EP2235439A2

EP2235439A2 - Pendular engine

Info

Publication number: EP2235439A2
Application number: EP09719323A
Authority: EP
Inventors: Albert Cohen
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-01-09
Filing date: 2009-01-08
Publication date: 2010-10-06
Also published as: US20110131987A1; WO2009112666A3; WO2009112666A2; WO2009112666A9; BE1017812A5; US8408000B2

Abstract

Pendular and differential periodic heat engines with theoretical efficiencies of ONE, and industrial efficiencies close to ONE, exclusively subordinate to the physical constraints inherent in any material device under ordinary conditions of use, operating with recirculation of the gases in closed loops between a thermodynamic pendulum (2/2, 2/4) made up of a chamber (1/2, 1/4) fitted with a piston (2/2, 2/4) connected to a free flywheel (3/2), and a regulated supply of heat (10/4, 10/4, etc.) positioned some distance away from the chamber of the thermodynamic pendulum (figure 2), with extension to turbine engines (figure 5) thanks to phase changes.

Description

Description - Pendulum motor

Contrary to popular belief, it is possible to obtain industrial thermodynamic conversions of theoretical UN yields from a single heat source as in human muscle, and close to one in common industrial uses. Such conversions can be acquired for any power, from any temperature, without prejudice to Neernst's law.

Of course, it is absolutely utopian to hope from the current devices. Such conversions, however, become possible by means of a novel device: A thermodynamic pendulum by definition adiabatic and isentropic simultaneously overloaded in heat and discharged in work during adiabatic expansion of gases.

The first thermodynamic conversion: that of the adiabatic thermodynamic pendulum is by definition pendulum and reversible. It serves as a cradle for the second: that of thermal overload. The heat / work efficiency of the first is conventional (T1 - T2) / T1. That of simultaneous thermal overload is ideally one. A second application extends the process to gas turbines by means of phase changes of the circulating gases in the return pathways.

The patent illustrates here a new and unprecedented conception of the conversion of heat into work in fundamental thermodynamics. It is therefore necessary first of all to explain the principle and to demonstrate its theoretical feasibility, and then to describe the industrial aspects of it in common uses.

A thermodynamic pendulum is a device exchanging heat for work, then reciprocally for reverso of work against heat in a periodic pendulum cycle in perpetual theory since by adiabatic definition as any theoretical pendulum motion. It does not carry out any exchange with the outside environment to itself, be it heat, work or gas. It is possible in industrial use to artificially perpetuate a true pendulum movement by means of maintenance corrections, because no physical assembly is perfect and every oscillation is destined to be spontaneously amortized as soon as it occurs in a concrete physical environment, unless maintained. We give below as an example _/ an example of ideal thermodynamic pendulum movement without prejudice to any other assembly.

Or a conventional cylindrical enclosure (1/1) filled with gas, closed by a piston (2/1). This piston can slide in (Figure 1). Under the thrust of pressurized gases the piston (2/1) will slide from an initial point A (Figure 1) to an end point B of its path. In A its pressure is P1, its temperature Tl and the volume occupied by the gases V1. The thrust of the gases communicated to the piston produces a work W between A and B. This work is of theoretical yield (Tl - T2) / T1, because in B its new pressure is P2 smaller than Pl, its new temperature T2 smaller than T1 and the new volume occupied by gases V2, larger than Vl (Figure 1). Arrived at B, in the device of Figure 1 the thrust forces exerted by the piston and the external resistors to the enclosure are balanced. The movement of the piston stops. It is reversible, subject of course to return to the piston all the work W operated between A and B by the expansion of the gas (Figure 1) to allow it to return to the initial state of the system (Pl, Vl, Tl, piston again in A). So far: nothing but very ordinary. We will place in such a chamber (1/1) a free flywheel (3/2) whose axis of rotation (5/2) will be perpendicular to the movements of the piston, and when the piston will occupy the position A, closest to it, we will connect the axis of rotation of the flywheel (5/2) to the piston by means of a connecting cable (4/2) according to Figures 2, 3, and 4. The piston is likely to move from position A to position B, because we will give this cable the length AB + that of the distance separating the piston from the flywheel (figures 2, 3, and 4) when the piston occupies the position At the closest to him. When the piston is in A, we will tightly wind all the free part of this cable (so the length AB) around the axis of rotation of the flywheel (5/2) by one of its ends and connect the other end to the piston (2/2, figure 2), then we put the gases under pressure. As soon as we let the armed system go under pressure, the thrust of the gases under pressure on the piston puts the flywheel in rotation, because simultaneously the piston moves between A and B and the connection cable (4/2) wound around of his axis acts on him. Once the end piston "

race in B, he can not go further. The cable (4/2) is then stretched completely between the piston (2/2) and the flywheel (3/2), at this moment it passes from one edge to the other of the axis of rotation of the steering wheel (5/2, 5/3) on which it is wound in the opposite direction of the previous direction (Figure 3) and the rotation of the flywheel continuing on its thrust, it will serve as a return to the piston by pulling on it by through the cable always stretched between the two. From A to B it is the piston pushed by the gas that acts on the steering wheel to rotate it. Once in B, the piston can not go further and the steering wheel continuing its momentum, the cable fully unwound and always stretched changing edge around the axis of rotation of the flywheel, it is the steering wheel then passive that comes into action and acts on the piston to bring it back to its original position ideally restoring the pressure at Pl, the temperature at T1, in the initial volume Vl (explained in Figure 2 and 3). Once the gases are pressurized again, the movement marks a short pause and the cycle begins again a new period, with a reversal of the direction of rotation of the steering wheel. The movement is illustrated in Figure 3.

A flywheel is in principle likely to return all the kinetic energy that has been communicated. It must therefore logically recall the piston to its initial position and restore in principle the enclosure in its initial configuration. We thus obtain a thermodynamic pendulum motion in perpetual theory. The piston is thus animated by a perpetual linear oscillation and the flywheel of a reciprocal circular oscillation whose meaning changes in each period. Once launched, such a pendulum device is ideally strictly adiabatic and isentropic. In theory, it does not carry out any exchange with the outside world. It theoretically produces no work and in theory consumes no calories. In A, the temperature Tl is higher than in B. In A the pressure Pl is higher than in B. In A the volume Vl occupied by the gases is smaller than in B. Let M be the mass of the gases and C their specific heat "We proceed thus to a potential / dynamic cross exchange in theory perfectly reversible of heat in work and vice versa of work in heat in an adiabatic system alternately hot and under pressure in A and cold and relaxed in B, between the flywheel and the _,

gas from the enclosure. We can express the quantity of heat thus exchanged between the flywheel and the piston in caloric value of Q calorie extensive against W work, and no longer in intensive temperature scale values Tl and T2 between Tl and T2. Let M be the mass of gases. Let C be their mass heat.

Q = Mx Cx (T1 - T2).

We are thus carrying out a perpetual cross exchange Q / W / Q / ... etc. This exchange is in principle perpetual and can be ideally produced without any theoretical expenditure of energy, as in principle in any pendulum movement proceeding to an ideally adiabatic potential / dynamic exchange. We will see with the description of the final device how to overcome the forces of friction to move from an ideal perpetual motion to a concrete movement necessarily imperfect.

The assembly given here as an example is reproducible by means of an infinity of assemblies. The steering wheel can be placed anywhere, under the sole condition of being in permanent opposition with the piston.

Either any gas undergoing expansion producing work, as in Figure 1 which gives up to date a simple simplified schematic version of any heat engine converting heat into work. Its initial parameters are: Pl, Tl, Vl (pressure, temperature, volume). At the end of the relaxation cycle they become P2, T2, V2 (same thing), as we have described above. Such a cycle of exchanges proceeds with the exchange without return of Q calories against W work and its theoretical yield is well known: it can be written (Tl - T2) / T1. This is the theoretical yield of Carnot. We do not make any particular comment on it.

We will use not a conventional conversion cycle, Figure 1, but the cycle of a thermodynamic pendulum, as described in Figure 2. We will introduce in the adiabatic cycle described in Figure 2 in favor of the heat exchange in work for rotating the flywheel (3/2) an additional heat load of Q ¹ = Q calories at higher temperature than T1, while the piston moves from position A to 'at position B, or just before _* We proceed to this overload of heat by means of a device which will be described with the description of a concrete cycle and no longer ideal. If the gases evolve from a temperature Tl, a pressure Pl, and a volume Vl, up to a final temperature T2 smaller than T1, a final pressure P2, smaller than Pl in a final volume V2, greater than Vl, we can produce this in such a enclosure, by raising the initial gas temperature to: T3 = Tl + (T1 - T2) before or during the revolution of the piston.

Indeed, if T3 = Tl + (T1 - T2)

(T3 - Tl) = (T1 - T2). Therefore Q ¹ = M x C x (T ³ - T ¹ ) = Q = M x C x (T1 - T2). since (T3 - Tl) = (T1 - T2) The practical arrangement of the thermal transfer is explained below with the concrete description of an illustration of the process.

It is well known that the pressure of a gas in a constant volume chamber is a function of its temperature.

Let delta P = f (delta T). likewise for any gas whose temperature is raised: delta Px = f (delta Tx). If we do that: delta T is equal to M x C x (Tl - T2) and delta Tx equal to M x C x (T3 - Tl) if (T3 - Tl) = (Tl - T2)

(delta Tx) = (delta T).

We are perfectly entitled to it, by taking T1 at the new temperature T3 = Tl + (T1 - T2)

The new theoretical theoretical pressure obtained by raising the temperature Tl to the new temperature:

T3 = Tl + (Tl - T2) will be mathematically P3 = Pl + (Pl - P2) with the thermal overload carrying the gases of the temperature

Tl at the temperature T3 = Tl + (T1 - T2) in the exclusive and precise case of our device. Which means that :

(P3 - Pl) = (P1 - P2).

Here indeed, in the case of our enclosure, P3 is only mentioned. This is indeed here exactly the same speaker.

It is unique, of the same function, and of the same ratio curve of temperature / pressure variations between two identical invariable terminals: point A and point B. An added heat load Q ' just take the place of the other (Q) retracted between A and B by rotating the steering wheel, which does not change the adiabatigue cycle, even at variable volume, during the course of the relaxation, in the specific case of our device. The heat load Q is simply removed from the enclosure gases by the rotation of the flywheel and at the same time simultaneously exactly replaced by substitution of Q ¹ to Q. If we place the temperatures in ordinates and the pressures in abscissa on a curve, we simply shifted the temperature pressure variation curve downwards by retracting delta T and simultaneously upwards by substituting delta Tx = delta T at all points of the curve. We therefore have the right to write here that P3 is virtual and that if:

(P1 - P2) is obtained between Tl and T2: (P3 - Pl) is between T3 (real) and Tl and that: (P3 - Pl) = (Pl - P2). it simply replaces him in addition between A and B without changing anything in the ideal adiabatic cycle.

If the real pressure differentials are identical for the same enclosure producing a single doped cycle, between two single terminals, the work differentials can only be identical.

A heat load is exactly substitute for the other during the relaxation of the gases. By bringing its new temperature from Tl to T3 (very real) it is therefore likely to produce a new work outside the enclosure: W = W

We do not have to take into account here the non-linearity of the relation between pressures and volumes as in the representation of Amagat by raising the temperature Tl to bring it to T3.

The enclosure of the adiabatic pendulum produces here its own cold source between the beginning and the end of the relaxation of the gases between A and B, because the thermal depression retracted by projection in the movement of the steering wheel ... is exactly corrected by compensation.

The heat load stored by the movement of the steering wheel is exactly equivalent to the one used. It will then be positively restored to the gas of the enclosure by the movement of the steering wheel from B to A at the end of the expansion of the gases. If we take the overload Q ¹ in the form of work while the piston (2/1) moves between the two terminals A and B, the thermal overload allows a second conversion exactly equivalent to the first one and this one can be exploited in outside the enclosure. In the end, we only built a clockwork movement that we doped, but a clockwork movement of a thermodynamic nature capable of producing work.

If in a classical cycle we double the differential of the temperatures by introducing in this one a delta Tx = delta T, we do not necessarily duplicate the differential of the pressures: in the curve of the variations temperature / pressures. A delta P is not equal to a delta T. But here P3 is virtual and only evoked. There are not two different curves. There is only one.

This paradox is explained by the fact that the work of rotation of the steering wheel is exerted not on a fixed resistance / as in a conventional speaker, but on a decreasing resistance in an enclosure which although dadiatic sees its temperatures alternatively decrease and grow. As the angular velocity of the flywheel increases, its moment of inertia decreases and the resistance it opposes decreases as well. There is a match between heat consumption and work production.

In an ordinary enclosure, if we want the movement of the piston to be rapid, it must have a gamma of substantial acceleration correlative to the gamma of the pressure differences, and therefore a significant difference between the push forces and the resistance forces. Here, it is not the case in the adiabatic enclosure that we modify. Between A and B, delta T = delta P.

If we wanted to obtain a 100% efficiency in an ordinary enclosure, it would require an exact match between push forces and heat consumption in order to avoid any waste, therefore an infinitely slow piston movement tending towards zero or even zero, this being the case. which would be absurd. Here, our enclosure is not inert, if one can express oneself thus, but in perpetual movement. It imposes its period, its cycle and its own speed to the transformations of the conversion of a heat load Q 'in work W.

Let Qz be the caloric compartment of a conventional speaker _"

ordinary. We seek to convert most of it / that is to say to obtain the best return and this one is inexorably (Tl -

T2) / T1 or (Q1 - Q2) / Q1. Here we are only trying to convert the equivalent of the exploitable work resulting from a conventional conversion and this production of work, unlike the other, can be obtained with a conversion efficiency Q = W (Joule law) of 100% .

If we take from a pendular chamber, as described above (figure 2) exactly all the extra work W produced by a thermal overload Q 'of the blow subtracted to be exploited, we subtract at the same time all the extra heat Q incident. If we subtract exactly all the incident heat supplement introduced into an adiabatic cycle, we produce no variation in it. It is certainly no longer adiabatic, since we have simultaneously added and subtracted exactly the same caloric value converted into labor taken, but it will behave exactly as if it were in spite of the exchange. Therefore, in the figure (2) or (4), our flywheel (3/2) must in theory bring back the enclosure (1/2, 1/4) exactly in its initial configuration in A (Pl, Vl, T1 initial remaining unchanged in A), once the work W product has been taken. At this moment, it is necessary and it is sufficient to recharge the enclosure with a new caloric value Q 'thus defined (FIG. 2) by again raising its final Tl temperature at the end of the period to the new temperature T3 = Tl + ( Tl - T2) to convert it back to work W = W and we can start the operation again indefinitely. This second conversion no longer enters the classical thermodynamic conversion pathways of the Carnot type ... whatever the yield of the first conversion (reversible and adiabatic which serves as its cradle). It is equal to it, superimposable, and is a substitute for the first whose thermodynamic conversion thermal potential has been simultaneously retracted by the movement of the steering wheel and restored by the thermal overload that replaces it. There is substitution of a heat load retracted by another active on the pressure. The work is pendular and differential at the same time.

As long and as far as we will not load the enclosure with a higher thermal overload than the adiabatic Q / W / Q exchange, we can convert all the overload into job. Ha new enclosure will therefore have a lower power and the limit equal to that of heat exchange capacity in work adiabatic enclosure. We can build of all powers to the best of our possibilities or our wishes. Beyond this, and for the rest, we will have to invoke Carnot's theory of theoretical returns for the rest. There will be in our enclosure in this case a residual heat overload T2 ', T3', etc ... at the end of the gas expansion cycle. Nothing obliges us ..

Unlike the Carnot cycle which tries to convert most of a heat potential present in a system, here we do not claim to convert a heat overload introduced into an isentropic and reversible system, but this second conversion obeys Joule's law, like the first: Q = W and its theoretical yield is 100% (Q '= W). It is obvious that to achieve ^concretely such cycles, ancillary physical devices are considered and physical corrections are to be made. The adaptation of this new principle of substitution to gas turbines with continuous motion and no longer alternative will be treated in a second part. They are common to both versions and will be exposed in the final description.

Description of the device

Or a cylindrical enclosure (1/4) closed at one of its ends in which can slide a movable piston (2/4). Let us note from now on that we will designate it throughout the description under the no of main enclosure. In the bottom of this enclosure a conduit end communication (6/4) communicates with a second sealed chamber (16/4) in which is a flywheel recessed in (3/4). Its axis of rotation (5/4) is perpendicular to the movements of the piston (2/4). The room (16/4) tightly encloses the steering wheel without touching it, so as to leave as little dead space as possible. We connect the axis of rotation of the steering wheel (5/4) to the piston by means of a flexible cable (4/4) placed in the communication duct (6/4) placed between the two chambers. The piston moves from position A (figure 2 of principle and 4 industrial) all against the wall ^' of the main speaker / up to occupy the opposite position B. Indeed. we will give to this cable the length AB, + the distance separating the piston of the flywheel when the piston occupies the position A. The piston is thus, prisoner between the two terminals A and B and can evolve only between them. We tightly wind all the available cable (4/4) around the axis of rotation of the flywheel (5/4) when the piston is in position A close to the bottom of the enclosure. We can place the flywheel anywhere, provided that its circular motions are all the time in opposition to those of the linear oscillations of the piston and that the cable interposed between the two (4/4) is all the time stretched between both. We start by immobilizing the steering wheel and the piston in their respective positions: A piston and flywheel, with all the free part of the cable wrapped around the axis of rotation of the steering wheel and the rest stretched between flywheel and piston.

In the closed bottom of the main enclosure (1/4) open two ducts (8/4, and 9/4). By one (8/4) we will supply the main enclosure with hot and pressurized gas when it is completely empty with the piston at A, and with the other (9/4) we will evacuate the gas cooled and cooled after their productive relaxation of work, when the piston moves from position A to position B. The movement of gases in the circuit of the device is in one direction in the direction arrow in Figure (4). Both ducts will be equipped with anti-reflux valves (23/4) to prevent any return of gas. At a distance, to power the main speaker, we place a whole battery of heat exchangers (10/4, 10/4, 10/4 etc ..). Each exchanger enclosure has exactly the same volume as the main enclosure when the piston which slides in is at the end of stroke in B. It is possible to give them smaller dimensions provided that their dysthermic potential Q ¹ = Q is always the same: That is to say that the heat load delivered to the main chamber is always the same, for example in the case of a phase change of the gases which would pass from the gaseous phase to a liquid phase under very high pressures , or in consideration of the temperature of the single source (14/4) in which they bathe. This must in any case be in all cases and by construction at a higher temperature T3 and the limit equal to that of the main enclosure, when the piston occupies the position A to be able to deliver heat. The heat-generating enclosures (10/4, 10/4, ... etc) of the battery are not necessarily immersed in the single heat source but may also be heated to the appropriate temperature by heating, ex solar, or means of a fuel or other. Each secondary enclosure (10/4, 10/4, ... etc) intended to provide in turn hot pressurized gases to the main enclosure (1/4) has two private conduits (12/4 and 12). / 4) fitted with non-return valves. The first, downstream delivers passage to hot gases under pressure to direct them to the main enclosure (1/4) in the arrow direction, through the channel of a single conduit (8/4) common to all exchange speakers of heat (10/4, 10/4, ... etc), and the second (12/4) through the channel of the common duct (9/4) which serves as a return duct to cooled and expanded gases discharged by the piston movement (2/4) after passing through the main enclosure (1/4). All the respective communication ducts of each enclosure providing heat (10/4, 10/4, ... etc) lead into the two large collectors: (8/4, and 9/4) which serve them. These open at the bottom of the main enclosure (1/4). Valves antireflux (23/4) defend the arrow direction in which the gases circulate.

We start by arming the device once and for all by producing in all the hermetically closed heat-producing enclosures (10 / 4,10 / 4, ... etc) the temperature T3 and the adequate pressure. This is defined by the power of the flywheel (3/4) and its heat storage capacity in kinetic form. The temperature T3 is supplied to the single source of heat (14/4) by means of a circulation of hot fluids (17/4) or produced in situ, or fed from the outside, or generated in the case of a natural hot spring of great capacity. It goes without saying that the temperature of the main enclosure (1/4) will always be and by definition lower than that of the heat source mother therraostatée. By opening an outlet valve (12/4) of any of the heat supply enclosures downstream thereof in the arrow direction, we deliver hot and pressurized gases to the main enclosure (1/4). At this moment the main speaker is totally empty. The piston is located against the bottom wall in position A, and the steering wheel is stationary. The sudden jet burst of the gases released by one of the speakers supplying heat and pressure by opening its downstream valve simultaneously sets the steering wheel (3/4) in rotation and allows the main speaker to produce a workable task. Once the piston (2/4) reaches B, the final pressures are balanced in the two speakers placed in communication. We then close the communication at the level of the caloric enclosure that has just delivered the caloric. We simultaneously open the opposite valve of the same chamber communicating with the main chamber (1/4) by the common gas reflux line (9/4). The return movement of the piston (2/4) actuated by the thrown wheel (3/4) flushes the gases in the relevant heat exchange chamber open at its upstream pole. We close the communication. Here, the cooled and expanded gases waiting to heat up in a hermetically sealed enclosure are again in contact with the sole source of warmer heat that it, or heated by any means at our convenience in a hermetically sealed enclosure where they will be able to heat again. When the piston returns to the starting position (A), with the entire available cable wound around the axis of rotation of the flywheel, we then immediately open the downstream valve of the next heat-generating enclosure and repeat the same operation. Since the time of a cycle will be short and the heating times will be longer, N is the heating time of an enclosure and n the time of a cycle, we will place in the single source (N / n + 1) pregnant and will work by circular permutations. When the last one has delivered its charge, the next will be automatically at the desired temperature. We can work continuously. For a turbine (Figure 5), mounting is simpler. We have a first chamber (18/5) immersed in a heat source where it can acquire the desired temperature and pressure or heated from outside or inside. This chamber filled with high pressure liquid gas communicates with the hot pole upstream of the gas turbine (19/5) by a single conduit (22/5). Between the two, an intermediate decompression chamber (24/5) where the gases pass into the gaseous phase by means of a nozzle (21/5). The turbine is thus continuously fed with hot gases and under pressure through the conduit (22/5). At the outlet of the turbine at its opposite pole in the arrow direction in FIG. 5, the same gases exit cooled and relaxed after having produced work. We will carry them to a point of temperature and pressure below their dew point. They then iron in liquid phase colder than entering the device. They fall in rain and are collected in a condensation chamber (20/5) in liquid form, and it is then necessary to drive them back into the heating chamber (18/5) by means of a second turbine (25/5). repressing the liquids, and supplementing the device with anti-reflux valves (23/5) to prevent the reflux of liquids and gases. It is thus no longer necessary to recompress the gases leaving the turbine for reinjecting them into the circuit. Liquids are by nature incompressible. Of course, if we consider a concrete device and no longer ideal, corrections are to be made. They are due only to the material imperfections of the device (friction, excess heat at the outlet of the turbine, various losses, etc.), and no longer to considerations of the principle of Carnot theoretical yields.

Two scenarios appear to us: In the first, called the hot way, the source of heat and the main enclosure are hotter than the environment surrounding them. In the second, which we call here the cold way, it is the main enclosure only equipped with its accessories that operates at a lower temperature than the natural environment in which it bathes. In this case, it is the environment: air, water, etc., which can serve as a single or subsidiary main source of heat depending on the case. It is then firstly necessary in this case to protect the main enclosure against inadvertent counterproductive heating during the reflux of gases in the cold run and in this case to possibly provide accessory passive cooling means, (eg 15/4 by means of a radiator), or active, because no insulation can be perfect both in the case of an alternative device that continuous.

In the hot run, for example, it is in our interest to isolate the main enclosure all the time warmer than its environment, but only during the expansion of the gases producing work, as well as for the alternative main enclosure (FIG. for that of the turbine continuously (Figure 5). Conversely, during the recompression of the gases by the flywheel or their return to the source in liquid form, a cooling promotes the pressure drop and thus facilitates the work of the flywheel or the reflux turbine at the price a loss of yield, of course, while a warming upset the return of gases by increasing their pressure in the return phase. Similarly, it is advantageous to isolate the supply ducts and the heat-producing enclosures during the gas reflux steps so as not to upset the movement of the flywheel. We thus distinguish two stages: the stages Afflux corresponding to the influx of gases in the main enclosure whatever it is, during which any contribution of heat is welcome, without however exceeding the capacities of production of work of the device (friction , for example in hot phases) to avoid overheating, and reverso the stages Reflux during which any heat input is negative and counterproductive in the balance sheet. Anything that brings additional heat in the turbine or in the alternative device in the production phase of work favors the performance and conversely all that brings in phase of recompression or discharge of gases in liquid form is to count negative in the final industrial balance. Such overheating must be corrected by active or passive cooling means (ex 15/4), depending on the case. We know perfectly how to cool a gas and we have motive power. We claim here the principle, without making any claim on the means to implement to cool a gas. These devices are well known and have nothing original. This is no longer an application of the second principle of thermo: lower T2, the cold source, in order to widen the differential (T1 - T2) from below, coircne in the recuperator of Watt, but only to correct material imperfections resulting from the passage of an ideal machine to a concrete machine because no machine could not be perfect. They do not significantly affect the final industrial output. There is nothing to prevent the surplus from taking, even in a hot way, additional heat in the surrounding environment and incorporating it into the cycle by means of annexes by further refining the device. In this case the yield will certainly not breederener sui inconvenient ... but could be breeder compared to the input of active heat sustaining the heating cycle.

In the cold lane, the reasoning is the opposite. If the enclosure is colder than its environment, we have an interest in exposing it during the expansion of the working gases, and conversely in isolating it during the phases of reflux and recompression. Since it will be impossible to cool a cooler colder than its environment, it is necessary to foresee in this case the accessory cooling means active and a poorer performance than hot, but a production of work that can be advantageous all the same because dispensed with all active heating (eg sea water, air, solar ... etc).

We can also design exposed / isolated alternations, eventual and piece by piece to gain yields in more sophisticated devices. They do not seem to bring decisive changes to the final industrial yields at the cost of technical complications, but they are not to be discarded. We quote them for memory. Of course, we record the impact of the various annexes (ducts, heat exchange enclosures, etc.) in the final industrial balance sheet. Rather than making a tedious inventory that would compose a factorial of high rank, we give here the rule to follow that hohme art will have no trouble understanding. It therefore appears that the same causes at different times of the period may become gains or losses depending on the circumstances. They are to be considered and are listed below;

Finally it will be necessary to count in the final balance sheet with the mobilization of parts and gases.

We wanted to identify all possible causes of degradation of a perfect ideal cycle and to classify them to show that we do not ignore them in any way.

We know Q and W. We can build speakers of any size and power on demand and adapt them to any source of calories. Of course, both must be compatible and we will never be able to produce more work than we will have calories at high or low temperatures. The calorie-giving source can be a natural environment. Any heat transfer fluid can be used. We operate in closed circuits. So the risk of pollution, even thermal, is avoided.

Let Q ^{1 be} the amount of calories transferred into the main enclosure (1/4) producing the work or that of the turbine (19/4) to be converted into work.

Either in the Influx phases, Ql, all the additional internal heat gains generated in the two paths due to the friction or the still warm walls of the previous cycle, and in the cold way the heat supplements coming from the outside of the contemporary enclosure. the relaxation of the gases resulting from the imperfection of the thermal insulation.

Either in the Influx phase, Q2, the heat lost in hot mode by the enclosure warmer than its environment, whatever the mode or the quality of the thermal insulation.

Either in the Reflux phase, Q3, all cold heat acquisitions from the outside.

Let Q4, always in Reflux phases in both channels all the acquisitions coming from inside the enclosure: hot walls, friction, more in the cold way the acquisitions coming from the outside, thus to count in losses beyond the point of reflux.

Let Q5 = W5 in Joule equivalents, the work spent in both ways to mobilize the fluids or gases in their circuit in loops during a cycle, as well as to mobilize the flywheel and the piston or the turbine (friction), in their reciprocal oscillations.

Let Q6 = W6 in Joule equivalents, the work or heat losses accumulated in the cold way, as in the hot run, deliberately dissipated by the heat loss device (15/4) which we can not dispense with to correct a cycle. inevitably imperfect industrial and maintain the movement, whether it is active or passive.

the exploitable work in fine will be

in hot lanes:

Wx = Q '+ Ql - (Q2 + Q4 + Q5 - Q6) with a final yield: Q ¹ + Ql - (Q2 + Q4 + Q5 - Q6) / Q'

and in cold lanes:

Wy = Q '+ Ql + Q3 - (Q4 + Q5 + Q6) with a final yield: Q ¹ + Ql + Q3 - (Q4 + Q5 + Q6) / Q' Negative effects on yield are not prohibitive. The yields no longer depend on the theoretical yield of Carnot (second principle), but only on the degree of sophistication of the devices. As soon as this technique is generalized the greenhouse effect born of the thermal machines will have lived. It could even reverse if we draw in the heat reservoir of the planet. If we use a nuclear or solar or geothermal fuel or a hot source of natural heat, the pollution will be reduced to nothing, since there is no escape.

Claims

1 / Periodic or continuous (19/5) pendular (1/2, 1/4) pendular thermodynamic conversion devices of all powers evolving from a single heat source (14/4, 18/5) from which they draw their thermal resources and no longer between two sources of heat at different temperatures, contrary to what the first principle of thermodynamics maintains as impossible.

2 / devices for pendular (1/2, 1/4) periodic or continuous (19/5) pendular thermodynamic conversions according to claim 1 /, with phase changes of the fluids during the cycle, supercharged in heat, characterized in that they are produced within a potential primary / kinetic exchange, during the expansion phase of the gases exclusively and that the work requested (Wx, 1/4 and Wy, 19/5) is not greater than that exchanged in the potential exchange / kinetics or in the relaxation / condensation process.

3 / thermodynamic conversion devices according to claim 1 and 2, with permanent closed-loop gas recycling, such that the heat taken from the single heat source passes alone through the device being conveyed by the closed circuit gases to be converted into work under a theoretical return of 100% and an industrial yield close to 100% inherent to the material imperfections of any concrete device.

4 / devices according to claim 1 and 2 wherein the kinetic potential exchange is produced through a phase change from a gas phase to a liquid phase and reverso a liquid phase to a gas phase.

5 / devices according to claims 1, 2 and 3, drawing their main thermal resources or accessories or exclusive of a hot natural environment in which they would be immersed: air, sea, nuclear heat, hotter than the device used. 6 / devices according to claims 1, 2, 3, wherein the production of heat is inside and no longer outside the device.

7 / thermodynamic conversion devices according to claims 1, 2, 3, 4, 5, in which it is carried out heat dissipation and / or passive (15/4) of necessity to correct the material stresses likely to degrade a perfect ideal cycle in industrial uses.

8 / devices according to claim 1 and 2 regardless of the heat transfer fluid used, including fluids with phase changes during cycles.

9 / devices according to claim 1, 2, 3, wherein the movements of the fluids are assisted by mechanical means of pumping or discharge to improve performance.