FR2972481A1 - Alternative heat engine for driving e.g. two-stage variable displacement compressor, has control unit controlling opening and closing of flow channels according to predetermined operation cycle - Google Patents

Abstract

The engine (1) has a first fluidic communication unit (2) communicating between an enclosure (20) and an outer side of the enclosure that include metallic bellows. A second fluidic communication unit communicates between another enclosure (30) and an outer side of the latter enclosure. A third fluidic communication unit communicates between the two enclosures. A heating or cooling unit heats or cools gas working fluid circulating in the third communication unit. A control unit (9) controls opening and closing of the three communication units according to a predetermined operation cycle.

Description

The subject of the present invention is an alternative thermal machine for gaseous working fluid with external heat input and a compressor, a motor, a motor / compressor comprising such a machine and a cogeneration system comprising such a motor or motor / compressor. . This alternative heat machine with gaseous working fluid and with external heat input, otherwise known as a hot air motor for its motor applications, is part of the thermodynamic conversion perspective of the great majority of heat sources.

Fast and efficient power variations are difficult to achieve with external combustion engines. These are more apt to operate at constant rated power. This point is a disadvantage especially for use in the automotive industry.

Indeed, the speed variation of these engines is particularly complex to achieve because it can be done only by acting on the compression ratio of the working fluid. FR2512881A1 discloses a thermal machine and a hot air motor comprising bellows as compression and expansion chambers. The compression or expansion chambers may be simple or annular, that is to say between two concentric bellows, in order to optimize the thermodynamic exchanges by the large exchange surface made available by the bellows, and minimize mechanical losses. This document also discloses a compressor provided with valves, and in particular valves whose compression chamber is based on the same principle of concentric bellows. However, the device described in this document does not allow fast and efficient load variation, and is optimized for only one operating point. In addition, the recuperators generate large dead volumes, which affect the performance of this engine. The present invention aims to solve all or part of the disadvantages mentioned above by the realization of a thermal machine 35 able to effectively respond to rapid changes in mechanical or electrical power, via its linear alternator and dedicated static power converter . Another object of the invention is to optimize primary energy consumption by its ability to integrate with existing or future cogeneration systems. For this purpose, the subject of the present invention is an alternative thermal machine for gaseous working fluid and with external heat input, characterized in that it comprises: a first enclosure, said first enclosure being delimited by a first mobile flange between a top dead center position and a bottom dead center position, and a first fixed yoke arranged facing said first flange, said first flange and said first yoke being joined by first side walls formed by at least one first amplitude bellows; variable, 15 - a second chamber, distinct from the first chamber, said second chamber being delimited by a second flange movable between a top dead center position and a bottom dead center position, and a second fixed yoke arranged opposite said second chamber; flange, said second flange and said second yoke being joined by second side walls formed by less a second variable amplitude bellows, first fluidic communication means between the first chamber and the outside of the first chamber, second fluidic communication means between the second chamber and the outside of the second chamber, third means of fluid communication between the first chamber and the second chamber; means for heating or cooling the gaseous working fluid circulating in the third fluid communication means; means for regulating the opening and the closing the first, second and third fluid communication means at the start and at the arrival of the first chamber and the second chamber according to a predetermined operating cycle. The bellows offers a large thermodynamic exchange surface, and a low thermal conductivity due to its thin walls, to limit the heating of the fluid during its compression in the first chamber, and to promote the heating of the same fluid during of his relaxation in the second enclosure. The power of the heat engine increases with its cubic capacity, ie the volume between the top dead center TDC and the bottom dead center PMB. The variable capacity of the thermal machine, proportional to the amplitude, is controlled by the servo laws adopted by regulating means. The regulating means automatically adapt the opening and closing of the valves to the appropriate thermodynamic cycle and to the amplitude or displacement of the thermal machine. According to one embodiment, the regulating means regulate the effective power of the heating or cooling means. According to one embodiment, the at least one bellows of the first enclosure and / or the at least one bellows of the second enclosure are metallic. This arrangement makes it possible to have a material that can ensure high mechanical stresses, temperature and pressure. According to one embodiment, the heating or cooling means comprise a heat exchanger arranged to recover a portion of the heat of an external heat transfer fluid circulating in the primary circuit of this heat exchanger to transmit it to the working fluid. gaseous circulating in the third fluid communication means, the secondary circuit of the same heat exchanger comprising a part of these same third fluid communication means, or comprise a heat exchanger arranged to recover some of the heat of the working fluid flowing in the third fluidic communication means for transmitting it to an external cooling heat transfer fluid circulating in the primary circuit of this heat exchanger, the secondary circuit of this same heat exchanger comprising a part of these same third fluidic communication means. According to one embodiment, the heating means comprise in addition to the first heat exchanger, a second heat exchanger, arranged to recover a part of the heat of the fluid expelled from the second chamber by the second fluid communication means 35, a part of which constitutes the primary circuit of this second heat exchanger, for transmitting it to the fluid circulating in the secondary circuit of the same second heat exchanger, the secondary circuit of the same second heat exchanger comprising a second part of the third fluid communication means arranged downstream of the first part included in the first heat exchanger.

This arrangement makes it possible to regenerate the fluid escaping from the second chamber by recovering part of its heat to transfer it to the fluid arriving in the first heat exchanger, for this same second chamber. According to one embodiment, the thermal machine further comprises first means for heating or cooling the fluid flowing in the third fluid communication means, second means for heating or cooling the at least one bellows of the second chamber and / or means for cooling the at least one bellows of the first chamber, the regulation means controlling the useful power of these heating or cooling means and / or these cooling means according to the work required for the alternative thermal machine. This arrangement makes it possible to maintain the hot or cold fluid after it arrives in the second enclosure by the third fluid communication means and / or to keep it cold after it arrives in the first enclosure by the first fluid communication means. In addition, the control of the second bellows heating means of the second chamber and the bellows cooling means of the first chamber makes it possible to select the thermodynamic cycle of the thermal machine in its motor application. Indeed, the increase in the heating power of the at least one bellows of the second chamber and the cooling power of the at least one bellows of the first chamber makes it possible to change the starting cycle close to the cycle. from Joule (adiabatic compression and expansion) to a cycle close to the Ericsson cycle (isothermal compression and expansion). Increasing this heating power of the at least one bellows of the second chamber and cooling the at least one bellows of the first chamber allows to further increase the power of the heat engine, but decreases its energy efficiency.

On the other hand, the ratio of the compression and expansion volumes varies according to the thermodynamic cycle in the presence. Indeed, the ratio between the volume of expansion and the volume of compression increases as the thermodynamic cycle approaches the Ericsson cycle. In this mode of operation, the thermal machine is sized to operate with the best efficiency in Joule cycle, that is to say when the heating of the second enclosure is minimum. In its engine application, in order to avoid the unnecessary production of a residual pressure at the end of expansion when the heating power of the second enclosure increases, a throttle reduces the mass of working fluid penetrating inside the first enclosure . The position variation of this throttle is thus controlled by the power of the heating system of the bellows of the second enclosure. On the other hand, the synchronism of the two working chambers is provided by guide shafts integral with the flange of the first enclosure and the flange of the second enclosure. According to one embodiment, the second heating or cooling means comprise a hot or cold fluid enveloping the at least one bellows of the second chamber, and / or the cooling means comprise a cold fluid enveloping the at least one bellows from the first speaker. This arrangement allows a homogeneous heat transfer through the at least one bellows of the second chamber and / or the at least one bellows of the first chamber, the terms hot and cold to be considered with respect to the temperature of the fluid. job. According to one embodiment, the at least one bellows of the second enclosure and / or the at least one bellows of the first enclosure comprises a double wall, the second heating or cooling means being arranged to convey a heat transfer fluid of heating or a heat transfer fluid for circulating inside the double wall of the at least one bellows of the second chamber, and / or the cooling means being arranged to convey a coolant for cooling to circulate to inside the double wall of the at least one bellows of the first enclosure. This arrangement makes it possible to exploit the annular zone between the two walls of the at least one bellows considered as circulation chamber of the heating or cooling fluid for the second enclosure, and / or cooling fluid for the first enclosure.

According to one embodiment, the two walls of the double wall are connected to at least one corrugation of the at least one bellows by a ring comprising a passage, the passage being arranged diametrically opposite from one ring to the other a corrugation of the at least one bellows, one of the heating or cooling heat transfer fluids being intended to circulate through all the passages of all the rings. This arrangement makes it possible to improve the heat exchange by increasing the heating or cooling heat transfer fluid pathway between the inlet and the outlet of the at least one bellows, and to reduce the bulk of the inlet and outlet channels. output of the fluid in the at least one bellows while maintaining a good homogeneity of heat transfer through the walls of the at least one bellows. According to one embodiment, the regulation means comprise a set of valves including at least one fluid inlet valve in the second chamber and at least one fluid exhaust valve in the second chamber, these at least one intake and exhaust valves being movable between a closed position and an open position, and arranged on the second cylinder head of the second enclosure. According to one embodiment, the regulation means comprise a set of valves including at least a first fluid admission valve in the first chamber, and at least a first fluid exhaust valve in the first chamber, these at least first intake and exhaust valves being movable between a closed position and an open position, and arranged on the first cylinder head of the first chamber, and at least a second fluid intake valve in the second chamber; enclosure and at least one second fluid exhaust valve in the second chamber, these at least second intake and exhaust valves being movable between a closed position and an open position, and disposed on the second breech of the second enclosure. According to one embodiment, the regulation means further comprise a set of control means acting on the position of at least two valves, at least one position sensor of the first flange and / or the second flange and / or at least one pressure sensor of the first enclosure and / or the second enclosure, acquisition means arranged to receive control data from the position and / or pressure sensors and arranged to transmit control data to at least a part of the control means.

This arrangement makes it possible to dispense with the use of a camshaft, a major consumer of energy, for controlling the positioning of the valves, and offers the advantage of individually controlling each of the valves and of adapting the operation of the valves. the thermal machine to the desired use.

Advantageously, the regulation means also comprise a movable butterfly between a closed position and an open position, arranged in the fluidic communication means and arranged to control the flow of the working fluid entering the first chamber. According to one embodiment, the control means comprise cylinders, for example electrically actuated pneumatic, to control the opening and / or closing of at least two valves. According to one embodiment, the control means comprise return means for controlling the opening and / or closing of the valves.

Advantageously, the thermal machine comprises a counterpressure ring having a cylindrical geometry, integrally connected along its axis to the tail of the at least one intake valve of the second enclosure and provided with at least one peripheral recess disposed between its posterior surface and its anterior surface.

This arrangement makes it possible to prevent the unintentional opening of the at least one intake valve of the second enclosure which may be caused by the strong pressure exerted on the collar of this same at least one intake valve of the second enclosure in any application of the thermal machine, the pressurization having taken place in the first enclosure. In addition, this arrangement makes it possible to limit the moving mass and therefore the inertia of the intake valve as well as to limit the appearance of leaks by creating pressure drops induced by the generation of a swirling flow inside. of the at least one peripheral recess According to one embodiment, the first yoke comprises a first boss extending respectively inside the first enclosure to a height between a height located beyond the plane of the first cylinder head and a height substantially equal to the distance between the first yoke and the first flange of the first chamber when the first flange is at top dead center, and / or the second yoke comprises a second boss extending respectively inside. the second enclosure on a height between a height located beyond the plane of the second cylinder head and a height substantially equal to the distance between the second cylinder head and the second flange of the second enclosure when the second flange is at the top dead center.

This arrangement has the effect of reducing or at best avoiding any dead volume of the at least one bellows of the first enclosure and / or the second enclosure. According to one embodiment, the first side walls of the first chamber are formed by two concentric bellows and / or the second side walls of the second chamber are formed by two concentric bellows. This arrangement makes it possible to create a first chamber and / or a second chamber in a volume having a general shape of a hollow cylinder formed between the two concentric bellows, the hollow inside the cylinder increasing the thermodynamic exchange surface between the first chamber and / or the second enclosure and the exterior. The present invention also relates to a motor comprising an alternative thermal machine as described above, the first chamber constituting a so-called compression chamber and the second chamber constituting a so-called expansion chamber. According to one embodiment of this engine, the first fluid communication means are connected to the second fluid communication means to form a closed circuit and having means for cooling the working fluid flowing in the second fluid communication means. This arrangement makes it possible to use a fluid other than air having physical properties making it possible to exploit the thermodynamic cycle of the engine under better conditions, for example inert helium not undergoing a phase change during the thermodynamic cycle. of the motor.

The subject of the present invention is also a two-stage variable displacement compressor comprising an alternative thermal machine as described above, the first chamber constituting a first so-called compression chamber and the second chamber constituting a second so-called compression chamber, and a device driving guide shafts integral with the flange of the first enclosure and the flange of the second enclosure. The present invention also relates to a motor / compressor comprising on the one hand an alternative thermal machine as described above, the first chamber being a so-called compression chamber and the second chamber being a so-called expansion chamber and the so-called chamber of compression being oversized relative to the said expansion chamber, and further comprising a sealed storage tank in communication with the third fluid communication means.

The present invention also relates to a cogeneration system comprising an alternative heat engine as described above or a motor / compressor as described above. This arrangement makes it possible to recover heat produced by a thermal source, such as combustion fumes, to produce electricity by the reciprocating engine or by the motor / compressor associated with a linear alternator. According to one embodiment, the cogeneration system comprises at least one linear alternator, the electric power produced by the at least one linear alternator being partially controlled by the control of the operating cycle of the motor or the motor / compressor. This arrangement makes it possible to damp the movement of the bellows when approaching the position of bottom dead center and / or top dead center. In any case, the invention will be better understood with the aid of the description which follows, with reference to the appended schematic drawing showing, by way of non-limiting example, an alternative thermal machine according to the invention. FIG. 1 is a general block diagram of an alternative thermal machine according to the invention used as a cogeneration system comprising an alternating heat engine.

FIG. 2a illustrates the beginning and the end of a first phase of the operating cycle of the thermal machine of FIG. 1.

FIG. 2b illustrates the beginning and the end of a second phase of the operating cycle of the thermal machine of FIG. 1. FIG. 2c illustrates the beginning and the end of a third phase of the operating cycle of the thermal machine of FIG. Figure 1.

FIG. 2d illustrates the beginning and the end of a fourth phase of the operating cycle of the thermal machine of FIG. 1. FIG. 3a shows a sectional profile view of a bellows of an alternative thermal machine according to a first embodiment. Figure 3b shows a top view of the bellows shown in Figure 3a. FIG. 4a shows a sectional side view of a bellows of an alternative thermal machine according to a second embodiment. Figure 4b shows a top view of the bellows shown in Figure 4a.

FIG. 5 shows a detailed sectional side view of a portion of the alternative thermal machine of FIG. 1 according to two different positions. FIG. 6 shows an overall cross-sectional view of a portion of the alternative thermal machine of FIG. 1.

Figure 7a shows a longitudinal sectional view of a portion of the thermal machine of Figure 6 equipped with a plurality of linear alternators according to a first embodiment. Figure 7b shows a longitudinal sectional view of a portion of the thermal machine of Figure 6 equipped with a single linear alternator according to a second embodiment. FIG. 8 shows a profile view in detailed section of a heat machine having a configuration with two concentric bellows for the first chamber and the second chamber. Fig. 9 is a block diagram of a heat machine 30 used as a compressor with two stages of compression. FIG. 10 illustrates the Clapeyron diagram of several thermodynamic cycles illustrating the operation of an alternative thermal engine according to the invention. As illustrated in FIGS. 1, 2a to 2d, 6, 7a, 7b, 8 and 9, an alternating heat-generating machine 1 with a gaseous working fluid F with external heat supply comprises a first enclosure 20 and a second enclosure 30. The first enclosure 20 is delimited on the one hand by a first flange 23 movable between a top dead center position PMH and a bottom dead center position PMB, and secondly by a first fixed yoke 21 arranged next to said first flange 23, said first flange 23 and said first yoke 21 being joined by first side walls 24 formed by a first metal bellows 40a of variable amplitude. The second enclosure 30, distinct from the first enclosure 20, is likewise defined on the one hand by a second flange 33 movable between a top dead center position PMH and a bottom dead center position PMB, and secondly by a second fixed yoke 31 arranged facing said second flange 33, said second flange 33 and said second yoke 31 being joined by second side walls 34 formed by a second metal bellows 40b of variable amplitude. The general shape of the first chamber 20 and the second chamber 30 is respectively determined by the shape of the metal bellows 40a, 40b. In the example shown in particular in Figures 1, 6 and 9, the metal bellows 40a, 40b have a general cylinder shape. Nevertheless, the present invention is not limited to this particular geometrical shape, the metal bellows 40a, 40b being able, for example, to have a generally parallelepiped shape of rectangular or square section. In addition, an alternative thermal machine 1 also comprises first fluid communication means 2, second fluid communication means 3 and third fluid communication means 4. In an application of the thermal machine 1 as a motor, the first chamber 20 is called compression and the second 30 enclosure is called relaxation. The first fluidic communication means 2 extend between an end 2a and an end 2b, respectively placing the ambient air in communication with an inlet of the so-called compression enclosure 20 in which is positioned a mobile admission valve 25a between An open position and a closed position of said inlet of said compression chamber 20.

As illustrated in FIG. 6, the end 2a of the first fluidic communication means 2 may advantageously be connected to an air filter 18. The second fluidic communication means 3 extend between an end 3b and an end 3a placing in communication respectively the ambient air with an output of the so-called expansion chamber 30 in which is positioned an exhaust valve 35b movable between an open position and a closed position of said output of said expansion chamber 30. The third fluidic communication means 4 extend between an end 4a and an end 4b respectively placing an output of the so-called compression chamber 20 in which is positioned an exhaust valve 25b movable between an open position and a closing position of said output of the so-called compression chamber 20, and an input of the so-called expansion chamber 30 in which t positioned an inlet valve 35a movable between an open position and a closed position of said inlet of said expansion chamber 30. These various fluid communication means 2, 3, 4 are partly achieved by the formation ducts inside the cylinder heads 21, 31.

The intake and exhaust valves 25a 25b of the so-called compression chamber 20 are disposed on a boss 22 of the cylinder head 21 in order to reduce or at best prevent a dead volume inside the so-called chamber. compression 20 at the top dead center TDC of the flange 23 thereof. The height of this boss 22 inside said compression chamber 20 is between a height beyond the plane of the yoke 21 and a height substantially equal to the distance between the yoke plane 21 and the flange 23 of the so-called compression chamber 20 when the first flange 23 is at top dead center TDC during the maximum compression of the metal bellows 40a.

In the same way, the intake and exhaust valves 35a and 35b of the so-called expansion chamber 30 are arranged on a boss 32 of the cylinder head 31 in order to reduce or at best prevent a dead volume inside. the so-called expansion chamber 30 at the top dead center TDC of the flange 33 thereof.

The height of this boss 32 inside said expansion chamber 30 is between a height beyond the plane of the yoke 31 and a height substantially equal to the distance between the yoke plane 31 and the flange 33 of the so-called expansion chamber 30 when the first flange 33 is at top dead center TDC during the maximum compression of the metal bellows 40b.

Thus, these bosses 22, 32 significantly reduce the dead volumes present when the bellows 40a, 40b are compressed to the maximum. As illustrated in particular in FIG. 1, an alternative thermal machine 1 used in a driving application also comprises first heating means 5 comprising a first heat exchanger 6 and a second heat exchanger 7, otherwise called a regenerator. The first heat exchanger 6 comprises a primary circuit 6a carrying a heating heat transfer fluid 43 preheated by an external heat source 6 'and a secondary circuit 6b comprising a part of the third fluid communication means 4 between an output of the so-called enclosure 20 and an inlet of the so-called expansion chamber 30. The second heat exchanger 7, otherwise called regenerator, comprises meanwhile a primary circuit 7a comprising a part of the second fluid communication means 3 putting in communication an output of the so-called expansion chamber 30 with the ambient air, and a secondary circuit 7b comprising a part of the third fluid communication means 4 between an output of the said compression chamber 20 and an inlet of the so-called expansion chamber 30, this part being arranged upstream of that of the first heat exchanger 6. The alternative thermal machine 1 comprises also second bellows 8 of the heating means 40b of the enclosure of said trigger 30 and 16 of the bellows cooling means 40a of said compression chamber 20 illustrated in part more particularly to Figures 3a to 4b.

In a first embodiment not illustrated, the heating means 8 of the metal bellows 40b of the so-called expansion chamber 30 consist in directly immersing the single-walled expansion bellows 40b in a hot fluid, for example fumes from the combustion of biomass, such as wood or organic waste.

By analogy, in a non-illustrated embodiment, the cooling means 16 of the bellows 40a of the so-called compression chamber 20 consist in directly immersing the single-walled bellows 40a in a cold fluid, for example air cooled by a cold water circuit. As illustrated in these figures 3a to 4b, in another embodiment, each of the metal bellows 40a, 40b comprises a double wall formed by an inner wall 41a defining the enclosure 20, 30 and an outer wall 41b in contact with the external environment to the enclosure 20, 30 considered. According to a first variant illustrated in FIGS. 3a, 3b, the two walls 41a, 41b of the metal bellows 40b of the so-called expansion chamber 30 respectively of the metal bellows 40a of the so-called compression chamber 20 are connected on the one hand to a its two ends assumed higher by the yoke 31 respectively 21 and on the other of its two supposed lower ends by the movable flange 33 respectively 23, and secondly on at least one corrugation 42 by a pierced ring 45 creating a passage 46 for a heating heat transfer fluid 43 intended to circulate between the double wall of the bellows 40b of the so-called expansion chamber 30, respectively a cooling heat transfer fluid 47 intended to circulate between the double wall of the bellows 40a of the said enclosure. 20. The passage 46 of a ring 45 disposed at a given corrugation 42 is disposed diametrically opposite the passage 46 of the ring 45 disposed at a ripple 42 nearest. The profile of a pierced ring 45 and of this passage 46 is more particularly visible in FIG. 3b, the latter having the shape of a circular arc with rounded ends to favor the flows of the fluids 43, 47. Similarly, the yoke 31 and / or the yoke 21 has an inlet passage 44a and the movable flange 33 and / or the movable flange 23 has an outlet passage 44b disposed diametrically opposite the passage 46 of the ring 45 of the the nearest ripple 42, the inlet 44a and 44b outlet also having a circular arc-shaped profile with rounded ends to promote the flow of fluids 43, 47. In this way, the heat transfer fluid 43, preheated by an external heat source 6 ', circulates inside the metal bellows 40b from the inlet passage 44a to the outlet passage 44b, descending successively from one corrugation 42 to another by running each time a half-perimeter on either side of the metal bellows 40b to reach the next passage 46, while transferring heat to the fluid F in the so-called expansion chamber 30 of the other side of the inner wall 41a. Furthermore, this external heat source 6 'can be the same as that used for the first heating means 5 of the working fluid F. In the same manner, the coolant cooling fluid 47, previously cooled, circulates at the same time. the interior of the metal bellows 40a from the inlet passage 44a to the outlet passage 44b, descending successively from one corrugation 42 to another, each time traversing a half-perimeter on either side of the metal bellows 40a until reaching the next passage 46, while absorbing heat to the fluid F in the so-called compression chamber 20 on the other side of the inner wall 41a. According to a second variant illustrated in FIGS. 4a, 4b, the two walls 41a, 41b of the metal bellows 40b of the so-called expansion chamber 30 respectively of the metal bellows 40a of the so-called compression chamber 20 are connected only on their end. higher by the yoke 31 respectively 21 and on their lower end by the movable flange 33 20 respectively 23. However, unlike the first variant described above, the yoke 31 respectively 21 comprises at least one inlet passage 44a opening into the space disposed between the two walls 41a, 41b. In one embodiment, four inlets 44a have the shape of a circular arc with rounded ends and each of them is disposed at 90 ° angular spacing with two others. Similarly, the movable flange 33 respectively 23 has four outlet passages 44b disposed opposite the four inlet passages 44a and 30 having substantially the same shape of a circular arc with rounded ends. Of course, these four output passages 44b can be shifted or multiplied without departing from the scope of the invention. Similarly, in these embodiments, the yoke 31 respectively 35 may comprise a fixed flange integral with the yoke 31 respectively 21 connecting the two walls 41a, 41b of the metal bellows 40b of the so-called expansion chamber 30 respectively of the metal bellows 40a of the so-called compression chamber 20 and having the inlet passages of the heating heat transfer fluid 43 respectively of the cooling coolant 47.

In this way, the heating heat transfer fluid 43, previously heated by an external heat source 6 ', circulates inside the metal bellows 40b from the inlet passages 44a to the outlet passages 44b, transferring in particular from the heat fluid F in the so-called expansion chamber 30 on the other side of the inner wall 41a. In the same manner, the cooling coolant 47, previously cooled, circulates inside the metal bellows 40a from the inlet passages 44a to the outlet passages 44b, in particular by absorbing heat from the fluid F located in the the so-called compression chamber 20 on the other side of the inner wall 41a. Finally, the alternative thermal machine 1 used in a driving application comprises means 9 for regulating the opening and closing of the various fluid communication means at the start and at the arrival of the so-called compression chamber 20 and the so-called expansion chamber 30. In addition, these control means 9 regulate the useful power of the first heating means 5, the second heating means 8 and cooling means 16. Thus, these control means 9 control and control d on the one hand the inclination of a movable butterfly 17 between a closed position and an open position, arranged in the first fluidic communication means 2 and intended to regulate the mass flow rate of the gaseous working fluid F entering the so-called compression chamber 20 and secondly the opening and closing of the various valves 25a, 25b, if they are not valves, 35a, 35b, the useful power of the means of heating 6 of the fluid F flowing in the third fluid communication means 4, the useful power of the external heat source 6 'necessary for heating the heating heat transfer fluid 43 and the cooling coolant flow rate 47 flowing to the inside the double wall of the bellows 40a of the so-called compression chamber 20 and the heat transfer fluid flow 43 circulating inside the double wall of the bellows 40b of the so-called expansion chamber 30. In addition, the control means 9 control and control the opening and closing of valves 19a, 19b allowing the circulation of the working fluid F respectively in the primary circuit 7a and in the secondary circuit 7b of the regenerator 7 in a closed position of the valves 19a, 19b and outside the regenerator 7 in a bypass circuit in an opening position of the valves 19a, 19b. Similarly, the regulation means 9 control and control the opening and closing of valves 19c, 19d respectively for regulating the flow of cooling coolant fluid 47 flowing inside the double wall of the bellows 40a of the enclosure said compression 20 and regulate the heat transfer fluid flow 43 circulating inside the double wall of the bellows 40b of the so-called expansion chamber 30.

Finally, the regulation means 9 control and control the opening and closing of the valve 19e to regulate the flow of the heating fluid 43 or cooling 47circulant in the primary circuit 6a of the heat exchanger 6. In addition, the means 9 comprise position sensors 13 of the movable flanges 23, 33 and / or pressure sensors 14 of the so-called compression chamber 20 and / or the so-called expansion chamber 30, the acquisition means 15 information provided by all of these sensors 13, 14 and control means 10 of the position of the different valves 25a, 25b, if they are not valves, 35a, 35b and adjusting the useful power of the heating means 8 of the bellows 40b of the so-called expansion chamber 30. The amplitude of the expansion and compression chambers 30 is controlled by the control over time of the different valves 25a, 25b, if they do not are not clape ts, 35a, 35b.

The type of thermodynamic cycle is in turn controlled by the variation of the effective power of the second heating means 8 and the cooling means 16. The regulation means 9 automatically adapt the opening and closing of the various valves to the thermodynamic cycle and at the desired amplitude or displacement of the heat machine 1.

In the embodiment shown, the control means 10 comprise pneumatic cylinders 11 arranged to bring the various valves 25a, 25b, if they are not valves, 35a, 35b to their open position, and springs 12 and compression return helical arranged to bring the various valves 25a, 25b, if they are not valves, 35a, 35b to their closed position. Nevertheless, the present invention is not limited to this particular embodiment, it may include pneumatic cylinders double effect, or even pneumatic cylinders bringing the different valves 25a, 25b, if they are not valves , 35a, 35b to their open position coupled with return springs 12 bringing the various valves 25a, 25b, if they are not valves, 35a, 35b to their open position. FIG. 1 illustrates a particular configuration of an alternative thermal machine 1 in its application as a motor, in an embodiment in which the yoke 31 of the so-called expansion chamber 30 is provided with valves controlled by pneumatic cylinders 11 and the yoke 21 of the compression chamber 20 is provided with valves controlled by the upstream and downstream pressure of the working fluid F otherwise called valves. Among others, this Figure 1 shows that the yoke 31 further comprises the boss 32 on which are arranged the intake valves 35a and exhaust 35b of the so-called expansion chamber 30, a cylinder head 50 supporting the two cylinders pneumatic tires 11.

On this point, as illustrated in more detail in FIG. 5, each pneumatic cylinder 11 comprises a piston pin 51 guided linearly by a ball bushing 52, both being arranged in the axis of a valve 35a, 35b. Each valve 35a, 35b comprises a valve stem 53 provided near its end with a circumferential recess 54, as well as a collar 58 or valve head provided on its circumferential contour with a bearing surface 60. The valves 35a, 35b respectively pass through a valve guide 56 disposed partly in the yoke 31 and arranged to ensure a straight movement to the valves 35a, 35b.

In the closed position, the seats 60 of the valves 35a, 35b rest on a valve seat 59 disposed on the boss 32 to ensure sealing in the closed position. For this purpose, this valve seat 59 has a shape substantially complementary to that of the range of the valves 35a, 35b. Of course, the intake valves 25a, 35a and the exhaust valves 25b, 35b may have a different dimensioning without departing from the scope of the invention. Each return spring 12 is compressed between a lower cup 57 resting on the yoke 31 and an upper cup 55 accommodating two half-moons (or keys) arranged to engage and be held in the circumferential recess 54 under the action of said return spring 12. This arrangement keeps the valves 35a, 35b on the yoke 31 and to give them a closed position by default. The length of a piston pin 51 of a pneumatic cylinder 11 is adjusted so as to ensure the proper closure of the valve 35a, 35b. In addition, no valve stem seal is necessary on this heat machine 1, the latter not requiring lubrication.

In an embodiment illustrated in FIG. 6, the yoke 31 also comprises a counter pressure ring 70, otherwise called a compensation ring, having a cylindrical geometry, integrally connected along its axis to the tail 53 of the intake valve 35a. of the so-called relaxation chamber 30.

In addition, this counter-pressure ring 70 is provided with two recesses 71, 72 peripheral disposed between its rear face 73 and its front face 74 disposed opposite the collar 58 of the intake valve 35a. A cylindrical valve guide 56 'disposed at the periphery of the counter-pressure ring 70 provides the guiding function of the intake valve 35a provided with its counter-pressure ring 70. The counter-pressure ring 70 is necessary in order to ensure a good closure of the intake valve 35a. Indeed, the alternative thermal machine 1 has the particularity of having a significant pressure upstream of the inlet valve 35a of the so-called expansion chamber 30, unlike traditional thermal machines where this pressure is approximately equal to the atmospheric pressure. . This pressure exerts a significant force on the collar 58 of this intake valve 35a which opposes the restoring force of the return spring 12 and which can therefore cause the inadvertent opening of the intake valve 35a. This device makes it possible to avoid increasing the stiffness and the bulk of the return spring 12, as well as the efforts made to actuate them.

The counter pressure ring 70 uses the pressure upstream of the collar 58 of the intake valve 35a so as to optimize the opening and closing of this valve 35a. In addition, the cylindrical geometry provided with at least one recess 71, 72 between the anterior face 74 and the posterior face 73 of this back pressure ring 70 gives a large application surface for the pressure force identical to that caused by an enlargement of the diameter of the valve stem 53 at this point, but whose mass and leakage rate remain lower. Indeed, the recesses 71, 72 cause successive pressure drops 20 leaks passing between the back pressure ring 70 and the valve guide 56 '. These pressure losses are due to the creation of swirling flow inside the recesses 71, 72. In another embodiment, the so-called compression chamber 20 can take up all the considerations relating to the so-called 30, including the intake valves 25a and 25b exhaust whose opening is controlled by the control means 9. In these embodiments, the metal bellows 40a, 40b of the compression speakers 20 and expansion 30 occupy a position of 30 natural rest in maximum extension. Of course, the metal bellows 40a, 40b of the compression speakers 20 and relaxation 30 can occupy a natural rest position other than that occupied in maximum extension. In addition, the yokes 21 and 31 are traversed by four outer guides 61 having a cylindrical rod shape. These four outer guides 61 are movably mounted relative to the yokes 21 and 31 which are fixed relative to a frame. For this purpose, the yokes 21 and 31 respectively comprise four ball bushings 63 of inner diameter substantially equal to the outer diameter of the outer guides 61 in order to impart a substantially rectilinear movement to each outer guide 61 by limiting the friction of the four outer guides 61. The movable flanges 23 and 33 traversed by the outer guides 61 are held integral with the four outer guides 61 by a holding means 64 comprising at least one clamping ring and / or a thread of the outer guides 61 and at least one nut tightened on the Thus, any radial twisting or misalignment of the variable amplitude metal bellows 40a and 40b during their extension and compression movement is avoided. Four compression springs 65 in compression are respectively mounted coaxially to the four outer guides 61 near the bolt head 50. These four compression springs 65 in compression bear on the one hand on the yoke 31 and on the other hand respectively on four retaining rings 62 mounted integral with each of the outer guides 61 on a height substantially equal to the height of the return springs 65 in compression at rest when the mobile flange 33 is at the top dead center TDC. The balance of the stiffness forces of the return springs 65 and the metal bellows 40a and 40b generates an equilibrium position of the so-called compression chamber 20 and the so-called expansion chamber 30 at the top dead center T H of the Mobile flange 33. Thus, these compression springs 65 generate a resistance force which tends to oppose the movement of the movable flanges 23 and 33 during their movement from the top dead center TDC to the bottom dead center PMB, c ie during the admission phase of a new fluid F in the so-called compression chamber 20, and the expansion phase of the fluid F in the so-called expansion chamber 30 simultaneously causing the extension of the bellows variable amplitude metal wires 40a and 40b of the so-called compression 20 and so-called expansion chambers 30.

Consequently, these compression return springs 65 produce a restoring force which causes movement of the movable flanges 23 and 33 as they move from the bottom dead center PMB to the top dead center TMP, causing the fluid F to escape into the so-called expansion chamber 30 and the compression of the new volume of fluid F admitted during a previous cycle into the so-called compression chamber 20. Of course, the compression springs 65 may be replaced by tension springs otherwise arranged in the external guides 61.

As illustrated in FIGS. 2a to 2d, the principle of the thermodynamic cycle of a heat engine 1 used as a reciprocating heat engine 100 with a gaseous working fluid F and with external heat input as described above comprises four phases corresponding to different positions of the metal bellows 40a, 40b respectively compression chamber 20 and expansion 30. As shown in the embodiment shown in these Figures 2a to 2d, the four outer guides 61 through the yokes 21, 31 respectively of compression chambers 20 and expansion 30 and are secured to the movable flanges 23, 33 respectively compression chambers 20 and expansion 30. The return springs 65 are here compression springs positioned between the yoke 31 of the expansion chamber 30 and stop rings 62 mounted integral with each of the outer guides 61 on a height substantially equal to the height of the r return springs 65 in compression at rest when the mobile flange 33 is at the top dead center TDC. Thus, these compression return springs 65 oppose the movement of the mobile flange 33 during its movement from the top dead center TMP to the bottom dead center PMB, that is to say during the so-called "active" phase of expansion. causing the extension of the variable-amplitude metal bellows 40b of the so-called expansion chamber 30 During the first phase I illustrated in FIG. 2a, the inlet valve 25a of the so-called compression chamber 20 occupies the open position , the exhaust valve 25b of the so-called compression chamber 20 occupies the closed position, the intake valve 35a of the so-called expansion chamber occupies the open position, the exhaust valve 35b of the so-called The trigger 20 occupies the closed position.

Thus, the fluid F reheated during the preceding cycle by the first heating means 5 enters the so-called expansion chamber 30 and begins to relax, which has the effect of stretching the metal bellows 40b with variable amplitude and driving the mobile flange 33 towards its bottom dead center PMB. This movement also causes the movement of the mobile flange 23 of the so-called compression chamber 20 towards its bottom dead center PMB, thereby sucking a new cold fluid volume F inside the so-called compression chamber 20.

During the second phase II illustrated in FIG. 2b, the inlet valve 25a of the so-called compression chamber 20 occupies the open position, the exhaust valve 25b of the so-called compression chamber 20 occupies the closed position , the inlet valve 35a of the so-called expansion chamber occupies the closed position, the exhaust valve 35b of the so-called expansion chamber 20 occupies the closed position. Thus, the fluid F contained in the so-called expansion chamber 30 continues to relax until the mobile flange 33 reaches its bottom dead center PMB thereby causing the mobile flange 23 of the so-called compression chamber 20 towards its bottom dead center PMB.

The inlet valve 25a of the so-called compression chamber 20 only closes at this moment in order to allow a maximum of fresh fluid F to enter the so-called compression chamber 20. In this position, the return force exerted by the return springs 65 is maximum.

These first and second phases constitute the so-called "active" phases in the thermodynamic cycle of the reciprocating heat engine 100. During the third phase III illustrated in FIG. 2c, the inlet valve 25a of the so-called compression chamber 20 occupies the closed position, the exhaust valve 25b of the so-called compression chamber 20 occupies the closed position, the inlet valve 35a of the so-called expansion chamber 30 occupies the closed position, the exhaust valve 35b of the said expansion chamber 30 occupies the open position. Thus, under the action of the return springs 65 in compression, the expanded fluid F in the so-called expansion chamber 30 is discharged by the second fluid communication means 3 towards the regenerator 7, and the cold fluid F found in the so-called compression chamber 20 is compressed. During the fourth phase IV illustrated in FIG. 2d, the intake valve 25a of the so-called compression chamber 20 occupies the closed position, the exhaust valve 25b of the so-called compression chamber 20 occupies the open position , the inlet valve 35a of the so-called expansion chamber 30 occupies the closed position, the exhaust valve 35b of the so-called expansion chamber 30 occupies the open position. Thus, the cold working fluid F compressed in the said compression chamber 20 escapes through the third fluid communication means 4 in order to be heated by the first heating means 5 firstly by the regenerator 7 and then by the heat exchanger 6. The hot working fluid F previously contained in the so-called expansion chamber 30 escapes by the second fluid communication means 3 and contributes to heating the cold fluid F from the so-called enclosure during the next cycle passing through the regenerator 7. The cycle then continues according to its first phase I. In a particular embodiment, it is possible to envisage that the pneumatic cylinders 11 are powered by a withdrawal of air, compressed by the so-called compression chamber 20. Similarly, it is possible, by means of a second cooling means of the working fluid F at its output from the enclosure called after having passed through the regenerator 7, to consider a mode of operation in a closed circuit putting the second fluid communication means 3 in communication with the first fluid communication means 2, the fluid F used then having physical properties enabling to exploit the thermodynamic cycle of the engine 100 under better conditions, for example inert helium not undergoing a change of phase during the thermodynamic cycle of the heat engine 100. This working fluid F must nevertheless be cooled before it enters. in the so-called compression chamber 20. The efficiency of the hot air motors is directly related to the temperature and the operating pressure. Advantageously, the AC thermal engine 100 previously described makes it possible to maintain the maximum efficiency of the thermodynamic working cycle by offering the possibility of exploiting the maximum temperatures and pressures, whatever the point of operation of the engine 100. The displacement variation , induced by amplitude variation, is an efficiency factor, especially in terms of primary energy consumption and reactivity with a reduced response time. In addition, the variable displacement and the external control of the suction pressure by the throttle valve 17 in the so-called compression chamber 20 make it possible to provide the right flow rate required for a given situation. On this principle and taking into account the thermodynamic cycle of the reciprocating engine 100 described above, the regulation means 9 will supervise on the one hand the opening of the throttle valve 17, as well as the opening of the valves 25a, 25b of the enclosure said compression 20, if they are not valves, and valves 35a, 35b of the so-called expansion chamber 30 according to the load exerted on the motor 100 and supervise the other hand the useful power of the heating means 8, and optionally cooling means 16. The opening frequency of the valves 25a, 25b, if they are not valves, 35a, 35b is set to the operating frequency of the motor 100 via the detection of low dead point PMB and high dead point PMH by the position sensors 13 (speed deduced from the position). A theoretical volume (admitted into the so-called expansion chamber 30 and intended to relax) is determined according to the chosen thermodynamic cycle, and is proportional to the displacement of the engine 100 for a power 25 defined in the previous cycle. The volume of air passed through the inlet valve 35a of the so-called expansion chamber 30 is measured via the position sensor 13. This volume must be greater than the theoretical volume in order to respond to a load increase, and lower theoretical volume to respond to a drop in load. The value of this volume defines the setpoint. Thus, the intake valve 35a of the so-called expansion chamber 30 remains open between the top dead center PMH and the theoretical volume at constant load. If the load increases, the valve will open longer. The exhaust valve 35b of the so-called expansion chamber 30 remains open from the bottom dead center PMB to the top dead center PMH whatever the load, the position of the bottom dead center PMB being able to vary according to this same load. On the other hand, the invention makes it possible to modify the thermodynamic cycle of the engine 100, and thus to modify the useful power from the maximum temperatures and pressures available in order to optimize the primary energy consumption. Thus, at low loads, the amplitude of the motor 100 decreases in order to reduce the displacement, and consequently the power supplied to adapt to the energy demand. The useful power of the second heating means 8 of the metal bellows 40b of the so-called expansion chamber 30 is minimal in order to operate on a cycle close to the Joule cycle, in particular with an adiabatic expansion in the so-called expansion chamber 30 to minimize the primary energy consumption. At high loads, the amplitude of the motor 100 increases in order to increase the displacement and consequently the power supplied to adapt to the demand. The adaptation to the maximum load is done by increasing the useful power of the second heating means 8 of the metal bellows 40b of the so-called expansion chamber 30, and the cooling means 16 of the metal bellows 40a of the enclosure said compression 20 by the regulating means 9 producing a tilting of the Joule cycle towards a cycle close to the Ericsson cycle with an almost isothermal relaxation in the so-called expansion chamber 30 to the detriment of an increase in the consumption of primary energy. These thermodynamic cycle tilts of the motor 100 as well as the different phases described above are illustrated in the Clapeyron diagram illustrated in FIG. 10. The regulation means 9 adapt the operating sequences of the valves 25a, 25b, if these do not are not valves, 35a, 35b to the above thermodynamic cycles with the pneumatic cylinders 11 with electric control allowing a flexible and precise control by prioritizing either the power available, or the conservation of the best possible performance. Thus, the variation in load causes a variation in speed and amplitude of the movable flanges 23, 33 integrally connected by the external guides 61. The measurement of speed and amplitude by the position sensors 13 makes it possible to reduce these parameters to their set point through a first control loop acting on the servo law of the valves, the throttle valve 17 and the power of the heating means 8 of the expansion bellows 30. The electricity is produced by at least one linear alternator 80 comprising a plurality of permanent magnets 81, preferably neodymiums secured to the outer guides 61 and moving inside one or more coils 82 fixed according to the oscillating movement of said outer guides 61, as illustrated on Figures 7a and 7b. In addition, FIG. 7a illustrates an embodiment in which several magnets 81 of several linear alternators 80 are each connected to an external guide 61 while in FIG. 7b the magnets 81 of a single linear alternator 80 are connected to the set of external guides 61. This at least one linear alternator 80 is coupled to a dedicated static power converter that can intervene to slow the speed of the mobile flange 33. In fact, the measurement of the instantaneous electric power makes it possible to anticipate the corrections. amplitude and / or speed thanks to a second regulation loop acting on the first control loop. Thus, by a modulation of the electric power controlled by the cycle of the motor 100, the at least one linear alternator 80 with permanent magnets 81 improves the kinetics of the latter by damping the movement of the bellows 40a, 40b as they approach their point. dead high PMH and their bottom dead PMB. This power modulation is absorbed by the filtering of a continuous bus of the dedicated power static converter, which is connected to the linear alternator 80 via electronic switches controlled by the motor 100 instead of the usual bridge-type rectifier elements. diode. In another embodiment illustrated in FIG. 8, the first lateral walls 24 of the so-called compression chamber 20 are formed by two concentric bellows 40a, 40c and the second lateral walls 34 of the so-called expansion chamber 30 are also formed by two concentric bellows 40b, 40d. The two concentric grooves 40a, 40c of the so-called compression chamber 20 and the two concentric bellows 40b, 40d of the so-called expansion chamber 30 are in this single-wall embodiment but could comprise a double wall allowing the implementation circulation of a heating heat-transfer fluid 43 between the double wall of the concentric bellows 40b, 40d of the so-called expansion chamber 30 and / or of a cooling heat-transfer fluid 47 inside the double wall of the concentric bellows 40a , 40c of the so-called compression chamber 20, in the same way as certain embodiments described above, in particular those presented in FIGS. 3a to 4b. In addition, the motor 100 presented by this figure 8 comprises two intake valves 25a and two exhaust valves 25b for the so-called compression chamber 20 and comprises two intake valves 35a and two exhaust valves 35b for the so-called relaxation chamber 30.

The synchronous movement of the intake valves 35a and the exhaust valves 35b of the so-called expansion chamber is controlled and controlled by the regulation means 9. The alternative heat engine 100 previously described by the significant simplification of its design and its manufacture can, in particular, find an application in a system of micro-cogeneration with external heat source resulting from the combustion of wood intended for the small residential, tertiary and industrial, to produce locally electricity from biomass but also find other applications in large installations for collective use, without excluding the exploitation of fossil energy. Finally, as illustrated in FIG. 9, this alternative thermal machine 1 finds an application as a two-stage compressor 200, the latter comprising the same structural elements as the reciprocating engine 100 previously described, but is furthermore provided with a driving device of the guide shafts 61, the regulating means 9 regulating the operation proper to this type of application. In this embodiment, the driving device of the guide shafts 61 can be made from the same magnets 81 and coils 82, here constituting linear electric motors 80 'instead of the linear alternators 80 used in the application. As engine 100 of the thermal machine 1. In addition, in a use of the thermal machine 1 as a two-stage compressor 200, the first compression stage is made in the first enclosure 20 and the second compression stage is realized. in the second chamber 30.

In addition, in this application, the heat exchanger 6 of the first heating means 5 used for heating the working fluid F flowing in the third fluid communication means 4 and the second heating means 8 used for heating the second chamber 30 are in this application of two-stage compressor respectively used to cool the working fluid F flowing in the third fluid communication means 4 and to cool the second chamber 30 from an external cold source 6 '. The second heat exchanger 7 of the first heating means 5 is not used in this application.

As such, the first heating means 5 and the second heating means 8 become first cooling means 5 and second cooling means 8. The primary circuit 6a of the first heat exchanger 6 of the first cooling means 5 as well as the second cooling means 8 of the metal bellows 40b of the second chamber 30 use a cooling coolant 47. The first chamber 20 is cooled by the same cooling means 16 of the bellows 40a of the so-called compression chamber 20 described in the application of the thermal machine as a motor 100. Similarly, the second cooling means 8 use the same means as those used to heat the so-called expansion chamber 30 in the application of the heat machine as motor 100 and illustrated in Figures 3a to 4b, the heat transfer fluid 43 being replaced by a coolant The air compressed first time in the first chamber 20 and then compressed a second time in the second chamber 30 is thus recovered to be stored in a sealed tank 201. In this application, the set of valves previously ordered 30 by the regulating means 9 may be replaced by valves. The regulating means 9 control and control the flange drive means 23, 33, the cooling power generated by the first cooling means 5 and by the second cooling means 8 and the position of the throttle valve 17 regulating the flow rate. of working fluid F entering the first so-called compression chamber 20.

This mode of regulation offers a very good performance of the compressor, whatever the work required. In a degraded mode, the heat machine 1 can be used as a mixed engine / compressor application.

For this, the motor 100 is modified by overdiming the so-called compression chamber 20 with respect to the so-called expansion chamber 30 and by connecting the third soft communication means 4 to a watertight tank using a means of additional fluidic communication. A part of the working fluid F under pressure at the outlet of the so-called compression chamber is thus directed towards a reservoir to perform the compressor function and another part is directed towards the so-called expansion chamber 30 to provide the engine function. . This motor / compressor is therefore autonomous and does not require an external drive device unlike the two-stage compressor 200 previously described. Although the invention has been described in connection with particular embodiments, it is obvious that it is not limited thereto and that it includes all the technical equivalents of the means described and their combinations. 20

Claims (20)

REVENDICATIONS1. Alternative thermal machine (1) with gaseous working fluid (F) and with external heat input characterized in that it comprises: - a first enclosure (20), said first enclosure (20) being delimited by a first movable flange ( 23) between a top dead center position (PMH) and a bottom dead center position (PMB), and a first fixed yoke (21) arranged facing said first flange (23), said first flange (23) and said first flange (23). first yoke (21) being joined by first lateral walls (24) formed by at least a first variable-amplitude bellows (40a), - a second chamber (30), distinct from the first chamber (20), said second chamber (20), 30) being delimited by a second movable flange (33) between a top dead center position (TDC) and a bottom dead center position (TAB), and a second fixed yoke (31) arranged opposite said second flange (33). ), said second flange (33) and said second yoke (31) being intes by second side walls (34) formed by at least a second bellows (40b) of variable amplitude, - first fluid communication means (2) between the first chamber (20) and the outside of the first chamber ( 20), - second fluid communication means (3) between the second chamber (30) and the outside of the second chamber (30), - third fluid communication means (4) between the first chamber (20) and the second enclosure (30), - heating or cooling means (5) of the gaseous working fluid (F) flowing in the third fluid communication means (4), - regulation means (9) of the opening and closing the first, second and third fluid communication means (2, 3, 4) at the start and at the end of the first chamber (20) and the second chamber (30) according to a cycle of operation predetermined. 2. An alternative thermal machine (1) according to claim 1 wherein the regulating means (9) regulate the effective power of the heating or cooling means (5). 35 3. Alternative thermal machine (1) according to one of claims 1 or 2 wherein the at least one bellows (40a) of the first chamber (20) and / or the at least one bellows (40b) of the second chamber (30) are metallic. 4. Alternative thermal machine (1) according to one of claims 1 to 3, wherein the heating or cooling means (5) comprise a heat exchanger (6) arranged to recover a portion of the heat of a heat transfer fluid external heating circuit (43) circulating in the primary circuit (6a) of this heat exchanger (6) to transmit it to the gaseous working fluid (F) flowing in the third fluid communication means (4), the secondary circuit (6b) of the same heat exchanger (6) comprising a part of these same third fluid communication means (4), or comprise a heat exchanger (6) arranged to recover a portion of the heat of the working fluid (F) circulating in the third fluidic communication means (4) for transmitting it to an external cooling heat transfer fluid (47) circulating in the primary circuit (6a) of this heat exchanger (6), the secondary circuit (6b) of this and a heat exchanger (6) comprising a part of these same third fluid communication means (4). 5. Alternative thermal machine (1) according to claim 4 wherein the heating means (5) comprise in addition to the first heat exchanger (6), a second heat exchanger (7) arranged to recover some of the heat of the fluid. (F) expelled from the second chamber (30) by the second fluid communication means (3), a part of which constitutes the primary circuit (7a) of this second heat exchanger (7), for transmitting it to the fluid (F) flowing in the secondary circuit (7b) of this same second heat exchanger (7), the secondary circuit (71) of this same second heat exchanger (7) comprising a second part of the third fluid communication means (4) disposed downstream of the first part included in the first heat exchanger (6). 6. Alternative thermal machine (1) according to one of claims 1 to 5 further comprising first heating or cooling means (5) of the fluid (F) flowing in the third fluid communication means (4), second means for heating or cooling (8) the at least one bellows (40b) of the second chamber (30) and / or cooling means (16) of the at least one bellows (40a) of the first chamber (20), the control means (9) controlling the potency of these heating or cooling means (8) and / or these cooling means (16) depending on the work required by the alternative thermal machine. An alternative thermal machine (1) according to claim 6 wherein the second heating or cooling means (8) comprises a hot or cold fluid enveloping the at least one bellows (40b) of the second chamber (30), and or the cooling means (16) comprise a cold fluid enveloping the at least one bellows (40a) of the first chamber (20). 8. Alternative thermal machine (1) according to one of claims 1 to 7 wherein the at least one bellows (40b) of the second chamber (30) and / or the at least one bellows (40a) of the first enclosure (20) comprises a double wall (41a, 41b), the second heating or cooling means (8) being arranged to convey a heating heat transfer fluid (43) or a cooling heat transfer fluid (47) intended to circulate to the interior of the double wall (41a, 41b) of the at least one bellows (40b) of the second chamber (30), and / or the cooling means (16) being arranged to convey a cooling coolant (47) for circulating inside the double wall (41a, 41b) of the at least one bellows (40a) of the first enclosure (20). 9. Alternative thermal machine (1) according to claim 8 wherein the two walls (41a, 41b) of the double wall are connected to at least one corrugation (42) of the at least one bellows (40a, 40b) by a ring (45) comprising a passage (46), the passage (46) being arranged diametrically opposite a ring (45) to the other of a corrugation (42) of the at least one bellows (40a , 40b), one of the coolant heating (43) or cooling (47) being intended to flow through all of the passages (46) of all the rings (45). 10. Alternative thermal machine (1) according to one of claims 1 to 9 wherein the regulating means (9) comprise a set of valves (25a, 25b, 35a, 35b) of which at least one intake valve (35a). fluid (F) in the second chamber (30) and at least one exhaust valve (35b) of the fluid (F) in the second chamber (30), these at least one intake valves (35a) and exhaust (35b) being movable between a closed position and an opening position, and disposed on the second yoke (31) of the second enclosure (30). An alternative thermal machine (1) according to claim 10 wherein the regulating means (9) further comprises: - a set of control means (10) acting on the position of at least two of the valves (25a, 25b , 35a, 35b), - at least one position sensor (13) of the first flange (23) and / or the second flange (33) and / or at least one pressure sensor (14) of the first chamber ( 20) and / or the second enclosure (30), - acquisition means (15) arranged to receive control data from the position (13) and / or pressure (14) sensors and arranged to transmit data. controlling at least a portion of the control means (10). 12. Alternative thermal machine (1) according to one of claims 10 to 11, comprising a counter-pressure ring (70) having a cylindrical geometry, integrally connected along its axis to the tail of the at least one intake valve. (35a) of the second chamber (30) and provided with at least one peripheral recess (71, 72) disposed between its rear face (73) and its front face (74). 13. Alternative thermal machine (1) according to one of claims 1 to 12 wherein the first yoke (21) comprises a first boss (22) extending respectively inside the first chamber (20) to a height included between a height beyond the plane of the first yoke (21) and a height substantially equal to the distance between the first yoke (21) and the first flange (23) of the first enclosure (20) when the first flange (23) is in the top dead center (TDC), and / or the second yoke (31) includes a second boss (32) extending respectively inside the second enclosure (30) to a height of between height beyond the plane of the second yoke (31) and a height substantially equal to the distance between the second yoke (31) and the second flange (33) of the second chamber (30) when the second flange (33) ) is at the top dead center (TDC). 14. An alternative thermal machine according to one of claims 1 to 13, wherein the first side walls (24) of the first chamber (20) are formed by two concentric bellows and / or second side walls (34) of the second chamber. (30) are formed by two concentric bellows. 15. Alternative thermal engine (100) comprising an alternative thermal machine according to one of claims 1 to 14, the first chamber (20) constituting a so-called compression chamber and the second chamber (30) constituting a so-called expansion chamber. 16. Alternative thermal engine (100) according to claim 15 wherein the first fluid communication means (2) are connected to the second fluid communication means (3) to form a closed circuit and having means for cooling the working fluid ( F) flowing in the second fluid communication means (3). 17. Variable displacement compressor with two stages (200) comprising: - an alternative thermal machine (1) according to one of claims 1 to 14, the first chamber (20) constituting a first so-called compression chamber and the second chamber (20) constituting a second so-called compression chamber, and - a drive shaft drive device (61) integral with the flange (23) of the first chamber (20) and the flange (33) of the second Enclosure (30). 18. Motor / compressor comprising firstly an alternative thermal machine (1) according to one of claims 1 to 14, the first chamber (20) being a so-called compression chamber and the second chamber (30) being a so-called chamber and said compression chamber (20) being oversized relative to said expansion chamber (30), and further comprising a sealed storage tank in communication with the third fluid communication means (4). ). 19. Cogeneration system comprising an AC motor (100) according to one of claims 15 to 16, or a motor / compressor according to claim 18. 20. Cogeneration system according to claim 19 comprising at least one linear alternator (80), the electric power produced by the at least one linear alternator (80) being partially controlled by the control of the operating cycle of the reciprocating engine (100). ) or motor / compressor.