EP0750719B1 - Internal combustion engine having rotary distribution valves - Google Patents

Description

The present invention relates to a motor with internal combustion, with distribution shutters rotary.

We have already sought to overcome the disadvantages of conventional valve distribution systems, in offering shutter distribution devices rotary.

We know, for example, by the document US-A-2,730,088, an internal combustion engine multicylinder including a group of cylinders in line of which the combustion chambers communicate, each, with an intake port and with an orifice on the one hand, and the exhaust ports, on the other hand, of said group cylinders being arranged in alignments, the means for opening and closing said intake and exhaust ports comprising two rotary nozzles, of section circular, each comprising a plurality aligned hollow shutters, rigidly connected to each other to others and communicating with each other, and whose wall side is provided with a plurality of lights spaced, 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 the intake port alignment of the group of cylinders, while the second allows opening and closing the alignment of holes exhaust of said group of cylinders.

Each rotary nozzle consists of portions cylindrical cylinders of different diameters, gas passage lights being provided in the reduced diameter portions. Each rotary nozzle of distribution is housed in a fixed sleeve and its larger diameter portions are sized to have a good rotation and sliding play fitted inside said fixed sheath, these portions being larger provided, in the vicinity of their ends, sealing rings to establish a gas tight seal.

The device described in the document US-A-2,730,088 has an important drawback which follows from the fact that the gas circulation takes place exclusively inside the dispensing rods intake and exhaust rotary.

It follows, in the case of admission, that the first cylinder is preferably supplied, then the second, then the third, etc.

These cylinders are therefore successively supplied, very unevenly, both in volume and gas mixture quality, so that we have a poor engine balance.

In the same way, the evacuation of the burnt gases takes place made only from inside the rotating rod exhaust, successively for each of cylinders, so that the gases escape also very irregularly depending on whether the cylinders are more or less distant from the exit of said rod.

Another drawback of the device described in the above-mentioned document, resides in the fact that has to place the carburetor or the exhaust at one end of the rods tubular rotary distributors, which constitutes a constraint when the engine must register in reduced volume.

An object of the present invention is to remedy to the drawbacks outlined above of multi-cylinder internal combustion, with rotary distribution, of the kind described previously.

According to the invention, this objective is achieved thanks to an engine according to claim 1.

Thanks to the above characteristic arrangements, gas circulation takes place at the same time, by inside and outside the nozzles of rotary distribution, in the space between these last and the internal surface of said collectors, in which the gas stream swirls (fuel and / or oxidizer), so that, in the case of power, all cylinders are powered substantially under the same conditions, both in volume as in the quality of the gas mixture, so that better combustion and better engine balance.

Similarly, the evacuation of gases which takes place at the both inside and outside the nozzle rotary exhaust, is greatly improved.

In addition, thanks to these characteristic provisions, it is possible to place the carburetors, or other power devices (injectors, etc.) and exhaust, in different cylinder head locations, which constitutes a very significant advantage when the engines have to be housed in reduced volumes.

According to a preferential provision of the invention, each intake port and exhaust is fitted with at least one movable seat allowing to modify the passage section of fluids, as well as when or when to close or the opening of said orifice, and means for adjustment allow to adjust the position of these seats mobile, these means comprising an installed cylinder, sealingly, through the sealing wall separating intake and exhaust manifolds, and in which is housed a piston subjected to the action of a compression spring tending to push it back into the direction of the exhaust manifold, one side at least this piston being connected, by means of a articulation, to a control rod itself connected to a rod wedged on a tree on which are also fixed rods connected, each, by through a transmission linkage to one at least mobile seats of at least one of rotary shutters.

The above goals, features and benefits, and others will emerge better from the description which follows and attached drawings in which :

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

Figure 2 is a perspective view of a example of realization of a distributor nozzle rotary consisting of two shutters arranged in the extension of each other.

Figure 2bis represents, by two half-sections axial, two other examples of conformation of a rotary distributor nozzle consisting of two shutters assembled in the extension of each other.

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

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

Figure 4 is an axial sectional view of a mode of the opposite end of the nozzle.

Figure 5 is a plan view in section of a distribution assembly according to the invention.

Figures 6 to 9a illustrate the operation of the distribution system according to the invention.

FIG. 10 is a schematic view, in plan and in section, of an exemplary embodiment of rotary intake and exhaust nozzles fitted the top of a four-cylinder engine.

Figure 10a is a character view schematic and on a larger scale along the line 10 - 10 in Figure 10.

Figure 11 is a perspective view and section showing a system control device for adjusting the movable seats of the rotary shutters.

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

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

Figure 14 is a front view of a flange lateral guide for mobile seats.

Reference is made to said drawings to describe a advantageous example of implementation, although by no means limiting, of the internal combustion engine according to the invention and, more particularly of the device distribution fitted to this engine.

Figure 1 shows the top of a cylinder 1 and a cylinder head 2 attached to the part upper part of this cylinder and delimiting the combustion or explosion 3. In the cylinder head 2, by example made of special aluminum and with a suitable conformation, the holes are provided intake 4 and exhaust 5 themselves fitted with seats 6, 7, respectively, shutters.

The shutters are made up of elements rotary 8, 9, hollow, of circular section, in the side wall of which a light 10, 11 is formed, respectively, for each engine cylinder to be served or to serve. These shutters may have a shape cylindrical, or conical, or ovoid, even spherical.

Depending on the number of cylinders to be served or serve, two or more than two rotary shutters 8, 9 are assembled in succession and in alignment, by example by screwing or otherwise.

Figure 2 illustrates two rotary shutters cylindrical 8a, 8b assembled one after the other and intended to equip a twin-cylinder engine. The T sets thus produced will be referred to as of "rotary nozzles" in the following description, in order to facilitate description.

Figure 2bis shows two other examples of conformation of rotary distributor nozzle T consisting of two shutters 8 or 8 'assembled in the extension of each other, with an ability to sliding amplitude limited one compared to the other, by means of simple grooves 61, which solves problems that might result from the effects of dilation or a slight misalignment. In addition, in this figure, the shutters 8 of the lower half-section present a concave conformation, while the shutters 8 ' of the upper half cup have a shape bulging in their central part, such a shape increasing the capacity for introducing fresh gases in the cylinders.

As stated earlier, the number shutters 8 or 9 constituting each nozzle T-8 intake and each T-9 exhaust nozzle is depending on the number of engine cylinders. So the Figure 10 shows T-8 rotary intake nozzles and exhaust T-9 each consisting of a 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.

Shutters such as 8a, 8b, 8c, 8d, ...., thus aligned and united to each other in rotation, constitute a tubular assembly according to which said shutters are in communication permanent by their bore.

It is understood that the rotary nozzles T-8 and T-9 can be arranged and sized to serve 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 parts in machined steel and the surfaces of which exterior and, if necessary, interior, can be provided, over all or part of their length, with a ceramic or other material coating capable of withstand thermal and other shocks during phases: explosion, detent and exhaust, in particular in the case of an internal combustion engine.

One end of the T-8 and T-9 nozzles is equipped with a designated drive and guide tip as a whole by the reference 12 (FIG. 3), while the opposite end of said nozzle can be provided with a closing end piece 13 (FIG. 5) which can consist of a simple fixed plate, sealingly, by screwing, on said end, or a tip 14 having an axial extension tubular 14a (Figure 4) allowing, as appropriate, its connection, for example by means of a joint rotary, to a fuel mixture inlet pipe or to an exhaust pipe.

Each T-8 and T-9 rotary nozzle thus produced and equipped, includes, depending on the mode of execution of Figures 2 and 5, at a distance from its portions provided with lights 10 or 11, parts of smaller diameter 15a, 15b, 15c (Figure 2) on which are fixed the inner rings of bearings 16a, 16b, 16c guiding in rotation and positioning in translation of said nozzles. The outer rings of these bearings are fixed to the housing wall described in the following of this presentation and arranged in cylinder head 2. The aforementioned bearings could be replaced by rings.

Each bearing 16a, 16b, 16c or friction ring outer is surrounded by two eccentric rings and concentric 17, 18 at least one of which can be driven in rotation, with however a possibility limited angular movement. This set, bearing and rings, is maintained and guided, at the level of bearings, between two pairs of half-shells 19. One half-shells from each of these pairs of half-shells 19 is provided with a lug 19a. These pins 19a penetrate one of the faces of one and the other of the two eccentric rings, so that we obtain a movement of movement tending to move away or move the rotary nozzle T-8, T-9 closer to the seats 6, 7 (which are described in more detail below present presentation), by a simple rotation of these half-shells whose method of attachment to the cylinder head allows to multiply the angular positions.

As a result, ease of adjustment appears; the screw 20 fixing these half-shells 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 fluids.

The axial positioning of the T-8 rotary nozzles, T-9 in their bearings 16a, 16b, 16c, is provided by a machined shoulder 22 on which one of the lateral faces of the cage of said bearings of which the other side is blocked by the end of the cage following rotary, or by a fixed ring 23 in what concerns the extreme 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 surface 25 on which the inner race of the bearing is mounted 16a and a shaft 26 on which is fixed, by example by keying, a toothed pulley 27 driven by toothed belt or a sprocket driven by chain.

The outer end 26a of this steel end-piece can be machined or shaped (Figure 3bis) so to be able to drive an igniter, for example of the type Delco (Trademark) or other necessary device during engine operation.

Any engine necessarily having two nozzles rotary T-8 and T-9, we can plan to train one or two ignitors serving and supplying, by a circuit different, two candles 28 per cylinder, as we can understand it by considering Figures 1 and 5. These candles 28 can be installed vertically or with a certain angle in the axial plane of the cylinder head, in two passages reserved in the latter and opening into the combustion chamber.

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

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

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

Greasing the nozzle guide bearings rotary is carried out from the lubrication network powered by the engine oil pump located in the Crankcase. Oil, through a through pipe in the bearings, retained by the half-shells 19 blocking concentric rings and outer cages bearings, fulfills its office and returns in the crankcase by another free duct and largely dimensioned.

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

Each obturator element of each of the nozzles T-8 and T-9 presents a cutout or light 10 or 11, respectively, carefully calibrated and sized and which, during the rotation of the nozzle, communicates periodically with one of the openings 4 or 5 opening in the combustion chamber of one of the cylinders, depending on the function assigned to the nozzle, this orifice being closed by the cylindrical wall of the shutter between two light passages.

On the other hand, when light 10 or 11 has left the communication position with port 4 or 5 access to the combustion chamber 3, it opens in the cavity 31 or 32 surrounding the rotary nozzle T-8 or T-9, respectively.

T-8 intake and T-9 exhaust nozzles are placed in two neighboring shaped cavities cylindrical or others, formed in the cylinder head 2 and tightly separated from each other, these cavities constituting, respectively, the collector intake 31 and exhaust manifold 32.

These intake manifolds 31 and exhaust manifolds 32 consist of longitudinal chambers or spaces surrounding the rotary intake nozzles T-8 and T-9 exhaust, respectively, on the most much of their periphery, these rooms or longitudinal spaces allowing gas circulation outside and along said distributor nozzles. It is understood that, in this way, the gases can move freely both inside and outside outside the nozzles. To allow free movement gases outside and along the nozzles distribution presses, the cages 63 which ensure the positioning of the sets 16-17-18 constituting the bearings of said nozzles and more particularly the cages receiving intermediate bearings between cylinders, are not waterproof, but perforated or provided with passages 62 authorizing this free circulation (Figures 10 and 10a).

The lights 10, 11 of each pair of shutters 8, 9 of the T-8 rotary distribution nozzles, T-9, have a position angularly offset one by report to each other, to allow them to complete the function assigned to them, ie "Admission" and "Escape", respectively.

When the crankshaft rotates, the nozzles rotary T-8 and T-9 are rotated at one speed which is half that of the latter like indicated above, so that each of them makes a U-turn when the crankshaft completes a lap.

We can use the rear zone of the cylinder head, after removal of the rear plate 30 thereof and its crossed 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 caps 14 like the one illustrated in FIG. 4 and comprising a sleeve 14a long enough to pass through 56 reserved holes in said rear plate 30 and lead out of this plate (drawn in broken lines in the figure 5), which will then receive a vertical dividing wall waterproof (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, respectively, in the outer area of the rear bearings 16c.

We can, in this case, without looking for a sealing between these added ends 14 and the part rear 30 of the cylinder head, use the latter to receive conduits for supplying engine cylinders and / or a flue gas outlet.

However, preferably, the conduits supply and evacuation, communicating with 31 and 32 exhaust manifolds are connected to the side walls 21 of the one or more cylinder heads 2 or on the cover (s) 33 this or these, which may present ports 58a, 58b, respectively, for connection to fresh gas inlet or outlet pipes burnt gases (not shown). This or these covers, on the upper part, joining in the axis of the waterproof central partition 34 separating the rotary nozzles T-8 and T-9, on the one hand, are fixed on one side on the latter, and for the other sides, screwed onto the or the cylinder heads leaving the heads of the tightening bolts and spark plug holes, injectors or others.

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

Considering the application of the invention to a twin cylinder engine and referring to the example illustrated in figure 5, we can understand the role determinant of the internal recess of the nozzles.

While the 10 ', 11' shutter lights 8a, 9a, nozzles T-8, T-9 serving the cylinder I are in the lower position, those 10 ", 11" which serve cylinder II are in the high position, at 180 degrees from the previous ones and in free communication with the surrounding cavity, that the supply ports or exhaust formed in the cylinder head (s) are lateral (57) or vertical (58a, 58b), or arranged at the rear (56) of the T-8 or T-9 nozzles, the free flow of fluids around and inside the latter promotes rapid flow.

In addition, note the great facilities which are offered for the layout of the entrances or fluids outlets. In the case of a motor with four cylinders have only one or multiple entry and / or exit points, because all lateral or upper surfaces, except for positioning locations of the front bearings, rear and intermediate between cylinders can be openwork and connectable on arrival or discharge fluids.

However, the intake system and the system are separated in a 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 of a schematic nature illustrating the four-stroke cycle of an internal combustion engine equipped with the dispensing device according to the invention, 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. Light 11 of the rotary exhaust shutter 9 still communicates with cylinder 1 while light 10 of the intake shutter 8 communicates with said cylinder. In FIG. 6a, the piston P descends, the rotary exhaust shutter 9 closes the orifice exhaust 5, while the rotary shutter 8 communicates through its lateral light 10, with cylinder 1 in which is sucked the fuel mixture.

Second step: compression (Figures 7 and 7a)

In Figure 7, the piston P is at PMB (point dead down), the exhaust port 5 is completely closed by the rotary exhaust shutter 9, while as the light 10 of the rotary intake shutter 8 communicates again, by a passage of reduced section, with cylinder 1. In Figure 7a which shows the piston 1 during its ascent stroke, the orifices exhaust 5 and intake 4 are hermetically sealed closed by the rotary exhaust shutters 9 and intake 8, respectively; 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 the TDC, the exhaust 5 and intake 4 ports are always closed by the exhaust valves 9 and intake 8, respectively. Inflammation of the compressed mixture caused before the piston P does not reach TDC leads to the explosion which propels the piston P down (Figure 8a).

Fourth step: exhaust (Figures 9 and 9a)

In FIG. 9, the piston P is again at the PMB, light 11 of the rotary exhaust shutter comes into communication with the exhaust port 5 of cylinder 1, the burnt gases begin to flow outward. In Figure 9a, the piston is being raised, light 11 communicates with the exhaust port 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 crossed the PMB at the end of its detente and started its ascent stroke (figure 9a), the shutter exhaust rotary 9 assigned to this cylinder is found in the open position and the rest until said piston has crossed the TDC (Figure 6) does not then closing (delay in closing the shutter only by the rotational movement which is transmitted via the toothed pulley or the pinion which drives it (Figure 6a). In the same time the light of the rotary shutter 10 8 enters communication with the orifice intake 4 (advance to shutter opening intake) and the rest until the piston P continuing its suction stroke (figure 7) crossed the PMB again (delay in closing the rotary intake shutter) and begins its stroke compression (Figure 7a).

On the other hand, during the relaxation phase and before that the piston 1 has reached the PMB, the light 11 of the rotary exhaust shutter 9 comes into contact with the exhaust port 5 and allows the flow gases burnt to the outside under the effect of their trigger (advance to the shutter opening exhaust).

According to another characteristic arrangement of the invention, each inlet 4 and exhaust port 5 is equipped with at least one mobile seat 6 or 7 for adjusting the fluid passage section and preferably two movable seats capable of to be reconciled to decrease this section or distant from each other to increase it. The adjustment of the dispensing device previously described, is obtained by means of an adjustment system the position of seats 6 and 7 of the rotary shutters 8 and 9, respectively, to modify the fluid passage time by decreasing or increasing the section of the access opening to 4 and 5 intake ports. that adjusting the position of seats 6 and 7 allows also to adjust the moment or instant of the closing and / or opening the intake ports and exhaust.

There are shown in Figure 1 two modes execution of the actuation linkages of this adjustment device.

On the left side of the figure, we see a first embodiment according to which the seats mobiles 7 are connected to control levers 35 can be operated remotely, from the outside of the cylinder head.

On the right side, there is a device for setting according to which all the functions of changing 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 manifold intake 31 or exhaust 32.

The operating command allowing to modify, during movement, the position of the movable seats may be obtained thanks to the adjustment device described below and shown in Figure 11.

This very simple design device is consists of a cylinder 36 in machined metal, fixed through the sealed transverse wall 34 separating the collectors intake 31 and exhaust 32. The cylinder 36 includes, for example in its intermediate part, a flange 37 provided with holes and allowing its fixing, by means of screws 38, to said wall. For reduce the thermal influence on the device, the part of the cylinder located in the exhaust manifold 32 is preferably also reduced as possible.

• d'une part, par l'intermédiaire de l'une de ses extrémités et au moyen d'une articulation, par exemple d'une articulation sphérique 41, à un piston 42 logé avec une aptitude de coulissement dans ledit cylindre, et,
• d'autre part, par l'intermédiaire de sa seconde extrémité et au moyen d'un simple axe goupillé 43, à une biellette 44 rigidement fixée sur un arbre 45.

The bottom of the cylinder, on the "Exhaust" side, is closed by a plug 50 removably attached to the end of the cylinder, for example by screwing, this plug having a hole 39 allowing the passage and movement of a control rod. 40a linked:

• on the one hand, by means of one of its ends and by means of a joint, for example a spherical joint 41, to a piston 42 housed with a sliding capacity 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 link 44 rigidly fixed on a shaft 45.

When used with a turbo compressor, the passage 39 crossed by the rod 40a will be provided with a O-ring, since in this case the depressive effect will be canceled.

The opposite bottom of the cylinder has a shoulder interior 46 against which one of the ends is wedged a compression spring 47 of which the other end bears against piston 42, this spring having the function of pushing said piston back direction of the exhaust manifold 32, when the pressures or depressions decrease or stop.

The characteristics of this spring (diameter, wire diameter, pitch and number of turns, length, material) are determined according to the use sought and the environment in which he works.

The compression of this spring can be changed by the simple addition of one or more shim washers placed in the bottom of the cylinder, against the shoulder 46. On the other hand, the end of the spring facing inward of 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 displacement excessive piston 42 under the effect of spring 47. It also protects the piston from heat, while its central hole 39 allows both the travel of the rod 40a and the passage of the gases acting on the bottom of said piston.

In addition, the piston is provided, for example at neighborhood of each of its ends, of a segment seal 48 made of nitrided or other cast iron material.

We observe that the absolute seal has no reason to exist and that a set of expansion between cylinder 36 and piston 42 must be provided at the start for take into account the thermal influence, in particular the "Exhaust" side, during prolonged operation.

Preferably, the piston 42 also includes a peripheral recess 49 provided between the grooves of sealing segments 48, this recess being intended to be filled with T.H.T.grease, during assembly or possibly later, thanks to a greaser (not shown) opening into the cylinder 36.

The face of the piston 42 oriented towards the intake manifold 31 is preferably also subject, by means of a joint and, for example, by means of a ball joint, a rod 40b, comparable to the rod 40a, and itself connected to a rod-shaft-rod-similar assembly to that previously described. Rods 40a and 40b may have an adjustable length and be arranged in any manner known per se to present this characteristic.

As previously indicated, in the montages that one of the extreme portions of the piston 42-cylinder 36 assembly is called to be exposed to significant heat, most of this set will be positioned on the "Admission" side where the temperature 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 phase "Exhaust" in an internal combustion engine, acting from on either side on the opposite faces of the piston 42, causes a translational movement of this piston which thanks to the two movable rods 40a, 40b connected, by means of articulations, on the one hand, for each of them, at piston and on the other hand, to a rod 44 fixed on the shaft 45 causes a slight rotational movement of said tree. On the tree 45, are also wedged transmission rods 59 connected to the linkages for operating the movable seats 6 and 7 of the shutters rotary 8 and 9 of the distribution nozzles T-8, T-9. We understand that we can fix as many rods 59 that this is necessary in different places desirable from tree 45.

• augmenter la capacité de l'ensemble cylindre 36-piston 42, en développant son diamètre ;
• allonger la ou les biellettes principales reliées à ou aux arbres à desservir ;
• augmenter le nombre d'ensembles cylindre 36-piston 42 ou conjuguer les montages précédemment décrits.

It is observed that the rods 44 and / or 59 may be of different lengths and placed as required and in various positions, on the shaft 45, depending on the amplitude of the movement which it is desired to make them transmit, it being understood that we can, if necessary:

• increase the capacity of the cylinder 36-piston 42 assembly, by 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 movable seats 6 and 7 of the shutters 8 and 9, respectively, via rods 59 and a rod 60, to the linkages of transmission 51 acting directly on said shutters and an embodiment of which is visible on the right part of figure 1.

Four in number per cylinder, each of movable seats 6 or 7 placed in the part of the cylinder head 2 provided with an inlet port 4 or evacuation 5 of fluids, is housed in a location machined directly into said cylinder head. These seats 6, 7 have a curved shape, as seen especially in Figures 1, 12 and 13.

The shape of this machining contributes to create a space regular between the T-8 or T-9 rotary nozzle and the mobile seats, respectively 6 or 7, whatever his position. The displacement of these, under the action of the rods which control their movement, between the cylinder head and the rotary nozzle at which they are affected, is thus perfectly controlled.

Each end of a mobile seat is limited in its lateral displacement, by a lateral flange 52 which also serves to improve the seal between the mobile seat 6 or 7 and the rotary nozzle T-8 or T-9. In addition, the lateral flanges 52 comprise, on their internal face, a curved groove 53 in which is engaged a lug 54 which laterally comprises the mobile seat 6 or 7 and which limits the displacement of said seat.

We observe that the ceramic layer reinforced with T-8 and T-9 nozzles just a tiny touch part of the mobile seats 6 or 7 whose length, width and thickness are determined according to the diameter of the cylinder served.

Seats 6 or 7 being subjected to shocks thermal and other and to chemical attack, are also treated to be able to withstand these harmful actions using either, preferably, ceramics armed with appropriate mixtures, i.e. high strength steels combined with special products.

Seats 6 or 7, curved as shown previously, are extended, opposite their edge free, by spaced rods 55, also curved and arranged equidistant from the side edges said seats, these rods comprising a head 55a by through which they are connected, to by means of a joint, at the linkage 51 (side right of figure 1) or to the control levers 35 (left side of figure 1), depending on the option of command adopted to obtain the displacement of mobile seat elements 6 or 7.

The invention provides a significant improvement, compared to traditional distribution systems valves, because it allows the removal of these last and all of their springs or other reminder systems, which makes it possible to envisage a significant increase in the speed of rotation of engines and their performance.

We understand the great simplicity and efficiency of rotary distribution system resulting from the provision, preferably in 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 collector 31 for the admission of fuel air or not, or carbonated, necessary for the proper functioning of the engine, contains the T-8 rotary assembly and its seats 6, 7 movable or not, replacing the intake valves and all the operating devices of these past.

This cavity, by its shape and by its volume significantly higher than that required for good operation of the complete rotary assembly and its seats as well as all the bodies influencing the modification of their position, ensures free transfer of gases from any point to another inside this cavity, around the whole rotary and in the middle of the annex organs allowing and facilitating the flow of gases to the cylinders also powered from inside the rotary assembly.

It can be perforated as needed in multiple locations and connected in one or more points with external air or air inlets gas mixtures necessary for the proper functioning of the engine.

The other cavity, forming a common collector 32 for the burnt gas outlet, contains the rotary assembly T-9 and its seats 6, 7 mobile or not, replacing the exhaust valves and all devices operation of the latter.

This cavity 32, whose shape and volume may be totally different from those in the cavity 31, must very easily contain the rotary assembly, the movable seats or not, as well as all the organs influencing the change in position of these last ; it ensures the free transfer of gases burnt, from one place to another, inside of this cavity, around the rotary assembly and at middle of the appendices, allowing and facilitating the path of the burnt gases from the cylinders to exterior, greatly improving their evacuation, also through the interior of the rotary assembly.

It can also be perforated according to the needs in multiple places and connected in one or several points with one or more conduits gas outlet.

In application to cooling engines by air, the implementation of the invention does not require substantial changes. The external parts of the cylinder head (s) may, however, in this case, have fins of appropriate shapes and dimensions to remove excess calories and ensure good cooling of the cylinder head (s) of this type engine.

If the engine is used in low temperatures, even by negative temperature, whatever the cooling system used, we observe that the pre-heating of fluids on admission is guaranteed, from starting the engine, by adding calorific transmitted by the middle partition of the area exhaust to the intake area, which avoids the icing in the latter.

This middle partition is also used in the other direction, to a transfer of appreciable frigories, thus allowing cooling of the burnt gases.

These intakes of calories or frigories can be increased, as required, either by forecast of finely placed fins, either by a reduction in the thickness of this partition, ie again by its partial replacement by a part of exchange executed in a metal having a coefficient higher heat conductivity.

Claims (12)

1. Multi-cylinder internal combustion engine comprising at least one set of cylinders (1), the combustion chambers (3) of which are each provided with an intake aperture (4) and an exhaust aperture (5), the intake apertures (4) on the one hand, and the outlet apertures (5) on the other hand of the said set of cylinders (1) being disposed aligned, the distributions means which permit opening and closing of the said intake apertures (4) and exhaust apertures (5) comprising two rotary nozzles (T-8, T-9) which have a circular cross-section, each consisting of a plurality of hollow shutters (8a, 8b) which are aligned one after another and communicate with one another, such as to permit flow of the gaseous fluids in the interior and from one end to the other of the said rotary nozzles (T-8, T-9), the lateral wall of which is provided with a plurality of holes (10a, 10b, 10c, 10d; 11a, 11b, 11c, 11d), the number of which corresponds to that of the cylinders to be used or activated, one (T-8) of these rotary nozzles permitting opening and closing of the aligned intake apertures (4) of the set of cylinders (1), whereas the second nozzle (T-9) permits opening and closing of the aligned exhaust apertures (5) of the said set of cylinders; characterised in that the rotary intake nozzle (T-8) and the rotary exhaust nozzle (T-9) are accommodated, the former in an intake manifold (31) and the latter in an exhaust manifold (32), each delimiting a space or chamber which surrounds respectively the said intake nozzle (T-8) and the said exhaust nozzle (T-9), these chambers (31, 32) being separated in a sealed manner and disposed such as to permit free circulation of the gaseous fluids outside and along the said rotary distribution nozzles (T-8, T-9), from one end to the other of the said intake manifold (31) and exhaust manifold (32).
2. Multi-cylinder internal combustion engine according to claim I, characterised in that the intake manifold (31) and the exhaust manifold (32) consist of cavities provided in the cylinder head (2) of the said engine.
3. Multi-cylinder internal combustion engine according to one of claims 1 or 2, characterised in that the rotary intake nozzle (T-8) and exhaust nozzle (T-9) are mounted such as to rotate in bearings or rings (16a, 16b; 16c), the cages (63) which support these bearings or rings being provided with passages or openings (62) which permit free flow of the gases from one end to the other of the intake manifold (31) and exhaust manifold (32).
4. Internal combustion engine according to one of claims 1 or 2, characterised in that each intake aperture (4) and / or exhaust aperture (5) is provided with at least one mobile seat (6, 7) which makes it possible to modify the cross-section of passage of the fluids, and the moment or instant of closing or opening of the said aperture, these mobile seats (6, 7) being accommodated inside cavities which constitute the intake manifold (31) and exhaust manifold (32).
5. Internal combustion engine according to claim 4, characterised in that each intake aperture (4) and / or exhaust aperture (5) is provided with two mobile seats (6, 7) which are mounted such that they can undergo movement of distancing or approach, these mobile seats (6, 7) being accommodated inside the cavities which constitute the intake manifold (31) and exhaust manifold (32).
6. Internal combustion engine according to one of claims 1 or 2, characterised in that one of the ends of the rotary shutters (8, T-8; 9, T-9) is provided with an entrainment joining piece (12), and in that the end portion (26a) of this joining piece is arranged or shaped such as to ensure entrainment of a device which is necessary for functioning of the engine.
7. Internal combustion engine according to one of claims 1 or 2, characterised in that one of the ends of the rotary shutters (8, T-8; 9, T-9) is provided with a joining piece (14) which comprises a tubular axial extension (14a) for connection to a carburised mixture intake pipe or to an exhaust pipe.
8. Internal combustion engine according to any one of claims 1 to 3, the rotary shutters (8, T-8; 9, T-9) of which are guided in rotation by means of bearings or rings (16a, 16b, 16c), characterised in that these bearings or rings are surrounded by two off-centred and concentric rings (17, 18), one of which at least can be entrained in a rotational movement of limited amplitude.
9. Internal combustion engine according to one of claims 4 or 5, characterised in that the seats (6, 7) of the rotary shutters (8, T-8; 9, T-9) have a curved shape and are guided in lateral flanges (52).
10. Internal combustion engine according to any one of claims 4, 5 or 9, characterised in that it comprises means for regulation of the position of the mobile seats (6, 7) of the rotary shutters (8, T-8; 9, T-9).
11. Internal combustion engine according to claim 10, characterised in that the device for regulation of the position of the mobile seats (6, 7) of the rotary shutters (8, 9) comprises a cylinder (36) which is installed in a sealed manner through the sealed wall (34) which separates the intake manifold (31) and exhaust manifold (32), and in which there is accommodated a piston (42) which is subjected to the action of a compression spring (47) which tends to thrust the piston in the direction of the exhaust manifold (32), at least one of the surfaces of this piston (42) being connected by means of an articulation (41) to a control rod (40a, 40b), which itself is connected to a connecting rod (44) secured on a shaft (45), onto which there are also secured connecting rods (59), each of which is connected by means of a transmission rod assembly (51) to at least one of the mobile 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, characterised in that each of the opposite surfaces of the piston (42) is connected by means of a rod (40a, 40b) and via a transmission (44, 45, 59) and a rod assembly (51), to at least one of the seats (7 8) of each rotary shutter (8; T-8; 9, T-9).

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