EP0062043A1

EP0062043A1 - Method and machine for obtaining a quasi-isothermal transformation in gas compression or expansion processes.

Info

Publication number: EP0062043A1
Application number: EP81902670A
Authority: EP
Inventors: Andrei Vasile Chrisoghilos
Original assignee: Individual
Current assignee: L'INSTITUT NATIONAL DE MOTEURS THERMIQUES
Priority date: 1980-10-08
Filing date: 1981-09-07
Publication date: 1982-10-13
Also published as: BR8108832A; SU1386038A3; US4502284A; EP0062043B1; RO77965B1; WO1982001220A1; RO77965A2; JPS57501789A

Abstract

L'invention se refere a un procede et une machine qui permettent realisation d'un processus de compression ou de detente quasi-isotherme dans n'importe quel cycle thermodynamique qui contient de pareilles transformations. Le procede est realisable par le fait qu'on utilise des echangeurs de chaleur (A et B) independants l'un de l'autre, que dans chaque echangeur (A et B) l'agent de travail circule avec intermittence et dans un seul sens et que les echangeurs (A et B) sont connectes et deconnectes successivement et de facon cyclique avec le volume variable de la chambre de travail (a).The invention refers to a method and a machine which allow carrying out a quasi-isothermal compression or expansion process in any thermodynamic cycle which contains such transformations. The process is achievable by the fact that heat exchangers (A and B) are used that are independent of each other, that in each exchanger (A and B) the working agent circulates intermittently and in a single direction and that the exchangers (A and B) are connected and disconnected successively and cyclically with the variable volume of the working chamber (a).

Description

TITLE OF THE INVENTION

Method and machine for obtaining quasi-isothermal transformation in gas compression or expansion processes

TECHNICAL AREA

The invention relates to a method and a machine which allow the realization of a quasi-isothermal compression or expansion process, that is to say a process in which the temperature of the working agent remains almost constant in undergoing practically unimportant variations, throughout the duration of the compression or expansion process, in any thermodynamic cycle, which contains such transformations.

PRIOR ART

Processes are known which have been developed with the aim of carrying out a quasi-isothermal compression or expansion process in accordance with which, with the aim of achieving the theoretical condition of an isothermal transformation, that is to say the maintenance of equality between the mechanical work, received in the compression phase, or transferred, in the expansion phase and the heat removed, in the compression phase or respectively the absorbed heat, in the expansion phase, the working chamber of variable volume of a engine was connected to a cooled heat exchanger, composed of one or more serial heat exchange units in the compression phase and to a heated heat exchanger in the expansion phase (US Patent No. 3,867,815). This process has the disadvantage that the volume of the heat exchangers adds up with the volume of the dead space, determined by the constructive parameters of the variable volume chamber, which does not allow the achievement of high compression ratios. In addition, due to the fact that only one heat exchanger is used, equality is not guaranteed at all times between the mechanical work received or transferred and the heat removed or respectively absorbed, the curve of the transformation deviating significantly from the isothermal theoretical curve, which leads to a deterioration in the efficiency of the cycle as a whole. Stirling external combustion engines are also known, produced according to different constructive solutions in which after the compression phase the working agent is cooled in a heat exchanger, then passed through a regenerator and introduced into an expansion chamber heated (Stirling engines by G. Walker). External combustion engines of this type 1a, regardless of their constructive solution, have the disadvantage of being able to achieve only reduced compression ratios, which affects the overall efficiency of the engine.

STATEMENT OF THE INVENTION

The method, in accordance with the invention, eliminates the disadvantages mentioned above, by the fact that, in order to carry out certain transformations, as close as possible to an isothermal theoretical transformation, as well as maintaining a ratio compression or expansion as high as possible, the volume of the heat exchangers does not add to the volume of the dead space determined by the constructive parameters of the variable volume chamber, since for this purpose heat exchangers are used independent of each other, in each exchanger the working agent circulating intermittently and in a single direction, exchangers which are connected and disconnected successively and cyclically with the variable volume of the working chamber, the duration of connection between this working chamber and one of the independent exchangers having two phases, in particular: in the compression isotherm, in the first phase, there is a flow of the working agent garlic from an independent heat exchanger cooled in a variable volume working chamber, until the pressures in the two volumes are equalized, the mixing process being polytropic, the working agent of the chamber transferring the heat to the working agent from the exchanger, and in the second phase there is a flow of the working agent from the chamber into the exchanger, transporting the related heat, while the total mass of compressed gas yields the heat via the cooled independent exchanger, and in the expansion isotherm in the first phase there takes place a flow of the working agent from the variable-volume working chamber in an independent heated heat exchanger, up to at equalization of the pressures of the two volumes, the working agent of the heat exchanger transferring heat to the working agent coming from the chamber by polytrope mixing, and a second phase in which the working agent flows of the heated heat exchanger da ns the working chamber, transporting the related heat while the total mass of the relaxed working agent receives the heat by the independent heated heat exchanger; the connection and disconnection of independent heat exchangers, to the variable volume working chamber, being done in such a way that the time, during which there is no connection between the chamber and the exchanger, ensures an isochoric evolution of the working agent of each exchanger when the heat is transferred to the outside in the compression isotherm and heat is received from the outside in the expansion isotherm the curve of the thermodynamic transformation in the compression process or of relaxation realizing as a result of the addition of some successive polytrope sequential transformation, whose points of continuity are located above and below the theoretical isothermal curve, so that the negative mechanical work in the quasi- isotherm of compression and the positive mechanical work in the quasi-isotherm of relaxation, are comparable with those of certain theoretical isothermal transformations, the pressures of the working agent independent heat exchangers which ensure the circulation of the agent in one direction being ensured by the same working chamber with variable volume, due to a self-storage process, until in each exchanger, after P series of cycles, a stabilized value necessary and self-repeatable for each cycle is reached.

The rotary machine, in accordance with the present invention, eliminates the disadvantages mentioned above, by the fact that for the purpose of carrying out the process presented above it uses groups of independent heat exchangers, i.e. -to say a group of cooled exchangers for the compression phase and a group of heated exchangers for the expansion phase *, the successive connection and disconnection between these exchangers and the working chamber of variable volume of the machine being carried out by through certain connection orifices, certain galleries, and pairs of windows made in two distribution discs and in the two fixed covers of the motor casing, windows which are arranged radially and sealed along a trapezoidal contour with expandable linear segments and certain pipes which are the same connections of the exchangers, a window ensuring the connection of the working chamber with the exchanger for the r realization of the first phase of the quasi-isothermal transformation process, the second window ensuring the connection for the realization of the second phase of the quasi-isothermal transformation process, the space between the two groups of windows corresponding to the groups of exchangers on the two covers being sealed with segments of trapezoidal shapes located continuously on blind trapezoidal contours, located on the same diameter as the windows. ^ The method and the machine for obtaining the quasi-isothermal transformation in the gas compression and expansion processes, in accordance with the invention, have the following advantages: ensures the realization of certain thermodynamic transformations as close as possible to a transformation theoretical isotherm. allows the achievement of certain high compression or expansion ratios. ensures the operation of a thermal machine with the highest yields for the same temperature difference, because it can work according to any cycle, including the Carnot cycle. allows the use of any heat source, including solar or geothermal sources and can use any type of gaseous, liquid or solid fuel. ensures the reduction of fuel consumption and reduces chemical and noise pollution. allows the operation of a thermal machine at reduced pressures and temperatures of the working agent which ensures a reduction in the stress regime and the level of wear.

SUMMARY DESCRIPTION OF THE DRAWINGS

An exemplary embodiment of the invention is presented below in conjunction with FIGS. 1 ... 8 which represent: FIG. 1. Schematic diagram of the quasi-isothermal transformation process in the gas compression or expansion processes. fig. 2. Pressure-volume diagram of the quasi-isothermal compression and expansion processes. fig. 3. Temperature-entropy diagram of the quasi-isothermal compression and expansion process. fig. 4. Theoretical pressure-volume diagram of the cycle of a rotary external combustion engine. fig. 5. Longitudinal section of a rotary external combustion engine according to the invention. fig. 6. Motor cross section in accordance with plane II of figure 5. fig.7. The detail of the sealing of windows t and u. fig. 8. Cross section of an engine according to plan II-II of figure 5. BEST WAY TO IMPLEMENT THE INVENTION

The method, according to the invention, is applicable to any thermal machine which works with a variable volume working chamber a and provides that this chamber is successively connected and disconnected cyclically with two groups of heat exchangers. heat independent of volumes Val, Va2, Va3 ... etc. namely a group of independent cooled exchangers, of identical construction A, and a group of independent heated exchangers of identical construction B.

Each independent cooled heat exchanger A, used in the compression isotherm, is made up of certain heat exchange units 1 which have a window b for the flow of the working agent coming from the exchanger A, towards the working chamber a and a window c for the flow of the working agent coming from the working chamber a towards the heat exchanger A. In the same way a heated heat exchanger B used in the isotherm of expansion, is formed by a heat exchange unit 2 provided with a window d for the flow of the heat agent from the working chamber a into the exchanger B and a window e for the flow of the working agent of the exchanger B in the working chamber a.

The working chamber of variable volume a can be produced, without the example being limiting, in accordance with the block diagram of FIG. 1 on a rotary machine C, formed of a stator 3 and a rotor 4 in which the pallets slide. 5. The rotary machine C has a suction connection 6, and a discharge connection 7, or a discharge connection 8. Following the movement of the rotor 4, the working chamber of variable volume a, the parameters of which state initials are P _O V _O T _O , will be connected successively in the compression phase with the heat exchangers A and in the expansion phase with the heat exchangers B via certain windows f, formed in the wall of bedroom. The working agent state parameters of the first heat exchanger A are P ' ₁ Va ₁ T " ₁ .

The duration of the connection between the variable volume chamber a and a heat exchanger A has two phases. In the first phase, in which the working agent of the heat exchanger A flows to the variable-volume working chamber a, through the window b of the exchanger A and the window f of the wall of the chamber , realizing with the working agent of the working chamber has a polytrope mixture whose state parameters are P _{z \} , V _O + V _al , T _z l, the working agent of the chamber yielding heat to the worker from the heat exchanger. Between the initial state values of the two gases there are the relationships:

while the polytrope blend places its state parameters as follows:

In the second phase window b is closed simultaneously with the opening of window c and the two volumes compress together, the gas now flowing from the chamber to the exchanger through windows f and c, taking away the heat pertaining to the mass which leaves the working chamber.

At the same time, part of the heat of compression of the combined gases of the exchanger and the chamber is discharged outside through the walls of the exchanger, the compression having a subadiabatic character. When the working chamber of the first cooled heat exchanger A is detached, when the orifice c has closed, the gas in the working chamber will be in the state (P ₁ , V ₁ , T ₁ ) and that of the first cooled heat exchanger A in the state (P ₁ , V _al , T ' ₁ ).

Compared with the initial states, the state parameters of the two gases are found in the relationships:

As soon as the working chamber £ detaches from the cooled heat exchanger A, is connected to the next cooled heat exchanger A, or the process is repeated exactly as at the first exchanger. The working agent of the heat exchanger A, disconnected from the working chamber a, evolves according to an isochoric curve by exchanging heat at constant volume throughout the duration of the waiting period, until 'it will be connected to the next working chamber, which will find it at state parameters which can be considered identical with the initial parameters existing at the time of contact with the first chamber (P' _1, V _al , T " ₁ ) . After having traversed all the heat exchangers in number of k, the working chamber a will pass successively through the states:

(P _O , V _O , T _O ); (P ₁ , V ₁ , T ₁ ) ..., (Pk, V _k , T _k ) with the following relationships between the state parameters:

while the polytrope mixture will have the successive states:

These are precisely the conditions for a quasi-isothermal evolution of the gas in the working chamber, that is to say, an alternative variation reduced on one side and on the other of an isothermal curve.

At the same time the heat exchangers will each pass alternately, through two states: (P ₁ , V _al , T " ₁ ); (P ₁ , V _al , T ' ₁ ); (P' ₂ , V _a2 , T" ₂ );

(P2, V _a 2, T'2) .... (P ' _k , V _ak , T " _k ); (P _k , V _ak , T' _k ); while between the state parameters we have the relationships:

We underline the essential fact that the filling of the exchangers with the working agent to the operating parameters and their reproduction at each cycle, is done automatically by the course of the same cycle in which the working agent is sucked by the connection of suction 6, by storing by degrees, in each exchanger the working agent at stabilized parameters, reproducible at each cycle. The succession of the phenomena of aspiration, polytrope mixing, common evolution of the combined volumes and isochoric cooling of the exchangers, all tend together towards a stable equilibrium of the system, by a monotonous variation of the state parameters of the gas in the chamber. as in heat exchangers, towards stable limits, self-reproducible at each cycle, limits whose values will be reached practically after a few tens of cycles from the beginning of the operation of the machine.

Those which we have just exposed above were established following a mathematical research of the phenomena, of which we present only the final results. Thus, the limits towards which the pressures Pj of the working chamber tend when it detaches from each of the exchangers are given by the equations:

in which, apart from the notations already defined above, the following have also been used: m1, the polytropic exponent of the mixture of the two gases; m2, the polytropic exponent of the common evolution of the gas in the chamber and the exchanger; the factor of the isochoric evolution of the gas of the exchanger number i during the waiting time between successive contacts with two working chambers.

If we consider that the gas in the variable volume working chamber isothermally mixed with the gas from the cooled heat exchanger, this assumption does not differ significantly from reality, that is to say m ^ ≈l, the above equations can be solved literally, by obtaining for the stabilized values of the pressures P ₁ , the relations:

The values P _i are finished if the relationship between the volumes of the working chamber (V _i ) and the volume of the independent exchanger (V _ai ):

and the circulation of the working agent in one direction in the heat exchangers A and B is achieved in one direction, that is to say in the direction explained above if the relation exists between the same parameters:

for the quasi-isotherm of compression and for the quasi-isothermal of relaxation.

Things take place in a similar way also in the expansion process, group B of heat exchangers ensuring that the phenomenon is described by the same equations as above.

The intensification of the heat transfer up to the level required by an isothermal evolution of the gas of the working chamber, via the heat exchangers in accordance with the invention, is demonstrated by the relationships established, from a dimensioned by the influence of the polytrope exponent of common evolution m ₁ to value close to unity and on the other side, by the isochore exchange of the heat of the exchangers expressed by the factor i which is less than l 'unit for the compression isotherm and higher than the unit for the expansion isotherm.

The qualitative diagrams of the quasi-isothermal compression or expansion processes, represented in FIGS. 2 and 3 show that the curve of the real transformations g for compression and h for relaxation are realized as a result of the addition of certain transformations sequential successive polytropes whose points of continuity i are located above and below the theoretical insothermal curve j for compression and ^ for relaxation. In FIG. 3 are represented in temperature-entropy coordinates only the curves of the real transformations, that is to say the curve n for compression and the curve o for expansion.

From the diagram shown in FIG. 2, it follows that the negative mechanical work in the real quasi-isotherm of compression g and the positive mechanical work in the real quasi-isotherm of relaxation h are comparable with that of certain theoretical isothermal transformations j and I

The process for obtaining the quasi-isothermal transformation in the processes of compression or expansion of gases can be applied to any operating cycle of any thermal machine with working chamber of variable volume and with outside heat sources such as: compressors, external combustion engines, heat pumps, refrigeration machines, etc. Next, a way of making a thermal machine, which operates according to the method, is presented, such as an external combustion engine.

The rotary external combustion engine, in accordance with the present invention, consists of a rotary cylinder 9 in which slides a double-acting piston 10 provided with sealing segments 11. The double-acting piston 10 is mounted halfway of its length using the cousins 12 on a crank pin journal of a crankshaft 13 and for mounting reasons is formed of two halves r coupled, on the plane of separation of the cousins using the prisoners 14. The crankshaft 13 rests with its bearing journals g in the side covers 15 and 16 by means of bearings 17 and 18 located on the same axis. The rotary cylinder 9 rests on the side covers 15 and 16 using the bearings 19 and 20 which define an axis III-III perpendicular to the longitudinal axis of the cylinder, dividing it into two equal parts. Attached to the crankshaft 13 is mounted a toothed wheel 21 with external teeth which meshes in ratio of 1: 2 a toothed wheel with internal teeth 22, integral with the rotary cylinder 9. In the side walls of the rotary cylinder 6 are formed four holes f communicating two by two with each room with variable volume a. Solid with the body of the bearings of the rotary cylinder 9 are mounted two distribution discs 23, one on each side of the rotary cylinder 9. The distribution discs 23 are each provided with two windows s from which galleries 24 which connect these windows s to windows f formed in the wall of the rotating cylinder 9. By turning, the distribution discs 23 together with the rotating cylinder 9, make the windows s pass in front of the radial windows t and u, formed in the fixed covers 15 and 16 and arranged on the same diameter as the windows s placed on the mobile distribution disks 23, t and u being sealed relative to s.

The windows t are used for the connection of the variable-volume working chamber a to a heat exchanger A or B in the first phase by means of certain fittings 25 while the windows u are used for the connection of the same working chamber to a heat exchanger A or B in the second connection phase via the fittings 25. The fitting 25 constitutes the outlet fitting and the fitting 26, the inlet fitting in a heat exchange unit 1 or 2 generally known and belonging to groups of heat exchangers A or B. Each of the windows t and u is sealed on a trapezoidal contour with linear and expandable segments 27 mounted in generally known seats, practiced in the fixed covers 15 and 16. Still with linear and expandable segments, located continuously on cαuntours blind trapezoids, arranged on the same diameter as the windows t and u, are also sealed the two spaces v located between the two groups of windows t and u corresponding to the groups of exchangers A and B.

On the outer covers 15 and 16 are made in the zone corresponding to the outer dead center of the piston 10 of the windows w, having the same shape and radial location as the windows t and u which are each linked with a suction connection 6. From similar to windows t and u, the windows w are sealed on a trapezoidal contour by the expandable linear segments 27. The suction windows w can be closed, after the engine has arrived at nominal operating speed with n ' any external control, correlated in a generally known manner, with the engine operating parameters.

A rotary external combustion engine according to the invention operates as follows. Under the action of the working gases, the double-acting piston 10 performs a transaction movement in the cylinder 9, at the same time also imposing the rotation of the crankshaft 13 and the rotary cylinder 9, around the axis III— III with a rotation speed equal to half the rotation speed of the crankshaft. The translational movement is purely harmonic, the maximum stroke of the piston being equal to four times the distance from the axis of the bearing journal p to the axis of the crankshaft 13, that is to say four times the eccentricity of the crankpin . All of the inertial forces result in a radial force, in phase with the position of the crankshaft, which can be balanced with fixed counterweights on the crankshaft, in a generally known manner. None of the inertia and pressure forces acting on the piston give normal components between the piston and the walls of the cylinder.

The alignment of the toothed wheels 21 and 22 does not participate in the transmission of the engine torque to the crankshaft. Theoretically the mechanism is completely determined without this anchoring. The 21-22 drive double the piston-crank pin cynematic oak and has the practical role of facilitating the control of the rotation of the cylinder when the direction of the actuating forces enters under the cone of friction, without participating in transmission of engine torque. The mission of the angénage is consequently that of overcoming the friction forces in the rotational movement of the cylinder or of the moment of inertia, caused by the variation of the number of turns, assuming the only normal forces which could have appeared between the piston and the cylinder walls and which would have determined the rotation of the entire cylinder. By the introduction of the angénage, the contact between the piston and the walls of the rotary cylinder is reduced only to the contact pressure of the segments necessary for sealing, The system of lubrication of the components of the engine is generally known.

The rotary external combustion engine, in accordance with the invention, operates according to a Carnot cycle composed of two quasi-isotherms g and h which are the result of the addition of certain successive polytrope sequential transformations whose points of continuity i are found above and below the theoretical isothermal curves j and I and two adiabatic curves x and y easily obtainable by external thermal insulation, generally known, of the cylinder in the area of the working chamber.

The Carnot cycle is carried out with an engine according to the invention, in that in the first part of the compression, the working chamber of variable volume has successively comes into contact with the cooled heat exchangers A on the path of the fittings 25 and 26, windows t and u side covers 15 and 16, window s on the distributor disk 23, galleries 24 and windows f located in the walls of the rotary cylinder 9, storing part of the agent working in these exchangers and by compressing in a quasi-isothermal manner, the rest of the working agent in accordance with the process described above.

When the variable volume chamber has left the last cooled heat exchanger A, adiabatic compression of the working agent remaining in the chamber begins, until the internal dead center of the piston. For this purpose the motor is provided with a corresponding thermal insulation, generally known.

As soon as the piston has reached internal dead center, the variable-volume working chamber a is connected to the heated heat exchangers B, on the same path described previously, with which an exchange of working agent is obtained according to the method described , by determining the quasi-isothermal expansion of the agent remaining in the chamber. After the chamber has left the last heat exchanger B, the work agent therein relaxes so adiabatic until the opening of the suction window w when the variable volume working chamber has reached a vacuum so that it will suck up a quantity of working agent equal to that which it has stored in the two groups of heat exchangers A and B during the previous cycle and then the cycle is repeated successively and alternately for the two working chambers a. The process of storing the working agent in the heat exchangers arrives, after a few dozen rotations of the crankshaft, in a stabilized state when the suction set is reduced to zero and the suction window w has to be closed. . After closing window w, the engine works with the working agent in a closed circuit. The mechanical work per cycle and the power of the motor increase proportionally with the increase in the suction pressure of the motor.

The suction of the work agent can be done directly from the atmosphere or from a closed tank, in which case, the state parameters of the work agent can differ in value from the atmospheric parameters. The working agent can be any gas, gas mixture or heterogeneous gas-liquid mixture. The cooling of the heat exchangers A can be done in a known manner with any cooling agent and the heating of the heat exchangers B can be done with any heat source, including geothermal water, solar source, nuclear power or fuel burner of any type.

The example presented concerning the production of a thermal machine, in accordance with the invention is not limiting. If a thermal machine, in accordance with the invention, operated as a compressor, it would be necessary to cancel, in comparison with the example presented, the group of heated heat exchangers B and the exhaust connection 7, keeping the group of exchangers of heat A and the inlet connection 6 widened and a discharge connection 8 will be used. A thermal machine, in accordance with the invention, which would function as a compressor, could compress in a single stage the gases at relatively high ratios of compression by discharging the compressed gas at temperatures close to those of the ambient medium. A compressor which would operate in accordance with the invention, due to the reduced temperature of the compression space, could use synthetic materials for the construction of the piston, segments, valves, etc. and would have a relatively simple construction, having a much reduced weight and dimensions as a result of the elimination of the intermediate compression stages. If the thermal machine, in accordance with the invention, operated as a heat pump or refrigeration machine, it would only be necessary to modify the arrangement of the two groups of heat exchangers so as to obtain the course of the cycle in the opposite direction than in the case of functioning as an external combustion engine. One group of heated heat exchangers B would be the hot source and constitute the part of the heat pump that heats, while the other group of heat exchangers A would be the cold source and would constitute the part of the refrigerating machine. which cools.

OPPORTUNITIES FOR INDUSTRIAL OPERATION

The method and the machine for obtaining a quasi-isothermal transformation in the gas compression or expansion processes can be applied in any industrial field which supposes the need for isothermal compression or expansion , such as the chemical, refrigeration industry, etc. just like in any technical field which supposes the use of thermodynamic transformation to obtain mechanical energy, this one being able to be used in the field of transport, the production of electric energy or in other areas.

Claims

1. Method for obtaining quasi-isothermal transformation in the compression or expansion processes of gases, characterized in that, for the purpose of carrying out certain transformations as close as possible to an isothermal theoretical transformation as well as the maintaining a compression or expansion ratio as high as possible by the fact that the volumes of certain heat exchangers do not add up to the volume of the dead space determined by constructive parameters of a volume working chamber variable, uses two groups of heat exchangers (A and B), in each heat exchanger, independent of each other, the working agent circulating intermittently and in one direction, exchangers which are connected and disconnected successively and cyclically with the variable volume of a working chamber (a), the duration of connection between this working chamber and an independent exchanger being made up of two phases namely: in the compression isotherm, in the first phase, there is a flow of the working agent from an independent cooled heat exchanger (A) in a variable volume working chamber (a) up to equalization of the pressures of the two volumes, the mixing process being polytropic, the working agent of the chamber yielding heat to the working agent arriving from the exchanger and in the second phase a flow of the agent takes place working chamber (a) in the exchanger (A) by transporting the associated heat, the total mass of compressed gas yielding heat by the independent cooled exchanger (A), while in the expansion isotherm in a first phase, there is a flow of the working agent from the variable-volume working chamber (a) in an independent heated heat exchanger (B), until the pressures of the two volumes are equalized, the work of the heat exchanger yielding heat to the work agent coming from the room by melan polytrope ge and a second phase, in which the working agent flows from the heated exchanger (B) into the working chamber (a) transporting the afferent heat while the total mass of relaxed working agent receives the heat by the independent heated heat exchanger (B), the successive connection of the independent heat exchangers (A and B) to the working chamber of variable volume (a) being done in such a way that the time in which it does not exist not a connection between the chamber and an exchanger ensures an isochoric evolution of the working agent of each exchanger when the heat is transferred to the outside in the isotherm of eompression and one

2. Method for obtaining certain quasi-isothermal transformations, according to claim 1, characterized in that, in order to achieve a thermodynamic evolution as close to an isotherm as possible, the transformation curve achieved by the successive connection and disconnection of the variable volume working chamber (a) to the independent heat exchangers (A and B) is obtained as a result of the addition of certain successive polytropic sequential transformations, their points of continuity ( i) lying above and below the theoretical isothermal curve, so that the negative mechanical work in the quasi-isotherm of compression (g) and the positive mechanical work in the quasi-isotherm of expansion (h) are comparable with those of certain theoretical isothermal transformations (j and I).

3. Method for obtaining certain isothermal transformations, in accordance with reventîcation 1, characterized in that, with the aim of ensuring circulation of the working agent inside an independent heat exchanger, in a only one way, the pressures of the working agent of the exchangers are ensured by even the variable volume working chamber (a) by a self-storage process until one reaches in each exchanger, after a series of cycles, a stabilized value of the pressure required and self-repeating for each cycle.

4. Method for obtaining a quasi-isothermal transformation in gas compression and / or expansion processes, according to claims 1 and 3 characterized in that in order to achieve the circulation of the working fluid in a one way and to ensure that certain stabilized values of the pressures in the additional heat exchangers (V _ai ) are reached, to which we give such dimensions that they can together with the variable volumes (V _iI ) of the working chamber ( a) in contact with an exchanger (A or B) of order "i" and with variable volumes (V _i ) when the working chamber (a) detaches from the heat exchangers (A or B) of order "i" check relationships:

for quasi-isothermal relaxation.

5. A thermal machine which carries out the process of claims 1, 2, 3 and 4, formed of a rotary cylinder, in which a double-acting piston moves, characterized in that it has a group of heat exchangers (A) independently cooled, for the compression phase, and a group of heat exchangers (B) independently heated for the expansion phase, the successive connection and disconnection between each independent exchanger and a working chamber at variable volume (a) of the thermal machine produced by means of the windows (f) made in the walls of a rotary cylinder (9) of the galleries (27) of the windows (s) made in certain distribution discs (23 ), windows (t and u) located on the fixed covers (15 and 16) of the motor carcase and arranged radially and sealed on a trapezoidal contour by expandable linear segments (27) and certain fittings (25 and 26 ) which constitute the connections outlet and inlet measurements in an independent heat exchanger (A and B).

6. A thermal machine, according to claim 5, characterized in that the groups of heat exchangers (A and B) are formed of independent exchangers, each exchanger being able to be connected to a working chamber of variable volume (a) by means of two windows (t and u) sealed on a trapezoidal contour, a window (t) ensuring the connection for carrying out the first phase of quasi-isothermal transformation, while the second window (u) ensures the connection to carry out the second phase of the quasi-isothermal transformation process.

7. A thermal machine, according to claim 5, characterized in that certain spaces (v), located between the two groups of windows (t and u) corresponding to the exchanger groups (A and B), are sealed by linear expandable segments (17) located continuously on blind trapezoidal contours having the same radial positioning as the groups of connecting windows (t and u).