarily having two rotary nozzles T-8 and T-9, one can plan to drive one or two igniters serving and supplying, by a different circuit, two spark plugs 28 per cylinder, as can be understood by considering Figures 1 and 5. These spark plugs 28 can be installed vertically or with a certain angle in the axial plane of the cylinder head, in two passages reserved therein and opening into the combustion chamber.

It is emphasized that, in the case of a diesel engine, the second perforation made in the cylinder head and ending in the combustion chamber, can be used to accommodate a glow plug or the like.

It is also observed that the nozzles 12 can be coupled to the pump drive device injection of diesel engines or be used for other functions such as, for example, controlling a direct injection device.

Access to the nozzles 12 and 13 of the nozzles is extremely easy after removing the front plates 29 or rear 30 of the cylinder head 2.

Lubrication of the guide bearings of the rotary nozzles is carried out from the lubrication network supplied by the engine oil pump located in the crankcase. Oil, through a conduit opening into the bearings, retained by the half-shells. The 19 blocking the concentric rings and the external cages of the bearings, fulfills its function and returns to the crankcase by another free conduit. and largely dimensioned.

Each rotary nozzle T-8 and T-9 driven by pulley 27 and toothed belt, or by pinion or chain, whose movement originates from the rotation of the vi lebrequin of a four-stroke engine, performs one revolution for two turns of this vi lebrequin.

Each obturator element of each of the nozzles T-8 and T-9 has a cutout or lumen 10 or 11, respectively, carefully calibrated and dimensioned and which, during the rotation of the nozzle, communicates periodically with one of the orifices 4 or 5 opening into the combustion chamber of one of the cylinders, according to the function assigned to the nozzle, this orifice being closed by the cylindrical wall of the shutter between two passages of the light. On the other hand, when the light 10 or 11 has left the position of communication with the orifice 4 or 5 for access to the combustion chamber 3, it opens into the cavity 31 or 32 surrounding the rotary nozzle T-8 or T-9, respectively. The T-8 intake and T-9 exhaust nozzles are placed in two adjacent shaped cavities cylindrical or other, formed in the cylinder head 2 and separated in a sealed manner from one another, these cavities constituting, respectively, the intake manifold 31 and the exhaust manifold 32. These intake manifolds 31 and exhaust 32 are formed by longitudinal chambers or spaces which surround The rotary inlet nozzles T-8 and exhaust T-9, respectively, over most of their periphery, these longitudinal chambers or spaces allowing circulation gases outside and along said nozzles distribu¬ trices. It is understood that, in this way, the gases can circulate freely both inside and outside the nozzles. To allow the free circulation of gases outside and along the rotary distribution nozzles, the cages 63 which ensure the positioning of the assemblies 16-17-18 constituting the bearings of said nozzles and more particularly the cages receiving the intermediate bearings between cylinders, are not waterproof, but perforated or provided with passages 62 allowing this Free movement (Figures 10 and 10a).

The lights 10, 11 of each pair of twin shutters 8, 9 of the rotary distribution nozzles T-8, T-9, have a position angularly offset relative to each other, to allow them to fulfill the function assigned to them, ie "Admission" and "Exhaust", respectively.

During the rotation of the crankshaft, the rotary nozzles T-8 and T-9 are rotated at a speed which is half that of the latter, as indicated previously, so that each of them performs a U-turn when the vi lebrequin completes a turn. You can use the rear zone of the cylinder head, after removing the rear plate 30 thereof and its traversed by perforation or replacement, then after removal of the plates 13 closing the end of the rotary nozzles T-8, T-9, to replace these plates 13 by end pieces 14 of the type shown in FIG. 4 and comprising a sleeve 14a long enough to pass through holes 56 reserved in said rear plate 30 and open out of this plate (traced in broken lines in FIG. 5), which will then receive a sealed vertical separating partition (not shown), arranged in the extension ¬ of the partition 34 placed between the cavities 31 and 32 containing the rotary nozzles T-8 and T-9, respecti¬ vely, in the outer zone of the rear bearings 16c. In this case, without looking for a seal between these added ends 14 and the rear part 30 of the cylinder head, it is possible to use the latter to receive conduits intended for supplying the engine cylinders and / or for evacuating the burnt gases. . However, preferably, the supply and exhaust ducts, communicating with the intake 31 and exhaust 32 collectors, are connected to the side walls 21 of La or the cylinder heads 2 or to the cover (s) 33 covering it or these, which may have orifices 58a, 58b, respectively, for connection to the conduits for the arrival of fresh gases or for the discharge of burnt gases (not shown). This or these covers, on the upper part, joining in the axis of the sealed central partition 34 separating the rotary nozzles T-8 and T-9, are, on the one hand, fixed on one side on this last, and for the other sides, screwed on the cylinder head (s) leaving Free The heads of the tightening bolts and the orifices for spark plugs, injectors or others.

We observe that all conducts, conveying a fluid - 1 3 -

and opening at any point in a cavity constituting an intake manifold 31 or an exhaust 32 and formed in the cylinder head 2 around one of the rotary nozzles T-8 or T-9, sees the transfer of this fluid largely facilitated by the possibility of passing from one cavity to another, through the interior of a nozzle which acts as a conduit in this case.

Considering the application of the invention to a twin-cylinder engine and referring to Example i illustrated in FIG. 5, one can understand the determining role of the internal recess of the nozzles.

While the lights 10 ′, 11 ′ of the shutters 8a, 9a, of the nozzles T-8, T-9 serving the cylinder I are in the low position, those 10 ", 11" which serve the cylinder II are in the high position, 180 degrees from the previous ones and in free communication with the surrounding cavity, whether the supply or exhaust orifices provided in the cylinder head (s) are lateral (57) or vertical (58a, 58b), or provided at the rear ( 56) of the nozzles T-8 or T-9, the free passage of the fluids around and by the interior of the latter promotes rapid flow.

In addition, it should be noted the great facilities which are offered with regard to the arrangement of the inlets or outlets of fluids. It is possible, in the case of a four-cylinder engine to have only one or multiple entry and / or exit points, since all the lateral or upper surfaces, with the exception of the positioning locations of the Front, rear and intermediate bearings between cylinders can be perforated and can be connected to the inlet or outlet of the fluids.

On the other hand, the intake system and the exhaust system are separated in leaktight manner by the central partition 34, as indicated previously.

Figures 6-6a, 7-7a, 8-8a, 9-9a, are views associated in pairs and schematic illustrating the four-stroke cycle of an engine equipped to explo¬ sion of the dispensing device according to the in- ^• vention, considering a single cylinder of said engine. First step: admission (Figures 6 and 6a)

In Figure 6, the piston P is at TDC (top dead center) at the end of its ascent stroke ending a four-stroke cycle. The lumen 11 of the rotary exhaust shutter 9 still communicates with the cylinder 1 while the lumen 10 of the intake shutter 8 enters into communication with said cylinder. In FIG. 6a, the piston P descends, the rotary exhaust shutter 9 closes the exhaust port 5, while the rotary intake shutter 8 communicates, through its lateral light 10, with cylinder 1 into which the fuel mixture is sucked.

Second step: compression (Figures 7 and 7a) In Figure 7, the piston P is at PMB (bottom dead center), the exhaust port 5 is completely closed by the rotary exhaust shutter 9, while the light 10 of the rotary inlet shutter 8 still communicates, through a passage of reduced section, with the cylinder 1. In FIG. 7a which shows the piston 1 during its ascent stroke, the exhaust orifices 5 and d admission 4 are hermetically closed by the rotary exhaust and inlet 9 intake shutters 8, respectively; the gases are compressed in the upper part of the cylinder. Third step: explosion and relaxation (figures

8 and 8a)

In FIG. 8, the piston P is again at TDC. The exhaust 5 and intake 4 orifices are always closed by the exhaust 9 and intake 8 shutters, respectively. The ignition of the compressed mixture caused before the piston P does not reach TDC causes the explosion which propels the piston P downwards (figure 8a).

Fourth step: exhaust (Figures 9 and 9a)

In FIG. 9, the piston P is again at PMB, the lumen 11 of the rotary shutter of escapement enters into communication with the orifice of escape 5 of cylinder 1, the burnt gases begin to s '' flow outward. In FIG. 9a, the piston is being raised, the light 11 communicates with the exhaust orifice 5, the burnt gases remaining in the cylinder are expelled by said piston.

When the piston reaches TDC (figure 6), the cycle is finished.

It can be seen that when the piston P of a cylinder 1 has crossed the PMB at the end of its expansion stroke and has started its ascent stroke (FIG. 9a), the rotary exhaust obturator 9 assigned to this cylinder is is in the open position and remains there until the said piston has crossed TDC (Figure 6) only then closing (delay in closing the exhaust shutter) only by the rotational movement which is transmitted to it by The toothed pulley or pinion which drives it (Figure 6a). At the same time, the lumen 10 of the rotary inlet shutter 8 communicates with the inlet port 4 (advances to the opening of the rotary inlet shutter) and remains there until the time where the piston P continuing its suction stroke (FIG. 7) has again crossed the PMB (delay in closing the rotary intake shutter) and begins its compression stroke (FIG. 7a ⁾ .

On the other hand, during the expansion phase and before the piston 1 has reached the PMB, the lumen 11 of the rotary exhaust shutter 9 comes into contact with the exhaust port 5 and allows the flow of gases burnt outwards under the effect of Them detent (advances to the opening of the exhaust shutter).

According to. another characteristic arrangement of. The invention, each inlet 4 and exhaust 5 are equipped with at least one mobi seat on 6 or 7 enabling the cross section of the fluids to be adjusted and, preferably, two seats mobi likely to be brought closer to reduce this section or distant from each other to increase it. The adjustment of the distribution device described above is obtained by means of a system for adjusting the position of the seats 6 and 7 of the rotary shutters 8 and 9, respectively, making it possible to modify the passage times of the fluids by decreasing or increasing the section of the access opening to the inlet 4 and exhaust 5 ports. It can be seen that the adjustment of the position of the seats 6 and 7 also makes it possible to adjust the moment or instant of the closing and / or opening of the intake and exhaust ports.

There is shown in Figure 1, two modes of execution of act i onment linkages of this adjustment device.

On the left side of the figure, there is a first embodiment according to which the mobi seats 7 are connected to control levers 35 which can be actuated remotely, from outside the cylinder head.

On the right side, there is shown an adjustment device according to which all the functions for modifying the position of the movable seats are contained and actuated inside the cylinder head, in the volume existing between the latter and the rotary nozzle T- 8 or T-9 and constituting the intake manifold 31 or exhaust manifold 32.

The operating command allowing to modify, during operation, the position of the movable seats can be obtained by means of the adjustment device described below and shown in FIG. 11.

This device, which is very simple in design, consists of a cylinder 36 in machined metal, fixed through the sealed transverse wall 34 separating the intake 31 and exhaust 32 collectors. The cylinder 36 comprises, for example in its intermediate part, a flange 37 provided with holes and allowing its fixing, by means of screws 38, on said wall. To reduce the thermal influence on the device, the part of the cylinder located in the exhaust manifold 32 is preferably as small as possible. The bottom of the cylinder, "Exhaust" side, is closed by a plug 50 removably fixed on the end of the cylinder, for example by screwing, this plug having a hole 39 allowing the passage and the movement of a control rod. 40a connected: - on the one hand, via one of its ends and by means of an articulation, for example a spherical articulation 41, to a piston 42 housed with a sliding ability in said cylinder , and, - on the other hand, by means of its second end and by means of a simple pinned pin 43, to a rod 44 rigidly fixed on a shaft 45.

In case of use with a turbo compressor, the passage 39 traversed by the rod 40a will be provided with an O-ring, since, in this case, the depressive effect will be canceled.

The opposite bottom of the cylinder has an internal shoulder 46 against which is wedged One of the ends of a compression spring 47 the other end of which rests against the piston 42, this spring having the function of pushing said piston in direction of the exhaust manifold 32, when the pressures or depressions decrease or cease.

The characteristics of this spring (diameter, diameter of the wire, and not the number of ^'turns, length, material) are determined depending on the desired uti lisation and mid location wherein it travai lle.

The compression of this spring can be modified by the simple addition of one or more round l Les-ca placed in the bottom of the cylinder, against the shoulder 46. On the other hand, the end of the spring oriented towards the inside the cylinder 36 is housed in a groove created in the bottom of the piston which also has a guide portion 42a of reduced diameter, oriented towards the shoulder 46 and opposing the possible buckling of said spring. The plug 50 makes it possible to avoid excessive displacement of the piston 42 under the effect of the spring 47. It also protects the piston from heat, while its central hole 39 allows both the movement of the rod 40a and the passage of the gas acting on the bottom of said piston.

In addition, the piston is provided, for example in the vicinity of each of its ends, with a sealing segment 48 executed in nitrided cast iron or other material.

It is observed that the absolute seal has no reason to exist and that an expansion clearance between cylinder 36 and piston 42 must be provided at the start to take account of the thermal influence, in particular on the "Exhaust" side. , during prolonged operation. Preferably, the piston 42 also includes a peripheral recess 49 provided between the grooves of the sealing segments 48, this recess being intended to be filled with a THT grease, during assembly or possibly subsequently, by means of a grease nipple (not shown ) opening into the cylinder 36. The face of the piston 42 oriented in the direction of the intake manifold 31 is preferably also subject, by means of a joint and, for example, by means of a spherical joint, to a rod 40b, comparable to La rod 40a, and itself connected to a link-shaft-link-assembly similar to that previously described. The rods 40a and 40b can have an adjustable length and be arranged in any manner known per se to present this characteristic.

As indicated previously, in the assemblies according to which one of the extreme portions of the piston 42-cylinder assembly 36 is called to be exposed to a significant heat, the major part of this assembly will be positioned on the "Admission" side where the conditions are different and extremely lower.

We understand that the depression created at a point in the "Admission" phase, combined with the pressure generated during the evacuation of gases during the "Exhaust" phase in an internal combustion engine, acting on both sides on the faces opposite piston 42, causes a translational movement of this piston which thanks to the two rods mobi 40a, 40b connected, by means of articulations, on the one hand, for each of them, to the piston and on the other hand, to a link 44 fixed on the shaft 45 causes a slight rotational movement of said shaft. On the shaft 45, are also attached transmission rods 59 connected to the operating linkages of the mobi seats 6 and 7 of the rotary shutters 8 and 9 of the distribution nozzles T-8, T-9. It is understood that one can fix as many rods 59 as necessary in different desirable locations of the shaft 45. It is observed that the rods 44 and / or 59 can be of different lengths and placed in function needs and in various positions, on the shaft 45, according to the amplitude of the movement that one wishes them to transmit, it being understood that one can, if necessary: - increase the capacity of the cylinder assembly 36 piston 42, developing its diameter;

- extend the main link (s) connected to the tree (s) to be served;

- increase the number of cylinder 36-piston 42 assemblies or combine the assemblies previously described.

The shaft 45 is connected to the mobi seats 6 and 7 of the shutters 8 and 9, respectively, by means of the rods 59 and of a rod 60, to the transmission linkages 51 acting directly on the said shutters and one mode of which is The execution is visible on the right part of Figure 1.

Four in number per cylinder, each of the mobi seats 6 or 7 placed in the part of the cylinder head 2 provided with an inlet 4 or discharge 5 for fluids, is housed in a location machined directly in said cylinder head. These seats 6, 7 have a curved shape, as can be seen in particular in FIGS. 1, 12 and 13.

The shape of this machining contributes to creating a regular space between the rotary nozzle T-8 or T-9 and the movable seats, respectively 6 or 7, whatever its position. The movement of the latter, under the action of the rods which control their movement, between the cylinder head block and the rotary nozzle to which they are assigned, is thus perfectly controlled. Each end of a movable seat is limited in its lateral displacement, by a lateral flange 52 which also serves to improve the seal between the movable seat 6 or 7 and the rotary nozzle T-8 or T-9. In addition, the lateral flanges 52 have, on their internal face, a curved groove 53 in which is engaged a lug 54 which laterally comprises the seat mobi 6 or 7 and which limits the movement of said seat.

It is observed that the ceramic layer reinforced with the nozzles T-8 and T-9 only touches a tiny part of the movable seats 6 or 7 whose length, width and thickness are determined according to the diameter of the cylinder served .

The seats 6 or 7 being subjected to thermal and other shocks and to chemical aggressions, are also treated to be able to resist these harmful actions by using, either, preferably, ceramics armed with suitable mixtures, or high-strength steels combined with special products. The seats 6 or 7, of curved shape as indicated above, are extended, opposite their free edge, by spaced rods 55, also curved and arranged at equal distance from the lateral edges of said seats, these rods comprising a head 55a by means of which they are connected, by means of an articulation, to the linkage 51 (right side of FIG. 1) or to the control levers 35 (left side of FIG. 1), according to the command option adopted to obtain the displacement of the movable seat elements 6 or 7.

The invention provides a significant improvement over traditional valve distribution systems, because it allows the elimination of the latter and all of their springs or other return systems, which allows to consider a significant increase in rotational speed of the motors and their efficiency.

We can see the great simplicity and efficiency of the rotary distribution system resulting from the provision, preferably in the cylinder head 2, of two cylindrical cavities, sealed together, but common to all the cylinders to be served.

One of these cavities forming the common manifold 31 for the admission of air, fueled or not, or gasified, necessary for the proper functioning of the engine, contains the rotary assembly T-8 and its seats 6, 7 mobile or not , replacing the intake valves and all their operating devices.

This cavity, by its shape and by its volume clearly greater than that necessary for the proper functioning of the complete rotary assembly and its seats as well as all the organs influencing the position modification of these, ensures Free Transfer gases from any point to another inside this cavity, around the rotary assembly and in the midst of the ancillary members allowing and facilitating the path of the gases towards the cylinder or cylinders also supplied by the inside of the rotary assembly. It can be perforated as required in multiple places and connected at one or more points with the external air or gas mixture inlets necessary for the proper functioning of the engine. The other cavity, forming a common collector 32 for the outlet of the burnt gases, contains the rotary assembly T-9 and its seats 6, 7 movable or not, replacing the exhaust valves and all the operating devices of the latter. . This cavity 32, the shape and volume of which can be totally different from that of the cavity 31, must very easily contain the rotary assembly, the movable seats or not, as well as all the organs influencing the position modification of these last ; it ensures the free transfer of burnt gases, from any point to another, inside of this cavity, around the rotary assembly and in the midst of the ancillary members, allowing and facilitating the path of the burnt gases from the cylinders to the outside, very significantly improving their evacuation, also being done from the inside of the rotary assembly.

It can also be perforated as required in multiple locations and connected at one or more points with one or more gas discharge conduits.

In the application to air-cooled engines, the implementation of the invention does not require any substantial modifications. The external parts of the cylinder head (s) may, however, in this case be provided with blades of appropriate shapes and dimensions to remove the excess calories and ensure good cooling of the cylinder head (s) of this type of engine. In the event of use of the engine at low temperature, or even at negative temperature, whatever the cooling system used, it is observed that the pre-heating of the intake fluids is ensured, as soon as it is put into operation. of the engine, by the heat input transmitted by the middle partition of the exhaust zone to the intake zone, which prevents icing in the latter.

This central partition is used, furthermore, in the other direction, for a transfer of appreciable frigories, thus allowing cooling of the burnt gases. These intakes of calories or frigories can be increased, according to the needs, either by the provision of wings judiciously placed, or by a reduction of the thickness of this partition, or still by its partial replacement by a part of exchange made of a metal with a higher coefficient of heat conductivity.

Claims

1. - Internal combustion engine mu Iti cy Li ndre. comprising at least one group of cylinders (1), the combustion chambers (3) of which are each provided with an intake orifice (4) and an exhaust orifice (5), the intake orifices (4), on the one hand, and the exhaust orifices (5) on the other hand, of said group of cylinders (1) being arranged in alignments, the distribution means allowing the opening and closing of said orifices intake (4) and exhaust (5) comprising two rotary nozzles (T-8, T-9), of circular section, each formed of a plurality of aligned hollow shutters (8a, 8b) following the others and communicating with each other, and the side wall of which is provided with a plurality of lights (10a, 10b, 10c, 10d; 11a, 11b, 11c, 11d) the number of which corresponds to that of the cylinders to be served or to be served, one (T-8) of these rotary nozzles allowing the opening and closing of the aligned intake orifices (4) of the group of cylinders (1), while the second (T9) allows the opening and closing of the aligned exhaust ports (5) of said group of cylinders; characterized in that the rotary intake nozzle (T-8) and the rotary exhaust nozzle (T-9) are housed, the first, in an intake manifold

(31) and, the second, in an exhaust manifold

(32) each delimiting a space or chamber surrounding, respectively, Ladi te inlet nozzle (T-8) and said exhaust nozzle (T-9), over a large portion of their periphery, these rooms ( 31, 32) being sealed and arranged so as to allow free circulation of gaseous fluids outside and along said rotary distribution nozzles (T-8, T-9).

2. - internal combustion engine mu It i cy li ndre, according to claim 1, characterized in that the intake (31) and exhaust (32) manifolds consist of cavities formed in the cylinder head (2) of said motor.

3. - internal combustion engine mu It i cy li ndre, according to one of claims 1 or 2, characterized in that the rotary intake (T-8) and exhaust (T-9) nozzles are mounted rotating in bearings or rings (16a, 16b, 16c), The cages (63) supporting these bearings or rings being provided with passages or openings (62) allowing a free circulation of gases from one end to the other of the manifolds d intake (31) and exhaust (32).

4. - Internal combustion engine according to one of claims 1 or 2, characterized in that each inlet (4) and / or exhaust (5) is equipped with at least one movable seat (6 , 7) making it possible to modify the passage section of the fluids, and the moment or instant of the closing or of the opening of said orifice, these movable seats (6, 7) being housed inside the cavities constituting the collectors of intake (31) and exhaust (32).

5. - internal combustion engine according to claim 4, characterized in that each inlet (4) and / or exhaust (5) is provided with two movable seats (6, 7) mounted with an ability to movement of bringing together or widening, these movable seats (6, 7) being housed inside the ca ities constituting the intake (31) and exhaust (32) manifolds.

6. - Internal combustion engine according to any one of claims 1 or 2, characterized in that one of the ends of the rotary shutters (8, T-8; 9, T-9) is provided with a drive end piece (12) and in that the end portion (26a) of this end piece is arranged or shaped to ensure L drive of a device necessary for engine operation.

7. - Internal combustion engine according to one of claims 1 or 2, characterized in that one of the ends of the rotary shutters (8, T-8; 9, T-9) is provided with a nozzle (14 ) comprising an axial tubular extension (14a) for connection to a fuel mixture inlet pipe or to an exhaust pipe.

8. - Internal combustion engine according to any one of claims 1 to 3, whose rotary shutters (8, T-8; 9, T-9) are guided in rotation by means of bearings or rings (16a, 16b , 16c), characterized in that these bearings or rings are surrounded by two eccentric and concentric rings (17, 18), at least one of which can be driven in a rotation movement of limited amplitude.

9. - internal combustion engine according to one of claims 4 or 5, characterized in that the seats (6, 7) of the rotary shutters (8, T-8; 9, T-9) have a curved shape and are guided in Les lateral flanges (52).

10. - Internal combustion engine according to any one of claims 4, 5 or 9, characterized in that it comprises means for adjusting the position of the movable seats (6, 7) of the rotary shutters (8, T-8; 9, T-9).

11. - Internal combustion engine according to La claim 10, characterized in that the device for adjusting the position of the movable seats (6, 7) of the rotary shutters (8, 9) comprises a cylinder _. (3.6) installed, in a sealed manner, through the sealed wall (34) separating the intake (31) and exhaust (32) manifolds, and in which is housed a piston (42) subjected to the action of '' a compression spring (47) tending to push it in the direction of the exhaust manifold (32), at least one of the faces of this piston (42) being connected by means of a joint (41) to a control rod (40a, 40b) itself connected to a rod (44) wedged on a shaft (45) on which are also wedged rods (59) connected, each, by means of a transmission linkage ⁽ 51), to at least one of the movable seats (6, 7) of at least one of the rotary shutters (8, T-8; 9, T-9).

12. - Internal combustion engine according to claim 11, characterized in that each of the opposite faces of the piston (42) is connected, by means of a rod (40a, 40b), and by means of a transmission ( 44, 45, 59) and a linkage (51) to at least one of the seats (7, 8) of each rotary shutter (8, T-8; 9, T-9).