FR2963645A1 - Thermal mechanism e.g. external combustion engine, has internal thermal exchanger provided internal to working volume or peripheral to working volume, where working fluid is contained in working volume during thermal cycle - Google Patents

Abstract

The mechanism has an internal thermal exchanger (5) that is provided internal to a working volume (4) or peripheral to the working volume. Working fluid is contained in the working volume during thermal cycle. Mass of the working fluid contained in the working volume is constant till at the end of the cycle. A thermal storage device is fixed to the thermal exchanger. The thermal exchanger has a cavity that serves as a reservoir that is provided at interior of the exchanger.

Description

The present invention relates to an improvement to external combustion engines, cryogenic and refrigerant mechanisms as well as to heat pumps through a new simpler, denser and more efficient design of these mechanisms. External combustion thermal engines (Stirling, Ericsson or Carnot) offer the best yields, theoretically the perfect performance of Carnot, however the management of heat flows is penalizing because complex and requiring a continuous movement of the working gas through mechanisms often complicated . These flow transfers most often require bulky and expensive control and control mechanisms. Each of them introduces new dead volumes that deteriorate yield. On the other hand, their mechanical cycle is most of the time similar to a four-stroke cycle, the Stirling engine type alpha, beta or gamma mechanisms, Stirling-Ericsson hybrid for some, have a two-cycle type cycle. but with two connected cylinders working together with a phase shift of 90 ° which is a false two-stroke and, although the different volumes are neither separated nor disconnected by valves, the working fluid continues to be driven away one cylinder towards the other, from one volume of work to another. The present invention simplifies and condenses the mechanical cycle of external combustion engines to only two mechanical times and on the other hand does not carry out any transfer of working gas. It works in a closed circuit, closed, closed to the single work volume. The mass of the fluid contained in the working volume remains constant during the entire cycle. Unlike Stirling engines, working in a closed circuit, the working fluid does not undergo any transfer here, not even that of transferring the working fluid from the volume in front of the displacer to the volume behind the displacer which is in the working cylinder. To do this, the invention fully exploits the patent that I am filing from spouse to it, the first figure of which gives an illustration. Although the invention is not limited to piston mechanisms only we will present the invention in this context which is the most commonly used and easy principle. The invention thus presents itself as a closed-volume mechanism, the volume of work, which contains a working fluid. Traditionally, external combustion engines use helium mono atomic gas which improves the characteristics of the mechanism. The working fluid is written to this single small volume, all the heat exchange necessary for its operation are provided to it via the heat exchanger which is either internal to the volume of work or peripheral to this volume of work. It is therefore no longer necessary to expel the fluid from the work volume. The natural walls of the volume of work no longer need to be pierced by numerous valves, valves, etc. their surface can be fully used as an exchanger and be improved in this sense, or conversely, when the heat exchanger is internal, their surface can be optimized to reduce losses and heat exchange between the working fluid and the body of the mechanism. Thus, the same mechanism according to the invention can also perform the three major cycles of thermodynamics, cycles at optimal efficiency (which is: 1 - Tf / Tc, if Tf is the temperature of the cold source and Tc that of the source The Stirling cycle, the Ericsson cycle and the Carnot cycle, and the accompanying figures illustrate this. Like every mechanism implementing one of these cycles it realizes the cycle by means of some concessions. Greater theoretical rigor is possible but expensive in terms of mechanism and therefore, ultimately, may become less interesting. Briefly we present the Stirling cycle according to the mechanism of the invention. In its relaxed phase the cold working gas occupies the maximum volume of the working space, corresponding to the bottom dead center of the piston. The piston rises and compresses the working fluid, an isothermal compression thanks to the excellent efficiency provided by the internal exchanger introduced into the working volume and whose shape intermesh with the piston as it is approaching its top dead center. The exchanger evacuates the heat released by the isothermal compression. A little before the piston reaches the top dead center, in this phase the piston is "almost" stopped a certain time, specificity of the mechanisms to connecting rod / crankshaft which suits us perfectly, during this phase, shortly before and shortly after, in a symmetrical manner with respect to the top dead center, the internal heat exchanger heats the compressed working fluid to near constant volume, then the piston goes down again and the internal exchanger continues heating. The fluid produces a relaxation work at constant temperature. Having reached the vicinity of the bottom dead center, the fluid is cooled to an almost constant volume in the same manner as before, its heat is stored in order to be returned to it during the reheating phase in the vicinity of the top dead center, as is done in all Stirling engine, delicate point of these engines. After which a new cycle begins, according to a two-cycle mechanical cycle integrating the four times of the thermodynamic cycle. The Stirling cycle is an interesting cycle because of its work-to-volume ratio, but it is difficult in the implementation of isochore recycling. The Ericsson cycle is more interesting because of the recycling of its isobars simpler, however this recycling handles a greater amount of heat which reduces its strong advantage from a better efficiency of its recycling. The Carnot cycle is by far the most interesting because it does not require any heat recycling, on the other hand its ratio work / volume is less good which is translated in term of yield by a higher penalty due to the mechanical losses. The triangular and trapezoidal cycles of which mention is often made are appended in Figures 16, 17 and 18 and their description. According to particular embodiments: the mechanism has a control mechanism that allows it to work according to one or more of the following cycles: Stirling cycle, Ericsson cycle, Carnot cycle, Carnot type cycles (are called cycles or Carnot type mechanisms the cycles or mechanisms obtained by the combination of two cycles or mechanisms of which both are triangular or one is triangular and the other trapezoidal, and the cycle or mechanism thus obtained has a yield equal to that of Carnot Carnot type cycles include these cycles as well as the Stirling, Ericsson and Carnot cycles), triangular or trapezoidal cycle, Beau de Rochas or Diesel cycle, steam cycle or combined cycle 2 in 1 or 3 in 1 derived from these modes and their combination. The combustion engine cycles are characterized by a two adiabatic cycle (in compression and relaxation). Carnot type cycles are characterized by a cycle with two isotherms (in compression and relaxation). Finally, the triangular or trapezoidal cycles are characterized by an isotherm and an adiabatic (either isothermal compression and adiabatic expansion or adiabatic compression and isothermal expansion, depending on the type of engine or thermal cycle, tip up or tip down). It follows that the combination of a triangular or trapezoidal cycle with a "motor-explosion" cycle is characterized by the fact that the isothermal compression or expansion of the triangular (or trapezoidal) cycle becomes partly isothermal and partly adiabatic. In the same way, the combination of a triangular or trapezoidal cycle with a Carnot type cycle makes that the adiabatic compression or expansion (according to the type of triangular cycle) becomes partly isothermal and partly adiabatic. Finally, the combination of an "engine-to-explosion" cycle with a Carnot-type cycle, as well as the combined 3-in-1 cycles that combine the three cycle families, are characterized by a partly isothermal and partly adiabatic compression. as well as a relaxation partly isothermal and partly adiabatic. As thermodynamics teaches, these cycles can be motor or thermal. Thermal mechanisms are heat pumps, refrigeration mechanisms or cryogenic mechanisms. the mechanism may or may not have a regenerating element, for example the invention designed according to the Carnot machine mode does not use a regenerator. according to variants of the invention the mechanism may have several heat exchangers which are not necessarily of the same nature; they can be internal to the work volume, peripheral, or in the extension of the volume of work and whose volume contributes to the volume of work. - The two input and output connections of the exchanger can be controlled by distributors or only one of these connections can be while the other is continuously connected to all circuits. The activated heating or cooling circuit is then that on which opens the single distributor of the exchanger and thus defines a closed circuit connecting the exchanger to the external circuit (heating / cooling / regenerator). the distributor can connect the internal heat exchanger (s) to a variable number of cold or hot thermal sources, according to the uses that wish to be made of them, and also allow them to be disconnected for adiabatic transitions. the exchanger can be either internal to the work volume of which a representation is given with the figures, or of any other invoice. the exchanger can be single or multiple; all can be assigned to the same functions, simultaneously or asynchronously, or have one / more functions specific to each of them. Thus a non-limiting example to the invention would consist in having a group of exchangers, an internal exchanger and a peripheral exchanger to the working volume is assigned to the heating function alone. A second group, an internal heat exchanger and a work volume device, assigned to the cooling function alone. Or the heating is assumed by an internal heat exchanger and the cooling by a peripheral exchanger. according to a preferred embodiment of the invention, the heat exchanges are carried out by the internal exchanger at the working volume while the peripheral surfaces at this volume are optimized in order to reduce heat losses. The total surface area of the peripheral surfaces is therefore minimized and the nature of the constituent materials are chosen for their low thermal conduction. according to variants of the invention, the heat transfers made between the exchanger and one or more external heat sources use the heat pipe technique; it thus allows heat transfer with the heat sources having a high efficiency without the need for a compression mechanism or pulse of the heat transfer fluid. The thermal transport carried out by the coolant between the heat exchanger 5 and the heat source (cold or hot) or the thermal storage device to which the heat exchanger is connected is by vaporization on one side and condensation of the other . The liquid and gaseous flows of the heat transfer fluid flow between these two ends naturally (in the absence of a mechanical device) according to the force of gravity or kinematic or dynamic mechanism, or they are pulsed or compressed or pumped using a suitable device. The heat flow linked to this thermal transport is permanent or variable, it can be activated or deactivated. according to other variants, the vapor or liquid flows of the coolant can be driven by pumps, fans, or compressors, in particular when the control mechanism precisely manages the heat flows and seeks to increase them or to increase them. reduce. For these reasons, variants whose heat transport is carried out by the heat pipe technique, which does not require any mechanical device for moving the coolant, may place a fan or a compressor on its circuit in order to increase heat exchange when the cycle requires it. . according to variants of the invention, the control mechanism adapts the intensity of the heat exchanges during a cycle by separately controlling different exchangers or elements of the exchanger, activating or deactivating them, whereby the surface and therefore, the intensity of the heat exchange varies, or by varying the flow rate of the heat transfer fluid through the exchanger, or by raising the saturating pressure of the vapor of the coolant when it is used for its vapor-liquid phase changes. Thus the control mechanism, preferably a computer (microprocessor or DSP), adapts the intensity of heat exchange during the heat transfer phases, either dynamically or according to a predefined algorithm. - The control system controls the flow of the heat transfer fluid or fluids, it can control valves or valves or control the activation of pumps. By way of non-limiting example, an exchanger only for heating the working fluid is continuously connected to the hot thermal source, only the activation of the pump which circulates the heat transfer fluid in the circuit connecting it to the source thermal distinguishes the activation of the exchanger from its inhibition. - According to variants of the invention the exchanger may comprise an internal cavity which serves as a reservoir, it contains the heat transfer fluid in liquid or solid phase. This cavity can be designed to promote heat exchange between the coolant and the walls. - The mass of the working fluid contained in the enclosed work volume may be homogeneous or heterogeneous. Its components can be in different phases (gaseous, liquid, solid) and can be in the working volume under several of these phases. according to variants of the invention, the fixed surfaces delimiting the working volume may comprise a cavity, forming part of the working volume, which serves as a reservoir for a liquid or solid fraction 40 of the working fluid. This cavity can integrate a heat exchanger or be integrated in the heat exchanger of the mechanism. The mechanism may have an orientation promoting the flow of the liquid working fluid to that cavity, or it is arranged according to the kinetics or dynamics of the mechanism so that the liquid or the solid is grouped therein. the mechanism is not necessarily a piston mechanism; if it can be the most traditionally in the world piston / connecting rod / crankshaft, it can be paddle or cylinder or piston, single or double-acting piston, or stepped, or differential, linear or rotary, reciprocating or oscillating. - According to a preferred embodiment of the invention comprises at least one heat exchanger 5, it is internal to the volume of work 4 or peripheral to the work volume or in the extension of the volume of work and participates in its volume. The heat exchanger 5 internal to the working volume is or conscript the dead volume or intermesh in the piston 1 or intermesh in the cylinder head 3 or is floating. It can be attached to the cylinder head or cylinder or linked to the piston or it can be floating. In the latter case the internal exchanger 5 is not linked to any part but floats, moves, in the work volume. Although not connected to the piston, sufficient pressure on the floating heat exchanger makes it remain permanently in contact with the piston 1. - the cylinder head and the cylinder (or liner) can be in one piece since the cylinder head has more utility as seat of many mechanical organs, it can become a privileged place for functions of heat exchange. according to variants of the invention, one or more mechanisms can be added to the invention so as to stop the stroke of the moving part for a certain time in its top dead center or its bottom dead point in order to complete the isochoric heat transfers. ; the same type of mechanism can be added to perfect isobaric heat transfer thanks to better control of the stroke of the moving part during these delicate phases; finally the object of the auxiliary mechanism may consist of a control of the stroke of the moving part for any thermal transfer whose sole purpose is, for example, to optimize the thermal recovery of the regenerator. Since this heat may have been obtained by an informal set of isochores and isobars, optimizing the recycling of this heat may require a finer control of the stroke of the moving part in conjunction with the heat exchanges. The stop produced by the mechanism on the movement of the piston, the moving part, or the control of its stroke is generally accomplished in the vicinity of one or both of the dead spots. - According to a preferred embodiment the control mechanism is constituted by a computer which has one or more algorithms providing the servocontrols corresponding to the cycles according to the variants of the invention. - According to embodiments of the invention it will have an angular sensor to know and calculate the position of the piston and the current working volume, it can be a position sensor for linear mechanisms, or any other mechanism whose data make it possible to calculate the position of the moving part performing the compression and relaxation of the cycle as well as the current working volume that it defines with the peripheral fixed surfaces. according to variants of the invention the computer may have various electronic peripherals such as memories, connections for maintenance and testing, a display system, control peripherals (user interface), buses, DACs for analog controls and conversely to convert analog to digital data, sensors necessary for its algorithms or informative about the state of the mechanism, its performance, etc. according to variants of the invention the mechanical device is associated with other mechanisms, not necessarily according to one of these claims, and forms a device where the mechanisms work in phase or out of phase with each other. These mechanisms can share mechanical, thermal, electronic, software, data, or a common control mechanism, or that the device thus obtained is of the Carnot type (the combination of the cycles of the mechanisms forms a Carnot type cycle: Stirling , or Ericsson, or Carnot or a combined cycle whose theoretical yield is that of Carnot but corresponds to a larger set than that represented by these three major cycles). In particular, and without limitation, such a mechanism can form a Carnot type motor by combining devices according to the invention which work in a trapezoidal cycle for some and triangular for others. They share a regenerator in which they store heat for some and consume the same heat for others. One mechanism can work in isochore while the other associated with it works in isobaric mode. The whole forms a Carnot type mechanism. Working temperatures such as the amounts of heat exchanged are identical. The same common control mechanism can realize a servo in a triangular cycle for one and in a trapezoidal cycle for others. according to variants of the invention the working fluid used by the mechanism may be a pure gas, such as helium or a monoatomic gas, it may be a vapor and the working volume of the mechanism contains this element under a , two or three of these gaseous, liquid and solid phases, it can be a mixture of gas or steam and the working volume contain several gaseous phases, liquid or solid.

The accompanying drawings illustrate the invention: FIG. 1 represents the invention as well as the internal exchanger to the working volume cited above. 2 shows a variant of the invention by its cycle characterized in that it allows the invention to operate Stirling engine, according to a small approximation. This cycle describes the PLC or the program of the control mechanism that manages the operation of the internal heat exchanger, among others. FIG. 3 represents a variant of the invention by its cycle, characterized in that it allows the invention to operate as an Ericsson motor. FIG. 4 represents a variant of the invention by its cycle, characterized in that it allows the invention to operate as a Carnot motor.

FIG. 5 represents a variant of the invention by its cycle, characterized in that it allows a hybrid mode between two cycles, here the Stirling cycle and that of Ericsson. FIG. 6 represents a variant of the invention by its cycle, characterized in that it allows the invention to operate according to a triangular cycle - I have not found its name, this cycle is based on three phases one isotherm , an adiabatic and a thermal transformation passing the working fluid from a warm temperature to a cold, or vice versa, hence the name by which I call it: triangular cycle - in this triangular cycle points down the Thermal transformation is done at constant pressure. The tip of the triangular cycle is the point where the isotherm and adiabatic join. As all cycles are reversible, in the same figure is presented the reverse thermal cycle to the motor cycle. The phases are not renamed according to their occurrence in order to accentuate the fact that it is the reverse cycle to the engine cycle. FIG. 7 represents a variant of the invention by its cycle, characterized in that it allows the invention to operate according to a triangular cycle pointing downwards where the thermal transformation is in isochore. Here too is presented with the engine cycle the associated thermal cycle. The two isobaric and isochoric triangular cycles have the same efficiency which depends only on Tf and Tc, ie: 1 - Tf / (Tc - Tf) * In (Tc / Tf) FIG. 8 represents a variant of the invention by its cycle, characterized in that it is triangular type tip up. FIG. 9 represents a variant of the invention by its cycle, characterized in that it is associated with a mechanism whose top dead center or low dead point marks a pose making it possible to carry out isochoric heat exchanges. Figure 10 shows a variant of the invention by its cycle, all the motor cycles can be reversed to give thermal cycles, heat pump, refrigerant or cryogenic, this and the following give two examples. This variant of FIG. 4 represents a heat pump based on the Carnot cycle. FIG. 11 shows a variant of the invention by its cycle, characterized in that it produces a cryogenic mechanism based on the Ericsson cycle. FIG. 12 represents a variant of the invention based on a mechanism of the piston / crankshaft / crankshaft type comprising planar and parallel internal exchangers served by distributors controlled by a control mechanism implementing one of the cycles described above. FIG. 13 represents a variant of the invention illustrating a more precise way of managing the heating / cooling phases of the working fluid, this figure is a partial view of the piston and internal exchangers which fit into it as well as distributors associated with each exchanger. FIG. 14 shows a variant of the invention where the internal exchanger is inverted and becomes an exchanger external to the working volume, although its internal volume containing the working fluid is always part of the enclosed work volume. The working fluid never leaves this volume of work, here too. FIG. 15 represents a variant of the invention inspired by the heat exchanges of the Stirling type engines adapted to the invention. Fig. 16 shows the triangular cycle pointing downwards according to a PV diagram. Fig. 17 shows the triangular cycle pointing upwards according to a PV diagram. Figure 18 shows the triangular and trapezoidal cycle which is extracted therefrom. Referring to Figure 1 we have a descriptive diagram, by section, of the mechanism according to the invention based on the technique of piston engines / connecting rod / crankshaft. We have the piston 1 comprising a cylindrical groove 6 in its head. The groove 6 allows the internal heat exchanger 5 to interlock with the piston 1 when it rises to the high position. A clearance 7 separates the groove 6 of the internal exchanger 5, a spirally wound tube and section 8. This game 7 contributes to the dead volume of the mechanism. A heat transfer fluid passes through the exchanger according to the flow 9, entering 11 (not shown in the section) and emerging at 12. The tabs 10 hold the coil 5 in position and the fixed to the cylinder head 3. The piston 1, the cylinder 2 and the cylinder head 3, removed from the volume of the internal heat exchanger 5, forms the working volume 4, closed volume from which the working fluid is never expelled. This volume of work is filled with a working fluid (generally one chooses helium for this purpose) whose pressurization and maintenance are done through the conduit 13. Theoretically, once the volume 4 put under pressure there is no need to intervene, in practice the sealing problems between the cylinder and the piston will make it necessary to return the work volume 4 in its commissioning conditions. The outlet 12, like the inlet 11, leaves the cylinder head 3 to arrive at a distributor 15, identical distributor 14 for the inlet (not shown), the distributor is controlled by a control mechanism 16. According to the instruction of the control system 16 the distributor 15 (respectively 14) connects the output 12 (respectively the input 11) with the circuit of the cold source 17 or the circuit of the hot source 18 or the regenerator circuit 19 when the mechanism corresponds to one of the variants of the invention requiring a regenerator (Stirling or Ericsson machines, for example), according to certain cycles the distributor also disconnects the internal heat exchanger 5 of all the circuits (adiabatic phase). The circuit 5-12-15-17 (respectively 18 or 19 when connected) -14-1 1-5 is a closed circuit which may comprise one or more mechanisms for circulating the coolant, or thermal sensors, for pressure, The arrow 9 indicates the flow of the coolant in the tube of the internal heat exchanger 5. The pump circulating the heat transfer fluid can either be controlled by the control mechanism 16, or be locally controlled by a sensor, for example, either, the simplest, be continuously activated. This is the case when the pump is located between the distributor 15 and the cylinder head 3 or between the cylinder head and the distributor 14. It pumps continuously that the circuit is that of the cold source, that of the hot source or the regenerator according to the instructions from the control mechanism 16 applied by the distributors 14 and 15. The distributors 14 and 15 have the same functions and work together to connect the inlet and the outlet of the internal exchanger 5 to the desired circuit. By abuse of language we will speak of "distributor" only or "distributor 15" being understood that the same treatment is addressed to the two distributors 14 and 15. The control mechanism 16 and the distributor 15 can be both electrical, mechanical Or other. The oldest technique in this field is the camshaft but the distributor does not need as much power as it is necessary to order valves so it is possible to envisage a multitude of simpler solutions such as an opening solenoid valve. on two or three inputs (respectively outputs) depending on the commands. It may also be chosen to use two-stage series solenoid valves enslaved by the control mechanism 16. The mechanical characteristics that determine the dead volume and the maximum volume that the working volume 4 will take when the piston will be at its low dead point, are specific to the use that will be made of the mechanism according to the invention, the ratio between these volumes intervenes indirectly in the efficiency of the mechanism for certain variants of the invention. To obtain very high compression ratios, particularly for high efficiency Carnot cycle engines, the choice of exchangers is crucial. That of Figure 1 probably would not fit. Then another type of internal exchanger will be chosen as a set of planar, parallel heat exchangers perpendicular to the axis of rotation of the cylinder in order to minimize the gaps 7 between the piston 1 and the heat exchanger 5. such that the grooves 6 are blind to allow the segments to be placed at the top of the piston 1. A great diversity of shape and texture characterizes the exchangers internal to the work volume, to these are added the existing techniques in the domain. Patented internal heat exchangers provide a considerable gain in heat exchange efficiency that is done internally. The improvement of internal exchanges, the position of the exchanger within the volume of work and no longer at its periphery, but also the improvement of thermodynamic cycles (for combined cycles 2 in 1 based on the cycles of Beau de Rochas or Diesel) not only avoid thermal losses via the walls of the engine but in addition the engine efficiency will gain to isolate these walls and to limit as much as possible these heat losses while they were formerly favored for a good operation of the engines. The internal exchanger 5, on all its surfaces, is only in contact with the working fluid and no longer with the mass of the cylinder 2 that we seek to make the least possible conductor. The cylinder head 3 has no reason to be since it can not stand any major and delicate parts except here the internal heat exchanger 5, it can be a single piece with the cylinder 2 (or the shirt). A variant of the invention consists in using several internal exchangers, for example three internal exchangers, one would be continuously connected to the hot source and would be active only when the phase of the mechanism requires its activation, another would be continuously connected to the cold source and similarly would be activated when the mechanism is in the phase corresponding to its activation, and a third would be with the regenerator in the same way. This introduces an extra amount of space and saves only the distributors. As we will notice in the following figure, figure 2, the variation of volume is weak during the phases 1 and 3 since we are in the vicinity of the dead spots, however it is not null which generates a loss compared to the yield of Carnot It may therefore be desirable to add to the mechanism piston rod / crankshaft a more complex linkage such as a number have already been patented to extend the dead spots. They produce a stoppage time of the piston in these positions thus making it possible to achieve real isochoric transformations, hence a better yield. The addition of such a mechanism may be useful for variants of the invention operating in Stirling engine, for example, and the following Figure 2 presents it to us. In this cycle, such a mechanism is more necessary for the isochoric heating phase S3 than for the isochoric cooling phase S1. Indeed, if Figure 2 gives a length equivalent to these two phases, this equal duration of heat exchange penalizes the efficiency. Better performance requires reducing the time allowed for heat exchange in phase 3 so that the variation in compression ratio related to 101a is equal to the variation in compression ratio related to 101 b. Losses from this mismatch of changes in actual compression rates during isochoric phases may add to neglected losses except when 101b and 101a will start to become significant. Therefore, the mechanisms whose speed of rotation is fast will favor the alternative to the invention described here to allow sufficient heating in S3 at the expense of a little efficiency or opt for a more complex linkage. An identical problem will be encountered for each cycle even if the Stirling cycle presented in figure 2 makes it stand out better. The current state of the art provides many technical solutions to this problem. Referring to Figure 2 we have a diagram giving the behavior of the preceding control mechanism 16, and the manner in which it orders the times / phases of the mechanism of the invention according to this variant, in particular the management of heat exchanges. Figure 2, and those that follow, does not represent the control mechanism itself, one skilled in the art will give it a suitable embodiment, traditionally the world of mechanics uses camshaft to achieve a such enslavement. This technique is a bit rustic and quite suitable for understanding the phases / time. Another solution, which we will privilege, uses a calculator. The latter receives digital or analog information on the state of the mechanism and sends its instructions in electrical form to the organs that it controls. Among this essential information is the angle of rotation of the engine. An angular sensor related to the rotation of the crankshaft provides this information to the computer. The use of calculator not only provides the mechanism with a simple and light way of managing the control process, but it brings all the power and the numerous potentials of the computer science to improve and refine this servocontrol. Subsequently we will consider that the mechanism of the invention is derived from the technique of piston / crank / crankshaft engines, which is in no way restrictive to the invention. The circle 51 of FIG. 2 represents the rotation of the crankshaft, at each rotation of the crankshaft is associated a position of the piston which corresponds, shall we say, to the projection of the point of the circle 51 on the vertical axis 61. The mechanism described according to this variant of the invention is a Stirling cycle engine. The direction of rotation of the engine is given by the central arrow. The piston therefore describes an oscillating movement between its top dead center 71 and its bottom dead center 91, at mid-stroke it is at 81. We begin the cycle at bottom dead center 91, in the middle of cycle 1 which starts at S1. The piston starts to rise. A singularity of the engine with crankshaft is to have a stroke speed of the sinusoidal type pistons. Very fast in 81, it is almost stopped in 91 and in 71. This quasi immobility is for us interesting because it allows us to make the phases of cooling / heating isochores (with constant volume) of the Stirling cycle in the vicinity of these points. Thus these thermodynamic transformations are very nearly isochoric, as indicated by the small positional deviation of the piston in these phases indicated in the drawing by 101a in the top dead position and 101b in the low dead position. From its low dead point the piston leaves its pseudo stop and therefore ends its cooling phase during which the heat of the working fluid is recovered in a regenerator for later recycling. This is indicated by the outgoing arrow and its value marked Qr indicating the amount of heat taken. This amount of heat Qr corresponds exactly to the amount of heat we will need a little later in the cycle, during reheating (phase 3). The mechanism therefore completes phase 1, the isochoric cooling. It arrives at point S2 through which phase 2 begins, the isothermal compression at low temperature. In S2 the control mechanism sends the instruction to the distributor to close the regenerator circuit and connect the internal heat exchanger to the circuit of the cold source. We are in a motor cycle so the isothermal compression is at low temperature. The exchanger discharges the amount of heat Qf corresponding to the isothermal compression. In compression fm, at point S3, when the piston moves little and therefore the volume varies little-here is relatively a little less true than at the bottom dead point as we are close to the dead volume-we enter the phase 3 of the Stirling cycle, isochoric warming. The heat Qr stored in the regenerator is then returned to the working fluid. The control mechanism then sends the instruction to the distributor to close the circuit connecting the heat exchanger to the cold source and connect it to the regenerator for a return of the stored heat. What is represented by the incoming arrow associated with Qr. At the losses we find the temperature of the hot spring. We then arrive at point S4, beginning of cycle 4 the isothermal expansion at high temperature. The control mechanism sends the instruction to the distributor to close the circuit connecting the internal heat exchanger to the regenerator and connect the heat exchanger to the circuit of the hot source. Then the piston carries out the isothermal expansion at the temperature of the hot source. It consumes a quantity of heat Qc, the arrow pointing to the circle 51 indicates that heat Qc is brought to the mechanism. After which, at the end of expansion it reaches the point S1, the control mechanism sends the instruction to switch circuit and connect the exchanger on the circuit of the regenerator. The mechanism enters phase 1, it stores the heat Qr corresponding to the cooling of the working fluid from the hot temperature to the cold temperature in the regenerator. Its working fluid changes to almost constant volume from the hot temperature to the cold temperature which produces a drop in pressure. And a new cycle begins when the piston has achieved only one return for a complete engine cycle and without any transfer of working fluid. This is a huge gain in time or otherwise in terms of weight since a half less heavy and half bulky engine produces a job identical to that produced by a conventional mechanism. We also gain a little in terms of weight in the fact that it is not necessary to expel the gas, so the entire stroke of the piston is functional. The race corresponding to the dead volume does not penalize the mechanism in a sterile manner during the expulsion / admission phases. Finally the mechanism gains enormously in simplicity by getting rid of control organs and transfer of work gas streams, their mass and their size. We note that the isochoric transformation, here, isobaric just after, are not natural transitions of the working fluid of a moving motor. Also the mechanism according to the invention will gain a lot and without additional weight and mechanical complexity to use an electronic control mechanism to monitor and control these phases to get as close as possible to the theoretical cycle. These isobaric and isochoric transitions are the Achilles heel of external combustion engines. The mechanism according to the invention provides a first advantage by its simplification, a second, and not least, consists in precisely controlling its thermal transformations no longer by simple deterministic mechanics but by dynamic and adaptive systems that are calculators thanks to their algorithms and their computation speed associated with a set of sensors and controls. Anyway there will always be a gap between the theoretical cycle and its hardware implementation, which left and leave the field to the inventors. With reference to FIG. 3, the diagram gives the behavior of the control mechanism which constitutes a variant of the invention producing an Ericsson cycle engine. As in the previous figure when the crankshaft performs a turn, the circle 51, the piston makes a return all between its bottom dead center 91 and top dead center 71, the point 81 being its median. The motor rotates in the direction of the arrow in the center of the circle. We start at low dead point 91 which is also point E1, point of change of phase, we enter the phase of cooling of the working fluid which, at point E1, is still at the temperature of the hot source and must, at term of phase 1 be at the temperature of the cold source according to an isobaric transformation. So at point E1 the control mechanism sends the instruction to the distributor to switch the inlets out of the internal exchanger circuit of the hot source on the regenerator circuit. During phase 1 the quantity Qr of heat is transmitted to the regenerator for its recycling. This amount of heat is important because this operation is done at constant pressure. Since the working fluid is generally Helium, the ratio between the recycled values at constant pressure (Ericsson) and at constant volume (Stirling) is 1.667 times higher. The losses are proportional to these manipulated quantities. During this cooling phase the cooled fluid contracts, the piston accompanies this contraction of the fluid, it then travels the path indicated by 101b. At point E2 the fluid is at the low temperature of the cold source. The mechanism changes phase to enter phase 2 of isothermal compression. The control mechanism sends the instruction to the distributor to switch the inlets out of the internal exchanger of the regenerator circuit to the circuit of the cold source. Phase 2 is completed, the piston compresses the fluid, the exchanger discharges the quantity Qf of heat corresponding to the isothermal compression of phase 2. At the top dead center 71 which is also the point E3, the mechanism passes into the phase 3 which is the heating of the working fluid at constant pressure. To do this, the control mechanism sends the instruction to the distributor to change the connection of the internal exchanger of the circuit of the cold source to that of the regenerator. The heat Qr is restored to him, with the losses near. The dead volume expands under the effect of the heat that is transmitted to it, the piston accompanies the fluid in this phase of expansion. At the end of phase 3 the fluid has found the temperature of the hot source, the ratio V4 / V7 (V7 is the dead volume) is the same as the ratio V1 / V2. Since the volume V1 is larger than the volume V7, ie V3, the path 101b of the phase 1 is much larger than the path 101a of the phase 3. At point E4 the mechanism goes into phase 4 of hot isothermal expansion. The working fluid is hot. The control mechanism sends the instruction to the distributor to switch the exchanger of the regenerator circuit to the circuit of the hot source. During phase 4 the working fluid relaxes in a hot isothermal expansion and provides work to the piston. The isothermal expansion consumes a quantity Qc of heat indicated by the incoming arrow. At the bottom dead center, the cycle is completed and returns to phase 1 after the control mechanism has switched the power supply of the internal heat exchanger. Here again, simply and in a single rotation, a complete cycle is performed in a closed circuit, without requiring the transfer of the working fluid as is usually the case.

With reference to FIG. 4, the diagram gives the behavior of the control mechanism of the invention, it constitutes a variant of the invention producing a Carnot cycle engine. The mechanism of Carnot is very interesting because much simpler, besides it does not require recycling and storage of heat, a very favorable point, because this point is a source of difficulties, loss of yield and congestion due to elements outside the engine. Unfortunately it does not have only strong points, its weak point is, to obtain high yields, to require a high rate of compression. If the invention does not deal with solutions to this problem, a high compression rate induces more mechanical losses, but it brings an advantage over the traditional mechanisms which is its non-cylinder head. Thus the gougeons fixing the cylinder head to the engine block are no longer of any use and the limitations related to their pulling stress are no longer restrictive. All mechanical difficulties are not swept away, the efforts that the rods and crankshafts undergo, nor the pressure that pushes the body of the crankshaft engine, however this small advantage is appreciable. As in the previous figures the circle 51 represents the rotation of the crankshaft while the position of the piston is represented by the projection of the position of the crankshaft on the axis 61. The piston is in the top dead position in 71 and in the dead position low in 91, in 81 he is in the middle of his race. The crankshaft rotates in the direction of the arrow in the middle of the circle. We start the cycle in low dead position 91 which corresponds to the point Cl, the beginning of phase 1 is the isothermal compression at low temperature. The control mechanism sends the instruction to the distributor to connect the internal exchanger to the circuit of the cold source. This compression produces a heat Qf the exchanger discharges to the cold source, hence the outgoing arrow Qf. At point C2 the control mechanism cuts the cooling circuit. The mechanism enters its phase 2 which is the adiabatic compression, without heat exchange, the compression continues to the point C3 which corresponds to the top dead center. There the working fluid has reached, by compression, the temperature of the hot source. The control mechanism sends the instruction to the distributor to open the circuit with the hot source. The exchanger supplies heat to the fluid during its phase 3 the hot isothermal expansion, where the incoming arrow Qc. At point C4 the control mechanism assigns the distributor to cut the circuit with the hot source. During phase 4 the relaxation continues in adiabatic, without heat exchange. At the end of phase 4, the complete relaxation, we arrive at the bottom dead point which is the point CI, starting from phase 1, the beginning of the isothermal compression. At the point Cl the fluid relaxed at the temperature of the cold source. We have just come here again to carry out the complete cycle, that of Carnot, either four times, in a single rotation, or two mechanical times, compression and relaxation. The adiabatic compressions and relaxation are of equal size, of energetically zero balance ... with mechanical losses. If the adiabatic compression stroke is greater it is that it takes place at the end of compression while the adiabatic expansion is performed at the end of expansion, or V3 / V2 (where V3 is equal to the dead volume) is equal to V4 / V1. We will notice that the cycle illustrated according to this diagram would be of a weak yield. The higher the efficiency, the greater the adiabatic compression / expansion strokes, since the Carnot yield depends on both low and high temperatures and is related to the adiabatic compression ratio. Hence the second weak point of this mechanism, a low power ratio released / volume. Its easiest and most appropriate application will therefore be in the field of heat pumps or in cryogenics, in an inverted cycle. As we pointed out at the beginning this cycle is simpler, it does not involve regenerator, delicate mechanism and deposit with loss of yield. Here, only two flows of heat transfer fluid occur and both are done at a constant temperature, which poses no technical difficulty. With reference to FIG. 5, we have seen the variants of the invention making it possible to operate according to the Stirling, Ericsson and Carnot cycles, just as there are a multitude of mechanisms deriving from the Stirling engine, Stirling. alpha, beta, etc. variations that take some liberties with the theoretical cycle sometimes by mixing cycles as the Stirling Alpha cycle is a mixture of Stirling cycle and Ericsson cycle, we can do the same here, a mix of cycles. In fact the mixing may occur without the knowledge of the designer of the mechanism if for example its internal heat exchanger fails to warm up quickly the working fluid during phase 3 of Figure 3 showing the invention according to the cycle of Ericsson, then the isobaric warming phase will include an adiabatic relaxation component not provided for in the theoretical cycle. Note that this adiabatic expansion component will increase the temperature difference between the working fluid and the coolant which will accelerate heat exchange. However, this will result in a loss of yield. Similarly during the cooling, phase 1 Figure 3, over a longer period, but if there too the heat exchanger was too low where the flow of heat transfer fluid insufficient then, without the knowledge of the engineer, instead of a simple cooling we would have an adiabatic compression component which would hinder performance. Hence the remark that was made about the benefits provided by a calculator. A calculator will significantly improve the management of thermal flows and therefore losses related to heat exchange. It is therefore necessary that the mixture of isobaric and adiabatic components, here, of the relaxation phase corresponds to the mixture of components of the compression phase. This is what we are looking for in the hybrid variant example of Figure 5. Cycle-specific points are prefixed "H". This is a variant implemented by other mechanisms, a hybrid Stirling-Ericsson cycle. The invention according to this variant starts phase 1 before the bottom dead point 91 as in a Stirling cycle, however it continues further and then acts as in a cycle of Ericsson by a lowering of temperature producing a contraction of the volume to constant pressure. Phase 1 which starts at point H1 consists in cooling the working fluid from its initial hot temperature to the temperature of the cold source by recycling the heat of the fluid in the regenerator. For this purpose the control mechanism sends the instruction to the distributor to connect the internal exchanger to the regenerator circuit. Here Qr is no longer purely isobaric, nor purely isochoric, it has an intermediate value between these two extremes which depends on the proportion of its isochoric components of points H1 to H1b and then isobaric from points H1b to 112. Having reached point 112, the mechanism enters phase 2. The control mechanism sends the instruction to connect the internal exchanger to the circuit of the cold source. Begins low temperature isothermal compression of working fluid. This releases a quantity Qf of heat towards the cold source. At point 113 the mechanism enters phase 3, warming up from the recycled Qr heat. There the control mechanism sends the instruction to connect the internal heat exchanger to the regenerator circuit for this recycling. A first part is isochorically points 113 to H3b and isobarically H3b to H4. Note in passing that we are losing heat. In phase 1 the transformation at low temperature is done at constant pressure which gives it an important factor Cp or its recycling in phase 3 is done at constant volume related to the factor Cv of the fluid, so there will be an excess Cp-Cv which will not be recycled. In the same way, the high temperature part is recycled in isochore so of a factor Cv whereas during the warming up in phase 3 this high temperature part is recycled in isobar so of a factor Cp, conclusion all Cv will be recycled and it will be lacking of it a Cp-Cv value which will require heating from the hot source. So the yield deteriorates the more as we move away from one of these cycles. Note that the first loss is an actual loss of heat while the second induces an underlying triangular cycle which is not a gross loss but a decrease in yield. At point H4 the mechanism enters phase 4, the control mechanism sends the instruction to connect the internal exchanger to the circuit of the hot source. The cycle ends with isothermal expansion at high temperature. The isothermal expansion consumes a quantity of heat Qc, incoming arrow. And we go back to the beginning of the next cycle, at point Hl phase 1, cooling and recycling. To the problem related to the thermal losses due to the periodicity of the cycle and not its symmetry (isochore + isobar in phase 1 associated with isochore + isobaric transformations in phase 3), we could consider some variants to the invention consisting of finishing as we started by an isochore to recycle the same amount of heat at the same temperatures. In this case we must start earlier phase 3 to warm up by the heat of the isobar between Hlb and 112 the working fluid from a point H3a to H3. This operation corresponds to adiabatic compression, which does not allow us to achieve the desired goal, better recycling. The new cycle will extend the hot isothermal expansion from H3b and will adiabatically compress H3a to H3. This leads to the loss of the heat taken in between points H1b and 112 in phase 1. The number of variants obtained by combining the three alternatives (isochore, isobaric, adiabatic) during the cooling phase and then, for each of them, combining it with one of the combinations of the same kind for the warming phase is very important. If we add variants from the same combinations in which there is only one or none of the isotherms instead of the two isotherms of the ideal cycles, then the list goes on considerably. Each cooling or warming can be composed of a combination of one, two or three of these transformations: isochore, isobaric and adiabatic. The isochore is a symmetrical thermal transformation with respect to the central axis, noted 61. The isobaric is an asymmetric thermal transformation, on one side of the central axis. Adiabatic is an asymmetric transformation on one side of the central axis in the absence of heat exchange; it produces or consumes energy directly related to the lowering or raising of the temperature of the working fluid. Among these cycles, some correspond to the equivalent cycle of internal combustion engines integrated in the mechanism according to the invention which accomplishes them in two mechanical times. Therefore we find adapted to the invention the cycles improving the efficiency of internal combustion engines, combined cycles 2 in let 3 in 1. These combined cycles result from the combination of two or three triangular or trapezoidal cycles, motor type explosion or Carnot type. The specificity of these cycles is for the triangular cycle a compression and a relaxation of which one is isothermal and the other adiabatic. The specificity of internal combustion engines and turbines is to consist of adiabatic compression and expansion. The specificity of Carnot type cycles is to have isothermal compression and expansion. Thus a combined cycle 3 in 1 which integrates in a single cycle these three rings triangle or trapezium, engine explosion Carnot type engine comprises a partly isothermal and partly adiabatic compression and a partially isothermal and partly adiabatic relaxation. We give briefly some examples of the cycles that the control mechanism can integrate according to one of these many variants. From Hla to 91 adiabatic relaxation; from 91 to 113 isothermal compression; from H3 to H3b isochore warming; H3b to Hla isothermal relaxation. The isochore, which could be an isobar, uses the heat of the hot source since there is no regenerator in this cycle as it is described. From Hla to 91 adiabatic relaxation; from 91 to H3a isothermal compression; from H3a to H3 adiabatic compression; from H3 to H3b isochore reheating; from H3b to Hla isothermal relaxation. - From 91 to H3a isothermal compression; from H3a to H3 adiabatic compression; from 113 to H3b isochore heating; from H3b to 91 adiabatic relaxation. This is one of the combined cycles 2 in 1 This variant is a further illustration of the interest of a control mechanism consisting of a computer since here this motor cycle requires an adaptive capacity of the cycle. Indeed according to the power variations requested from the engine the hot temperature will be higher or lower. In order for the cycle to work and for the mechanism to return to the previous states, for example in the vicinity of the bottom dead point 91, it is necessary to vary the position of the point H3a as a function of the heating temperature. Note that the positions of the points indicated on the circle 51 what matters in the sequences given here is their order. The length of their phases needs to be adapted to cycles and conditions of use. To give a last cycle, we will give that of the adapted gasoline engine here without making any improvement: - From Hl to Hlb isochoric cooling (the heat is evacuated towards the cold source); from Hlb to H3 adiabatic compression; from 113 to H3b isochore heating; from H3b to Hl relaxation adiabatic. Note that here the adaptive capacity of the control mechanism is not necessary since the thermal waste ensures the stability of the cycle. Note in passing that it would not be necessary to superhuman effort to improve this cycle, simply by recycling the heat of the isochore Hl-Hlb.

Of the many variants that can be combined from the described cycle phases a number produce heat. As a result they have a lower yield than Carnot's yield since they give off heat which increases their losses. However, these variants implicitly include a triangle cycle. But it is possible from any triangular cycle to associate another triangular or trapezoidal cycle (a modified triangular cycle) as associated they compose a perfect cycle either Stirling type or Ericsson or Carnot type or other. It is therefore possible, by the addition of a triangular or trapezoidal cycle-dependent mechanism or their implementation according to variants of this invention which are presented below, to find globally, the two closely associated mechanisms, the ideal yield of Carnot. .

Referring to Figure 6, we present two variants of the invention the one motor, rotation according to the arrow A, and the other of the heat pump type, the reverse cycle, rotation according to the arrow B, adapting to the invention the triangular cycle. Figure 6 is a cycle integrating a transformation at constant pressure, the following figure, 7, presents the equivalent variant to constant volume. The circle 51 corresponds to the rotation of the crankshaft which turns in the direction A for a driving mechanism, note that in all these figures this meaning is a convention the crankshaft can physically turn in opposite direction just replace the phases depending on the direction agreed; or it turns in the direction B for a heat pump type mechanism. At each angular position of the crankshaft is associated a position of the piston which is obtained by projection of this point on the axis 61, in reality it is a little more complicated since the length of the connecting rod intervenes, so the piston oscillates between the top dead center 71 and bottom dead center 91. Depending on the motor variant, direction of rotation A, the mechanism starts in phase 1 at bottom dead point 91 or TP1, the control mechanism sends the instruction to the distributor to connect the internal exchanger to the circuit of the cold source. From point TP1, bottom dead center 91, to point TP2 corresponding to top dead center 71, the mechanism carries out isothermal compression at low temperature. The internal exchanger evacuates the quantity of heat Qia, outgoing arrow. In TP2, at top dead center 71, the control mechanism sends the instruction to the distributor to switch the circuit of the cold source on the circuit of the hot source. The mechanism enters phase 2, heating at constant pressure, it absorbs the amount of heat Qa, incoming arrow. Note that this heating can come from a continuous and abundant hot source such as an external burner or a regenerator or something similar whose temperature varies between Tf and Tc. At point TP3, the mechanism enters phase 3, the control mechanism sends the instruction to the distributor to disconnect the internal exchanger. The mechanism performs adiabatic relaxation from point TP3 to point TP1, bottom dead center 91. When it reaches bottom dead center 91, the cycle is complete, the mechanism enters phase 1 again and starts a new cycle. For a variable temperature Tc the position of the point TP3 varies so that in 91 the working fluid is always at the temperature Tf of the cold source. The associated variant in the thermal cycle of the heat pump type rotates in the direction B. At bottom dead point 91 it enters phase 3, the control mechanism sends the instruction to the distributor to disconnect the internal heat exchanger. The mechanism adiabatically compresses the bottom dead center to point TP3. At point TP3, the mechanism enters phase 2, the control mechanism sends the instruction to the distributor to connect the internal exchanger to the cooling circuit, which can be a regenerator associated with another mechanism, from point TP3 to top dead center. the working fluid is cooled to constant pressure. It produces a quantity of heat Qb, outgoing arrow. At point TP2, top dead center 71, the mechanism enters phase 1, the control mechanism sends the instruction to switch the connection of the exchanger of the cooling circuit to the cold source circuit. From high dead point to low dead point the mechanism is an isothermal relaxation at low temperature, it absorbs a quantity of heat Qib, incoming arrow. Arrived at the bottom dead center it has completed a complete triangular cycle and enters a new cycle passing in phase 3.

Note: if this variant is used as a heat pump and not in the composition of a Carnot type cycle, then only part of the heat Qb produced can be exploited. In this case, either the cooling of the phase is completed by the cold source, which is waste, or in TP2, the top dead center 71, the temperature of the working fluid is higher than that of the cold source. This heat will then be exploited by an adiabatic expansion until the temperature of the working fluid reaches the temperature Tf in TP2b. In this case the control mechanism sends in 71 the instruction to the distributor to disconnect the internal heat exchanger and it is only TP2b he gives the instruction to connect it to the cold source. The efficiency of a heat pump operating in a triangular cycle is less than the efficiency obtained by a heat pump working according to one of the optimal cycles, and all the more so that the temperature at the end of adiabatic compression is away from the desired temperature. However, as for the motor cycle, this cycle is better suited for variable temperature heat exchange. For example to warm a cold fluid to a higher temperature. With reference to FIG. 7, the variant presented here according to the motor mode, rotation according to the direction A, and thermal such that the heat pumps, according to the direction of rotation B, are the counterpart of FIG. is accomplished in isochore. According to the variant of the motor type, direction of rotation A, the mechanism begins its cycle in TV1 at low dead point, entering phase 1 the control mechanism sends the instruction to connect the internal heat exchanger to the circuit of the cold source. From the bottom dead point 91 to the point TV2 the mechanism carries out an isothermal compression which releases a heat Qia, outgoing arrow. At the point TV2, the mechanism goes into phase 2, the control mechanism sends the instruction to switch the connection of the internal heat exchanger with the heating circuit, which can be a regenerator or the exhaust gases of a heat engine - there is no incompatibility if the source provides heat at constant pressure and this mechanism works, internally, at constant volume - this for example, from point TV2 to point TV3 the piston moves very little as shown the difference 101, the variation of volume is quite small (it depends strongly on the compression ratio) and is assimilated to an isochoric transformation. In order to obtain a purely isochoric transition it is possible to modify the linkage, or the equivalent mechanism, in order to prolong the top dead time of the point TV2 at the point TV3, these points are precisely symmetrical on both sides of the axis 61 which is perfect for simple mechanical solutions. Many such patents are already in the public domain. At point TV3 the mechanism enters phase 3, the control mechanism sends the instruction to the distributor to disconnect the internal heat exchanger. The piston performs an adiabatic relaxation of the working fluid from the TV3 point to the bottom dead center 91. In 91 the triangular cycle is completed, the mechanism enters phase 1 and starts a new cycle. The thermal variant, of the heat pump type, turns in the opposite direction, direction b. At the neutral point 40 low 91 it begins by entering its phase 3, the control mechanism instructs the distributor to disconnect the internal heat exchanger. From the bottom dead point 91 to the TV3 point the mechanism makes an adiabatic compression. Arrived in TV3, the mechanism enters phase 2, cooling at constant volume. The control mechanism gives the instruction to connect the internal exchanger to the cooling circuit. The exchanger discharges a quantity of heat Qb, outgoing arrow. At point TV2 the working fluid is at the temperature of the cold source. The mechanism changes phase and goes into phase 1. The control mechanism instructs the distributor to switch the internal exchanger of the cooling circuit to the circuit of the cold source. The piston performs a cold isothermal expansion from the point TV2 to the bottom dead point 91. The mechanism consumes a quantity of heat Qib, incoming arrow. Here its thermal triangular cycle is completed, it starts a new cycle and enters phase 3. The previous remark is here also applicable in the case of operation as a heat pump, it is then possible to introduce a small component adiabatic relaxation between points TV2 and TV2b to consume residual heat neglected by the source exploiting the thermal properties of the mechanism whose temperature is higher than the cold source. Or to evacuate through the cold source, which is pure loss. Note that the specificity of these last two thermal cycles based on the triangular cycle is to produce a heat whose temperature is not constant (from Tc to Tf), here it is not a plateau contrary to what the thermists appreciate. This specificity may be interesting in some cases as a differentiated heating that manages different temperature ranges for a single heating system. For example a high temperature in the nursery and the main place of life, softer in the rooms and other rooms and finally a cool temperature in the cellar and other annexes. Note that if the working fluid is a refrigerant working in the presence of two or three phases (gaseous, liquid or solid) we then find the usual cycles for refrigerators and thermists. The characteristic of the invention provides an appreciable advantage in limiting the use of greenhouse refrigerant to the minimum necessary for thermodynamic cycles since the entire mass of refrigerant required for the mechanism is contained in its working volume. For these steam mechanisms isothermal detents differ from those for dry gas mechanisms since the amount of heat (consequent) Qib provided by the exchanger is used to evaporate all or part of the liquid contained in the working volume. The trigger is then at constant temperature and pressure. To the variants presented in FIGS. 6 and 7 we can associate a variant of general order which is indistinctly isobaric or isochorous, that is to say whose point TV2 is neither the top dead center, nor such that there is symmetry between the points TV2 and TV3 on both sides of the axis 61, the point TV3 remaining closer to the bottom dead point than the point TV2 in a motor cycle. Thus, the mechanism will have an isochoric component and another isobaric component. This does not affect the performance of the mechanism. We can also notice that the designer of a mechanism according to the invention will have to take into account the hazards of the technique, thus the delays between the instruction and the action that it is supposed to involve because of the lengths of tubes, masses, ... for reasons of losses in the internal exchangers or the regenerator all these hazards will make that the cycle actually implemented in the control unit computer or simply mechanically as by a camshaft mechanism will be different from the theoretical cycle because of these delays or advances that they will have to take even of the introduction of brief adiabatic sections not appearing in the theoretical algorithm described that they will apply.

With reference to FIG. 8, the variant presented here according to the motor mode, rotation according to the direction A, and thermal according to the direction of rotation B corresponds to the triangular cycle pointing upwards (the point being the junction point of the isotherm with adiabatic in a pressure-volume graph). The thermal exchanges are here arbitrary, a confused mixture of isobaric and isochorous as it is possible to do for each of the cycles presented. It is thus a kind of general case distinct from the isochoric or isobaric case. The motor cycle according to the triangular cycle points upwards, according to the direction of rotation A, behaves as follows. The working fluid of the mechanism is in its initial state, under ambient conditions for most cases (reference state), at point TH1. In TH1 the control mechanism sends the instruction to disconnect the internal exchanger. The mechanism enters phase 1 of adiabatic compression. The piston having reached its top dead point 71 (TH2), the compressed working fluid is hot and its compression was such that its temperature corresponds to that of the hot source. The mechanism enters its phase 2, the control mechanism sends the instruction to connect the internal heat exchanger to the hot source. The mechanism begins its hot isothermal expansion, it consumes a quantity of heat Qa, incoming arrow. At the point TH3, the control mechanism sends the instruction to switch the connection of the internal exchanger of the hot source to another source (cold source ... or other), the mechanism enters phase 3. During phase 3 the working fluid is cooled. This cooling is arbitrary, a mixture of isochore and isobar or even other, as shown in Figure 8 by a TH3 point before the bottom dead center and a TH1 point well above it. During this cooling phase, the working fluid contracts. The internal exchanger discharges a quantity of heat Qfa. At the point TH1 the cycle is complete, the mechanism enters phase 1 and starts a new cycle. We note that the yield of the triangular cycle points upwards is less than that of the triangular cycle points downwards. This poor performance results from a consequent heat loss Qfa. However, this heat which corresponds to the cooling of the working fluid from the hot temperature Tc to the cold temperature Tf corresponds precisely to the range for which the triangle motor cycle points downwards is optimal. Whence obtained the optimal cycles, Stirling, Ericsson and Carnot (more generally, Carnot type mechanisms) from the composition of these two cycles which at the mechanical level can be obtained by the combination of these two engines to triangular cycle. However, the efficiency of the triangular cycle does not depend on the type of heat exchange, it is therefore possible to mix the motors and to compose, for example, a triangular tip down motor whose heat exchange is arbitrary with a triangular motor points in high whose thermal exchange is in isochore. It suffices that the temperatures Tc and Tf as well as the quantities of heat exchanged are the same. The two partners then give a Carnot-type mechanism whose yield is that of Carnot.

A subgroup of Carnot type mechanisms is obtained by associating two triangular mechanisms, one pointing downwards, the other pointing upwards, suitably chosen. These form a Stirling or Carnot mechanism when they are isochoric. They form an Ericsson or Carnot mechanism when they are isobars. The isothermal compressions are always those of the triangular cycle which depends on the difference of the hot and cold temperatures. However, many Carnot type cycles do not use such high compressions. These cycles which interest us, since easier to realize, will be obtained by the association of mechanisms one purely triangular, the other modified triangular. The purely triangular cycle, pointing downwards or upwards, corresponds to the compression ratio of our Carnot type fmal mechanism. The modified triangular cycle of the associated mechanism is obtained by removing the point of the triangle so that the compression ratios are the same for the triangular cycle and the trapezoidal cycle thus obtained. The thermal exchange from Tf to Tc is done in one go on the trapezoidal component whereas it borrows the two cycles (the two mechanisms) on the other side of the cycle (Stirling or Ericsson) obtained by the association of the two mechanisms. The heat exchange of the small side of the trapezium is associated with that of the triangle to regenerate the amount of heat of one of the two sides of the Carnot type mechanism cycle obtained. These two sides absorb, for one, and produce, for the other, the same quantity of heat. Carnot type mechanisms thus constituted have a reduced compression ratio and can however have a temperature difference (hot-cold) high. It is the same with the triangular cycle pointing upwards as others can be modified or combined with another cycle. Thus, according to one variant, it is possible to give an additional compression by isothermal compression of the TH10 point at the TH1 point, the initial state then being the TH10 point and no longer TH1. Note that the compression ratio of the mechanism changes, so the points TH1, TH10 and TH3 are caused to be repositioned on the circle 51. The end of cycle cooling is then from the point TH3 to the point TH10. It follows that part of the hot isothermal expansion will correspond to this cold isothermal compression and will constitute a Carnot-type under-cycle, for which the yield of heat consumed is that of Carnot. The remaining part of the isothermal expansion corresponds to the triangular cycle with, associated, the corresponding triangular yield. The thermal mechanism obtained thanks to this cycle and to the enslavement that corresponds to it is obtained according to the direction of rotation B. It behaves as follows. In the initial state the working fluid is at the cold temperature Tf, this state corresponds to the point TH1. In phase 3 the control mechanism sends the instruction to connect the internal heat exchanger to the heating or preheating source. The cycle of Figure 8 being any but with a strong isobaric component, it results in a dilation of the working fluid. The internal heat exchanger supplies a quantity of heat Qfb to the working fluid. The piston having reached the point TH3, the heating is completed, the mechanism enters phase 2. The control mechanism sends the instruction to connect the internal exchanger to the mechanism exploiting the heat (if it is a pump to heat or variable-to-continuous heat converter, the reference source, ambient air for example, if it is a cryogenic or refrigerant mechanism). During phase 2 the mechanism performs isothermal compression. The exchanger discharges a quantity of heat Qb. When the piston reaches its top dead center 71 (TH2), the mechanism enters its phase 1. The control mechanism sends the instruction to disconnect the internal exchanger, the mechanism performs an adiabatic relaxation of the working fluid. When the piston reaches the TH1 point the adiabatic expansion is completed, the working fluid has returned to its reference cold temperature, a new cycle begins. With reference to FIG. 9, the variant presented here corresponds to a mechanism whose heat exchanges are made in isochore and for this reason the mechanism has a linkage, for example, allowing it to suspend the movement of the piston for a certain period of time. top dead center or at its bottom dead point. Thus the mechanism can describe a triangular cycle tip down (indexed a) but also triangular tip up (indexed b) or a Stirling cycle (index c), and finally a steam cycle (indexed d). As a result, we only present the motor cycles, the thermal cycles being deduced as shown in the previous descriptions. Note that contrary to the cycles presented above the circle 51 no longer represents the rotation of the crankshaft which rotates while the piston is stationary in his / her dead point but only the movement of the piston along the axis 61. The circle 51 is a truncated representation the rotation of the mechanism: the indexed cycle "c" would then be identical to FIG. 2 where the bottom dead point 91 would be the projection of the points S1 and S2 on the axis 61 and the top dead center 71 the projection of the points S3 and S4 on axis 61. The triangle motor cycle tip down behaves as follows. In the initial state the mechanism is in phase 1, the piston is at its bottom dead point 91 (Ml). The control mechanism sends the instruction to connect the internal heat exchanger to the cold source. The working fluid is compressed in isotherm, the internal exchanger evacuates the amount of heat Qia. Arrived at top dead center 71 (M2), the piston marks a pose corresponding to the crankshaft system used. The control mechanism sends the instruction to connect the internal heat exchanger with the hot source or a heating circuit that can be a regenerator. During the immobility of the piston and thus in isochore the working fluid is brought to the temperature of the hot source. At the end of this period of immobility of the piston, the control mechanism sends the instruction to disconnect the internal exchanger. The mechanism enters phase 2, an adiabatic relaxation. When the piston has reached the bottom dead center 91 (Ml), the expansion is completed, the working fluid has returned to its initial temperature. The mechanism enters phase 1 and begins a new cycle. He accomplished three times of which a compression and a relaxation in a rotation.

The triangle motor cycle tip up behaves as follows. In the initial state, when the piston is at its bottom dead point 91 and is about to begin compression. The mechanism between phase 1. The control mechanism sends the instruction to disconnect the internal exchanger. The piston adiabatically compresses the working fluid. This compression is such that it brings the working fluid to a temperature close to Tc, the temperature of the hot source.

Arrived at top dead center 71, the control mechanism sends the instruction to connect the internal heat exchanger to the hot source. The mechanism enters phase 2, the hot isothermal expansion. During this relaxation, the internal exchanger gives a quantity Qib to the working fluid. Arrived at bottom dead center 91, the piston marks a pose in accordance with the mechanical arrangement of its linkage. The control mechanism sends the instruction to connect the internal exchanger to a cold source (or any other source ... a regenerator for example if it is associated with a mechanism exploiting this heat). During this downtime the working fluid is cooled in isochore, its pressure drops. The internal exchanger discharges a quantity of heat Qb. When the piston is about to resume its stroke, compression, the mechanism enters phase 1. The working fluid has returned to its original state and the isothermal compression will begin. A new cycle begins. The indexed Stirling engine cycle "c" behaves as follows. When the piston is at its bottom dead point 91, the working fluid is in its initial reference state, cold and relaxed. The mechanism enters its phase 1, the control mechanism sends the instruction to connect the internal heat exchanger to the cold source. During cold isothermal compression the internal exchanger discharges a quantity of heat Qfc. When the piston reaches its upper dead point 71 (M2) the mechanism leaves it a still time. The control mechanism sends the instruction to connect the internal heat exchanger to the regenerator circuit in order to recycle the heat stored therein. The exchanger heats the working fluid and provides a quantity of heat Qrc during an isochoric transformation. When the piston is about to resume running, the fluid is hot and its pressure has increased. The mechanism enters phase 2, the control mechanism sends the instruction to connect the internal exchanger to the circuit of the hot source. Begins the hot isothermal relaxation. The internal heat exchanger supplies a quantity Qcc of heat to the working fluid. When the piston reaches its bottom dead center the linkage mechanism gives it a time of installation. At the beginning of this installation, the control mechanism sends the instruction to connect the internal exchanger to the regenerator in order to cool the working fluid and to store the heat for the next cycle. The cooling is done in isochore. The amount of heat Qrc is transferred and stored in the regenerator. When the piston is about to resume running, the working fluid has returned to its reference cold temperature. The mechanism goes into phase 1. A new cycle begins.

Several vapor cycles are possible, we will only describe one. An indexed steam cycle "d" behaves as follows. When the piston is at its bottom dead point 91 and is about to begin to return to the top dead center 71, the mechanism enters phase 1. The residual vapor is at the saturating pressure of the cold source. The control mechanism sends the instruction to connect the internal heat exchanger to the circuit of the cold source. Phase 1 consists of a contraction and condensation of the vapor at constant pressure and temperature. The exchanger discharges a quantity of heat Qfd corresponding to the condensation of the steam contained in the volume V9-V7. Arrived at the point M2, the top dead center 71, the control mechanism sends the instruction to heat the condensed liquid. Here a fraction of the constant volume condensation heat at low dead point can be recycled. We consider that the volume of steam when the piston is at the top dead center is almost zero. The dead volume is occupied by the fluid in the liquid state. When the piston is about to come down the liquid is at the temperature of the hot source, the steam is at the saturating pressure of the hot source. The control mechanism sends the instruction to connect the exchanger to the hot source. The piston begins a pressure and constant pressure expansion from point M2 to point M3. The exchanger supplies a quantity Qvd of heat in order to vaporize the liquid contained in the working volume at the temperature of the hot source.

At point M3, the mechanism enters phase 3 of adiabatic expansion. The control mechanism sends the instruction to disconnect the exchanger. The steam is relaxed in adiabatic, a fraction condenses by providing a job. When the piston reaches its bottom dead point 91 (Ml), the residual steam can be expanded and at the temperature of the cold source. More commonly, especially if we have a large temperature difference between Tc and Tf, the steam will be higher temperature than the cold source. In this case the mechanism may be designed so as to mark a pose at low dead point so as to condense the residual steam and reduce its temperature to that of the cold source. The control mechanism sends the instruction to connect the exchanger to the cooling circuit. A small part of this heat could be recycled. Its totality could be exploited by a triangular cycle mechanism. When the piston is about to resume running, the mechanism enters phase 1. A new cycle begins. With reference to FIG. 10, the variant of the invention describes here a thermal mechanism that can be a heat pump, a low compression indicates that the hot temperature is not far from the cold temperature. This variant of the invention is based on the Carnot cycle. The thermal cycle is therefore reversed cycle as indicated by the arrow of the center. At bottom dead point 91 the mechanism enters phase 4 (we keep the numbering and arrangement of the normal Carnot cycle, engine). The control mechanism assigns the distributor the disconnection order of the internal exchanger. During phase 4 the mechanism performs adiabatic compression of the point C1, bottom dead center 91, at point C4. At point C4, the mechanism enters phase 3. The control mechanism assigns the distributor the order to connect the internal heat exchanger to the heat-generating circuit produced by the mechanism, in the case of a mechanism such as a heat pump, the ambient air if it is a refrigerating mechanism, for example. During phase 3, the mechanism carries out a hot isothermal compression of the point C4 at the point C3, the top dead center 71. The compression releases a heat Qc that the exchanger evacuates, outgoing arrow. Arrived at top dead center 71, point C3, the mechanism enters phase 2. The control mechanism assigns the distributor to disconnect the internal exchanger. From top dead center C3 to point C2, the mechanism performs adiabatic expansion. At point C2 the mechanism enters phase 1, the control mechanism assigns the distributor to connect the internal exchanger to the circuit of the cold source, whether it is air, water, a heat source in a pump function heat or medium confined in a refrigerant function. From point C2 to point C1, bottom dead center 91, the mechanism achieves isothermal expansion at low temperature. This trigger consumes a quantity of heat Qf, incoming arrow. The cycle is thus completed, the mechanism enters phase 4 and begins a new cycle with this new rotation of the mechanism. The adiabatic compression rates corresponding to the movements of the piston 101a and 101b are identical. We see that the compression corresponding to such a low compression ratio that it will raise only slightly the initial temperature, respectively will lower only slightly the temperature, after the adiabatic expansion (phase 2). It is therefore a mechanism such as a heat pump or a refrigerating mechanism. We will notice, more precisely in this framework, that the choice of a control mechanism based on a combination of an angular position detector of the mechanism tree with a computer allows to bring an adaptable instruction and not more fixed as would be a similar mechanism to camshaft system. In this way, by means of the thermal sensors necessary for such a mechanism, the control mechanism is then able to adapt the adiabatic compression ratio so as to maintain the purpose attached thereto, the refrigeration temperature or the heating temperature, and this while remaining in an optimal cycle thus of minimal consumption of energy. Thus, for an air conditioner, if the outside temperature then increases the air conditioner will automatically increase its adiabatic compression rate so as to maintain the internal temperature constant while releasing this heat of air conditioning to the outside at the minimal cost that thermodynamics allows, knowing that the mechanisms of Carnot are simple, without regenerator, and that their yield is thus closer to the optimal theoretical yield. The adaptability afforded by a computer saves the additional compression induced by the traditional use of a valve regulating the evacuation of compressed steam as a function of the saturating pressure of the hot circuit, it is then necessary to exercise on it an overpressure greater than the return force of the valve. The ultra-closed characteristic of the invention (with a constant mass of fluid in the working volume) as well as the use of a calculator also make it possible to save on the surcharges due to the depressions and overpressures related to the admission and the expulsion of the steam by the narrows that are the admission and the exhaust. With reference to FIG. 11, the variant of the invention describes here a thermal mechanism that can be a cryogenic system as well as the strong expansion by heating the watch. The variant of the mechanism is based on the Ericsson cycle, a similar variant is obtained from the Stirling cycle. Its thermal specificity is shown by the direction of rotation, arrow of the center, inverse to the motor direction (figure 3). The initial phases and initial points of these phases keep the same values as for the motor cycle. Everything is identical to the variant of the same engine-type mechanism at the instructions near the control mechanism. It is therefore possible to design a mechanism according to the invention which is totally reversible, which can also function as a motor or heat pump only by modifying its operating mode, the computer then knowing which controller to use and how to manage the optimal conditions at this mode. This and its adaptive aspect will give very interesting applications to the invention. The mechanism according to the invention starts its cycle at the point El, bottom dead point 91, it enters phase 4, the isothermal compression at high temperature. The control mechanism assigns the distributor to switch the circuit of the internal exchanger on the operating circuit or removing the heat produced. From the bottom dead point to point E4 the mechanism carries out a hot isothermal compression producing a quantity of heat Qc which is evacuated by the exchanger, outgoing arrow. At point E4, the mechanism moves to phase 3. The control mechanism assigns the distributor to interchange the internal heat exchanger on the regenerator circuit to cool and store the heat. During this cooling phase, the working fluid contracts at constant pressure. The quantity of heat Qr is then evacuated by the internal exchanger to the regenerator, outgoing arrow. Having reached point E3, top dead center 71, the mechanism enters phase 2. The control mechanism assigns the distributor to switch the circuit of the internal exchanger of the regeneration circuit to the circuit of the cold source. During phase 2, the mechanism performs a cold isothermal expansion from point E3, top dead center, to point E2. During this relaxation it consumes a quantity of heat Qf, incoming arrow. At E2 the mechanism goes into phase 1. The control mechanism assigns the distributor to switch the circuit of the heat source circuit heat exchanger to the regenerator circuit to heat the working fluid from the heat previously stored in the regenerator circuit. this one. The working fluid receives the amount of heat Qr and expands at constant pressure from the point E2 to the point E1, the bottom dead center 91. It absorbs the amount of heat Qr, incoming arrow. Arrived in E1, dead center low 91, it completes, the time of a rotation, the complete cycle. He enters phase 4 and begins a new cycle. The positions of the piston corresponding to the points E3 and E4 and the points E2 and E1 define a displacement of the piston 101a and 101b. These deviations produce a similar contraction / expansion rate - the limitations near the components - since both realize the same but opposite transition from Tc to Tf during phase 3 and from Tf to Tc during phase 1. The contraction / dilation takes into account the dead volume which, by definition, adds to the volume traveled by the piston. The important value given to the phase 1, 101a occupies most of the piston stroke, allows to deduce that the thermal mechanism thus defined is of the cryogenic type. The variant of the invention realizing a thermal mechanism based on the Stirling cycle is not described, those skilled in the art will not have the slightest trouble adapting the many examples given to this cycle. According to the thermal variants of the invention it is also possible to mix the cycles as we have described for the drive mechanisms, and possibly to associate the mechanism with a triangular cycle auxiliary mechanism to improve performance. With reference to FIG. 12, the diagram gives a representation of the invention according to a variant based on a mechanism of the piston / crankshaft / crankshaft type where the control mechanism is a computer whose memory contains one or more servocontrol algorithms enabling to perform one of the variants described above or a combination of them. The piston 1 contains the grooves 6 in which the planar and parallel internal exchangers 5 interlock when the piston 1 rises towards the cylinder head 3. The piston 1, the cylinder 2, the cylinder head 3 and the clearances between the internal heat exchangers and their groove 6 of the piston form a closed working volume containing a working fluid (usually helium) closed in this volume. The working fluid describes a cycle in which its volume goes from a minimum, the dead volume when the piston 1 is at its top dead point, to a maximum volume when the piston is at its bottom dead point. The peripheral surfaces (1, 2 and 3) tend to limit thermal leakage by reducing their surface, by the treatment and coating of these surfaces as well as by the alloys composing the various elements constituting these surfaces, whereas in the volume The workpiece penetrates the internal heat exchanger 5, ideally bathed in the working fluid to which it transmits / withdraws the heat. The latter will tend to increase its heat exchange surface, promote conductive alloys, occupy one or more positions within the work volume that will promote its heat exchange with the working fluid. The peripheral surfaces are optimized to reduce heat losses, the internal exchanger is optimized to promote heat exchange with the working fluid. The internal heat exchanger 5 is fixed to the cylinder head 3. The inlet 11 and outlet 12 connections make it possible to circulate a heat transfer fluid in the internal heat exchanger 5 according to a circuit that is specific to it. The inputs / outputs 11 and 12 of the internal exchanger 5 are connected to the distributors 15a for the input and 15b for the output. The piston 1 is connected by means of a rod schematized by the dash 22 to a crankshaft whose rotation describes a circle 21. Linked to the rotation of the crankshaft, an angular sensor 20 gives the current angle of the crankshaft to the computer 16 which deduces the position of the piston 1 and the current working volume 4 in real time. Depending on the angle of the crankshaft that can be supplemented by other data collected by appropriate pressure, temperature sensors, and the current operating mode (if it has a choice of several servo control algorithms), the The computer 16 sends the various instructions to the elements that it manages, in particular the distributors 15 of the internal exchangers 5. According to the instructions addressed to the distributors 15 by the computer 16, the distributor can either connect the exchangers to external circuits or isolate them. The external circuits can be three in number as for a Stirling mechanism, namely a cold source circuit 17, a hot source circuit 18 and a regenerator circuit 19. For a regenerative circuit, according to the technical choice made to this ci, it can correspond two connections to each distributor 15 associated with the inlet and outlet of the exchanger. According to certain technical choices the regenerator can work according to a methodology comparable to the management of piles in computer named LIFO, last in first out, according to this technical choice it is necessary that each entry and each exit of the heat exchanger is sometimes connected at one end from the regenerator, sometimes to the other. The same variants can be adapted with the triangular cycles according to the remarks that have been made previously. We can notice that a heat exchanger is not `polarized 'so input and output can be freely swapped, which can simplify the number of connections needed by distributors 15 in the simple case above but does not change if we want to manage at most near the case of management of multiple cold / hot sources. This management can also be accomplished by a system-specific mechanism that exploits this cold production, for example. According to the instructions of the calculator addressed to the distributors, the incoming flow 9a comes from the circuit connected to the internal heat exchanger 5 by the distributor 15a. Same for the outgoing stream 9b. Note that the variants using a regenerator do not need to have as much regenerator as the motor element (cylinder / piston). A single regenerator will suffice for several out of phase motor elements, if not all. With reference to FIG. 13, the diagram gives a partial representation of the piston 1 containing the internal exchangers 5a, 5b and 5c (not shown) contained in the grooves 6 of the piston 1. The internal exchangers 5 each have a tube 12 at their ends. serving as input / output. These input / output tubes pass through the cylinder head (not shown) to connect to the distributors 15a, 15b and 15c respectively connected to the exchangers 5a, 5b and 5c. Thus according to this variant the computer manages not a single internal exchanger 5, which would have been the case considering the three heat exchangers as forming only one internal exchanger at any point integral. This variant makes it possible to exploit the powerful potential offered by computers to precisely manage heat exchanges continuously. Indeed, according to the management that will be made of thermal exchanges the losses related to these transformations will be more or less reduced, or if not more or less important. Thus, the computer 16 can control the flow of the heat transfer fluid through the internal exchangers in two ways, or by acting on the mechanism managing this flow, the simplest is here when this function is held by an electric pump, accelerating or slowing down. this flow according to the needs and the speed of the piston, or by acting on the surface of the heat exchange by controlling various exchangers with different exchange surfaces. The difficulty, in a number of the variants exposed, is to recycle all the heat taken during cooling during the heating phase. These phases are asymmetrical. The variations in amount of heat transferred are not symmetrical during these two phases. If we take the diagram corresponding to the Ericsson cycle, it is clear that phase 1 is disproportionate by 1.0 compared to phase 3. But also that phase 3 is mainly accomplished when the piston is quasi-static whereas in phase 1 it ends where the piston has its maximum speed. The same is true of the position of the hot and cold points at the ends of these phases, again there is asymmetry. These asymmetries of the mechanism are sources of nuisances which disturb the yield of the mechanism. It is therefore appropriate to manage them as best as possible. It is here that a calculator will bring a considerable advantage to a mechanical mechanism, and hence a better efficiency of the mechanism according to the invention. With reference to FIG. 14, the diagram gives a representation of a variant of the invention such that the closed working volume containing the working fluid comprises an external extension acting as a heat exchanger. The piston 1 compressing the working fluid reduces it from the working volume 4 to the internal volume 54 to the external exchanger 5. The heat exchanges in this external exchanger 5 are managed by the control mechanism (usually numbered 16). The volume 54 may correspond to all or part of the dead volume of the mechanism, when the piston 1 is at its top dead point which may be the cylinder head 3. It may also be larger than the dead volume if the piston is provided with a protuberance, such as stepped pistons. This protrusion 25 engages in the neck 56 connecting the cylinder to the external exchanger 5 and thus occupies a certain volume within the volume 54 of the external exchanger. It therefore contributes to the compression ratio and increases the volume 54 without penalizing the compression ratio of the mechanism. By pushing this step further we return to the ordinary mechanism with a peripheral internal exchanger. Then the external exchanger 5 becomes a simple specialized extension of the cylinder 2. The cylinder 2 30 in which the piston 1 moves comprises a portion 25 which can act as a heat exchanger. Thus the exchanger 25 may have a cold source function while the exchanger 5 may have a hot source function, for example. The mechanisms according to the invention working with phase-changing fluids may have a cavity serving as a reservoir for the liquid or solid involved in the thermodynamic cycle that the mechanism uses. This contiguous and participating cavity in the working volume can take the form of the exchanger 5 of FIG. 14. It can be a heat exchanger or comprise an exchanger by means of which the control mechanism manages the phase changes of the working fluid, its temperature and its saturating pressure. Thermal mechanisms designed according to the invention will therefore use a mass of refrigerant reduced to a minimum. This characteristic of the invention will make it possible to contribute effectively to reducing the use and the resulting losses of fluorinated greenhouse gases used in thermal engineering. The heat pipe technology is useful for internal exchanges to the volume of work. It is as much for the external circuit of the exchanger to convey quickly and at minimal cost, without motorization, the heat to the organs served by the mechanism.

With reference to FIG. 15, the diagram gives a variant of the preceding figure inspired by the heat exchanges of the mechanisms derived from the Stirling engine. The mechanism consists of a distinction between the front part of the peripheral surfaces to the working volume (closed) and the rear part. The front part consists of the cylinder 2 in which the piston 1 slides, its connecting rod is symbolized by dotted lines. This first part is dedicated to mechanical functions, guiding, sealing, resistance, ... The second part is the exchanger 5, it is like a protrusion to the working volume. It is located in the extension of the cylinder 2 and attached to the cylinder head 3. The material that constitutes it and its thickness are chosen so as to promote heat exchange with the working fluid that comes into contact with it on its inner face. These heat exchanges are symbolized by the arrow and the amount of heat Q exchanged via the exchanger 5. The heating mode (or cooling) of the exchanger 5 is free. It can be traversed by a heat transfer fluid, as it can be, on its outer surface, directly immersed in the hot gases from a combustion, etc.. The heat exchanger 5 and the heat flux are managed by the control mechanism according to the technical choices and the thermodynamic cycle performed. The internal volume of the exchanger 5 communicates with the internal volume of the cylinder 2 via the opening 36 of the cylinder head. These two volumes form the working volume 4 in which is the fluid that the piston 1 compresses / relaxes. In order to increase the compression ratio the piston 1 has a protuberance lb which occupies part of the internal volume of the exchanger 5 when the piston is close to its top dead center. The shape of the exchanger 5 and the piston 1 and 1b in the Stirling type engines are often rounded and the exchanger 5 is generally in the extension of the cylinder 2, a feature that this variant of the invention can share. With reference to FIG. 16, this represents the triangular cycle in a PV (Pressure / Volume) diagram for a heating / cooling performed at constant pressure (isobar), the triangular cycle is the tip at the bottom (the point here) . The engine cycle consists of an isothermal compression 91 followed by a heating of the working fluid 92 at constant pressure, and finally the triangular cycle adiabatic expansion 93 which returns the working fluid to the initial state for a closed mechanism (without chemical transformation, combustion, working fluid). In this case pressure, volume and temperature are exactly the same as at the beginning of the cycle, at point a. In the case of an open mechanism such as an internal combustion engine the problems caused by the condensation of water vapor (for a return to the initial temperature) as well as the chemical transformation resulting from the combustion of air and fuel changes the return state which can no longer be identical to the initial state. As the cycle shows, and even more so a next cycle, figure 18, for which the compression ratio is much higher than the one used here to describe this cycle, the tip of the triangle represents little work (few 'energy would say we improperly) also the theoretical cycle can be adapted and, with a very small loss of efficiency, gain in power density. The engine becomes more powerful at the same volume or mass. The triangular cycle thus modified becomes a trapezoidal cycle. Like all thermodynamic cycles, the triangular motor cycle can be inverted to produce a thermal cycle. The triangular motor cycle is 91-92-93, the corresponding thermal cycle is 93-92- 91. Naturally heating the cold source with adiabatic compression is absurd ... but it will find very interesting uses. The triangular and trapezoidal cycles excel particularly in the treatment of thermal flux of material (solid, liquid or gas). The motor cycle optimizes the heat-energy conversion of the heat conveyed by a material flow (solid, liquid or gas) by exploiting all the heat between the temperature of this material and the cold source we have, from Tc to Tf. The reverse cycle, thermal cycle offers exactly the same excellence. It is precisely in this context that it offers the best efficiency (efficiency), when we heat a mass or a material flow from a temperature Tf to a temperature Tc or when we cool a material flow of a temperature Tc at a temperature Tf, whether this flow of material is the primary source of heat (cold or hot) or a secondary circuit carrying the heat of a primary source. The mechanisms according to these cycles will be much more efficient than the traditional mechanisms for functions such as the freezing of products on a production line or the heating of the air flows compensating the hot air flows lost by the doors of the stores, by example. This hot air is lost without being able to recycle its heat, to compensate it it is necessary to take a cold external air and to bring it to the interior temperature. In this case, a triangular heat pump is more efficient than a heat pump according to a Carnot cycle. It is the same for an air conditioning in summer. The yield of the triangular motor cycles tip down is: 1 - Tf / (Tc-Tf) * ln (Tc / Tf). With reference to FIG. 17, the triangular cycle illustrates a top-up cycle whose heating / cooling is done in isobar (constant pressure). If we are in the reference state at point c, the motor cycle behaves as such: phase 93 is an adiabatic compression which brings the working fluid from the cold temperature Tf to the hot temperature Tc. It is followed by a hot isothermal expansion, phase 91. The triangular cycles the tip up work like most engines, with a constant heat source continues what allows the noble energies such as gasoline, diesel, coal etc. The phase 91 returns the system to the initial pressure, but the working fluid is always at the hot temperature, so dilated, the volume is given by the point b. Phase 92 cools the working fluid at constant pressure to bring it back to the initial conditions at point c. The engine cycle is complete. We will notice that this cycle is not optimum in terms of energy production because a substantial part of heat is wasted during phase 92. This is why the yield is: 1 - (Tf / (Tc-1 ) / ln (Tc / Tf) is worse than that of the yield of the triangular bottom-up cycle given above. But this "lost" heat corresponds precisely to the area for which the triangular cycle points downwards. This observation leads us naturally to notice that the three main thermodynamic cycles offering the optimal yield, the Carnot yield, these three cycles "are written" by the composition of two triangular motor cycles, one being triangular tip down and the Another triangular tip up -respectively thermal mechanism by reversing the direction of rotation of the cycles. More generally, the Carnot type cycles can be written with two triangular cycles, and when the compression ratio of the Carnot type cycle is lower than that of the triangular cycle corresponding to the working temperatures (Tf, Tc), or by modifying the triangles. For this it is necessary to set the compression ratio of one of them on the compression ratio of the reference cycle, Carnot type, the second triangle corresponds to the triangular cycle (Tf, Tc) which is removed the triangular tip so that the compression ratios of the two cycles are the same so that they correspond to the compression rate of the Carnot type cycle (Stirling or Ericsson). The modified triangular cycle takes a global shape of trapezoid. The sides of the trapezium are formed by the relaxation and the compression, one adiabatic the other isothermal, and two heat transfers (isochores or isobars, for example) of which one, the smallest, corresponds to the point removed from the original triangle. The combination of two triangular cycles, complete or modified (trapezoidal), makes it possible to obtain all Carnot type cycles. The possible associations are therefore triangle-triangle, triangle-trapeze, trapeze-trapeze. The trapezoidal cycles being modified triangular cycles, we find the two families `peak 'at the bottom and` peak' at the top. Thus, using the cycle of Figure 16, at constant pressure downwards, with the cycle of Figure 17, at constant pressure upwards, we obtain the Ericsson cycle by the juxtaposition of the cycles according to the adiabatic side by matching the points a and c. The Ericsson cycle obtained starts from the point a of the cycle of FIG. 16, it makes a low temperature isothermal compression, figure 16 phase 91, it continues with the heating at constant pressure of the cycle of FIG. 16, phase 92, and reaches at the end common to both cycles. The cycle of Ericsson continues on the second cycle that of Figure 17. It is then a hot isothermal expansion, phase 91 Figure 17, followed by a constant pressure cooling phase 92 Figure 17. The cycle is complete. We returned to point c in Figure 17 corresponding to point a in Figure 16. The adiabatic compression work of the top-up cycle is equivalent to the adiabatic relaxation work tip down. The two triangular motor cycles form an Ericsson cycle. Similarly, the Carnot cycle is obtained by juxtaposing these two cycles by their isothermal side, or by making the points a and b of the two cycles coincide. The triangular cycle points upwards according to various variants may have the heat exchange phase no longer in isobaric but in isochore or a free composition of both. Just as it has been shown for the Ericsson and Carnot cycles, from the isochore triangular cycles upwards and downwards, we obtain the Stirling and Carnot cycles. These cycles offer the best performance that can be obtained, but the two engine cycles that compose them have a lower yield than Carnot.

With reference to FIG. 18, the cycle described in this diagram is a triangular cycle (nmo cycle) and trapezoidal cycle (qmop cycle) tip down isochore. For a given fluid a given pair of temperatures (Tf, Tc) there is a single triangular cycle pointing downwards and a triangular cycle pointing upwards, on the other hand an infinity of trapezoidal cycles extracted from these are possible. The cycle begins with an isothermal compression, phase 91, succeeds to it isochore heating (at constant volume), phase 92, the third phase of the triangle is the adiabatic expansion, phase 93. At the end of the adiabatic expansion the working fluid returns to its initial state. We note that the example illustrating the cycle corresponds to a high compression ratio and therefore to a heating, which for the data corresponding to the curves of this figure this translates into a high cycle efficiency: 0.63 whereas it is 0.82 for a Carnot yield at the same temperatures. We notice that the tip of the triangle is very slender. It follows the adaptation of the cycle of amputating the "useless" part of the triangle by isochoric cooling for example, the section p-q of the cycle of Figure 18, in a closed circuit. More than half of the volume used produces almost no work. It is therefore possible, by losing very little efficiency, to significantly reduce the volume of the engine and thus to gain power / weight ratio. The triangular cycle thus modified, qmop, is a trapezoidal cycle. This adaptation applies to all triangular and trapezoidal cycles, whatever the form of their heat exchange. The mechanism according to the invention is particularly suitable for external combustion engines, low and high temperature and should find a preferred use for engine systems operating with renewable energy, heat pumps and refrigeration or cryogenic mechanisms. If the small motor or thermal mechanisms will be a preferred field of the invention, the means and large systems can find in the invention simple, robust and efficient solutions.

25 30 35 40

Claims (10)

CLAIMS1) Mechanism engine or thermal characterized in that the working fluid is closed in the working volume 4 during the entire engine or thermal cycle, the mass of the working fluid contained in the working volume 4 remains constant from the beginning to the end of the cycle and does not undergo any transfer. 2) Mechanism according to claim 1 characterized in that it comprises at least one heat exchanger 5, the heat exchanger 5 is internal to the working volume 4 or peripheral to the working volume or in the extension of the work volume and participates to its volume, that the heat exchanger 5 internal to the working volume is or conscript the dead volume or intermesh in the piston 1 or intermesh in the cylinder head 3 or is floating. 3) Mechanism according to claim 1 or 2 characterized in that the thermal transport carried by the heat transfer fluid between the heat exchanger 5 and the heat source (cold or hot) or the thermal storage device to which the exchanger is connected itself. made by vaporization on one side and condensation of the other, that the liquid and gaseous flows of the heat transfer fluid flow between these two ends naturally (in the absence of mechanical device) according to the force of gravity or kinematic or dynamic of the mechanism (heat pipe technique), or are pulsed or compressed or pumped using a suitable device, that this thermal transport is permanent or variable, that it can be activated or deactivated. 4) Mechanism according to one of the preceding claims characterized in that at least one heat exchanger 5 comprises a cavity or is constituted by a cavity serving as a reservoir, that the reservoir is internal to the exchanger (for the use of fluid coolant) or external to the exchanger (for the use of the working fluid), this reservoir contains a fluid in gaseous or liquid or solid state. 5) Mechanism according to one of the preceding claims characterized in that its control mechanism 16 allows it to accomplish the automaton of one of the following cycles, cycle Stirling, Ericsson, Carnot, type Carnot, triangular, trapezoidal, steam, Beau de Rochas, Diesel, or combined cycles 2 in 1 or 3 in 1, including the combination of two or three of the following cycles: cycle type explosion engine, cycle type Carnot and cycle triangular or trapezoidal. 6) Mechanism according to one of the preceding claims characterized in that the control mechanism 16 is a computer which, among its peripherals, has a memory comprising one or more algorithms providing the servo mechanism according to the cycles mentioned claim 5 the computer can have sensors informing it of the state of the mechanism (s) enslaved or contextual information or instructions addressed to it, it can have devices such as DACs allowing it to control the elements electric it manages (solenoid valve, valve, pump, ...). 7) Mechanism according to claim 6 characterized in that the computer 16 manages the heat exchange by varying the flow of heat transfer fluid or by connecting or disconnecting heat exchangers 5 or elements of the exchanger 5 or by raising / lowering the pressure saturating the heat transfer fluid so as to adapt the intensity of heat exchange during the heat transfer phases. 8) Mechanism according to one of the preceding claims characterized in that it is provided with a device for extending the stopping of the movable member 1 (a piston in a piston mechanism) to one or the dead time of the mechanism or to slow down and control the stroke of the movable member 1 during parts of the mechanical cycle, particularly in the vicinity of the top dead center or bottom dead center. 9) Mechanism according to one of the preceding claims characterized in that it is of the type with vane or piston, piston single or double effect, or staged, or differential, linear or rotary, or reciprocating or oscillating. 10) Mechanism according to one of the preceding claims characterized in that it is associated with other mechanisms, not necessarily according to one of these claims, and forms a device where the mechanisms work in phase or out of phase some by relative to others, that these mechanisms can share mechanical, thermal, electronic, software, data, or common control mechanism 16, or that the device thus obtained is of Carnot type (the combination of the cycles of the mechanisms forms a cycle Carnot type: Stirling, or Ericsson, or Carnot or a combined cycle whose theoretical yield is that of Carnot). 25 30 35 40