CA2622829A1 - Rotating drive machines, polyturbines and turbomachines with maximized thermodynamic efficiency that burn diesel fuel - Google Patents

Abstract

The object of the present invention is to show how to perform a calibration of the positional and orientational aspects of the kinetics of the compressive parts of rotary machines, polyturbines and turbine machines in such a way as to enable them to achieve maximum thermodynamic efficiency rates. The present invention also intends to show that the reworking of this orientational and positional calibration can be obtained by the methods that materially modify the compressive parts themselves in order to allow the realization of new kinetics, or by modifying their mechanical structures, or finally by changing their piston design. It will be shown that the specific arrangements of their compressive parts can also be made in such a way as to sufficiently increase the compression of these types of machines so that it is possible to achieve them with a burning of the diesel type gases. The rotary engines, polyturbines and turbines thus produced will produce a thermodynamic efficiency not only superior to current machines, but also to conventional piston engines, without distortion or dispersion of the expansion of the explosion,

Description

Rotary, multi - engine and rotary turbine engines thermodynamic efficiency maximized and diesel bridging Disclosure Some preliminary ideas relating to thermodynamics Thermodynamics is a complicated sciencf requiring for :: on advancement, more and more advanced knowledge from engineers. I1 is therefore important here from mention that the present invention has in no way the presentiment to bring new gas burning configurations in rotating machines, polyturbines and machines turbinatives. The present invention may however very in place practical conditions for the possible realization of such searches more depth.

Moreover, it is important to mention that there are huge differences between the theoretical thermodynamics and applied thermodynamics. In other words, while theoretically two volumes of gas compressed and ignited gives off the same amount of energy, in practice, everything else is different. Indeed, the way these gases are on, the composition of compressive parts performing compression and mechanical ki used for lead to the cooling of this heat by the expansion in rotation in a motor axis, are many factors which, in the end and for the same thermodynamics: theoretical, result, by varied practical achievements, with differences in energy efficiency very important, motor capacities being sometimes doubled, even tripled for a same explosion. Of these this, for example, the consideration of direct heat transfer of material to equipment, which theoretically is not considered, ma.is which is practically very important. Similarly, the type of mechanics realizing the rotational rendering of thermodynamics, which theoretically is not considered, and which practically, leads to many impeccable questions such as those of friction and the overheating of some parts of the engines, or, as such, of maximum acceptance of the actual expansion wave.

In summary, if there were no significant differences between the theoretical thermodynamics and the actually real and practical rendering of this thermodynamics, u; i engine rotary of the same Compression volume that a conventional piston piston would make the same efficiency thenmiodynalnique. But despite the notable subtractions of depeizse driven by the absence of mechanical valves and the little accelerating deceleration of pieces, rendering The practice of the thermodynamics of rotary niotors is so deficient that these engines do not arrive not, at the end of the day, to surpass or even ereretic, yet quite weak, piston engines.

As we have shown in many of our previous works, the rendering practice of The thermodynamics of rotary motors can be considerably improved. The present invention will complete this work, and will show that under certain conditions, the rendering of any machine, whether it is conventional piston, rotary type, polyturbine, or type turbinator can be equivalent.

Examples of thermodynamic and thermodynamic thermodynamics- practical in the field conventional piston engines.

As we have just mentioned, when it was carried out under the engine, the Thermodynamic is subject to mechanical constraints which can modify greatly the practical results of energy rendering.

Let's give some examples first of all relating to piston engines conventional.
In theory, when one compresses a given volume of gas, and that or.i in produït ignition, one must to obtain the same result of power; created by progressive cooling of this heat in relaxing course. According to such a statement, the compression of a piston more small, moved by a crankshaft and a longer connecting rod, should always, if the compressed volume is identical, give the same thermodynamic result, the same energy efficiency as if one had built the compression with the use of a larger piston connected by a connecting rod to a crankshaft whose turning radius had been shorter. (Fig. 1 a) In practice, however, we realize that we must also consider the exchange of heat that will occur between the elements. Indeed, a heat par will heat the head of the cylinder, that of piston, as well as, during the d-piston stroke, that of the walls of the cylinder. Taking account of this factor, we see that the engine whose piston and cylinder has larger volume will achieve a greater heat exchange unrecoverable between the elements.
The results The final and practical mechanical properties of these two motors will therefore be different, while theoretically, they had to be idex {ticks.

In a second example, (Fig. 1b) we consider that a same; volume of compression is on the one hand by a structure ~ onventional, and other parI;
complicity of two pistons, inserted in opposite directions in the same cylinder. Again, even if we can show that, theoretically, the efficiency of the two engines should be identical, the practical performance will be different, since the inert head of the conventional emmaagasine cylinder more energy heat that the head of a piston aõtif.

In a third example, (Fig. 1 c) we can compare, always for the same volume, the performance of two engines whose i in would have a piston and a cylinder: ~ e conventional, while the other one would have a piston and a <ylindre square shape. So if, theoretically, we can say that the pressure is equal on the surface of the pistons and cylindret :, whatever the In practice, it will be seen that the development of ignition and of expansion performs less well in such a type g form. Indeed, we know s:, u today the phenomenon of schril, mini storm that produced the explosion, as well as the Bed that the explosion has an origin and a diffusion that are progressive. As a result, the corners of a square piston are more belatedly burned, and filled by pressure. Piston and cylinder Perfectly round seem to be the most economical way to achieve the thermodynamic effort.

Let's give another concrete example. Suppose, as has already been done by some motorists, that an engine is consuited (Fig. 1 d) by placing the relative cylinder to ignition on the side of the piston and not above. Again, we will consider notable differences between basic theory and practice. Despite a compression iõt of a equal pressure, the two opposite parts of the head of the cylinder, to be side by side will store one more large amount of heat which will not be realized in force of descent. Moreover , Development of the exploding explosion will be laterally, and we will lose the movement proper this expansion, to preserve only the result, more inert, is the pressure. Engine will look more like an air motor, than an internal combustion engine.

Let's give a last example (Fig. 1 e). Compare, always for the same amount of gas compressed and lit, a motor mir by a crankshaft and a standard rod, a motor driven by a standard crankshaft and a sliding rod, and a motor driven by a staging of crankshafts Bunk. Although possessing :. identical compressive parts, some mechanical aspects these engines will be very different. For example, the two; last will not have a point death down, and will not have to paralyzed Lion angular piston connecting rod in c bear descent. Otherwise, the level of friction of the parts necessary to ensure the movement strictly rectilinear vertical sliding rod, n ~, me the friction achieved p2r the moving, too rectilinear, but this time lateral, of the joint piece joining the connecting rod with crankshaft, will produce more friction, and therefore less heat irretrievable, that both top and bottom attachment of a biellf, conventional. In total, yields of both in practice will be very different and will depend on the methods used to secure the respective movement of the connecting rods. The same statement applies to the double engine crankshafts superimposed. The gains made by canceling the tem: :) s death low and high, and cancellation of losses by angulatic m of bielie, will be counterbala.n ,, és by losses due to accelerations more direct decelerations of the connecting rod, in motion strictly rectilinear, same as by the friction driven l- ar the gears producing it e specific movement of the upper crankshaft.

These last two examples are eloquent. It show that in debit qualities mechanical appearances superior, some nioteurs, if tio-nt account of the &iction and deceleration acceleration ,. become more energizing than those the recouss to a rod. standard.

Piston engines and rotary and turbine engines.

The same thinking applies when one is trying to compare a piston and an engine rotatable. In theory, if these engines achieve exactly the same volume of compressed gases and on, they should produce the same mechanical energy Snaleõ And yet, despite their undeniable intrinsic qualities, rotating machines remain, in the fiitai, more energetic than piston engines.

We can only deduce the following While theoretically, for a moment amount of gas compressors, a piston engine and a rotary engine should have a identical yield, the theory is at this point different from the practice that d deficiency has thermodynamic efficiency rotary motors can not even compensate for the mechanical losses due to at the valves mechanics and acceleration of demolition, which, however, limit c, :) nsidably the power piston engines_ This means, in simpler terms, that in theory and practice, there is a gap of more than thirty percent. This also means that the huge difference between the power theoretical and practical power of rotary motors is due to a set causes to which after having correctly identified them, we can identify soli.itions relevant. This wants so to say, finally, that it is dan; practice, in concrete c; eu may be reinstated, at point at which it should be, the thermodynamic performance of the anotors rotary and turbines, in such a way that they can enjoy significant advantages weight, valves, and so on .

Reminder of the main defects of rotary engines and our solutions previous It is necessary to recall here, as briefly as possible, the main defects of the engines rotary, at the thermodynamic level ~, as well as the contributions we have could contribute to realize in the matter. This brief review will allow us to see the remaining problems, and to identify how these can not be solved by this solution technical. (Fig 2) Reminder of these defects Rotary motor defects are four-way, that of the, rendered mechanical, that of the segmentation, that of design, that of kinetics. Principalemait, we can point fingers:
a) the rear unbalance of the thrust on the comprE: ssive portion in progress downhill b) the imbalance before the push on the compressions part,; ive in progress downhill c) too heavy mechanics (eccentric) d) Segmentation too heavy e) the dead time along the machine (f) the excessive length of the compressive properties offered for the explosion (g) the defect of the parietal kinetics of the rear part of the piston of the descent h) the lack of amplitude of the thrust before, due to the lack of:
radius of Piston turning i) the deficient design of the forr. ie combustion chambers during the explosion or explosions j) the square character of the pi :: ton It should be noted that many of these events occur in cascading being from others. The most general source of all these Jefa.uts is that tszoteurs rotary, from Wankei, have been to a single motor mechanics part, and a set of p, uties compressive, the piston and the cylinder. Recall that i in the rotary engines of the going Wankel, the recovery the crankshaft was accompanied by the rertressement of the piston. But this entangled curvatures of cylinder too pronounced, and Wankel, correcting this problem, reduced the engines at one only expansion, which makes the mac hine mono inductive.

Partial correction of these defects in our previous work (mechanics and kinetic) We have shown to several reprfes that the mechanical push ~ on a piston machine Wankel type mono-induction rotary machine produced a against thrusts back, a set of ceritral thrusts allowing the neutralization, and a set of forward thrust lever.

The object of the present invention is to pursue several of our inventions previous (Fig. 4) and to show that it is possible to realize on the piston of a machine rotating, turbinating or type poly turbine, a thrust that does not push against pushed <:: s on the previous bet, and on outbreaks on the posterior side,. And who on the contrary, distribuf:
energy from low to high in respecting the report of retro rotation, or post orienlial filming of a piston in the machine. show that you can rebalance work on surfac. of piston like this that it is proportional, this means in such a way that it varies from weak to strong, this respecting the kinetics of pre-rotorotatil, ye, for orientational rotational post of the piston in the machine. (Fig. 3) The practical objectives achieved by the advances of the present invention are therefore the following:

a) a reduction in the machine's dead time, which will result in a decreased time direct heat exchange from material to material (b) an increase in the rate of compression, which will permit make engines rotary variable speed engines, rotary diesel engines, sa: as achieve cascade of parts compressive.
(c) an improvement in the shape of the combustion chambers during ignition, this allowing to better position the candles, and even to keep only one when of realization of the machine, d) an improvement of the segmentation which will allow better po:, itionner candles without losing pressure between the chambers when the segments pass.
(e) a reduction of the material parts directly available to the explosion, this allows reduce the heat exchange of irreplaceable material irrevocably f) a softening of the movement of the compressive parts of J. machine, this leading a decreased wear of rites g) an increase in the power of the descent, allowing an effort rotational retro increased, (h) a reduction in the duration of the loss, the effect of which is only to maximize the power of the explosion, to reduce the downtime, i) a possible increase of the 1 filling inips without turbo compressor.

First part of the present invention: improvement of the tli, ermodynainic by re partition of the orientation-3el and positional character by dividing the piston into component piston and pistons of curvature.

As we have just mentioned, we have shown in our work previous, which one could produce advances of ty; > e mechanics susceptible, for cylinder figurations of identical machines, to allow i. better capture of development of the explosion, and a limitation of the indirect exchanges of heat by friction, by echange direct.

First series of observations that are relevant to the present invention, n To better understand the present invention, it is necessary to remember two remarks that we have already made previously, and which relate to rotary machines, these observations being the following.

When we observe a certain point of a piston of a rotary engine when of a revolution complete of this piston, one realizes that the kinetics realized by this point varies according to two parameters, namely, the first, sek in the distance separating it from the center of the engine, and the second, the piston dial eji which point is chosen.

Indeed, in a rotary engine star, dart, the more the observed point is located near the center, plus the the curvature of its kinetics is pronounced, and the greater the relative amplitude of the difference between internal and external endpoints are strong. Conversely, the more the p ~) int chosen is located in verse the outside, plus the curvature realized by this point during a convolution the engine will be soft.
Moreover, the kinetics of a point ~~ rarie also taking into account the dial in which he is positioned. A point on a li, uniting the center of the pistori and one of the ends of piston tips will describe a similar shape and in the same axis clue that of the cylinder. By elsewhere a point on a line passing through the center of the pistor. and the center of one of the sides, will also describe a shape similar to the cylinder, but this time opposite angle to this one.
Finally, a point between these two positions will also describe a shape similar, more or less acute, but this time obliquely to the first two positions. (Fig 5) These observations make it possible to say that the longer the relative length of the piston of a rotary machine is small compared to its length, ie crankshaft, more, as we come to see him, the curvature of the cyündre is exaggerated ei: becomes inadequate, since it entails a change abrupt direction of the piston and dc-s segments which leads to its 1: for a premature wear of them. In addition, the counterforce on the back part of it are less important, and turn into forces. The rear part of the piston becomes more active, more downward, set to against the direction of the moteui, more positive, which maximizes the power of the machine.
It is therefore found that if on the one hand the inappropriate curvature of the cylinder risk of causing premature wear of the segments, on the other hand the thermodynamics of the nnachine would be found improved, since for the same volume of compressior.i, we would have used a piston less activated by a crankshaft plizs large, and one would consequently got not only a positive effort on the rear part, the pale, but also, a low, surface of exposure of the piston and cylindricc to the explosion, thereby reducing as much as the exchange between these parts. These observations also allow de, romrend.re that the dimension piston, when one hear prodt ire a rear curve of pistoai similar to primer down to the end-of-arc curvature of the cylinder, must be defined as such way it's pretty bulky. There is the obvious contradiction. To avoid against: forces on the back part of piston, engineers are forced to hii confer a dimension that will also cause kinetic of its rear part of way negative, that is to say, activating laterally against the meaning of the machine, rather than in, ente.

The present invention consists in distancing, materially or mechanically , or at the level of Opiston's design, the orientational and positional character of the pisifon rotary machines in such a way as to be able to better control. balance and proportion their potential to perform the thermodynamics of the machine. We app-clons the positional aspect of the movement of the piston, its moving -nt the movement of the center of it by report to the center of the machine, and we call it the orientational aspec of it, soiz rotational motion by compared to the crankpin, or the center of the eccentric.
supports.

In its first part of the present invention, realize this balancing ds caractière orientational and positional approach by showing that one can produce the boosted part rotary machine such as one of the parts of the piston, that we will call the corur-piston or piston compressii n, makes a modification of the character original positional the machine, realizing an increase of the compression by the, recourse to the a curvature exacerbated, more pronounced, whereas: the secondary part of the piston that we will call piston of curvature, will make a change in the orientation of the machine, since, in one single piece or in a fragmented way, it will achieve kinetics corresponding to the curvature of the cylinder, this stiffness being not only softened, to allow a conservation or improvement of the low solicitation of these, but more, drawn from such way to get simultaneously several objectives, scit, to maximize the volume of expansion and to di.minute thernic exchange surface during the explosion, and finally, to auigmenter the quality of it and the resulting expansion.

First realization: complicity tk curvatures of first deginés The first realization of this c. invention is to show that one can produce the machine by a complicity of pisto-As, whose two pistons seroni: all two of rotary type.
In this first embodiment, it is based on a same axis rotational two eccentric of different sizes, on which is mounted two pistons, of te lle way that one two be ixMixed in the central extrusion of the other. Each is attributed to:, emble an induction, by example by mono induction. The two sets of that their size general, while taking care that the external set is , in total, somewhat more voluminous, so that it is this one whose segn: ientation of the piston touch cylinder. Moreover, the induction of the inner whole is carried out more bulky than that of the outer assembly, which means that the piston of the interior will be smaller. We can produce the outside assembly with a shorter crankshaft, and a piston longer than standard, while the crankshaft will inevitably be produced (the the inner set of larger dimension, and the piston I dimension smaller. Such as we recalled it in the last observation, the curvature wirie according to the degree of distance_at bringing the crank pin of the piston center of the machine. As a result, may increase intentionally the length of the compression tube while preserving or by decreasing that of the curvature piston.

When we operate the crankshaft, we can observe that this way, the piston the curvature will be softer, is paired, in complicity, with a inner piston of which the kinetic curvature is exacerbated, and more ample .. (Fig. 6) In this arrangement, we will therefore desigr-erate the piston realizing the cylinder kinetics as the piston of curvature-, and we will designate the piston realizing a movement more ample compression, the compression piston, or the heart pistoii.

From then on, we will be able to realize uw ie first version of the preselte invention by producing, from two pistons of figuration of rotating machines to move similar planetary but different, first of all a deeper expansion, and then a conservation of softness of the cylinder curvature. (Fig. 7) After making this configuration: .on, we will realize that b ;; piston having the most curvature pronounced, either the inner piston, also called compression piston or heart piston, realizes with respect to the outer piston, the curvature iston, a court, Translational. Starting from this Moreover, we can distinguish the two pistons by a double sliding assembly, which will seal the entire piston (Fig. 10) In a version derived from this first solution, we note that we can for one gear set the piston of, urbature, support and incluction, produce, on the eccentric supporting a second crankpin disposed further away from the center and who will receive the heart piston. In this case, the orientation character of p, iston must be provided by the piston of curvature. Note that the heart-piston moves conveniently translationally relative to the piston of curvature. As a result, we can link the one and the other by a small crankshaft, whose radius will be equal to the difference of the radius of the matneton of the piton cAeur and radius of the curvature piston. This small v4ebrequin can be activated pEirti a support gear placed directly on the eccentric (Fig. 11) As before, it is the case that the gap between the pistons is coronely realized by means, it will be seen that the upper court of the cylinder erigend by the piston of curvature pennettra to redesign the head of the heart-piston of way more adequate as that of rotary piston heads of conventional engines. Conversely, o, a will find a more important ratio of compression to the montel and descent of the whole system of compression, based mainly on the descent of the compression p ston, the heart = -piston is more important.

As a result, for the same heat exposure face of the parties compressive during the explosion will hold a larger expansion volume expansior1 Control of all tractor and towed piston tents.

In our previous examples the pstons were ordered from half independent, or again, it was the piston of curvature that realizing the orientation of the piston assembly. While the piston heart was located higher, in such a way to realize a more strong amplitude of it.
As we have just shown, besides, it is possible to co. mmander together by a only master induction, and to comm the second piston from the first.
So we will say that a tractor piston and a towed piston are orientated. In this last version, version therefore, the piston to bend is the orientrational tractor piston, and the piston of compression is the towed piston.

Inversion We can produce the inversion of this situation, by first realizing the induction of the piston which will be, then consequently simultaneously the plunger piston. from when we install, this once in a shorter radius, a second crankpin on the excenter:
tractor piston base, whose radius will be shorter, in such a way that the piston of structure perform a stiffness softer. In this case, the translational control crankshaft will control the piston stroke of stiffness. This possibility of procedure is of the utmost importance.
this for several reasons. First, it allows the piston to break up (.
Piston curvature single body pains. As we <~, as can be seen, the segmentation) n of the double slide linking the pistons is simply not easy, but also because it makes even more difficult the usual segmentation of side. Sn splitting the piston of circulation into pistons of stiffness units, it will be possible to reduce the difficulty of making the pistons sealed between them.
partition We can break up the piston core, and do it in the form of pistons conventional, what we realized in our previous work. The present adds that these pistons can be required by a single heart member, and that can even be made poly fi fi cameo, in such a way subtract the slides 1'unissa zt piston (Fig 10, Fig.11).

By the way, after defining the piston as the piston tractor, we can improve the piston of curvature in pistons of individual aches, one of these being inserted into one corners of the piston. (Fig. 12.1) As before, each one will receive a command, imilaire, semi independent of that of the corur piston. But we can also use the piston driver tractor piston.

Means for isolating the plunger pistons and plunger pistons, and modifications mechanical As we already mentioned:, we must isolate the piston piston: and the, or the piston of curvature in such a way that the gases do not go between the parts, which would cancel the effects obtained by their complicity .. For example, we could use i.me double exchange backstage, or one can use - a single slide insert dan> a part itself inserted in two pivoting parts Simplification Such sealing represents, as we can see, a challenge appreciable technique ..
Several means can be used to counter this difficulty. These means all consist of lighten the double sliding means i allows him to seal the two l: istons complementary each of their points. For this purpose, it is necessary, in all cases, to simplify the double vertical and lateral ratio of movement of the pistons in the points. In other words, it's especially the lateral aspect of the movement of the piston of curvature that is necessary decrease, see subtract.
But this can not be done on one of the points of the piston without keys inappropriate consequences, as by displacements in dE outside the path of the curvature, it comes on the tips the piston, which should be excluded. The advantage is immediate and important of the splitting of the curvature piston into upright stiffness pistons is that we can have each two independently :, in each corner of the piston core, and that, therefore, we can continue to benefit from their vertical income, and subtract from:
completely or totally lateral.

In a first version of cetti; nianière to do, we will insert iians every corner of the heart piston a cylindrical oscillating element, which will be provided with a sliding receive one of the pistons of unit curvature, the unitary piston is available, and will be connected with the extremity crankshaft of it. they are side-by-side, without losing the effiicacii the machine, and without modifying substantially the curvatures of the cylinder. (Fig.12.1) In unr;> other way of doing things, segmentation between the piston core and the unit stiffness pistons will be still easier if one inserts each of these pistons of unitary currencies through, single vertical slide in each point of the pisto; est. From then on, it will be necessary to link them to.
crankshaft by a slide, this time lower mechanical. ] as it has already been done for poly turbines, one will be able to fix each of the unit pistor of curvature by an element able to rely on a central eccentric Means of support The connecting means of the piston, unit of curvature and the piston core pistons will be able when simplified. The three main achievements of this procedure will be the following. In a first case, we will link each of these pistons being linked to the pistorn by a oscillatory pieces comprising a wings. In the second case, each of these pistons being at top inserted in a single slide of the compression piston, and connected to the bottom, ar.i crankshaft by one second slides. In a third case, we will relocate the vilebrecluin association slide, by a eccentric and a rod, or an eccentric counterpart. (Fig 13) Polychanted gears The first is to realize a seele, or both inductions with the use of gears polycamés, that is accelerator decelerative engrei ages. (Figure 12.2) The consequences direct use will be to check for differences in acceleration deceleration between the two aches and pains, while not controlling differences, depth of them result in allowing those parties to use only one single sliding member insulation, which will greatly reduce the difficulty mentioned.

Double shared slide.

The breaking of the piston of the court) a.ture in pistons of curvature s unit will allow in other to give a single slide to the upper part of the piston, and cle transfer the other to crankshaft. In this way the stall produced by the two pistons will be enormously more easy, since each piston unit: e of curvature sers tristemerit inserted in a sliding way, and not in an oscillatory and coulissiunte way, or in a translational way in the heart pistons. (Fig. 8) Slide and means of induction The purpose of returning to the piston ccõur the work of induction and inecision is mainly to strongly reduce the pressure: on the pistons or pistons.
Starting from this fact understands that it will be acceptable to trade the induction by crankshaft eoulisse, by induction simple cam or eccentric ,,: t push rod. In this case, the cylinder will rim the pistons of body aches or the system will be completed by a double cam.

Induction means From this fact, each piston ii.e unitary curvature can be activated different means, including The main ones are by poly induc tion, crankshaft slide, connecting rod with slide and seal oscillating at the top, by crankshaft: a slide, and slide at the top, by cam alone or cam against cam, central or inductive poly, p, tr eccentric, and eccentric ,, - omposé.
(Fig 13.2) Summary of this first part of the invention In this first part of the article, it has been shown that it is open to serve as two parts complementary pistons for each of the different curvatures, all of two of first degree, but with larger amplitudes to achieve with the cylinder curvature outside, in complicity the compression of a rotary machine, We also saw that these two pieces could be driven by inductions different, or by crank pins of the same axis aci ivant the two pistons.

These two parts must include parts ensuring the sealing ~ :: between they. We also saw that one of the pistons. preferably the list of stiffness, can be realized from fragmented way of in such a way as to be inserted in a flexible (oscillating or sliding in the second piston, preferably the piston pisto! i. This simple way of doing things:
necessary elements to seal the pistons together.

On the basis of this fact, each unit curvature piston can be ejected.
different means, including The main ones are by poly inducticn, by crankshaft slide, connecting rod with slide and seal oscillating at the top, by crankshaft slides, and slides at the top, By caine alone or cam against cam, central or inductive poly (Fig 13.2) So far we have shown that it is possible to realize iiin engine rotating or turbinating three parts without this understanding the reliability of the engine. l: n effect, while the crankshaft superimposition underground a connecting rod, remains mechanically hypothetical and risky, complicity of corur pistc n and pistons of curvature, simple or unitary, supported partially by the same mechan that or by two mécartiques enough independent is not an impending mechanical challenge. In addition, she brings many machines, improving the propensity for compulsion and acceptance of E:
xpansion, while retaining softer cylinder curvatures. Although appreciable, the results obtained include still some gaps, which as we will see it can be corrected. These gaps resemble those which are soft; encountered in some of our innovation earlier, either in the mechanics by polycammed gears in the mechanical superimposition of crankshafts, by the mechanics by poly pistons (Figs.
15) Indeed. we noticed that each and every one of these mechanisms realize the same number fluctuation, or correction of> cylinder per revolution than that d. as ares.
As a result, well that bulges brought in 1: s machines can only be under a only one angle at a time.

For example, during the realization; ition by polycamês gear., if one has the gear in the direction of the piton, one softens the neck of meeting of the arcs of the cylinder, but we do not improve the descending effect of departure. Inve ly, when the gear is available in the contrary sense pistons, we improve the effect descerant, but the curvature of rerx;
bows becomes too pronounced.
Similar results occur: nt when making mwõhines by stagings of crankshafts. Where, for example, for post-burial machines, crankshafts are superimposed in height at the top dead death, and that the crankshaft subsidiary goes inside during the descent, the compressioiz is higher, but the cost of encounter very bows pronounced. Conversely, when the subsidiary crankshaft passes worm outside and that addition properly speaking, the crankshaft is f? it la.tely, the meeting ares of cylinder is soft, but the expansion undergoes contrary forces on both crankshafts.

In addition, it is important here to remove the poly cylinder turbiiDnes, who, realizing a curvature that we have previously defined as being of bi-rotating type, succeeds in realizing positive effects, simultaneously at the top and bottom of the cylinder.
Unfortunately, the surface of pistons composing the paliq ue structure of these machines is too short, and therefore the Compression volume is too little.
Ideal cylnldre curvature of bi rotating type If you look closely at the cylinder of a rotating engine, you know it. makes account that on the one hand, its upper curvature may be improved and softened. Not only this would allow realize better rate of compressic, n, but also, that would allow. of bring the design closer to the piston head of the cylinder during the explosion, which would avoid the usual double cylinder, not compatible with a correct> xplosion.

Moreover, if we look at the standard cylinder, we realize that is usually a height ratio of seven ninth, which produces tremendous loss volunnétrique. If the curvature of the cylinder is increased, this will mean that the piston will enter more deeply in eIIe, and that consequently the elongated parts of the piston will realize mo ins of against effects, and the parties before a better effect. (Fig. 16) It is important to note that, in the engines whose number of side of the piston is odd, as for example triangular, the lower bore of the can, i will have to compensate for the character oblique the attack against the pis ~ on curvature, and therefore be more enlarged.
Increased degrees of caracti, re curvature of the machin * c So far we have stated that it was possible to make a puussée deep piston, everything by performing a gentle cylindrical curvature. But, the curvature dc, s cylinders of maehines In our view, we believe that we can improve the quality of the rotations. Indeed, to the extent we can separate: r the piston of compression and the one or those of curvature, we will show that is that the curvature of the pistons of courbat iires of rotary and tur binative engines is a curvature of second degree, while maintaining a curvature of heart pistor: first degree. Indeed, we think that if we can, by the t, ffl of pistons in compositior.i already mentioned, to enlarge the width of the cylinders, and to increase the height, without having to increase the width of the pistons at moment of the explosion.

Recall of the notion of degree in the; curvatures We say that a curvature obtained by a mono induction of t; ype Wanket, or any other Mono induction mechanism that we have developed is a +,;
first degree Similarly, we say that a curvature obtained by adding a crankshaft master and Auxiliary crankshaft is an inductive inductive type inductive and clerical also a curvature of first degree identical to the cycles of niono induction.

We reiterate that by adding u ri staggering crankshafts to the mono induction or even to Induction by poly induction gives a curvature of second degree In these case, this staging put the machine and its courburc to a macbine and a curvature of second degree so are for example obtained from machines with curved cylinders, or else: poly Gold turbines in our previous work, we have ascertained that the curvatures achieved with the resort to one induction was to be called curvature, of first degree. We have too, we also showed that It was possible to produce second-degree courts, which we did not have.
said curvatures of second degrees, Among the most typical curvatures, we note the curvatures per ac celeration decelerations, that we made by polycammed gears. Other innportant figures were obtained by addition of superimposed crankshafts supporting the piston. Finally, we have also shown that one birol curvatures, which serve, in particular, to receive structures The development of this first part of this invention is intended to object to show that, since the piston of curvature, or the pistons of fractured paroxysms support more than pressure, the latter being supported, for example, by the heart pistan, could apply them these mechanics without which we 1 could realize other curvatures of cylinder First example of combination of first and second degree curvatures We can therefore show here a first example of the second part of the present invention, know the one in which one will couple in heart piston realizing a curvature of first degree to unit-aiding pistons reflecting a second degree curvature.

To do this, we will remind you that we have already shown that it was possible to support hinges of palet structure of p,) ly turbine ,, this machine has ay-it a second degree curvature, by subsidiary crankshafts c (important geomorphic addition, these crankshaft being shown planetarily and retrore: to the crank pins of a -vilebrequin Here, these crankshafts will be realized of way 1 confused with the piston of irourbature, and will realize by therefore the desired curvature (Fig 18) As we have already seen for poly turbines, it is possible to support points of the palatal structure by pressing them on the sliding support rods on a central cam Double figure An important advance of the present invention is to show Ideally, if we could produce a cylinder with these two bulges at a time, everything not changing points the passage of the points of the piston lor, the dead time, one would have the di>> effects thermodyn.amiques important since one of them is to achieve a curvature of cylinder and piston eliminating side pockets, the compression ratio and allowing an explosion more central, and on the other hand, one would allow a larger volume upward and down gas expansion, and that, while not enlarging the dimensio:, i of the piston during the expiosion.
This realization can be done mechanically by making,:, that the stems of the cons pistons of aches are activated;
complete turn, but well, for a triangular piston figure, four times, We will obtain this result from several ways. First of all in pcily induction, we will realize the subsidiary crankshaft such that they turn twice tilus quickly, or else this time, it will be more of an elliptical curvature elliptical, so duplicate cam. In this way, the desired effect is produced. Similarly, if the stems counter pistons are repulsed by a crankshaft o, has a subsidiary eccentric this: ntral, one double, semi transmission of the speed of these, or rather, instead of realizing them;
simple cam, we realize in double cam, so almost elliptical.

Refinement of the curvature of the cy Lindre piston So we have a certain advance in being able to ensure that the cyli; ldre can to be curved towards outside, both at times up and down, and at the same time the fir.i of bulbs, without the curvature is changed to vi; the points of the piston to the tem <:) s death below and below. Of this way, we maximize the explosion and expansion, while preserving its minimum the size of the piston, and therefore the parts s of it and the cylinder offeites to the explosion.

But, a closer look at us; unene to the finding that the bulge needed at the top and bottom of the cylinder and those needed; in the arches do not have to nessarily be made with the same amplitude. However, with the previously disclosed methods, this is the case.

To make entries and support it will be necessary to realize L: s cams in such a way that these are done in pairs, e !: that these pairs are associated alternately. In other terms the cams allowing to bear the rods low conler pistons during the dead time must not be the same as those who support these same rods when realization of bulb arches.

Bent compliety machine of third-party and third-party cc, When examining the irotative curvature we have produced, until now, we can still aim for a supplementary refinement. Indeed, these curvature, predict a on swelling of parts corresponding to the times up and down, as well as parts the times maximally lateral anterior and posterior. However, with used, which plan to carry out successively> four exacerbations of the first cylinder, will attend pushing of the vertical vertical cylinders in length and amplity for all cases, .

But by analyzing, ideally the conflicts that should undergo the bending of the cylinder so that the niachine attains its maximum perfo rmance, we realized that the raise of the elevation of the cylinder must correspond to certain prerogatives, ~, that its enlargement must correspond to other intentions. What follows from this affirmation is to say that it is no only possible, but very sure, that the vertical exaggerations of the cylinder should not be identical to side increases I this one.

To give here an approximation, let us say that, ideally, the meeting of upper ares of the cylinder should reflect a good step :: age of the piston head, dc; such how to focus the compression at the center, and avoid 1õs double, see the triple pockets of compression of the chamber during ignition, of a manna which it should allow to preserve, for a certain time equal compression, so tello way to allow ignition exceeding briefly the dead time of the machine.

Moreover, it is known that one of the major difficulties of the motors;
consists in that, with a presumably equal pressure on the entire blade, one must train;
inflection of this one towards the front corresponding to 60 degrees = one hundred and twenty. To achieve this, the blades should be a little longer on one side, el this length should be delineated such way of not, conversely entail additional rotation orientation before.
The lateral extension the cylinder does not follow the same constraint as the extension ~ Rerticalisée. (fig 19) Therefore, a third degree cylinder curvature is needed. L: 'n cylinder of third degree is a cylinder which, in poly induction i would ask three heights of i, subsidiary ilebrequins. Here in Indeed, it would be a third subsidiary crankshaft, which would come increase one of the parameters and lower the other. Indeed, if the ori instalait on this structure bi rotating, a third subsidiary crankshaft which rotates at a rate of two turns per ri ' wolution of the blade, we could for example somewhat lowered the birotative height of the cylincler and increase its width. (fig.
20) Here conunent will be carried out 1eï mechanics higher esecommitted for in get the effects the specific cams above menfi.) nnes Mechanical by poly induction To achieve an alternativi thrust; different lengths of the ti ;;
against pistons of curse, we can, through the outside, unite the three gears of subsidiary crankshaft of a poly induction by a gear cc uronne, this gear being rr.iuni of successive cams of sizes equally equal. Consequently, it can be defined that the cams shorter enough in the center up and down, during downtime and up, and that the more long pass during the arches of the bulbs. When the macloin will be delivered by central crankshaft we can realize a second crankshaft whose cam number of different size will be doubled, and whose speed will also be double. Similarly, if the, me is located in the side of the machine, we can either provide for four members in pairs: -, opposite of niênie size, cu still, to unpack set of two opposing cams of different size, but this time rotatively mounted in the machine.

Third degree curvatures p: ir polycarved gears It is possible to obtain third-degree gears by gears polycamés. In fact, Polychrome gears can be made in very different ways.
can be arranged in the piston in the opposite direction, where in a hybrid position these two angles. By For example, one can make a polycamé engreg on four sides. Moreover, they can composting forms. For example, a gear of four: side can be paired with a gear six, which will keep the ratio, by e, xample two three machine, but also to produce more accelera-decelerations per turn.

In addition these subforms may not be asymmetrical, and therefore we can produce accelerations more and better decelerations of the elements of the machine. ( Fig. 26) Mechanics by cam translation, of the central eccentric, or of the support gear.
We can, to push back the rods of the pistons of curvature also to have resort to an eccentric central, round or multiform, whose movement will be translational.
eccentric, round, support indirectly on the pistons of curvature by the recourse to a parts intermediary, this parts being of different length on the sides and on the length., or if the polycames of the eccentric are of length diperent on the height and on the width, one will get the desired repetitions in the widths and widths of the rolls. (Fig.
22) This hypothesis leads us to decant the following idea which considers find that conventional production of the cylinders and piston of the machine, could realize the gearing of support in such a way that it achieves a translational dynamics. Fig 23 This will be possible if the sonmm of the differences between the support gear and eng engage induction, and the length of the crankshaft of the support of the trs.national gearing is equal to radius of the master crankshaft.

Therefore, two main kinetics can occur. On the one hand the i>, gears of support can be placed at the top, at the time of the temp. ~. dead top of 1 machine, or cumme in engines conventional, at the bottom. In the first case, it will come down at the same time the crankshaft master, and in the second case, he rem intera. It can be seen that in two cases, the translation is realized in the same area as that of the crankshaft.
In the first case, will have to reduce the size of the two gears, and in the second. the fat.

The two versions analyzed in downhill run give res. ultats interesting. In the In two cases, the gear in translation i is considered to be a machine of planetary support of ratio one on one, which allows the tra islation. The interest of this type of realization is that this one can be supported by a po ly induction stopped, namely p, ir a double crankshaft. of the during the orientation rotation of the iÅston can not incidenc.-indirect positional. By Therefore the positionnellc incidence, is directly from the crankshafts of the gear. In in other words, the blocking of the orientational effectives, positive and negative, turns into advantage positions, positive on all; the length of the blade.

Indeed, we can see, in <on any part of the room it forces the descent crankshafts of the support gear and simultaneously the crankshaft central. Otherwise if the crankshaft is arranged at the bottom, in the heel of the crankshaft central, he is moving in the same direction, he will find himself, going downhill, in scm end rear side.
As it will be rising, it will offer resistance to some sort of support.
the back of the piston, and the push on the back of it will be channeled on the rotation of the vikbrequin.
Like the gears are magnified, the support,) u the orientational armament di piston is will do more backwards, which will increase the nastiness of the machine.

For the cases, or the translation would be made in counter sense of the crankshaft master, it would design the gear of inductior. as a planetary gear, entering a rotational gear, which will be !: very difficult to achieve.

Several methods of training and synchronization of eng: i-enage crankshafts translation with respect to the master vilebreqjiin are possible. The method more sirnple of training consists simply of inducing each of them by an induction by gear internally, this internaediate gear being preferably shared by each of inductions. It can also be deduced from previous observations that the translation can also have positive effects, not only when it comes to the translatiori of the pale, in machines kinetic turbines with Clokwise, or when it comes to we come from the show, of translation of caxne pusher pistons of courbatare, or of translation of the support gear (Fig. 24) Second part of the present invention: recalibration of e Orientational and positional rotatk machines and turbines by redistiibution inductions Positional and Orientation Reminder of previous observations in this section To better understand the purpose of; this section we are sharing with observation reader that we have realized in relation to the mechanical presses.

The principal of these is the follow-up, if we observe the piston of a rotary machine, type post rotary, with respect to its crank support axle, this p: iston realizes an action retrorot.atiortnelle orientational. For example, for a rotary engine of triangular piston, turning in a cylinder in eight, where i attend a rearrangement of the order two-thirds of a turn per turn. Moreover, if we observe: the action of this piston by rapl: ort to its general rotation, we observe that the piston has when even advanced a hundred twenty degrees degrees by report to his initial position. .

This observation entails the following. If we look at the front of a rotatii piston; we see that he unfolds in relation to its crankshaft before retreating, while its previous folds on it even before unfolding.

These observations lead to a third. All the mechanics used to train a piston of a rotary machine proceed according to one or other of these observations and never the two simultaneously.

As an example, some mécarjics, such as the mono induction Wankel Island, or again mechanical by poly induction don we sum the inventor, distributed the piston, produce one on front power of the piston, .- t against the rear forces. other mechanical, such For example, the mechanics of Wankel's middle age, still by hoop gear, of which we are the inventor, favor the anterior part of the pesto, and produce counter efforts on the front part.

Another remark must still be made about the mechanics. It is necessary note that post-offensive type mechanics, usually reduce the piston to third, the rear third acting on the other hand, whereas the Nielsen by 4 of the retro type offe.nsif divide the piston into parts unequal, but much less unbalanced ..

Another finding must be made. While the mechanics post offensive try to directly drive the lm -sitional aspect of the crankshaft, the Retro-friendly canines, act, so to speak in chisel, by transforming the force orienf: ational in positional strength, One last observation must be made, and that is very subtle. If we correctly measure the volume report produced by the kinetic development of the positionally in relation to the orientation part, we see that the positional power is for two thirds of the total power. This can be seen more easily when observation of a machine basic turbinator. It is clear that the displacement of the piston alone, who corresponds the positional aspect produces two thirds of the volume, while that of the cylinder produces the other tieurs.

This leads us to say that whatever the mechanics used, the ratio Orientational positional the power that the piston develops with the recourse to this mechanic is unequal to the report positional and orientational of the partition of the volume and by cowquent of the power that the machine should have.

.Therefore, it can be deduced that not only in the mach: ines rotating, one of the most major is that the rear end or the front of the piston undergoes forces or against forces depending on the case, but also that the forces wt do not respond to Orentational report and POSITIONED;

Induction method of unitary orientaon In this section, we want to show that the character:
Orientation of the piston can to be achieved by reducing the number of samples, which will decrease the contra, .dictions Positional commented above ..

Indeed, if one supposes a member I in planetary set, and which one make a push on this member, one realizes that more this mernbre with a ray of retrorotatio n short, see shorter than that the rotation of the crankshaft centra I, plus rotational rotational force isional orientation is inferior and subject to the force of positional xctation. By ailleius more we extend this member, and that his radius of orienial filming becomes larger than ~. that of filming master crankshaft, the greater the backward force is powerful. (Fi ;; 28.1 and 28.2) Now realizing the piston in one piece with an orieniationnel member, we realize at the same time an excess of oriente force on the poskional force, who, although beneficial on one side of the magpie, one is downright negative on the other side.

Consequently, it should be noted that it will be preferable to Orientational control of a piston by a member himself mid-activated planetarily, this member being attached not rigidly to a place of the piston. any induct: we can be used to govern this plan member;
governor orientation.

By performing this type of induction, where it will shift the proportions of the effort provided on the head of the piston, and one's center of gravity; this one relative to the rendering of the explosion. We will be able therefore, coordinate more centrally and more accurately the center of gravity of the explosion and the rendering of the piston head.,.

Indeed, as we can see during the descent, the lxrtie back can work even if this is relatively weak, positively, and therefore, what is most importantly, the the central part of the piston may, instead of counterbalancing the eflects back on the piston, absorb correctly, in complicity with the party before part of the ex ~ ansion, whose course of action thezmodynamics is more particularly between these places. (: what about us?
come from to state it, one of the major defects in rotary engines is even more at the naechanical which perform guidance guidance as in kinetics same because most of these mechanics produce effn .; negative in the early part of the piston exploded at the pressure of the gas expansion, because the front part produces strong forces in leverage. We have shown repeatedly that it was possible to reduce these contn. strengths back, and that consequently, the power of the foas before the lever dimmed.

This realization represents the limit point of the previous ones in that the Orientational control exactly the same curve as the point of attachment 'free to piston would realize if it was driven by a fixed rudder. From a moment a diffi ence quite important will separate conventional induction, induction by a single point. At a induction by a single point, indeed the subsequent pushes at this point, whatever dircetes on the front of the piston, or indirect, on the back of the blade, will be superior but the distribution character orientated and positional of the USP will rather be depending on the point as such.

Method by complicity of orientational and positiii-nual identification This brings us to a second part of the present invention, in which will show that he is possible to relativize the orientational and positional character of the movement of a party compressive, like a rotary or turbinating machine piston.

First achievements As we have shown more lta.ut, it is possible to achieve the support gear of a rotating machine in a translational manner. Now, observing the acti, :) n of this one for a revolution of the machine, we realize that this is the same of the central crankshaft.
(Fig.27.1.1) This leads us to note that we can realize the eccentric, i: entral of a rotary machine in the form of an eccentric traaslationneL In this realization, we suppose a piece cylinder, later used as eccentric will be mechanically driven by two, or more, crankshafts, of the same length and rotating at the same speed and in the same meaning, these two crankshaft can be driven in this way by gears being steadily arranged, and simultaneously coupled to the same, gear connected to a central axis. We will be able the following rotatively the piston on this exce nical. When carrying out the mach.ine with a conventional eccentric, one cor: state that must be trained retrormally the piston by report to this one. Now, in the case of the present, as this eccentric; does not have any action orientational, but strietely a positional action, we dewa operate positively the piston relative to it. In this case, we will provide one or more crank pin viiebrequin subsidiary of an engr, mage of support, and one will couple this gear to that of the blade.

These gears will rotate in the same sense as the crankshaft e1:
will therefore involve consequently the piston pot rotativemert with respect thereto.

At theoretical level, the division of the teinps that we have just realized ~ ;; r is not new, she was stable in poly induction and in cicletic turbine machines clokwise. But what he There is again, it is the distribution these circumferential actions. In effect, positional action crankshaft, in secondary poly induction, will be made to the cent. re, and we will have more crankshaft master. (Fig 29.1) This will have serious consequences, including the main site.
at the reporting level of rotation. While in a pol ;, standard induction, the crankshaft master turns to reason of half a turn for a turn of the vilebr ;; quin quinaires, and that consequently gearing of induction are half the weight of the gearing supl: ort, here, support gear and induction motivate eccentricity, and a second series of engr-cnage support and induction will motivate the piston. These new er-grenings will be in a report either one in two, but one in three.

This will result in a point of anchoring or arming of the mental aspect.
piston more backward, and consequently decrease; i considerably against the the miachines, as well as the forces before needed to atract them. (Fig. 28.2) Therefore, if one realizes the kinetics of the cylindrical part and the dynamics of the piston, one realizes that the movement circular of that it is respected, but that while it; e move orientally two-thirds of all retrorotational compared to the millimeter of a standard crankshaft, here at contrary, for to maintain its speed, it must be post-rotated ac-this one.

This maneuver proves, out of doubt, that once again, it is possible to achieve a rotary machine by addition of velocity, and not by subtraction, such as this is achieved in the prior art. But there is more. E: i inverting the poly induction if,: lon its height, that is to say in positioning the positive motivation, namely that which produces:
two-thirds of the volume, center and motivation orientatiorn-ielle, the one that produces a third ilu volume, periphery, one restored to poly induction in a better ratio, and automatically in staging inductions. Recall that the retIisation of the central eccentric form translation has a a beneficial effect similar to that described above, namely that rotation on itself can not be obtained, and therefore, it can serve simultaneously. point character support Orientation of the piston, which nc: can be obtained in any induction carrying out the control of the piston by parts that can be realized simultaneously, simultaneously with their rotation around a general axis, a rotation around itself.

With this type of eccentric centril, perfectly translative, one realizes really of necessity to drive post rotationally * ~ e piston relative to it. appearance post offensive piston therefore appears here much more clearly than in any other induction. Thus, here, one simply adds to the crank pins of the support crankshaft.
of the eccentric gears that will be coupled to the piston induction gear. As these crankshafts rotate post rotatively, and that there is need for a post rotation of the gear piston induction and under piston, it will thus be possible to obtain the desired effect.

A finding of improvement i the forces can be found in progress downhill.
As can be seen, the oppcsitions between the retro forces functional and post rotational piston can not be realized. All forces are channeled into the rotation positional of the eccentric centr, he. Indeed, as we will be able find, by pressing the left before the piston, we realize, at the level of the rotation orienl: ational, a pull on the crankshaft that makes this action impossible, and consequently the force must to drift on positional rotation. We can see the same thing, even if we use the back of the piston. By moreover, in the beginning of descent, one acts more positively on the front side, without creating counter forces from the back side ..

Post rotation driven by the induct.on masters, and post rotation trained by induction of connplicité.

Several means can be implemented to train post rotativally the piston in relation to his eccentric axis As we have previously shown, we can achieve a gear of support not fixed, or retentive, but planetary, but well translational. (Fig. 27.5) This is another way of doing things better: zcepter energy in the engine rotatable.

We can go further in mor.trant than the crankshaft, or the eccentric a rotary engine can also be strictly translat: onnel. Indeed, we can build the eccentric of an engine rotating one using two or four crankshafts that will be mounted rotatively in the side of the machine in such a way that those if, as is the case for the piston engines turbines, are activated in the same speed and in the same direction. We can do this by example by providing each crankshaft with an induction gear and coupling each of these induction gears to wi central gear connected to an axis.

Subsequently we install on the May-ieton these crankshaft an eleanent of cylindrical shape that will serve as an eccentric machine. We will then mount the piss ton rotatively on this eccentric so that it is simultaneously inserted into the cylinder.
We will have consequently the armature of the piston is positionally we can to notice, the center of niouvemeni; translation of the eccentric, will describe a circumference identical to that of the center of a standard centric e.

By there will be in this type of niacriine a fundamental difference between the movement oritalization of its translational eccentric and that of the rotational of a eccentric standard. In fact, the r. orientational movement of the transitional xcentric is so to speak absent. This has a major occurrence on Mishine. In effect, whereas in rotary motors, standard, the pistg in moves against sense, to ~ have in a retro rotary way compared to its central eccentric, resulting in all the :: inductive speeding, in turn causing undue counter forces, here the piston moves in the same sense as the eccentric, that is to say post rotati vement So we can coor <'onner post rotativity the elements, such as gears in, making rotaxiormel movement orientational. .

In the previous example, the easiest way to train post ratively the movement of the piston will install on each at least one of the crankpins of the vili, brequin a gear of Support of a new type, that gold [could nonuner gear (I support orbital, which one will couple to the gear to the induction gear arranged rigidly on the blade.

When we have the items in the course of descent, we can see the benefits of a such method of supporting the piston. Indeed, as can be seen from the orientational force dysfunctional in mechanics; standard is here absent, is ic:
perfectly distributed. In Consequently, if we press on the front part of the piston we will produce, all as much on the teeth of the gear only on its center a positive ekt. By the way, if we have: :) pui on the back part of the piston, we will produce at most a top of the mechanics but we do not will not produce the cons undue forces that are found genetically in this type of macliine.

Moreover, what is here an important effect sought, one will realize, a proportionality of the thrust on the piston which is com- patible with the proportionalisatiori forces ay be developed, ie that the forces on the piston of such that two third of these are made by the positional training of the p: iston and a third by his Orientational training ..

We realized this last ve-rsion by respecting the cut of the poly induction but by redistributing it to the level of the elements. So so instead of make the crankshaft, as in the case of the first pre-induction, since it is sup-crankshaft master and supporting the piston, or instead of disposing of such a that they support the piston, as was the case in turbines, base, we arranged them here of such nunière that they support: the eccentric of the machine, the orientational movement being then driven by other elements.

Induction of complicity.

As previously shown, the piston induction gear was induced to party gearbox arranged rigidly on the crankshaft crank pins (:, the the eccentric. (Fig 27.5) Application to turbinat machines, es.

We can imitate this process, and apply it to the turbinali machines of type Clokwise., for balance the orientational force, here realized by the cylinder and the f) rce positional, realized by the pistons. For example we can make a central crankshaft and u: n or two crank shaft subsidiary, interrelated> chain or stem, (Fig. 29,2, 29.3 and 29.4) We will use subsequently, for example, the intermediate meshing of this indi.ictio0n as a father of peripheral support for driving the induction gear of the cylinder, this who will produce the retro rotation.

Generalization of inductions The purpose of the next statement is to make this subdivision of elements at all inductions. Indeed, we will be able to avoid any induction to lead movement strictly translational of an excen cal, then, starting from movement, induce post the rotational movement of the piston (Fig. 30) For example, we can induce the translational mecU ulation of the ex:.
by induction by intermediate gear, or by semi-translational gearing, or by gear hoop. In any case, it is possible to induce a post i = otation of the piston that realize the same advantages as those described in the translational example by poly induction stopped PPréCédent.

Enlargement of the notion of eccentric motivated planetary.

We have repeated to several people that one of the fundamental problems rotary motors depends on the type of induction with which it is realized. In one case, with the mono induction, we do not realizes that very little of the rotational potential of the machine, which counts, in terms of moving elements for a volume, while with others inductions, for example by intermediate gearing, the relapses should be completely Orientational guidance, whereas they should be proporte: onalised. The proclaains about show that we can arrive to realize one of the mechanics of rotary macros compatible with their volume construetion (Fig 34).

We can therefore state, following> last demonstrations that we can achieve it the excipient of a rotating machine in such a way that it turns into a different speed, orientationally, that of standard eccentric uri, and that this is not not litnitë to the only transitional configuration.

Indeed, it is possible to make an eccentric assembly of a machine that is producing everything first of all a piece of cylindrical form, which one will call! ra overexcentric and that one will then be mounted on an eccentri [connected to a motor shaft or to a motor crankpin of a crankshaft.
We will name this eccentric, eccentric heart or eccentric master. We will subsequently induce on eccentric a post or retrorotational movement by rappoit-t to the heart eccentric, and that induction is usually used to move the piston itself.
Even this piece, which we nominate as overexcentric, therefore has a circular movement coupled with movement on itself. . The surE-xcentric therefore realize a movement planetary.The piston will then be rotatively disposed of on this f: xcentric steering, and previously agreed, the necessary elements are available to carry out the governs orientational.

This governance will have this specificity. First, it can be made from the on eccentric. As the surexcentriciue will already have a pl movement, meta'vre, the movement planetary piston relative to the eccentric will be eccentric will be Generally weak. By example, one will install on the core eg, entric a gear, and on The eccentric govern a intermediate gear., which will eventually be connected to the gear of indluction arranged on the piston.
(fig 31, 32, 33.1) Control of the piston by the induction of the eccentric or by inducing complicity.

As we have seen, the motivation of an eccentric whose rotation on he himself will not be circumferential, as in standard or translational machines, but pluton planetary.
In all these cases, the piston does not have the same speed of retro or po st rotation that his eccentric. In some cases, it would have to accelerate it, and in others it would decelerate.

Differences in speed can be used between vi'.ebrake master and the eccentric cylindrical crankshaft to motivate an inter-gearing -mediate, or a double gearbox, which was then used to drive gears.
of the gear piston induction Moreover, it will be possible to drive this interme- diate gears, or c: e double gears intermediary arranged rotatively ir an axis itself arranged on the master crankshaft, in the coupled to a cage support gear rigidly fixed to the machine. The gear of piston will subsequently be rotated post rotorotativer.iient, the speed of sub rotation that will have been conferred on the cylindrical luin subvilebret.

But in doing so, we realize that we partially check the piston with induction type positional, and the other type of orientation.

This will have several advantages, and the two main ones will be the following ones.

We will move back significantly the arming point of the gear d: .- support crankshaft positional, and therefore 1-iiston. We will realize an inductio n orientational that will come to modify the reports of post rotatioiz and reversion of the inducaion positional, which will enable us to obtain exactly the ratio of post rotation and general reversion that we expect the machine.

Slinky movement We have already shown in our turbines that we could make a movement virtual piston that made sure that its total kinetics of the cylinder was realized in more than one short. To do this, we have it iter that if one chooses, intentionWally a report of rotation close to the tandard ratio, we will have little reconection orientation to perform, and yet, as the re-resolutions will require more im tower, we will have a report size of the gears that will be heavily modified, while demei.irant close standard reports.
As a result, gears gear ratios will inevitably be affected, while affecting slightly those of retro-tournagi: piston, which will consequently to be corrected easily. For example, in multi-explosion mi ~ tions, we managed to move back arming point of the gear cor sidérement while conserwmt a motion lying close to the motion clokwisre.

This is very important, because by quantifying the gross ratios of gears, we move back inking, coupling of the piswn and considerably modifying the proportions of forces, increasing the rear force, and dim: nuking the front lever forces.

It is the same here. The kinetics of slinky movement of a point taken hard 1'excentrique suvbasidiaire parmettra to realize wi rotation report whose e-agrenages will be of much more voluminous, in size of set, but not in one by reipport to the other, which keep the radius of the crankshaft E gal. As these dynamics me will change that little aspect rotational movement of the piston this will require little d4 ~ correction orientational.
As a result we will gain a lot on the point of inking, and we re will balance again more the ratio of effort of ch, each of the sides of the pistons by the induction orientational added, without that it does not cont.amin the whole system, by i.me too strong equalization of the thrust.

As a result, we will obtain exactly the right pushing positional, and desired orientation set.

It should be added that this is the most important element of present solution. So on uses to motivate planetary lic, overexentric, induction type post offensive, by example, a mono induction or an induction by poly induction, it will be possible complete with Induction of piton for example by c-gear hoop. We will complete by therefore a induction reduced in intensity of post-offensive tyf, by induction, also reduced in intensity, but retro-type offensive.

As a result, we will be able to achieve exactly the post-turnaround of piston without counter forces, and with as a set of recces forces proportionaliés to the quantum shooting positional and turning post orientational, or retro orient.atïorinel, depending on whether it is dune post or retro rotary machine, which one needs.

Application to turbinativi-ls machines Mechanical and turbine machine Similar mechanics can be realized for the machines: - binative.

However, some speci fi cations must be made. We know for example that in the machines turbines, one must realize the mechanics in function not of:
real cylinders but rather in function of the curvatures of cylindrical cylinders, realized by the points of pistons. Similarly here, peaks of muscle soreness, should be calculated in such a way as to receive from mechanical capable of performing modified virtual curves.

That being said, it seems to us that ~ mechanical downward induction could be realized from the overexcentric.

Mechanicals It should also be noted that the kinetics of the urexcentrics can all be more post rotary than the piston as more retrorotative. As a result, the induction gear the piston will have to to go according to the case in the same selis, or in the opposite direction. Dî, ns the measurement or kinetics with slinky kinetics, the orientational piston inductio: i will be little effective. More calculations In-depth studies will determine the best configurations for this.

Part III of the present invention, recalibration of currencies Orientational and positional of rotary and rotary machines by piston design Thermodynamics proves us Nature has her intelligence. In consequence, when Draw the head of the pi.ston with a straight line. We see that during the amo rce of the descent, this one sinks into the cylinder and closes, the cavity of it. This now gives I'imreesio that the the rear part of the piston is still and is compressed, and consequently, the engineers on intentionally drawn the part ai ~ interior of the piston of such fate that she gets married in the figure of cylinder. But even with such an external curvature, we are enc in this part a little room that after one of the explosi4 ~ n will close.

But, as we have just said, it is possible to realize which, if it do not produce any positive mechanical action on the rear part of the piston, do not produce no more action against force, rather a passive action. t:) r, the addition of a passive action, of a latent force to be completed by force before is quite rmjeur.

But this must be endorsed kinetically. We found qi; .e if we imposes on the piston, in its rear part, not a curve to the outside, but rather, to inside, under the bulebe before the cylinder at the level of the explosion chamber, the piston will move, and the cavity the result of this inner curvature 'na stand sour bulebe c, ffindre meeting bows, at high, thus contradicting the disguise of Ika chamber of conbwlion to this level, and at this point.
Preliminary calculations have allowed us to conclude that not only space could thus be maintained, but also increased slightly, even with erigriages standard, which can be aniplified with polycamé engren tges.

Therefore, we think that instead of trying to close this part of pisiton during the explosion, the mechanics associated with the present design of piston will allow to produce a positive explosion, and to make good use of the back of the piston for press the part before it i -lus later during the expansion nF:
really works post active Brief description of the figures Figure 1 shows some examples of differences between the theoretical thermodynamics and the practical thermodynamics. Only if, in theory, the same volume of compression and expansion of the gases leads to a similar amount of power, in practice <<ers mechanical can significantly influence the final results.

Figure 2 recalls, as briefly as possible, the main issues:
rotary engines, thermodynamic level, likewise, read the contributions that we have contribute to achieving ma.tière. This brief look will allow us to see the remaining problems, and identify how these can be solved by the present technical solution.

Figure 3 shows what is the interest of reproportionalising the thrust on the piston Figure 4.1 summarizes the principle: two mechanics by which we have to realize a better distribution of the thrust if ir the blade, this resulting to focus more than power in the center and the third before the piston, and not strictly, one hundred on the outer part, this which finally allows better access to the thrust of the explosion, which is developed priority to this place.

Figure 4.2 recalls the main ways in which we have so far managed to advantageously modify the shapes; compressive parts, either by polycammed gear, has , by superposition of crankshaft and inductance in b, by segment.Aion oscillating in c, and by poly rotary piston, conventional in d,,> ar poly turbine.

Figure 4.2 reiterates that one of the most interesting c onsformations is to delay the tip before the piston in the course of descent:, which has the effect of flattening the curve from the back part of this one, and to conceal that of the lower part. This is achieved twice a turn, we'll have a lowering the back part of k. combustion chamber, and a increase of its part before, in which it is possible to arrange the candle.
curvatures can be accompanied by curvature of the complementary pisto n, curved towards the rear, and curved towards inside, towards the front. .

Figure 4.2.2 shows the evolution of the volumes during the procedure piir deceleration acceleration orientational. We can see that the rear volute increases as we go.
the evolution of the cylinder made. This is reflected, mechanically by a progressive decline of cortex rear forces, obtained by polycamation or other acceleration deceleration means. The motf: ur is by therefore without volumetric loss. We will notice (read the shape before the piston dci it to be lowered for allow his entry into the ac celerative phase. Volumetric loss is product no longer in beginning of expansion but, as dar sn piston engine at the end of expansion.

Figure 4.3 recalls the various main concepts of engrewges polycamés, as well as the possibility to realize them with a number of degrees higher and out of phase.

Figure 4.4 shows an example of the intentional control of accelerations.
piston deceleration in some of its phases.

Figure 5 recalls a notion of b ~ ~ relating to rotating machines and which consists in that every point of a piston of a rotating machine, other than a ma - hine to piston movement translational, has a different kinetics specific to the dial in which it is find, and fit for the distance from the center to which this point is.

Figure 6 shows in a, a first geometric deduction that can flow last stated, that one could build two sets of vi: crankshaft and pistons realizing cylinders of approximately the same size, but with curvatures for one more soft and for the other more acute, realizing the first set;
crankshaft smaller and a bigger piston, and the second one with a bigger crankshaft and u: ne smaller piston.

Figure 7 shows the dynamics of the movement of the parts of the figure previous for a ride.
It shows that the decelerating accelerations of the pistons are different and that the center piston can produce a bigger impulse, compared, while the ~ piston outside allows keep a soft curvature.

Figure 8 shows that to obtain the efficiency of the coupling of pi, tones of rotary type, it takes keep the parts inside the pistons tight. Here, we use set of double slides , who will be able to keep the pistons linked to some difference in kinetics: kills these will produce.

Figure 9 rises that one could use the inner piston coinme driving element of conventional pistons, which would allow subtraction of the key rods poly pistons set, for which one would keep, for each one, only a slide of rac zordement.
.

Figure 10 shows that it is possible to subtract the differences c: acceleration deceleration side of the two pistons without any difference in movement vertical, realizing one or the two sets with the resort Here of polycammed gears, di-, such way that acceleration and deceleration of the two pistons are coordinated.

Figure 11 shows that it is not necessary to realize for the heavens pistons two commands different. Indeed, we can see that one of the pistons is disassembled in a relationship translational with respect to the other one can therefore ccimmander one of the pistons in the submitting to the other.

Figure 12.1 shows that it is possible to split the short piston into several pistons of body aches, which will simplify the fetus the watertightness between In this way we will be able to independently check each ends of the pistons.
It will be possible to modify laterally the parameters of realization of the curvature of the pistons of stiffness. Here, the pistons are c)) controlled by a main member mounted planetarily.
Each is slidably inserted in a cylindrical part cc-mportant a slide, this piece itself being pivotally or oscillatoryly inserted into each end of the piston.

Figure 12.2 shows that it is possible to subtract the cyRldres oscillating and insert in a strictly sliding way ~ the unitary pistons of courbatlare if we control the accelerations deceleration of the support member by polycammed gears .

Figure 13.1 shows the principal means of connection of the unit pistons of curvature and Piston heart pistons will soon be easier. The figure meiter the three main ways to do it.

Figure 13.2 shows that pivoting torso pistils will be connected to the same axis center of the machine.

Figure 13.3 shows in a and b. how to reduce accelerations decelerations in the good dial.

Figure 14 shows that when using eccentric, they can also be willing to unitary and peripherally, 91, still dynamically rt central 96. In this case, will see later that several dynam: ques can be used.

Figure 15 shows in a, that by some mechanical already comn) ented by ourselves,. we succeeds in bulging the cylinder either with these bulbs, or in these arches, then only in the cylinders polyturbine type machines, iion parvena.it to achieve cylinders bi-rotating type, successively realizing these two adjustments. , as shown in c but in mechanics by poly Pistons.

Figure 16 reminds us that if we carefully re-examine the cylinder rotary engine, one surrenders account that on the one hand, its upper curvature can be improved, and softened. Not only would this make it possible to achieve better compression ratio, but a: ussi, this would allow bring closer, especially on the back side, the design of the pisten's head that of the cylinder during the explosion, which would avoid the usual cylinder pain, uncompromising with a correct explosion.

Moreover, if we look at the standard cylinder, we realize that is usually a height ratio of seven ninth - which produces tremendously r, the loss volumetric. If the curvature of the cylinder is increased, it will mean that the piston ejitrera deeper in it, and that consequently the piston parts will realize against effects, and the parties before a better effect.

Figure 17 is a reminder of the notion of - first second wave, and third degree here represents this notion with the effect of superexposed poly-induction.

Figure 18.1 shows another possible cam dyruznique of pushed on piston rods of unitary curvature. Here, the cam ~ [the same number of sides as that of the piston, but realizes a planetary motion in the inverteous direction, which produces four consecutives faces.

In b of the figure, we find a ca not fixed but this time of faith sorting rotating, and who by Therefore, it will be possible to realize the anticipated trirotative fiie.

Figure 18.3 shows successively these three types of curvature. l:? na) on find, curvature standard rotary mono. In b) we find the bi-irotative curvature.
In c) of the figure found the curvature of sort rotational type, the latter being drawn exaggerated of course.

Figure 18.4 shows other exer. iple of cam allowing to reach indre these types of curvature. In a) the reverse dynamic cam is now double-buffered, then that the cam to The same meaning is almost tribal.

In 18 5, we see that we can desiior the cam as much as itself of form sorting, in taking into account, as already mentioned, acceleration and decelerations, as well as angulation of the rods of the pistons of unitary curvature. We will get then with a fixed cam, complex cylinder shapes.

Figure 19 shows in a) that one can also realize curves of third degree by polycammed gears. Here, while at the same time, there are three in two, the polycamation it will have a report d :; four out of six, which will result in four acceleration decelerations per revolution, which is the desired effect.

In b) the figure shows that it is possible to obtain a figure of third: ~ ie degree in a simplified way in adding a poly induction subsidiary to an element itself therefore even second degree.

Figure 20 shows that machir. are of retro-type in a ', i, and type poly turbines in b) can also be performed with the return to double curly;
obtained by the twinning of heart piston and pistons of curvature: ure unitary. In both cv's, this will increase their compression, which is here one of the desired effects.

In Figure 21 we show that the improvement of the shapes of positive effects similar for turbina machines i-- ~ es. Indeed, first, the best figure of the room explosion produces the same effect. Moreover, the lengthening of the piston by the exit of the piston of curvature produces an additional tingling effect on the cylinder in moving positively its center of gravity, and therefore the couple that it will clear around the axis centrat.

In Figure 22.1, we can look at each of the methods of E: support plus mentioned for turbines. First in the kinetic engines Clokwise, we can provide the cylinder of a fixed cam of almost elliptical shape and subsequently provide the against piston of stem curvature resting on this ellipse. We will then obtain the out and back in counterbalance piston.

In Figure 22.2. a spinning rod is made single stroke pistons by a central eccentric moving in a translational way, this support realizing a amplitude of translation greater than that of the piston core which has a.
the volumes of the already commented way.

In Figure 22.4, for a turbinal turbine with 1-s rods unitary stiffness pistons would be driven by cam, and would like to produce a sort curc rotating, we see that the cam must be made in eight steps.

In FIG. 23, it is shown that the curvature of the piston can be reshaped in such a way catch the explosion.

Figure 24.1 shows that when installing a member of faf;
planetary on a crankshaft any thrust on that limb, if its length does not exceed that of the radius of filming crankshaft, produces a ciu cular action on this crankshaft. Dars them rotary machines, this limb is the piston, and generally its extremities exceed by turning radius crankshaft.

In Figure 24 2, we give; two examples of such a procedure. In of the figure, a planetary unitary unit of contiSle of orientation is conducted:
pLanétairement by induction by intermediate gear. . In t-, the member is led by one. induction by mono induction Figure 25 shows that a conventional segmentation will have to be added to each of single pistons of curvature. However, it must be mentioned that we consider that the pistons units may also be fitted with helical coil segments in (b), or will be able to receive tangential oscillating segments as we have discussed them previously in c). These segments will be connected to the piston by: 'oulement, or by oouage gears polycamé, partially round, aru lué or rack in d).

In the present invention, we are reminded that the realization of oscillating segments and split or the suppo rt of daring segments and dg: doubled will also allow subtle way to achieve the lion falsifici of height and larguer clu cylinder.

Figure 25.1 recalls the notion of oscillation Figure 25.2 shows some ways of securing iriechanically movement rectilinear pistons of stiffness; . In a) we see that we can 3imply use bearings, on each side of each piston. These bearings can be replaced by gears. In (b) of the figure, oscillating supports are supple piston.

Figure 26, recalls in a, the main gears deeuositions polycamés., one producing accelerations of the piston on the bulbs clu cylinder, and the other in the corners.

Figure 26.1 shows that gold. could also activate the stems of pistons of stiffness unit with the use of a polyca whose movement would be translational B in the figure we recall the mechanics by pc ly induction starxlard, in which we have shown that The master could support two subsidiary crankshafts. This cutting helped realize that a peripheral translatienal movement can be adclined to a movement central circular to obtain the desired curvature of the cylinder.

Moreover, by matching this information, one can also oberver that installing a cylindrical element given on two central crankshafts, one had a movement rotational similar to that of an ex ,, standard entric, what mortre the Figures c) and d).
However, if these movements do the same positional shift, they have an aspect dynamic orientation very different. In the first case, each point of the cylindrical element produces exactly one circumference of radius identical to the circumference from the center point of the system. In d) we points are far from the center of sotournn. ~ Ge, plus the circumference is big.

Figure 26 recalls the notions of poycamation and shows that the year can realize these at third and fourth degree, which makes it possible to acceleration decelerations relevant.

Figure 27 reminds us that when I support machines motric: e post most standard rotary by mono induction, a third of the rear part of the piston acts against strength.

In b, of the figure, we see that the other forces are exerted rather mr the cylinder, in machinery turbines, and compared to the cent, -e, which produces little loss of energy, and that especially as the cylinder realizes the orientational part of the movement, the losses realizes to this level have a lesser effect.

Figure 26.2 shows the impacts read this type of new realiza- tion of the cylindrical piece of support brings, when these elements will be the supporting elements of a rotating machine.
In Figure 27.3, we see that it is quite easy to induce in simultaneous rotation crankshaft supporting the tranlational flow, fixing a gear, which gears will be coupled indirectly a third gear 934 pr, having to be fixed to a central axis Figure 27.4 shows the machine ai. dead time up, in cross-section, in, and in perspective in b) Figure 27.5 shows the elements eYi. downhill course Figure 28.1 shows the dynamics; pre-described elements, potz a ride of the machine. We sees that the central crankshafts 9'i0 supporting the eccentric tra nslational turn to the same speed, on the other hand, the induction drives arranged on their m turn on themselves and cause rotation of the engagement of the piston.

Figure 28.2 shows the advantage of this kind of (;:
mechanical support of the piston. Primarily, we see that even if the geomeletic relationships are respected, and that by therefore the turning point on itself of the piston, orientaticinnellement and positionnellelement remains identical to that of a mono inductir or any other other induction simple first degree, 980, cc cc reactions behind this point are partially countered by the fact that the coiiplage point of the inductance gear of the piston 981 to his Support gear stays further forward. As a result a, assigned strength back from filming point, despite the fact that it entails a retrocession 984, relies materially on a post-rotating turning point, there is more to an anaulation of forces that one creation of negative forces to propert were said. This negative energy saved is doubled by the fact that there is also economy of energy before necessary normal to neutralize it that will here be realized positively.

Figure 29.1 shows that this procedure can be adapted to turbinataf The gear 990 cylinder can result in a coupled peripheral gear assembly Has crankshafts. 992 These crank pins of these crankshafts will be equipped with gearing supporting the piston center gear, which will therefore perform a c inetic Translational.

Figure 29.2 shows that one can realize the machine with a vi: .ebrequin central. supporting the translational eccentric To c) mplete the mechanics of tran? cation, one dispose in the flank from the machine a crankshaft subside, and we will add his mane! tone to the eccentric. We will couple the central crankshaft and the subsidiary crankshaft of such, iorte that their action be identical, for example by a chau -e, a hoop gear, a E: gears intermediate. For finish, we add to the crankpin of the subsidiary crankshaft a engri nage of support that we will couple the piston induction gear.

Figure 29.4 shows that when the previous mechanicals are carried out to support parts of a turt-inative form machine Clokwise, the eccentric;
translational is realized from way confused with the piston, and the gear connection of the eiigrenages of crankshafts center and periphery can be neck, to that of the cylinder and perrn-cttre his activation in sense reverse.

Figure 29.5 shows that the radius of attack of the mechanical mechanisms turbinative, R1, is different from the one presented above, R 2 Figure 29.6 shows another example, in which the synchronicity (;:
crankshaft is insured by their coupling to a crankshaft ci ntral, by the recourse 'a third like a connecting rod 1.

Figure 30 shows that one can mechanize with any inducti (in one for one , the eccentric of a rotating machine, so that its movement is in motion translational.
Fans in figure a) n obtain a translational movement of the excent;
induction by intermediate gear, and in b), p ir induction by gear, water.

Figure 31 rises only in the mesi ire where the planetary active form is cylindrical, she can receive any other planetary dynamisati nt that only the translational dynamism, and that in spite of these modifications of retro or post-rotation Orientational, this piece will perform, like the translational piece, a positional rotation similar to that of a eccentric standard.

In this example, the part with u does not retrorot on the manetor of the crankshaft whose result that this piece turns on it even half a turn of the vilebcquin.
If it is about the piston, he should turn only one of yours. As a result reversion of the surplus is high, and it will be necessary to use a retroreflective filming of the piston in relation to this eccentric. Here for example, ion utHse two external iype link gear successive.

In Figure 31.2, the 1 ~ iston is mounted on the eccentric.
In Figure 31.3, we see the perspectives in perspective.

In Figure 32, we establish the orientational dyna nique of excenque planetary so reversed. To do this, we have placed on this eccentric a virtual piston, that we operate planetary, for example to c ~ = eer a virtual figure of exc;
retro-active four. As can be seen in this figure, the movement retrorotational the eccentric is greater than that expected for the piston. One will Therefore make an intermediate gear i uiissant the piston and this excenti.ique in such a way that this gear rotates post rotatively and restores the relative speed of the piston, whereas as one saw it previously, if the derotation speed of the eccentric e; t lower than expected for the piston, it will be necessary to add derotation by realizing an eni, xenage intermediate piston drive by the excei itrique which will work retrorotaïvely.
But the piston has always a rearward effect and avar t on this gear, that it is activated post or rétrorotativement. The interest of this section is therefore of find the way to magnify the support and induction gears of the eccentric, change the teat of the crankshaft and therefore the difference between the gears, what will show the next Fig.

Figure 34 recalls our synthetic planetaryizations motions: s, applied in machines turbinatives. In these we show that a planet-driven element can make a number of faces, but this time not con con: ecutive. This will enable you to gears while keeping between them a distance equal to that of the expected turning radius.

Figure 35 shows the interest of the latest procedures. The principal of this this is to back down the coupling point of the gears, which will make the counter-forces <<rrière really active more in back. This will increase moreover; the coupling up radius of couplagf:
gears. But the gain in direct knockdown reduction: huge. If this structure is:
surplus realized so polycamée what is shown in acomme in our first wire; ures, we'll have there a machine very fluid.

Figure 36 shows that if the piston retrorcation is unequal, this; who can be achieved by polycammed gear, and whether simultaneous induction of positioning and of orientation, some working differently, and others in we must develop a explosion which, at the time of death, i-arcera minus the piston forward, orientation, and towards center, in orientation reflexion, will force it more. We can therefore let the back work of the piston proportionally to the central explosion, and aiming at an explosion descending better located, for example by producing 1irtie of the piston.

Figure 37 shows in a, that the surface of the piston can be extruded in a variable of such way of producing a breakdown the explosion and expansioii appropriate for kinetics.
In b) of the figure, it is shown that s: we make a hole of each side from cylinder to level of the dead time of the piston, it will be possible to pull out the piston rings and replace with new, without having to open the cylinder, these holes being able to clogged by coins cylindrical.

FIG. 38 shows that with a suitable rear piston diameter, in which we realized an inner curvature of it, - ~ -010, this curvature will move towards washing downhill 3011, and in doing so, will come to test the closing of the cylinder I:
passage of the formed bulb by the meeting of the upper arches. 3012. As a result, comnie the watch the following due calculations surfa.ce relating to these spaces,: 1013,1'ear between these parties will not decrease, as in standard engines, but will remain stable, or produce light growth. This means that kinetically, one will be assured then that the machine i-st positive, even in his back parts. This is of the greatest importance, since we can deduce that in this part, the work of the rearward orientational force is started-, and that we would be wrong as does industry, to sacrifice the energy that this space could create:
by the support method by mono induction. The capacity Figure 39 shows that in coupling the notion of intra-back curvature of the piston and that of gear cylinder curvature; polycamé, (or other means acceleration and deceleration of the piston) we obtain a kinetics which not only produces no more compression after the idle time, this is the case, c the machines of the prior art, or still a handful of compression, as is the case in our previous figure, but increase gradual and significant volume> greater than the increase in wlume of the front part, for all the first part of the expans, one.

Figure 40 shows that these methods of guidagi can be turbines, in coupling the cylinder, by an induction gear, an inductive descendant, of which the peripheral support gear is attached to the sub crankshaft Brief description of the figures Description somma.ire figures Figure 1 shows some exempl -s of differences between thermodynamics theoretical and the practical thermodynamics. It is true that if, in theory, the same volume of compression and The expansion of gases results in a similar amount of power, in practice mechanical can significantly influence the final results.

Figure 2 recalls, as briefly as possible, the main faults rotary engines, thermodynamic level, as well as the contributions that we have been able to contribute to realize in the material. This brief look allows us to see the remaining problems, and identify These can be solved by the present technical solution.

Figure 3 shows what is the point of reproportionalising the growth on the piston Figure 4.1 mainly reminds us of two mechanics by which we have to make a better distribution of the thrust on the blade, resulting in focus more than power in the center and at the front third: of the piston, and not strictly on the outer part, this which finally allows to better acccess the thrust of the explosion, which is developed priority to this place.

Figure 4.2 recalls the main ways in which we have so far managed to advantageously modify the shapes of compressive parts, either by polycammed gear, has , by superimposition of crankshaft and induction in b, by segment, ition oscillating in c, and by poly rotary piston, conventional d) poly turbine.

Figure 4.2 reiterates that one of the most interesting is to delay the tip forward of the piston in the downhill, which has the effect of flattening the curve from the back part of this one, and to conceal that of the lower part. This coming true twice a turn, we'll have a lowering the rear part of I [combustion chamber, and uw:
increase of its part before, in which we can arrange the candle. I're ;;
curvatures can be accompanied by curvature of the pisto :: i complementary, curved ve: -s the back, and curved towards inside, towards the front. .

Figure 4.2.2 shows the evolution of volumes during procedure I; ar deceleration acceleration orientational. We see that the rear volume increases as the evolution of the cylinder made. This is reflected, mechanically, by a gradual decline in rear forces, obtained by polycamation or other means of de + acceleration. The word - ur is therefore without volumetric loss. It will be noted that the front shape of the piston is lowered for to allow his entry into phase a, celerative. The volumetric loss is product no longer in beginning of expansion, but, like a sn piston engine at the end of e: -: pansion.

Figure 4.3, recalls the various main positions of engrerings polycamés, as well as the possibility of realizing them with a greater number of degrees and of phase.

Figure 4.4 shows an example of intentional control of accelerations piston deceleration in some of its phases.

Figure 5 recalls a notion of b relating to rotat machines: .ves and which consists in that every point of a piston of a rotating hin, other than a m: Lchin.e to piston movement translational, has a different kinetics, nte specific to the dial in the qixel it is found, and fit for the distance from the center to which this point is trotuve.

Figure 6 shows in a, a first geometric deduction for arise from the last stated that one could build two sets of crankshaft and pistons realizing cylinders of approximately similar size, but with curvatures for one more soft and for the other more acute, er realizing the first set with a crankshaft smaller and a larger piston, and the second one a larger crankshaft and i;
smaller piston.

Figure 7 shows the dynamics of the movement of the workpieces.
previous for a ride.
It shows that the decelerating accelerations of the pistons are different.
and that the center piston can produce a larger impulse compared, whereas the piston outside allows keep a soft curvature.

FIG. 8 shows that to obtain the effectiveness of the coupling of the pistons of rotary type, it takes keep the parts where the pistons are tight. Here we use w: e set of double slides , which will be able to keep the pistons connected to some kinetic difference these will produce.

Figure 9 shows that one could use the inner piston as driving element of pistons, which would remove the connecting rods from poly pistons set, for which we would keep, for each one, only a coulisse of connection.
.

Figure 10 shows that it is possible to subtract the differences deceleration acceleration side of the two pistons without affecting the difference in displacement vertical, realizing one or the two sets with the recourse, i polycammed gears, such key way that acceleration and deceleration of the two pistons are coordinated.

Figure 11 shows that it is not necessary to realize for the d-cux pistons two commands different. Indeed, we can see that one of the pistons moves in a relationship translational with respect to the other We can therefore order one pistons in the submitting to the other.

Figure 12.1 shows that it is possible to split the shortened piston into several pistons of body aches, which allows to simplify the elements ensuring the watertightness between pistons In this way we can coi-control independently each one of the ends of the pistons.
It will be possible later to change the parameters of realizatio: :) the curvature of the pistons of stiffness. Here, the pistons are c:) ntrôlés by a principal member: al mounted planetary.
Each is slidably inserted into a large cylindrical piece a slide, this the piece itself being inserted in a pivotal or oscillatory fashion end of the piston.

Figure 12.2 shows that it is possible to subtract the cylindrical parts oscillating and insert in a strictly sliding way: the single pistons of curvature if we control the acceleration deceleration of the limb of support by gears;
polycamés.

Figure 13.1 shows the principal means of connection of the single pistons of stiffness and heart piston pistons will be able to start as early as 14, rs be simplified. The figure to master the three main ways to do it.

Figure 13.2 shows that swivel pistons may be connected to the same axis center of the machine.

Figure 13.4 shows that in the rifle or points of the pistols of aches do not accelerate and do not decelerate accordingly. ) in time, but rather partially successively, we can, by grinding them, realize them in a way each other.
Figure 14 shows that when using eccentric, these can also be willing to unitary and peripherally, 91, still dynamically and centrally 96. In this case, will see later that several dynamis can be used.

Fig. 15 shows in a, that by mechanical means already comm; -, owned by ourselves,. we succeeds in bulging the cylinder either with these bulbs, or in these ares, then only in the cylinders machines of the polyturbine type,) n was able to produce cylinders of bi rotating type, successively realizing these two augmentations. as shown -.nc but in mechanics by poly pistons.

Figure 16 reminds us that if we carefully check the cylinder rotary engine, one surrenders account that on the one hand, its upper curvature can be improved, and softened. Not only this would make it possible to achieve a better compression ratio, but more this would allow bring closer, especially on the back side; e, the design of the pistcin's head that of the cylinder during the explosion, which would avoid the doub the usual cylinder, not compaible with a correct explosion.

Moreover, if we observe the standard ~ = e cylinder, we realize that it is usually a height ratio of seven ninth, which produces a great deal of: - ~ loss volumetric. If the curvature of the cylinder is increased, it will mean that the piston will eritrera deeper in it, and therefore the rear parts of the piston will realize monris of against effects, and the parties before a better effect.

Figure 17 reminds us of the notion of first second wave:
third degree represents here this notion with the recourse to poly-induction sup õrposées.

Figure 18.1 shows another possible unique dyn cam cam on piston rods of unitary curvature. Here, the cam has the same number of sides as that of the piston, but realizes a planetary motion in the inver direction, which produces four conective faces.

In b of the figure, we find a fixed cm ae but this time of form tri rotating, and who by therefore will realize the f <trirotative anticipation.

Figure 18.3 shows successively these three types of curvature. In a) find, curvature standard rotary mono. In b) there is the bi-rotating type curvature. In c) of the figure on found curvature type tri rotai ive, it being drawn from: there exaggerated of course.

Figure 18.4 shows other cam followers to achieve these types of curvature. In a) the reverse dynamic cam is now double-protected, while the cam to The same meaning is almost triangular.

In 18 5, we can see that we can draw the cam as itself by itself sorting, in taking into account, as mentioned p: - recently acceleration and decelerations, as well as angulation of the rods of the pistons I unitary curvature. We will get then with a fixed cam, complex cylinder shapes.

FIG. 19 shows in a) that it is also possible to realize curvatures of third degree by polycammed gears. Here, while dumbing up gear of three in two, the polycamation it will have a ratio &, four out of six, which will result in four acceleration decelerations per revolution, which is the desired effect.

In b) the figure shows that it is possible to obtain a figure of third degree in a simplified way adding a poly subsidiary induction to an element itself planar, therefore even second degree.

Figure 20 shows that retrorotative type machines in a), and of type poly turbines in b) can also be achieved with double curvature i:
obtained by the twinning of heart piston and unitary pistons. In both cases, this will increase their compression, which is here one of the ffets sought.

In Figure 21 we show that the improvement of cylinder shapes has positive effects similar for turbinat machines, ves. Indeed, first, the best figure of the room explosion produces the same effects. Moreover, the lengthening of the piston by the exit of the piston of curvature produces an additional effect of te urnage on the cylinder in moving positively its center of gravity, and therefore the couple that it will clear around the axis central.

In Figure 22.1, we can describe each of the support methods more mentioned for turbines. First of all in kinetic motors Clokwise, we can provide the cylinder of a fixed form cam, ruasi elliptic and subsequently equip the against piston of curvature of stems resting on this ellipse. We will then get le3 out and back in counterbalance piston.

In Figure 22.2. , one carries out a t., rpe of repoussage of the stems of single stroke pistons by a central eccentric moves; in a translational way, ie support realizing a amplitude of translation greater than that of the piston core which has the volumes of the already commented way.

In figure 22.4, for a turbinator, whose piston rods unitary curvature would be driven by cam, and whose ion would wish to produce a coi, irbure rotating sort, we see that the cam must be made in eight con's.

In Figure 23, it is shown that the bending of the piston can be reordered in such a way catch the explosion.

Figure 24.1 shows that when: 'we install a member planetary way on a crankshaft any thrust on this limb, if its languor does not exceed that of the radius of filming crankshaft, produces a circular action on this crankshaft.
China: Rotary, this limb is the plunger, and generally its extremities exceed by much the turning radius crankshaft.

In Figure 2 we give two examples of such a procedure. In a the figure, a Planetary unitary unit of contnile of orientation is conducted planetary induction by intermediate gear. . In b, the limb is led by: induction by mono induction Figure 25 shows that a conventional segment will not be able to added to each of single pistons of curvature. However, it should be noted that consider that the pistons units may also receive; coil springs in b) , or will be able to receive tangential oscillating segments, which we eommented them previously in c). These segments will be connected to the piston by rc ulement, or by coupling gears polycamé, partly round, arqi ed or racked in d).

In the present invention, our tenon to remember that the realization (ie oscillating segments and duplicated or that of support of oscillating and unresolved segments will also allow subtle way to realize falsificat on height and to dump of cylinder.
Figure 25.1 recalls the notion of oscillation Figure 25.2 shows some me (ens to secure rn.bcaniquement movement rectilinear pistons of soreness ~. In (a) we see that we can > implement use of bearings, on each side of each pistons. These bearings can be replaced by gears. In b) of the figure, oscillating support t s supports the piston.

Figure 26, recalls in a, the two main positions of engreiiages polycamés., one producing accelerations of the piston pots in the cylindrical cylinder bulbs, and the other in the corners.

Figure 26.1 shows that one could also activate the stems of pistons of stiffness unitary with the use of a polycavie whose movement would be translational B in the figure we recall the mechanism by po: y standard induction, in lacquer1 (e we have shown that crankshaft may be able to support two subsidiary crankshafts, this cutting helped realize that a movement translatio wel peripheral can be adclitionned to a movement central circular to obtain the desired curvature of the cylinder.

Moreover, by matching this information, one can also observe that installing a cylindrical element given on two central crankshafts, one in ol had a movement similar to that of a standard excentric, which is Figures c) and d).
However, if these movements achieve the same posional displacement, they have an aspect dynamic orientation very different. In the first case, each point the cylindrical element produces exactly one circumference of radius identical to the circumference of center point of the system. In d) we points are, far from the center of sotournal, the more the circumference is big.

Figure 26 recalls the notions of oycamation and shows that o ri can realize these at third and fourth degree, this makes it possible to accelerate décélérationions relevant.

Figure 27.1.1 reminds us that rs of machinery support me: rice post most standard by mono induction, a tie; s the rear part of the pistori acts in against force.

In b, of the figure, we see that the cc ntre forces exert rather rather si.ir the cylinder, in machinery turbines, and compared to the centru, which produces little loss of energy, and that especially since the cylinder made the orientational part of the In the event of a loss, the losses this level have a lesser effect.

Figure 27.1.2.1 shows that from a point of view, the engines stiind has has one third of against forces, on the whole udder, while the engines turb: inatives of base has a perfectly equal force on his pist ~) n, and unbalanced on the cyâ [-dre, also because of a report about four out of five.

Figure 27.1.2.2 shows in b) that, according to the drawing of the pistons and cylinders of the prior art, the rear part of the piston and the cylinder, for the first phase of ssa descent seems to continue to compress, and therefore kinetic kinetics contrary to that of the energy expenditure of explosion and expansion.

However, in a, we see that the distance separating the rear tip of the center piston of the motor is gradually reduced p; w the folding of the piston on the crankshaft.
The mecanic therefore contradicts the kinetics, since the latter seems to produce job. We will see in the last flips that the courbi trees of cylinders to mechanical polycamés, associated with some piston bends made it out of this work instead of the deny.

Figure 27.2 shows the impacts of this type of new realiza-cylindrical piece of support brings, when these ele ments are the elements of supp + ~ -rt a rotating machine.
In Figure 27.3, we see that it is quite easy to induce in a:
simultaneous rotation crankshaft supporting the tranlational eccentricity, by attaching to + each gear, which gears will be coupled indirectly a third gear 934 poor be fixed to a central axis Figure 27.4 shows the machine with high dead time, in section tiransversale, a, and perspective in b) Figure 27.5 shows the elements and i downhill Figure 28 .1 shows the dynamics, pre-described elements, polished cr a lap of the machine. We see that the central crankshafts 9 50 supporting the axial eccentric turn to the same speed by the way, the gears c induction arranged on their mi meton turn on themselves and cause the piston to rotate.

Figure 28.2 mounts more) the advantage of this type of mechanics support piston. Mainly, we see that even if geometric relations are respected, and that therefore the turning point on itself of the piston, orientatically and positionelellelement remains identical to that of a mono inductii) n or any other induction simple first degree, 980, the counter reactions behind this point are partially countered by the fact that the point of this uplage of the inductive gearing of the piston 981 to his Support gear stays longer, forward. As a result a: force attributed back from turning point, despite the fact that it entails a 984 relies nma.tériellement on a post-rotating turning point, we thus witness more than one year of forces that one creation of negative forces proper. This negative energy saved is doubled by the fact that there is also saving of energy before necessary normally to the neutralize who will here be realized positively.

Figure 29.1 shows that one can adapt this procedure to the masters turbinataf. The gear of the cylinder 990 may result in gear gears peripherals coupled with crankshafts. 992 These crank pins of their crankshafts which will be provided with, -supportive gear the piston center gear, which will therefore realize a c: inetic Translational.

Figure 29.2 shows that one can realize the machine with a vile, -, brequin central. supporting the translational eccentric To understand the translation mechanics, we dispose in the flank from the machine a crankshaft subsüd; area,, and we will join his mane-the eccentric. We will couple the central crankshaft and the subsidiary crankshaft of such;
that their action is identical, for example by a chain e, a hoop gear, a gears intermediate. For to finish, we add to the crankpin of the subsidiary island a grape! swimming support that we will couple the induction gear of the piston.

Figure 29.4 shows that when previous mechanicals were not carried out to support parts of a turbo-shaped machine: native Clokwise, the eccentric, translational is realized from confused with the piston, and the connecting gear of the gears.
crankshafts center and peripheral can be coul k to that of the cylinder and peririettre his activation in sense reverse.

Figure 29.5 shows that the ray (the attack of the conver-tional mechanics turbinative, R1, is different from the one presented above, R 2 Figure 29.6 shows another example, in which the synchronicity of crankshaft is insured by their coupling to a contral crankshaft, by the use of a third party like a connecting rod 1.

Figure 30 shows that it will be possible to mechanize with any inductor.
one, the eccentric of a rotating machine, such that its movement is Lin translational movement.
In figure (a), we obtain a translational movement of the excel-induction by intermediate gear, and in b), p; ir induction by hoop gear.

Figure 31 rises only in the air where the planetary active form is cylindrical, she can receive any other dynamüsati Dn planétaiire that only the translational dynanvsation, and that, despite these modifications of retro- or post-rotation Orientational, this piece will perform, like the translational piece, a positional rotation.
similar to that of a eccentric standard.

In the present example the piece with i: does not retrorot on the handle of the crankshaft whose result that this piece turns on it even, a few times per turn of crankshaft.
If it is about the piston, he would have to turn only one tier; of retrorotation. As a result reversion of the excinent is high, and it will be necessary to icaliser a retrorotatig shooting:, nnel of the piston in relation to this eccentric. Here, for example, two type of link gear is used.
successive external In Figure 31.2, the mounting is mounted on the eccentric.
In Figure 31.3, we see the parts in perspective.

In Figure 32, we establish the orientational dynatiousness of exceryic planetary so reversed. To do this, a virtual piston has been placed on this eccentric, that we operate planetary, for example to show a virtual figure of eccentric retro-active four. As can be seen in this figure, the motion; ent retrorotational the eccentric is greater than that expected for the piston.

Figure 33 recalls our motions of synthetic planetaryizations, applied in machines turbinatives. In these we show - the element driven planetarily can make a number of faces, but this time not com ecutive. This will make it rude gears while keeping between them a distance equal to that of the expected turning radius.

Figure 34 shows the interest of the last two procedures. The principal of this this is to back down the coupling point of the gears, (e which will make the counter forces;
really active more in back. This will increase further, the rising radius of coupling; of the gears. But the gain in direct knockdown reduction es i: huge. If this structure is at surplus realized so polycamée what is shown in a) as in our first fi;, ures, we will have there a machine very fluid.

Figure 35.1 shows the interest of the last procedures. The principal of this one is to back down the coupling point of the gears, 4th which will make the counter forces,; urrière really active more in back. This will increase the radius of the coupling; of the 2004. But the gain in knockdown reduction say is huge. If this structwe is at surplus realized so polycamée what is shown in a)., as in our first fi fths, we will have a machine very fluid. The second interest is, to bring the piston, by the coupling, of preference , of induction post effective and retro el fective, to work, mechanically, in a manner proportional to its kinetics, which is the major difficulty of the michean presses.

In figure 35.2 we show na, that it is possible to train the intermediate gear leading the gear that is possible ~ to drive the gearing intemaédiaire leading to the gear of piston induction from a gearset support disposed, igidement in the center of the machine. As the external gear will be arranged on a mat sub crankshaft, and that the planetization speed of it is not identical to that of a standard crankshaft, or of a traniferous crankshaft, the gear set will be different, and depending on the case, that is to say, it is slinky rappelling backward in retrorotation more rapii or slower than the standard rotrorotation chosen, my is retrorotative or post rotary.

Figure 35.3 shows that the concept of crankshaft can be applied cylindrical to the machines of Turbine type. This crankshaft 3C DO can then have a cine-lique different from that of the virtual kinetics of the piston. And this kinetic will be preferable, a kinetics of slinky type, especially if the piston does not realize it itself.

FIG. 36 shows that the piston can be connected by means of a the gear to a crankpin located on the intermediate gear:> i this one is calibrated for one equivalent number per turn only the number of arcs of the cyliadre, or a double of this number. This will achieve accelerations decelerations without having to use polyvcamés gears.

Figure 37 shows in a, that the surface of the piston can be extruded.
variable way of such how to produce a breakdown of the explosion and expansio;
appropriate for kinetics.
In b) of the figure, it is shown that s: we make a hole of each side from cylinder to level of the dead time of the piston, it will be possible to release the conris segments and replace with new, without having to open the cylinder, these holes can consequently be clogged by coins cylindrical.

Figure 38 shows that with a suitable rear metric of the appropriate piston, in which we realized an inner curvature of it, 3 D10, this curvature will move: ra vers washing downhill 3011, and in doing so, will counteract the closure of the cylinder by the passage of the formed bulb by the meeting of the upper arches. 3012. As a result, as shown in following due calculations areas relative to these spaces, -1-013,1'ear between these parts r, will not eliminate, as in the standard motors, but will remain stable, or will produce i, only light growth. This means that kinetically, we will be assured that the machine E! st positive, even in his back parts. This is of the utmost importance, since we can deduce that in this part, the work of the rearward orientational force is started, and that it would be wrong as does industry, to sacrifice energy that this space could create, by the support method by mono induction. The capacity Figure 39 shows that by coupling the notion of intra-curvature piston and that of polycammed gear cylinder curvature, (or other means (Acceleration and deceleration of the piston) we obtain a kinetics which not only produces more than compression after the dead, as is the case, in machines of the prior art, or still a maintain of compression, as is the case in our previous figure, but a increase gradual and significant volume> greater than the wolume increase of the front part, for the first part of the expa.ns on.

This shows beyond any doubt that the mechanics we proposed to over the years and in the present invention have leu - corroboration kinetic, and pitr therefore that the concepts of thermodynamics relating to the volume and production of work apply here favorably.

Detailed description of the figures Figure 1 shows some examples of differences between the thern theoretical iodynamics and the practical thermodynamics. In the first in a) we see that while theoretically, parts compressive material producing the same compression fluid should be able to same energy thermodynamics, in practice this is different. Indeed, after a such statement, the compression of a smaller piston, naked by a crankshaft and a bieale plus long 1, should, always if the compressed volume is the same, give the same result thermodynamics, the same energy efficiency as if we had built the compression with the resort to a more big piston connected to a crankshaft pa - a connecting rod to a crankshaft must turning radius is more short 2. But in practice, if the co npression is performed by a big paus piston, the surface of piston and cylinder 3 offered to exp: osion is much bigger and direct heat exchange between the explosion and the material is much more important than if the piston is smaller. In Consequently, we have here a first example which shows that the final energy of the two identical compression volume engines can be very different in the convenient. In 3 of the figure, we find a motor with i more calibrated dimensions. By Elsewhere excess of a set of cylindrical piston re as presented in a dilute expansion 5.

In b of the same figure, there is another example of different thermodynamics, resulting from volume of compression and ignition, but with the recoi.irs to compressive parts 7 in comparison with a standard motor 8. In a second example, a given volume compression and expansion is achieved by the complicity of two pistons, inserted, as the industry has already produced it, in the opposite way in a single cylinder. Again there, if the performance theoretical of the two engines should ~ `be identical, the performance pr? itique will be different, since the Inert head of the cylinder stores more heat energy than the head of a cylinder.
active piston.

In the same figure, one may consider a third.
example of difference between theory and practice. Indeed, in a third example, the pi tone and the cylinder are not of cylindrical form 9, as is the case in a conventional motor, conventional but rather square shape 10. While theoretically, we can di: e that the pressure is equal on the surfaces of the pistons and cylinders, whatever their shape.
practice, we know today the mini-fest 11 phenomenon that the explosion produces, likewise that the fact that the explosion has a progressive origin and diffi ision. In.
therefore, the corners 12 of a square piston are later filled by pressure, and the pistons and cylinder perfectly rounded seem to be the most economical way of realizing the thermodynamic effort.
Figure 1 d reminds of cases of ceri: so engines built by p!
part of the cylinder relating to ignition on the side of the pisù in and not above 13. Encori: there, we will find notable differences between basic theory and practice. In depil of a compression and a equal pressure, and in comparison with ~. ~ ec a piston engine and cylin, be more conventional, 14, the two opposite sides of the head of the cider on the other hand large amount of heat which will not be realized in force of descent: 2.

In the same figure, we show <some examples of mechanization different parts identical compressive. At first we have a motor driven by an i + crankshaft and a standard connecting rod 15, then by a standard crankshaft l coupled to a sliding rod 14 , and a motor driven by supenosed crankshaft staging 17. Although possessing parts compressive identical, on certain mechanical aspects, these engines will be different. For example, the last two will have no low point, and will not be defeated.
angular piston connecting rod going downhill. In addition, the level of friction of the necessary to ensure the strictly rectilinear movement of the sliding rod, likewise the friction achieved by the moving, as straight as the seal piece uniting it to crankshaft will produce more than friction, and therefore cottage r not only unrecoverable but to cool, as well as total, the performance of the two motives will, in practice, be very different, and will depend on methods used to calculate them] .- fina.l. The same wnstatation applies for the double crankshaft motor. The gains made by the elimination low dead time, and the cancellation of the losses by angulatio ri of connecting rod, will be counterbalanced by acceleration more direct deceleration of the connecting rod, in strictly rectilinear motion, as well as by the friction caused by the gears necessary to drive the movement of the upper crankshaft.
Figure 2 recalls, as briefly as possible, the main d, E: Rotary engine faults, thermodynamic level, as well as the contributions we have, could have contributed to achieve in the material. This brief look will allow us to see the problems. remaining, and identify how these can be solved by the present solution tehique.

These defects are of three kinds, design, kinetics, and mechanics;

(a) the deficient design of the combustion chamber construction the explosion or explosions 18, rotational post rotational inefficiency (inelle 22 b) the square character of the udder 19 (c) the excessive length of the compressive panies offered to the explosion;
(d) the defect of the kinetics by: particular of the rear part of the;
during the descent 21 e) the dead time along the path 20 f) the rear imbalance of the oussée on the compress part: ive in progress downhill 23 g) the imbalance before the p (ussée on the compressivi part in the course of descent 24 h) lack of amplitude of the thrust before, due to lack; length of radius of rotation, age of the piston 25 i) too heavy (eccentric) mechanics j) too heavy a segmentation ~; 27 Recall that these defects lead others cascading, comine by example require it to add cooling systems, the great friction of the elements corner and side, and and so on. The correction of the basic defaults will lead to that of the cascading faults that in arise.

Figure 3 shows what is the point of reproportionalising the growth on the piston Figure 4 recalls mainly the mechanical ones by which :: we have achieve a better distribution of the thrust on the blade, resulting in focus more than power 32 in the middle and third of the piston, and not strictly on the outside, which ultimately makes it easier to accept the explosion of explosi expands priority to this place. We can summarize our previous work in saying that we have showed that one could, and this in several ways mechanical, raieux spread the thrust on the piston, partially or totally neutralizing counterforce; ï
back on the piston. In the Wankel motors, mechanized by me o induction, we find an important against force on pa the rear portion of the piston 28, and excessive leverage towards the end 31.
The center of gravity of these two opposing forces are very weak, and do not correspond to the center gravity the explosion, 32, and this despite the fact that the engineers moved it: -forward, by the candle later. . We managed to mitigate the back forces against these machines the price at to pay for this neutralization will have a decrease in the leverage before the machine. The total pushes will therefore remain the same, but we will have subtracted from the machine an important quantum of friction, because the ceiiter of gravity of receptivity nrr.economic corresponds better to the one for which we can determine an explosion. 32 The new liquidity machines will have allowed to support the piston by a single crank pin, which will eii for effect of subtracting only more friction, but also a lot of the pressure of oil necessary for good lubrication of it. This in turn will have reduced the Segment pressure side scrapers. It is besides this, read we also managed to produce at the kinetic level, by the turbines. Effectively, instead, by the necessity of to toggle orientationally the piston at its center in the machiiie standard, we realized the contradiction of the cylinder, and the gravity of it rctrouve directly in front of that of the piston, and therefore does not undergo this addition, or deportation Conventional machines. This gravity gap, which is the same for piston and the cylinder, is further back, and adequate to the explosior. . In the standa.rd rotary engine, the more we move towards the front of the piston, the more mechanical power is produced. By aillt: urs, plus we move away from the center of gravity of the explosion. For the same total general power, and for the same volume of expansion, we think it is ~ far better to move back the center of gravity, and position exactly where you want to position a positional rotation for two rotations orientation, about 58:, from the center of the piston, ir to achieve 1, explosion.
Among these mechanisms, we find the gear mechanism chauie, 34, and that by polycammed gears 35.

Figure 4.1 recalls the main ways in which we have so far managed to advantageously modify the form-- of compressive parts, either by polycammed gear, has , by superimposition of crankshaft and induction in b, by segmentî: tion oscillating in c, and by poly rotary piston, conventional in d l l iar poly turbine.

In this figure, we emphasize the notion of mechanics:
polycammed gears 36, 38, 39, that it was possible to regenerate accelerations decelerations retro character orientational rotation of the piston by: - realizing the machine with gears of support and induction said polycarbonate gears. These gears have the characteristic of not being round, but rather to make fig ares similar to those of the figui-es basic engines rotatable. When rotary machines are made with such types of gear, we note that the distance separating 1i ~ coupling point from the point of coupling of the gears center of the machine is, contrary to what happens when the machine is made with standard gears, variable. Therefore, we can arrange the-s gears in such a way to that the coupling point, at the top of the pen, be as close as possible from the center of machine. In doing so, one will accentuate: e pivoting of the lower point, and we will soften curvature of the cylinder at this point. i: and softening will allow, for a same cylinder, of change piston and crankshaft size ratios, by rapping out the piston and growing the crankshaft, Consequently, it will be eliminated, for the same cylinder, the exhibition area at the heat of the piston and cylinder lor5 of the explosion, which will improve:
machine performance It will also be possible to arrange the gears in the opposite direction, and on the contrary produce a bigger lateral displacement of the upper part of the piston during the top dead time, which will soften the upper part of the cylinder, and per = ttra to make a head of p iston more rounded.

In b of the present figure, we retrace the method by superpositi.:)n crankshafts. In the vileba equins overlay method, we showed that he was possible to support a piston by supporting it with an excel rotatably mounted on a first crankshaft. In the first case, for the word mrs retrorotative and rotary, one;
pass the crankshaft staggered inside the crankshaft merrier 40 and reduce the arcs of d (; scente in rotary engines, and increase them in arorotative engines.

Conversely, if one passes the crankshafts masters to the outside, post rotatively by compared to the master crankshafts 42, Dn increases the bulbs of the arcs;
post rotary engines, and increased penetration in the e: the corners of the piston tips in the retro engines rotatable.

In this figure, we point out that the use of segn = tents osciliants also helps perfect the drawing of the cylinder as a friend inducing the meeting angles of the arches forming the cylinder 43, and by enlarging the bulbs of (them 44.

In d) of this figure, we describe the method by poly-p.
rotary and conventional, which shows that in the engine rots, tifs, one can create on the excenti second litter and y attaching conventional pistons, preferably with turning radius will be greater than that of the eccentric, and that in view of joining, for each side of the piston, a set of connecting rod and piston 45, each of these pistons being installed in a cylinder iiisposé
in each of the sides of the piston.

In e) of this figure, we take a look at the notion of poly turbine 46, for which we have shown that this type of maclù ies had a cylinder whose characteristic was to be of rotary type. This means that the 4 cylinder curvature of this type of machines was between those of the post-rotating machines, the more convex, and that of the macl ines retrorotative more acute.
We also show that these machines were second-rate machines level, that is to say than during the mechanical operation of the palic structure of the latter, poly induction, one had to use two sets of superimposed veiled trees. We have subsequently shown that we could make the economy of these more complex mechanics.
showing that one could lengthen one of the mechanics of an element named rod of geometry, or again, serve as a central cam on which the rods supporting the hinges !, from the palic structure will be supported, Remember that these mechanisms involve difficulties, that this invention intends overcome. The first two mechanics include the same dielliculty in what that is improved on the one hand leads to gaps on the other hand. mechanics by superposition of the crankshaft is on this point eloquent. Indeed, when the vilebrecluin Subsidiaries and masters are both trained post rotativem.; nt, the bulbs of the ares is allotted. By elsewhere the dead time top is also lengthened, during the pa .. ~ sage inside the crankshaft.in subsidiary. Conversely, when the subsidiary crankshaft is on the inside during the descent, he ua addition of crankshafts at the top dead center. The curvature of the cylinder, at the bottom, during this top dead center is therefore very acute, and to weaken it must increase the piston by rapprirt crankshafts.

Figure 4.2 reiterates that one of the 4 most interesting fea-already made by gear polycamé, consists in delaying the pc integer before the piston in the course of descent 99, which has effect of smoothing the curve of the back part of it 101, and of l: omber that of the party lower 102. This being done twice a turn, we will have an abal the back part of the combustion chamber, and an augrr entation of its front part, in which we can Therefore arrange the candle 104. These curvatures can be a: -compagnées curvature complementary piston, curved ve, s back 105, and curved towards the interior 106, forward. .
The figure shows an example of intenlional control of accelerations deceleration of the piston in some of its phases. Here, for example, we intentionally the mid descent, a Relative deceleration of the piston by r Lembort to are crankpin. 101. G, sci will cause flattening of the curvature of the trajectory 102 the the rear part of the piston, el: par consequent curvature rear of the cylinder when the time is up. 103 the consequences on the third parite of the pisont and on the part of the cylinder being recluctive, are also interesting. In indeed, this part of the piston starts the compression. The curvature of piston kinetics at this location will leave his trajectory conventional, and therefore the cylinder will be at this point, more curved 104. The same The procedure will take place a half-turn later, which will make it possible to establish high, the curvature of the combustion chamber, which will have advantages in two ways, in that it will have been flattened backwards, and convex 105 to 1 front. taking into account that post work rotating rotational piston is worth thirty-three for the general dynamics of this type machine, we will have so the one curvature that will allow me to carry out an explosion between them at the time a movement positional and orientational movement. Moreover, this type of cplindre will limit for a period appreciable the release of chalei r in this part of the cylinder, this limiting the parties offered to untimely warming. The head of the piston 107 can marry, not after the explosion, as in the standard machines, but at the name of the explosion the curvature of the cylinder 106. In front, it can be lowered 108 without causing loss of compression since the anterior part has been narrowed. As a result, the ignition key of this type will be ideal.

Figure 4.2.2 shows the evolution of volumes during the procedure l: -ar deceleration acceleration orientational. We see that the rear vok me increases as the evolution of the cylinder made. This is translated, mechanically: by a gradual decline of creels rear forces, obtained by polycamation or other means of deceleration acceleration. The engine is by therefore without volumetric loss. It will be noted that the front shape of the piston has to be lowered for allow his entry into the a.rcélérative phase. Volumetric loss is product no longer in the beginning of expansion, but, as a result of piston engine at the end of expansion.

Figure 5 recalls a concept of tase relative to rotational machines and which is to notice that any point of a piston of a rotating shaft, other than piston movement translational, has a different kinetics specific to the dial in which it is find, and fit for the distance from the center to which this point is traced. Indeed, as we can see the figure, the further this point is located near the center 47, the greater the curvature of its kinetics is pronounced 48, plus the relative amplitude of the difference between its internal endpoints <<re and outside is strong.
Conversely, the more the chosen point is: located towards the outside 49, plus the curvature achieved by this point during a convolution of the ruler will be soft 50. For example, the kinetic of a point also varies taking into account the range in which it is located.
point located hard a line uniting the center of the piston and one end of the piston tips decried a similar form and in the same axis as that of C; Aindre, and will be as before, more acute or more soft, depending on whether this point is respectively closer to the center, or closer to the surface exterior. 52, 54 In addition, a C point situated on a pass line, the center of the piston and the the center of one of the sides, will describe if it is a sin-this time in a opposite angle to this one. Finally, a point between these two positions will also describe a similar form, more or less acute: but this time obliquely to the first two positions.

These observations make it possible to determine that the relative length of the piston of a rotary machine is small compared to its crankshaft length, plus, as we come to see him, the curvatures of the cylinder is exaggerated and becomes inadequate, but also, less the forces on the part back of it are important, and the more this part is active the ositive, which maximizes the power of the machine. It is therefore found that had it not been colarbure not appropriate cylinder, the energy of the machine will have improved, since for the same compression volume, we would have used a lower piston activated; ~ by a larger crankshaft, and we would have therefore obtained. not only a positive effort on the rear part of the blade, but also, a lowering of the area of exposure to explosive n piston and cylinder, thus reducing the heat exchange between these parts Figure 6 shows in a, a first geometric deduction pc) uvant arise from the last statements, according to which one can ,, build two sets of crankshaft and pistons realizing cylinders of approximately the same size, 56 but with curvatures for one softer 55, and for the other more acute 57, realizing the first together with a crankshaft smaller and one piston larger, and the second with wii crankshaft bigger and one smaller piston.

In b of the figure, it is assumed that these crankshafts have the same axis central and that the piston making the most smooth curvature will be extruded at its center, such way to allow the inclusion of the piston 59 achieving the sharpest curvature. Or.i suppose as each eccentric crankshaft assembly piston will have its own einsemble support gear and each of these assemblies must be proportionate to each of the eccentric and pistons. We will call the piston realized, at the curvature of the cylinder, the piston of curvature, and the piston realizing the effort of compress: one, the caeur piston, pu piston die compression.

Figure 7 shows the dynamics of the movement of these parts for one lap. We sees that the accelerations deceleration of the pistors are different and that the piston of the center can produce a larger impulse 61, compared 63, while the outer piston allows you to keep a soft curvature 60.
FIG. 8 shows that to obtain the efficiency of the coupling of the pistons of rotary type, it takes keep the parts inside the pistons tight. Here, we use urie set of double slides 66, which will be able to keep the piston connected: for some difference of ciri that these will produce.
Figure 9 shows that one could use the inner piston itself driving element 59 conventional pistons, which would make it difficult to remove the rods from poly pistons set 64, for which one would keep, for each one, only a slide of E!
connection. .

Figure 10 shows that it is possible to subtract the differences acceleration deceleration side of the two pistons without revealing the differences in their appearance.
vertical, by reducing one or the two sets with the recourse, i polycammed gears 72, of such way that acceleration and deceleration of the two pistons are coordinated.

Figure 11 shows that it is not necessary to perform for pistons two commands different. Indeed, we can obsf -rver that one of the pistons moves in a relationship transitional with respect to the other. We can therefore ccmmander one of the pistons in the submitting to the other. One or the other. two pistons may be the piston who will realize the basic training mechanics, and that is why we will name it the tractor piston. He will be therefore controlled semi-independently, or e-ncore, it was the piston of curvature which realizes the orientatioil of the piston assembly. In inslallera on the case, the crankpin of heart piston support was located above, in such a way to achieve a higher amplitude of it. In this version, the piston of curvature is the pisto; z orientational tractor, and the compression piston is the towed piston.

We can produce the reversal of this situation, by first realizing the induction of the piston heart, which will be, then simultanémenrn the tractor piston. From then on i; nstatlera, this time in a shorter radius, a second m.neton 68. 70 the basic eccentric of the piston tractor, whose radius will be shorter, in such a way that the stroke piston: realizes a more stiffness soft.

The figure starts from the previously stated idea that, the rarest Orientational compressive parts can rather be done on the piston corur, we can find that one will be able to break up the piston of piston curvature without difficulty.
of single curvature.
An observation will allow con; tater that the piston tips realize , One with respect to the other 67, a translational movement168. We can control the piston in connecting these spikes by small crankshafts trained; rotatively by engrena; es, an example is shown in B. 69, 70, 71.

On the other hand, in c of the figure, we can see that we can also assume heart piston and piston will have the same center: 800. From then on we will be able to connect to a crankshaft 801 subsidiary mounted on the heart pistort to the oscillating piston of curvature by the use of a bietle 802, or a cam with a coulis: -se. This subsidiary crankshaft and this cam can be activated by an induction gear attached thereto and a support gear being set the eccentric, or else a polycammed gear fixed rigidly to the side of the nxiteur. As the piston of bending and the heart piston a common center, we can ilisérer one to the other by additional arc-shaped element corresponding to the oscillations, which is shown in c).
Figure 12.1 shows that it is possible to break up the piston in several pistons of Unit aches 73, which will help to simplify the elements sealing between In this way we can independently control each of the ends of the pistons.
We can then modify laterally the parameters of realization.
Piston curvature of stiffness. Here, the pistons are controlled by a main member nwnté
planetary 76.
Each is slidably inserted into a cylindrical piece having a slide, 64, 75, this piece being itself inserted in a pivoting or oscillatory manner in each end of piston.

Figure 12.2 shows that it is possible to subtract the cylinders oscillating and insert in a strictly sliding way the unitary pistons of courtbalure if we control the accelerations deceleration of the support member by engrenal =; es polycamé 78.

Figure 13.1 shows the principal means of connection of the single piston.
of stiffness and heart piston pistons will soon be easier. The three priricipales achievements of this procedure will be as follows. Dai is a first case, we will link each of these pistons being linked to the piston by oscillating parts cc taking a slide 80. Datis a second case, each of these pistons being at the top inserted into a -. single slide of the piston of compression 83, and connected to the bottom, crankshaft by a second cow 83. In a third case, will replace the association crankshaft slides, by an eccentric and a stem 87. Moreover, crankshaft or cam, or sliding part of attachment. 86 may be subsidiary, 81, central, 82, Figure 13.2 shows that pistons with pivoting curvature will be connected to the same axis of center of the machine. It will produce; therefor accelerations decelerations side. Who will improve the curvature of the cylinder, reducing the exposure surface to the ex-erosion and increasing it in downhill course.

Figure 13.3 shows in a) that the mechanical accelerations produced by connecting rods are not in the same dial as the accelerations natural decelerations :, from the piston.

Figure 13.4 shows that to the extent that the tips of the pistons, ns of aches do not accelerate and do not decelerate correipondantly in time, but rather partially successively, one can, by marcelant, realize them in a way enbouvetée each other.

The figure shows in b that if we veirt achieve accelerations mechanical hazards, it is up to say without polycamé gears, and without splitting the pLskon, we must, as shown in b), perform a transverse directional induction to the system, d: -, such that these accelerations decelerations be iians the same cadranc that those of the piston.

Figure 14 shows that when using eccentric, these can also be willing to unitary and peripherally, 91, still dynamically,; t 96. In this case, will see later that several dynamics can be used. Finally, these cams can be rigidly attached to the sides of the machine 98. Taking into account the acceleration and deceleration of the piston, the angle of the rods of stiffness pistons: 73 realize the shape of cams depending on the cylinder res we want to get.

FIG. 15 shows in a, that by some of the mechanics already comr.i iented by ourselves,. we succeeds in bulging the cylinder either in these bulbs, 101 in this case 102, while in the cylinders of polyimine 103 type machines, it was possible to use cylinders type bi rotating, successively realizing this> two increases. 104, as shown e niais in the mechanical by poly pistons. In fact. We have noticed that each of these mechanical devices achieve the same number of fluctuations, or correction of cylinder by turn that eelui; ares. As a result, the bulges brought from the machines can the being only under one angle to the faith s. For example, during the gear realization polyamines, if we have the gear in the direction of the piston, we can:
encounter curvature of the cylinder, but we do not improve the descending effect of departure.
Conversely, when has the gear in the direction of the pistons, it improves: 'effect descending but the curvature of the ares become too pronounced. Results similar situations arise the production of machines by crankshaft etching. Lor :; than , for example for post rotary machines, the vilebrecl uins are superimposed in ha.uteuir during from the top dead center, and that the subsidiary crankshaft passes inside during the descent, the compression is higher, but the curvature of meeting wcs very pronounced. Reverse, when the crank shaft Subsidiary goes to the outside and reads the actual addition of crankshaft is done laterally meets the ares of c ylindre is sweet, but expaa-sion undergoes contrary forces on both crankshaft.

Moreover, it is important here to inspect the cylinder of poly turtines, who, realizing a curvature that we have previously challenged as bi rot, ative, succeeds to achieve effects positive, simultaneously at the top and bottom of the cylinder. Unfortunately, the pistons surface component of the palic structure of these machines is too short, therefore the volume of compression is too small Figure 16 reminds us that if we pay close attention to the cylinder of a rotary engine, one surrenders considers that, on the one hand, its upper curvature may be improved, and softened 109. No only this would make it possible to achieve better compression ratio, but also, this would allow to bring closer, especially on the girrière face, the design of the piston head of that of the cylinder during the explosion, which will avoid the usual double cylinder, little compatible with correct explosion.

Moreover, if we look at the standard cylinder, we realize that is usually a height ratio of seven ninth, which produces a great deal of loss volumetric. If the curvature of the cylinder is increased, it will mean that the piston will eritrera deeper in it, and that therefore the art parts of the piston will realize monris of against effects, and the parties before a better effect. 108 Figure 17 recalls the notion of curvatures of first and second third degree This notion is easier to understand i; n using the notion of poly iniluction. If we turn planetarily a first engrenagic and that we observe during a turn of rotation, for example a tooth of it, it will be seen here that it describes a trajectory, similar, according to gear ratios chosen, the curvature of a rotating machine, basic.
That's what we can observe in a) Moreover, if on this piece, one pc could install a second sub =
driven rüequin planetary, and that one observed the kinetic of his crankpin, one.
would notice, according to the report chosen, that for example one could soften the shape of the cylinder by bringing out the crankshaft for the period of arcing, which will have the effect of soften them, which is shown in b.

In addition, there may be a desire to increase two successive increases in volume, one in the encounters of the bow, and one in the bulbs. We would then need achieve a third correction, which is shown in c. Of course, such manipulations would train superposition of crankshaft and will be: unachievable, industrially. These examples had the purpose of this is to show the type of cylinder that we can tend. The flexibility of cams that we have:., shown above will achieve these complex figures with great simplicity.

The figure shows that we can realize in complicity a piston core of curvature of first degree, and unit pistons of cc second-degree groove. For this do, we will call back that we have already shown that it is possible to support the palic structure of poly turbine, that machine having a second degree curvature, by subsidiary crankshaft having a geometric addition I, these crankshaft being mounted planetary and retrorotatively to the crank pins of a central crankshaft. Here, these 1, the crankshafts will be realized from way confused with the pistons of curvature, and will realize consequently the stiffness desired.

But by analyzing, ideally, the costs that the curvature should undergo of the cylinder so that the niachine reaches its maximum degree of perfonnance, one realizes that the raise of the elevation of the cylinder must correspond to certain prerogatives, whereas its enlargement must correspond to other intentions What follows from this statement is to say that is no only possible, but certainly that the vertical exaggerations of the cylinder should not be identical to lateral increases of it.

To give here an approximation let's say that, ideally the meeting of the arcs of the cylinder should reflect a good pitch of the piston head, tolle how to focus the compression at the center, and avoid l. s double, see the triple pochc7ss of compression of the chamber during ignition, as it should allow to keep , for a certain time equal compression, so tellc manner to allow aIluriuriiage exceeding briefly the dead time of the machine.

Moreover, we know that one of the major difficulties of rXative engines consists in that, with pressure supposedly equal to the entire blade, we must inflection of this one towards the front corresponding to 60 degrees one hundred and twenty. To achieve this: i, the blades should be a little longer on one side, and this length should be determined in such a way not, inversely to drive of surcl, arge rotational orientates lle before. The lateral extension The cylinder does not follow the same constraints as the -rersatile extension.

Figure 18.1 shows another possible cam dyamic:
piston rods of unitary curvature. Here, the cam 302 has the same number of sides as the one of the piston but realizes a planetary motion in the opposite direction that produces quatrc; sides consecutive 303.

In b of the figure, we find a ca fixed me but this time of f, rme sorting rotating, and who by Therefore, it will be possible to realize the anticipated trirotative l-Drme.

We can deduce from the preceding thread: ure that if one hears modifies cylinder curvatures successively in encounters (, the bow, and in the bulbs, one will deira multiply the number of corrections. Therefore, for the curvature of two arcs, one must achieve four corrections, therefore realize a hybrid curvature between curvature in two sides and one curvature in four sides. This is what we call a curvature sort rotataive.

Figure 18.3 shows successively these three types of curvature. In a) find, curvature standard rotary mono. In b) we find the bi-rotating type curvature. In c) of the figure on finds the curvature of sort tri rot; itive, this one being drawn so exaggerated of course.

Figure 18.4 shows other examples of cams that can be used to types of curvature. In a) the reverse dynamic camõ is now double protected, while the cam to The same meaning is almost trianic in form.

In 18 5, we see that we can inert the cam as much as it tri-rotating form, in taking into account, as mentioned 1 previously acceleration: and decelerations, as well as angulation of the rods of the pistom of unitary curvature. We will then with a fixed cam, complex cylinder shapes.

Figure 19 shows in a) that oi i can also perform curvatures of third degree by polycammed gears. Here, while meshes of rappelling from three in two, the polycamation she will have a report <: e four out of six, which will cause-ra four accelerations decelerations per revolution, which is the desired effect.

In b) the figure shows that one can get a third-degree figure in a simplified way adding a poly induction subsidia ce to an element itself plan ': silent, therefore l.ui even second degree.

Figure 20 shows that retrorotative type machines in a), and of type poly turbines in b) can also be achieved with the: double curvature obtained by twinning piston core and single curved pistons. In both cases, this will increase their compression, which is here one of the ~ Cffets sought.

In Figure 21 we show that the improvement of the cylinder shapes has positive effects simiiaires for turbine engines. Indeed, first, best figure of the room explosion produces the same effect ~. Moreover, the lengthening of the piston by the exit of the piston of curvature produces an additional heating effect on the cylinder in moving positively its center of gravity, and therefore the couple it will clear around the axis central.400 In figure 22.1, we can deconfide each of the support methods more mentioned for twirling engines. First of all in kinetic motors Clokwise, we can provide the cylinder of a fixed cam of almost elliptical shape and subsequently to unite the against piston of curvature of stems resting on this ellipse. We will then obtain the out and back in counterbalance piston.

In Figure 22.2. it is possible to carry out a piston rod pushing pattern of single curvature by a central eccentric moving in a translational way, this support realizing a amplitude of translation greater than that of the piston core which aixgment the volunnes of the already commented way.

In figure 22.4, for a turbinatious mactiine with piston rods of unit curvature would be driven by cam, and don ~, ion would like to produce a co urure rotating sort, we see that the cams must be made in eight colors.

In Figure 23, we show that the; Piston bend can be realized in such a way catch the explosion.

Figure 24.1 shows that when installing a planetary member on a crankshaft any thrust on that limb, if its length 402 does not exceed that radius filming Crankshaft 403, produces an actior: circular on this crankshaft. In the rotary machines, this limb is the piston, and generally its extremities far exceed the turning radius crankshaft. So, to counter this problem, you can make a member unitary planetary directional orientation in a), this being a cowboy, not the piston, to connect the end to the piston, in one of its points in b) or in the one of these Listed in (c) In the counter-effects of the rotational mictors will be canceled. Ili will result from the back parts of mechanical blockages, denuded against effect, which will be used notable improvement in this type of machine.

In Figure 2 we give some examples of such a procedure. In of the figure, a Planetary unitary contrc member of the orientation is driven planetary induction by intermediate gear. Ei-i b, the member is led by ia.n induction by mono 502. In both cases, the unitary orientation member is linked to the piston 501.
It should be noted that the place of connection can be chosen in any sedion of piston, and that it is it is preferable that it be made from a joint including a in such a way that retain only the lateral aspect of the referral. We are pe example find that when the place of attachment is so close to the center of the side, there is little rotational incidence thrust, and that mainly 1 positional incidence is coriservated.

In addition, note that all in.iuction remains possible to activate member planetary orientation, which will be highlighted in one or more points at piston.

Figure 25.1 shows that a conventional segment na) can be added to each of single pistons of curvature. However, it is worth mentioning that consider that the pistons units will also be able to receive helicoidal segments: x in b), or will be able to receive tangential oscillating segments, which we have previously in c). These segments will be connected to the piston by rc ulement, or by ccuplage gears polycamé, partly round, arqi ed or racked in d).

In the present invention, our tenoris to recall that the realization of oscillating segments and split or suppori of oscillating and unstuck segments will also subtle way of achieving height falsification and dropping cylinder. Indeed, during his passage in the ares, the lowering of the forward passage of the segment may be increased, and compensated by the rear part. This will have the effect of subtracting a part reports of encounter unacceptable ares of rotating machines, when they are mounted with crankshaft longer. In addition, the width of the section segmenl:
will force the increase of the amplitude of the bulbs of the cylinder, which is also a desired effect, hey Figure 25.2 shows some tools for nechanically securing movement rectilinear pistons of curvature; In a) we can see that we can simply use of bearings, on each side of each of the pistons. These bearings can be replaced by gears. In b) of the figure, oscillating support brackets supl;
piston.

Figure 26 reminds us of the notion of polycamation, and shows that we can to realize polycamations of third, fourth degree allowing re <<read acceleration various decelerations of the machine Figure 27.1.1 shows that, according to the mechanics by which the piston movement of a rotating machine, the ability to receive it is very different. In aO in mono Induction and poly induction, the rear third of the piston acts in contrf ~ force, while the front part acts in effect of leverage. As for the central part, it neutralizes, against the forces of the rear prtie.

In b) of the figure, the intermeshing gearing Wankei, and induction by hoop gear of which we are the inventor. In the first place, the rotational force The orientation is distributed evenly over the piston.
In the second, one more much of the reception force is located in the back of the piston.

Moreover, for the same piston, Lii, distribution of the force of reception is also diofferent depending on whether it is a post otative machine, or a retorative machine.
In part c of the figure, we see that a mono post rotary induction controls the iston and that the counter forces back are third. In the machini, retrorotative, four cylinder listed, the report of the gear is three in four, and the piston induction gear is external type.
The majority of the receiving force is on the rear part of the pistcene for a percentage about three quarters of it.

Figure 27.1.2.1 shows that from this point of view, the engines stand in has one third of against forces, on the whole udder, while the engines turb: native of base has a perfectly equal force on his pisi on, and unbalanced on the cylinder, Jre, also because of a report about four out of five. This motor should produce less friction. by elsewhere, the cylinder, producing one third of the expinsion volume, should produce a tier; of the power The push of the posterior part of the cylinder are superior to that of its part the interior, not only because that it is wider, but also because the action descended from the rear part of the cylinder is gonui-iée by displacement laté: -al front of the piston. We will see that if the piston is drawn suitably, as shown in Figure 38 and 39, if this is done together with polycammed gears, and that final, nente one induces separately.- the cylinder and piston, one will have one machine whose v ~) lummetric losses will be nonexistent ::.

in that when supporting post-rotary machinery the most standard by mono induction, a third of the rear part of the pistoii acts against force.

In b, in the figure, we see that the other forces exert themselves rather on the cylinder, in machinery turbines, and with respect to the center, which produces only a small loss of energy, and that all the more so as the cylinder realized the orientation part of the movement, the losses realizes to this level have a lesser effect.

Figure 27.1.2.2 shows in b) that according to the drawing of the pistons and, cylinders of the prior art, the rear part of the piston and the cylinder, for the first phase of; ssa descent seems to continue to compress, and therefore to a kinetics contrary to that of the energy expenditure of explosion and expansion.

On the other hand in a, we see however that the distance separating the rear point of the center piston of the motor is gradually reduced by the folding of the piston on the vilc-brequin.
The mecanic therefore contradicts the kinetic, since it seems to produce job. We will see in the last few digits that short of cylinders mechanics polycamés, associated with some piston bends make it count of this work instead of the deny.

Figure 28.1 shows that when installing a planetary member on a crankshaft any push on this member, if its length does not exceed that of the radius of filming crankshaft, produces a ciri action, ulaire on this crankshaft.

In Fig. 28, we give two examples of such a hard problem. In a the figure, a planetary unitary member of control of the orientation is conducted planetary induction by intermediate gear. . In b, the member is led by a nduction by mono induction Figure 29.1.1 shows that one could also activate the stems of pistons of stiffness unitary with the use of a polycarbonate 900 whose movement translational 901.
In b of the figure we recall the -nechanical by standard poly induction, in which we have shown that a master shave 902 could support two vilebi = equin Subsidiaries 903. This cutting enabled us to realize that no translational movement px;
can be added a central circular motion to obtain the desired curvature; of cylinder.

Moreover, by matching this information, we can also observe that installing a cylindrical element given on two central crankshafts, there was a movement similar to that of a standard eccentric, which Figures c) and d).
However, if these movements perform the same posional shift, they have an aspect dynamic orientation very different -cnt. In the first case, each point of the cylindrical element produces exactly a circumference of identical radius to the circumference of the center point of the system. In d) all the points are ~ away from the filming center, plus the circumference is big.

Figure 29.1.2 shows the impacts that this type of new achievement of the cylindrical piece of support brings, when these elements will be the elements of deletion of a rotating machine. Of In fact, we will have here a rotati-e machine whose distribution of the movement orientational and Positioned motion will be reversed + .; compared to staniard machines and poly machine Inductive. Compared to the machine; standard, the piSton movement will be orientationnellemt addition to the motion of the crankshaft, and not subtracted from it: is the ace normally. By relationship to the nia.chine poly inductive% rotatormal motion will be peripheral and non-centric as is the case generally. In fact, this means that: if one actuates the piston of a standard rotary machine by means of a gear that would fit on the eccentric, we should then use an inter-channel gear that achieves an action rétrorotative. In court of descent, we can see that this act will be contrary to that of the descent of the piston. Eite would equalized by the weight on the back of the pistori. This action reaction of equal i: ntensity is inadequate if we take into account that the action of the piston switch from half of degrees forward to each degree I rotate the hundred crankshaft: -a1.

With a translational eccentric, one realizes that the action of the piston in relation to this one is not retrorotative and fast, imi.is pluto post rotary and slower.
At each advancement of thirty degrees of the crankshaft standa d, one must carry out a retro rotation of came degrees for position the piston. at each 20 degree stroke of the crankshaft translational, we must advance the piston two. We therefore reduce the friction by half. oa will rather, from a gear arranged on the eccentric c-ntrain post rotatively 92; a intermediate gear, which in turn will cause the piston induction gear, steered: ionellement.

In Figure 29.1.3, we can see that it is quite easy to induce in simultaneous rotation support crank 930 of the tranlational excentric 931, each a gear 933, which gears will be cotipled indirectly a third party 934 can be attached to a central axis 935.

As will be shown later, we will be able to realize various induction of the gear intermediate leading from the subsidiary crankshaft to the piston, by any induction of relationship for example, the more the three-sided piston figure, one po ;; t turning the piston one on three of that of the crankshaft of support of the eccentric translaticinnel.
For now, let's note that a way by a.illeurs very simple to realize the post turning of the piston will be to provide the eccentric support crankpin of an engrenal: e external 936 that we will couple to the support gear of piston 937.

Figure 29.1.4 shows the machine at top dead time, at, and in perspective in b) Figure 29.1.5 shows the elements undergoing descent Figure 29.1.6 shows the dynamism, read from the elements described above, for a tower of the maclùne. We sees that the central crankshafts 5-50 supporting the eccentric tr: mslationnel turn to the same speed, moreover, the induction gears arranged on their crank pin turn on themselves and cause the piston 951 to rotate.

Figure 29.1.7 shows in a more precise way the advantage of this typc of mechanical support of the piston. Mainly, we see that even if the geomE reports are respected, and that therefore the turning point is itself piston, orientally and positionelellement remains identiilue to that of a mono induction or all other induction simple first degree, 980, the reactions behind the point are partially countered by the fact that the location of the induction gear of the piston 981 to his Support gear stays plui forward. As a result an assigned force back from turning point, despite the fact that it entails a retrorotatiün 984, externally on a turning point post rotatii ', so we are witnessing more of an arnulation of forces that one creation of negative forces proper. This negative energy econvsée is doubled by fact that there is also economy of energy before the necessary normal:
neutralize it that will here be realized positively.

Figure 29.1.8 shows that this procedure can be adapted to. engines turbinataf. The gear 990 cylinder can drive a set of gear periph 3ric coupled Has crankshafts. 992 These crank pins for these crankshafts will be equipped with gear supporting the piston center gear, which will therefore realize a kinetic Translational.

Figure 29.2 .1 shows that the machine was designed with a central crankshaft. 1000 supporting the eccentric translation nel 1003 To complete the mechanics of translation, we dispose in the side of the machine a crankshaft subsidiary, 10 31, and will join his crankpin to the eccentric 1006. We will couple the central crankshaft and the crankshaft subsidiary so that their action is identical, for example by a chain 1004, uii hoop gear, a intermediate gear 1005. Pow finish, we will add to the crankpin I of the subsidiary crankshaft a support gear 1007 to which the piston induction gear will couple 1008.

Figure 29.2. 3 shows that the crankshaft!
subsidiai.res supporting the eccentric crankshaft by the recotirs to a metal rod 1000, :) with a link to a vi.the central breuin.

Figure 29.2.4 shows that when -. previous mechanics:
carried out to support the parts of a machine of form turl rinative Clokwise, the eccentric translatüonnel is made of confused with the piston 103 ~), and the connection gear .1031 gears of crankshafts of center and periphery can be coupled with that of (: ylindre 1032 and allow his activation in the opposite direction.

Figure 29.2.5 shows that the mechanical strikes turbinative corrosion, R1, is different from the one presented above, R 2 Figure 30 shows that one can mechanize with any inducti:
one, the eccentric of a rotating machine, of such a kind that its movement is im motion translational.
In figure (a), we obtain a translational movement of the excenque by induction by intermediate gear, and in b), iar hoop gear induction.

Figure 31 rises only in the me.wre where the planetary active form is cylindrical, she can receive any other planetary dynamisai ion that only liii tranlational dynamisation, and that in spite of these modifications of - retroactive or post rotatiorinel Orientational, this piece will realize, like the translati piece (melle, a positional rotation similar to that of a eccentric standard.

In the present example the piece with, i.ne retrorotation on the crank pin of the crankshaft whose result let this piece turn on it half a time every turn of a vilel, shark.
If it is about the piston, it would have to turn only one tier 3 of back turn. As a result, reversion of the excinent is high, and it will! -realize a retrorotati shooting: :) nnel of the piston in relation to this eccentric. Here for example, ion ul ilise two type link gear successive external In figure 31.2, the piston is mounted on the eccentric.

In Figure 31.3, we see the parts in perspective. Planetization of the sub-crankshaft will only not equivalent to that received by the piston, motivated by a mi, direct canalisation. In As a consequence, the completed action of the ston will be either backward:) ar compared to that of the csub vilebreuin, either a post rotation. As a result, ur.i or double gears starting from the induction gear clu sub crankshaft which, installed rotativmeent on a crankpin arranged rigidly on the central crankshaft i will couple to the eng-go cy, Indre. We will train directly to the cylinder gear, or we will produce an inversion s -lon the case.

It is important to note that, in this procedure, we realize:
simultaneously coupling of induction by mono inductior, and induction by engre swimming hoop, consequently induction with a posterior effect, and induction with anterior effect. By coupling, not only will we be able to achieve some of the backward effects and piston, but also to balance, according to the selected gear ratios, in such a way to proportion the effort, between the piston and the cylinder depending on the kinetics, the design, and finally developing of the explosion. The proportionalization of the piston receiving force will be due to the fact that This will be shared between the imbalances of different types employed.
the weakening and strengthening of one or the other of inductions Moreover, as will be pointed out>
to use dynamics Slinky for the sub crankshaft, important modifications of the sizes of gears, without altering the shape of the gear.
As a result, will considerably reduce the point of the inking of moron induction.
induction.

In Figure 32, we show that, as in our turb inative machines, we can talk here about virtual figure, the latter being established, In the present example, the virtual dynani crankshaft is that of a square. To calculate the mechanics to appli piston, depending on the subvilebrequin, it will be necessary to calculate the difference in this figure and the figure real to get. In the present, by the trajectory of a defined pole of the subvilebrequin to: r a tower. establishes the dynamics orientation of planetary eccentric inversely. For (: do, we have disposed on this eccentric a virtual piston, that the:) n operates planetarily, p, ar example to create a figure virtual of eccentric retrorotal ive in four. Comnze we can note, in this figure, the retrorotational movement of the eccentric is superior to that which is waited for the piston. It will therefore be necessary to locate an intermediate gear uniting the piston and this eccentric in such a way that this gear rotates post rotatiti, ement and restore speed relative to the piston, whereas, as we saw earlier, if the speed of derotation from the eccentric is smaller than that stretched for the piston, we will have to add derotation realizing an intermediate gear; piston drive by the eccentric who will work rétrorotativement. But the piston always has a rear equal effect before on this gear, which he either activated post or retrorotativemert. The interest of this section is therefore to find the means of enlarging the gearing s support and induction of the eccentric without changing the teat of the crankshaft and consequently the distance between the crankshafts, what will the next figure.

All the virtual figure of sub vi: ebrequin are possible, but ccrtaine will be preferable to others. Preferably, we will aim the conjunction of a mechanic: retro efficient, and of, a post effective mechanics. Here for example, as, by oppositiori in the figure previous, the mechanical is retro effective, it can be coupled to a mono indluction post rotary, for operate the piston.

Again, not only does it seem preferable to cut induction of such way to achieve together post and retro effective incl.uction, i nais also, in such a way to proportion the performance of each. So, we will show more far the importance of Slinky dynamics, already used by ourselves for the pistons of, ~, machines turbines, and use here by sub crankshafts.

Figure 33 recalls our motions (! Planetaryizations synthetic>, or according to another terminology, Slinky kinetics of planarization. applied in years turbines.
In these we show that a planet-driven élémerit can realize a number of faces, but this time not consecutive. As a result, the number of: faces will do on more than one trick.
As a result, the ratio of eni: xenages will be high. For example, here producing a year a figure at eight sides not consecutive, ei: in b) a figure has twenty sides a'ton consecutive.
In the first case we will have a rapl: ort of three eighth of a turn el in 1 second case, a report nine twentieth turn.

This will make the cracks rude while keeping in between them a distance equal to that of expected turning radius.

Figure 35.1 shows the interest of the most recent procedures.
this one is to back down the coupling point of the gears, which will make the counter forces back really active more in back. This will increase the amplitude of the coupling beam, 2004. But the gain in knock reduction din.:ct is huge. If this structu.re is at surplus realized so polycamée what is shown in a), as in our previous figures, we will have a machine very fluid. The second interest is to bring the piston, by coul.ilage, of preference, of post-operative and retroactive induction, to work, mechanically, in a manner proportional to its kinetics, which is the major difficulty of naehines presses.

In figure 35.2 we show in a, that it is possible to train the intermediate gear driving the gear that it is possib: .e to drive the intermediate gear leading to the gear piston induction from e; gears of support rigidly arranged in the center of the machine. As the intermediate gear will be placed on a net fixed to sub crankshaft, and that the planetary speed of this one is not identical to that of a standard crankshaft, or of a tranlational crankshaft, the jeii. gear will be different, el according the case, that is to say, it is rappelling slinky by, back in retrorotation faster or slower than the standard rotrorotation chosen, either retrorotative or post-rotating.

Figure 35.3 shows that we can apply the notion of crankshaft [luin cylindrical to the machines of Turbine type. This crankshaft 31100 can then have a kinetics different from that of the virtual kinetics of the piston. And this kinetics will be preferable kinetics of slinky type, especially if the piston does not make it itself. In this case, the cylinder; will be activated by several mechanical, of which for example by im gear of peri-plasic carrier 3001 rigidly attached to cylindrical crankshaft, this gear being coupled to an engrenagi ;:
central induction coil 3002 to cylinder 3003.

Depending on the speed of induction of the crankshaft sizb which will be corrmanded rotation speed of the support shaft of the internal gear gearing to the gear;
piston, we will be able therefore have a post-reaction action of it quite slow, Figure 36 shows that the piston can be connected by a the gear to a crankpin located on the intermediate gear, if it is calibrated to turn a equivalent number per the number of arcs of the cylinder, or a doubling of this number. This will achieve deceleration accelerations san: have to use polyvcamés gears.

Figure 37 shows in a, that the s--face of the piston can be extrt: .dé de variable way of such way of producing a breakdown of the explosion and expansici appropriate for kinetics.
In b) of the figure, it is shown that, one carries out a hole of chai lue side from cylinder to level the bottom dead time of the piston, we can take out the segments of coiins and replace with new, without having to open the cylindri :, these holes can consequently be clogged by coins cylindrical.

Figure 38 shows that with a rear geometry of the piston apprc: requested, in which we realized an inner curvature of it ,: 010, this curvature will move toward washing downhill 3011, and in doing so, will counteract the closure of the cylinder by the passage of the formed bulb by the meeting of the upper arches 3012. As a result, conwie shows it following due calculations surfaces relative to these spaces, 3013, the area between these parts will not decrease, as in standard engines, but will remain stable, or produce a slight growth. This means that kinetically, we will be assured then that the machine cst positive, even in his back parts. This is of the utmost importance, since we can deduce that in this part, the work of the rear orienu ~ tional force is started, and that we would be wrong as the industry, to sacrifice the energy that this space could create;
by the support method by mono induction. The capacity Figure 39 shows that in coupling the notion of intra-back curvature of the piston and that of gear cylinder curvature; polycamé, (or other means acceleration and deceleration of the piston) we obtain a kinetics which not only produces no more compression after the dead time, as is the case, in machines of the prior art, or still a niaintient of compression, as it is the caa! in our previous figure, ma.is a increase gradual and significant volume higher than the increase in volume of the front part, for all the first part of the expan, ion.

This shows beyond any doubt that the mechanics that we proposed to over the years and in the present invention have the kinetic corroboration, and by therefore that the concepts of thermodynamics relating to the v il ilume and the production of tra-rail apply here favorably.

Figure 40 shows that these methods of guida; e; e can be adapted to turbines, in coupling the cylinder, by an induction gear, of an inductiion descendant, of which the peripheral support gear, is fixed on the sub crankshaft evendications Reve ication 1 A mac of rotary type, inactive turt or type poly turbine., Whose component positional the theoretical component of the kinetics of l ~~ iston, when it comes to one active compressive part are real:

a) in two inductio each sup ~) ortant part of the piston, the first etan heart piston and the second one of co urbatures, (b) in two inductions, the teacher supports the center of the pistc ,, n, and es induction positional, and the second is a planetary induction terminated by a member of guide, this member being connected to a plunger, this induction being i.me duction oroientationnelle, (c) in two inductions, the first of which leads to a planetary plane cylindrical mounted planetically in the body of: a hine, this induction has called induction positional, and the second, coni rol the ori tational movement of the piston by resorting to an induction linked to the subirabillary blood, this production being nonuned induction Orentational piston is done in two parts, the pistil and the tone of curvature, this parties carrying out similar kinetics, from the latitudinal point of view, but minus l. rononcées from the standpoint vertically, and this in such a way that 1 ~, pi on caeur realizes omprcIssion and more expansion ample, and that the piston of courbatw realizes a curvature cy.lindre of first, second, or third degree, each of these being activated orientationally.

Claim 2 A nia.chine whose rear part cù piston is drawn such naanière have a curvature performed inside, peeled intra-curvature anterior (: du piston, cradled such way of breathing or increasing the volume of gases is in this for all the first part of the descer te.
Claim 3 The machine producing a cylinder curvature, the rear part of the two bows of cy dre

Claims

claims Claim 1 A rotary type machine, turbinator or poly turbine type whose component positional and the orientational component of piston kinetics, when it comes to the only active compressive part are realized:

a) in two inductions each supporting a portion of the piston, the first being called heart piston and the second piston of aches, b) in two inductions, the first of which supports the center of the piston, and is called induction positional, and the second being a planetary induction terminated by a guiding member, this member being linked to a plunger point, this induction being an induction oroientationnelle, c) in two inductions, the first of which leads planetarily a crankshaft cylindrical mounted planetary in the body of a machine, this induction being called induction positional, and the second, controlling the orientation of the piston by resorting to an induction linked to the subtle planetary brine, this induction being named induction Orentational piston is made in two parts, the heart piston and the piston of curvature, this parts realizing similar kinetics, from the lateral point of view, but more or less pronounced from the standpoint vertically, and this in such a way that the heart piston compresses and more expansion ample, and that the curvature piston achieves a cylinder curvature of first, second, or third degree, each of these piston being activated orientationally.

Claim 2 A machine whose rear part of the piston is designed in such a way have a inward curvature, called intra-anterior curvature of the piston calculated from to maintain or increase the volume of the gases in this room for the first part of the descent.
Claim 3 A machine producing a cylinder curvature whose rear part of both cylinder arches get joining to the dead times up and down the piston is lowered and the part front elevated, this being possible thanks to accelerations decelerations of the piston on its axis, made by gear4 polycamé, or cam, or mechanical means of occillante rod.

Claim 4 A machine whose central eccentric is a cylindrical element activated by an induction causing it in a planetary motion, this induction being, the piston being mounted rotatively on the cylindrical eccentric, so to be simultaneously inserted in a cylinder, and this piston being provided with an induction gear, of internal type, this gear and this piston being driven postrotatively with respect to the eccentric cylindrical by one or more gears mounted rigidly on crankpin of support crankshafts of the element cylindrical.

Claim 5 A machine as described in 4, whose movement of the sub crankshaft is translational, and activated in this way by induction one on one, or by induction for this case, preferably composed of two crankshafts with gears linked together by a third party gearing driving the central axis of the machine, these sub crankshaft comprising on their crankpin a support gear coupled to the piston gear, which piston is mounted rotatively on the tranlational exentric.

Claim 4 A machine as defined in 3, whose translational realization of the eccentric is produced with a mechanical induction usually used to induce movement of a piston of turbinator machine.

Claim 5 A machine as defined in 3, whose eccentric set is composed an eccentric central, on which is mounted rotatively a cylindrical element, this element being induced planetary by an induction of art generally serving to drive the piston itself but of different planetary ratio, this planetary cylindrical element receiving rotatively the piston, this piston being rotatively controlled by mechanical elements, of which preferably one element, soitt the intermediate gear drives the induction gear of piston is mounted rotatively on an axis located on the planetary cylindrical element Claim 5 Claim 6 A machine as defined in 4, whose intermediate gear has as support gear a) a mounted gear of the cylindrical element b) a gear mounted on the central eccentric c) a gear mounted in the neck of the machine, this gear being usually polycamé, or the intermediate gear being, or both.

Claim 7 A machine as defined in 4 and 5, one of which is an induction post type induction effective, such a a) a mono induction b) a poply induction and the induction is of the retro-effective type, such as for example, but not limitativem, ent a) an intermediate gear induction, b) hoop gear induction c) heel gear induction.
Claim 8 A machine as defined in 4, 5, whose induction due to the element cylindrical realizes a virtual figure of a basic geometric shape, triangle, square and so following, this figure being realized by the kinetics that a point of this element describes for a turn, or a set of towers crankshaft.

Claim 9 A machine, whose virtual movement describes a kinetic slinky, movement planetary of slinky type, characterized by the fact that the total figure is no only produced by more than one crankshaft, but also by the fact that it is made by jumping listed, or by quoted alternative, until the figure is fully executed, this figuration being made of such angle between each jump is close to the perfect angle, standard machine, these angles being somewhat smaller, or somewhat larger.

Claim 10 A machine as described in 8, including the support gear intermediary will be directly related to the piston induction gear, or indirectly linked by a gear inverter.

Claim 11 A machine as described in 8, including the intermediate support gear will be provided with a crankpin receiving an element fixedly connected to the piston, this element being provided with a slide in which it will be engaged, causing a decelerating acceleration of the piston.

Claim 12 A machine with one piston, either the piston core, or the piston curvature is subdivided into unitary piston hearts, or pistons of unitary body aches.

Claim 13 A machine as defined in 11, whose unit piston cores are standard pistons inserted into the plunger piston, these pistons being interconnected by a planetary element, and related to this planetary element for a slide, or by a point of simple attachment, if this planetary element has an accelerating decelerative stroke, obtained by polycammed gears.

A machine as defined in 1, whose piston of curvature is broken up in piston of body aches, each of which is inserted in each corner piston heart a) pivotally and slidably (b) in a strictly pivoting manner c) strictly sliding A machine as defined in 11, the lower part of each of piston of stiffness unitary is supported by:

a) by a crank pin of a peripheral crankshaft b) by a central crankshaft c) by a central active cam d) by a cam with several central active faces e) by a cam with several faces describing a virtual figure f) by a central active cam whose movement is translational g) by a central fixed cam h) by a slide linking it to the central axis Claim 12 A machine as written in 11, whose split cams are not same length, depending on the coupling situations for which they are responsible, these cams producing curvatures of fourth degree cylinder.

Claim 13 A machine as defined in 1, 7, including the unitary curvature pistons receive oscillating segments.

Claim 14 A machine as described in 1 the piston is rotatably mounted on the central eccentric and simultaneously introduced into its cylinder, and whose steering element and Orientational is a member planetarily mounted on the same eccentric, this member being bound non-rigid way one or more points of the piston, the length of this member being preferably enough restricted to reduce harmful directional impacts, this planetization of this member being performed with any induction of the prior art Claim 15 A machine whose piston core describes the kinetics of a machine to walk degree, then pistons of curvature describe the curvature of a machine of second, third or fourth degree.

Claim 16 A machine as described in 3, including the deceleration acceleration of the piston is realized by a member whose lower party is coupled to the central axis by a slide, whose central part is pivotally mounted a sub crankshaft whose crankshaft support is oriented across the eccentric piston e whose end is connected to the piston.

Claim 10 A machine as described in 3, including the translational support gear describes a translation in the opposite direction to that of crankshaft rotation master, the gear of support of it being then inductive poly.

Claim 11 A machine, comprising a rotary type piston mounted on an eccentric and inserted into the cylinder, this machine having orientational induction driving a third member in a planetary action, this member having a length is less than that of the length of the radius of the crankshaft of the piston of the machine, the piston being made in such a way to own a internal extension allowing to connect it to this member, in a non rigid.

Claim 12 A machine as defined in 3, including the unitary induction induction is one of the following.
^ ~ mono induction ^ ~ induction by intermediate gear, ^ ~ hoop gear induction Induction by poly induction ~ ~ induction by engrange chain hoop ^ ~ polycombic gear induction Claim 13 A machine as defined in 1, including the insulation between the piston core and the piston of curvature is made by a double slide game.

Claim 14 A machine such as to realize in one whose piston heart is the piston tractor, the induction of piston of curvature being made from the induction or the piston of the induction of the heart piston.
Claim 15 A machine as defined in 1, the piston of curvature is broken up into several pistons of single curvature, each of these plungers being inserted from sliding way in a third party, this part being itself cylindrical and being itself even inserted so oscillatory in each of the points of the piston, the lower part of each of the piston state equipped a collar for attaching it to a crank pin of a crankshaft different speed than the central crankshaft, or a central crankshaft manetor, depending on the number of revolution of this crankshaft expected, corresponding to the number of cylinder corrections per turn we hear achieve.

Claim 16 A machine as defined in 1, whose bending pistons are inserted in so sliding directly into each slide where each corner of the piston is provided, the part lower of each piston of unitary curvature being provided ^ ~ a slide, this slide being attached to a crankpin crankshaft ^ ~ a supported each of these supports being supported on a central eccentric replacing the crankshaft Claim 17 A machine as described in 7 and 8, each of which crankshafts or eccentric of rudder pistons is mounted planetary on the piston and trained rotatively by means such as a gear coupled with a support gear rigidly attached to the central eccentric.
Claim 18 A machine as defined in 7, 8 9, including the crankshaft, or the eccentrics turn over once per cylinder bulbs.

Claim 19 A machine, as defined in 8, whose eccentric has several parts junkies.
Claim 20 A machine, as defined in 7.8, 9 whose single cam, or in polycam, is willing rigidly in the cylinder, fixed or rotational, or rigidly, in the turbines, in the crankcase of the machine.

Claim 21 A machine as described in 1 ,. including the rectilinear motion of the pistons unitary is secured by bearings, or gears rotatably installed in the heart piston or on each piston of curvature.

Claim 22 A machine such as define in 1, rotary type, polyturbvine, turbinator, whose curvature of the cylinder is obtained by the use of polycammed gears, these gear being first degree, or higher degrees, the cams being then split, a further being made of asymmetrical and irregular way.

A machine as defined in one, the cylinder induction of which is realized from a peripheral support gear arranged rigidly on the sub crankshaft of the piston, and the induction gear is rigidly disposed in the center of the cylinder.