WO2024083478A1

WO2024083478A1 - Thermal compressor

Info

Publication number: WO2024083478A1
Application number: PCT/EP2023/077086
Authority: WO
Inventors: Pierre Bignon; Anton BOUWER
Original assignee: ISSOP, Abdoul, Azeez; NATIVEL, Eddy, Sébastien; PETERS, Pierre, Alexandre; OMARJEE, Bilal
Priority date: 2022-10-19
Filing date: 2023-09-29
Publication date: 2024-04-25
Also published as: FR3141218A1

Abstract

The invention relates to a thermal compressor (100) comprising a lower sealed enclosure (1) filled with refrigerant in phase balance and an exchanger (4) allowing the flow of a hot medium in order to increase the temperature and the pressure of the refrigerant contained in the lower sealed enclosure (1), an upper sealed enclosure (12) filled with refrigerant in phase balance, located higher than the lower sealed enclosure (1), the lower sealed enclosure (1) and the upper sealed enclosure (12) being connected at the top by a first pipe (18) that can be selectively interrupted by means of a first solenoid valve (14), the lower sealed enclosure (1) and the upper sealed enclosure (12) being connected at the bottom by a second pipe (19) that can be selectively interrupted by means of a second solenoid valve (15), and the upper sealed enclosure (12) further comprising a liquid level detector (10) which is able to control the first solenoid valve (14) and the second solenoid valve (15), which are open for a high level and closed for a low level. The invention is useful for producing a reciprocating rectilinear motion, a pumping means, a reverse osmosis desalter, and a rotary motion.

Description

Title of the invention: Thermal compressor

Technical area

The invention relates to a thermal compressor capable of producing pneumatic energy and its application to the production of reciprocating rectilinear mechanical movement, pumping or rotary mechanical movement.

Prior art

Pressure production is most often achieved by means of a mechanical compressor. Such a mechanical compressor has the main disadvantage of consuming significant energy which, in the case of electricity or fuel which may be fossil, is costly economically and/or ecologically.

In addition, such a mechanical compressor is generally noisy. Which creates noise pollution.

In addition, such a mechanical compressor is generally a machine with moving parts subject to wear and requiring lubrication, a source of pollution.

The invention proposes an alternative solution by replacing mechanical compression with compression of thermal origin, obtaining with thermal energy, coming from a hot source, via a phase change of a refrigerant, a significant expansion of the fluid refrigerant within a sealed enclosure.

The hot source is advantageously obtained from a medium preferentially heated by solar energy, for example by means of a conventional planar solar water heater. This then makes it possible to produce compression, including at night, from a hot medium stored in a balloon.

This still allows for silent compression.

This also allows compression to be carried out by thermal compression, eliminating moving parts and therefore any wear and lubrication. This also makes it possible to carry out an alternating rectilinear movement, pumping, desalination by reverse osmosis, or rotary movement, going from a significant cost in electrical energy to almost no cost of the necessary energy.

Summary of the invention

According to a first aspect, the subject of the invention is a thermal compressor comprising a low sealed enclosure filled with refrigerant in phase equilibrium and an exchanger allowing the circulation of a hot medium, in order to increase the temperature and pressure of the fluid. refrigerant contained in the lower sealed enclosure, a upper sealed enclosure filled with refrigerant in phase equilibrium, located higher than the lower sealed enclosure, the lower sealed enclosure and the upper sealed enclosure being connected in the upper parts by a first pipe, selectively interruptible by means of a first solenoid valve, the lower sealed enclosure and the upper sealed enclosure being connected in the lower parts by a second pipe, selectively interruptible by means of a second solenoid valve and the upper sealed enclosure comprising also a liquid level detector capable of controlling the first solenoid valve and the second solenoid valve open for a high level and closed for a low level.

Particular characteristics or embodiments, usable alone or in combination, are:

- the upper waterproof enclosure is located so that its lowest point is approximately halfway up the lower waterproof enclosure,

- the liquid level detector includes a hysteresis in order to move the high level away from the low level,

- the liquid level detector comprises a float arranged in the upper sealed enclosure so as to float on the surface of the liquid, secured to a magnetic element capable of being magnetized and detected by a magnetic sensor arranged outside the high waterproof enclosure,

- the hysteresis is carried out by means of a rod, secured to the magnetic element, respectively to the float, sliding with distant stops in a sheath secured to the float, respectively to the magnetic element, the distance between the stops determining the extent of hysteresis, - the thermal compressor also comprises an additional sealed enclosure located at least as high as the upper sealed enclosure and connected by a third pipe in the upper part of the upper sealed enclosure,

- the sealed enclosures are bottles comprising a single neck, arranged downwards, a connection in the lower part being made at the level of the neck, in order to draw/fill liquid, and a connection in the upper part being made by a tube passing through the neck and rising to the top of the bottle, in order to draw/fill gas,

- the exchanger comprises a plurality of capillary tubes forming loops plunging into the lower sealed enclosure and emerging through a neck,

- the refrigerant is carbon dioxide, CO ₂ ,

- the hot medium is heated by a solar water heater and is preferably water,

- the lower sealed enclosure further comprises a temperature sensor and/or a pressure sensor, and the hot medium is replaced by a cold medium in order to cool the refrigerant when the refrigerant risks exceeding a predetermined temperature or pressure.

According to a second aspect, the invention relates to a motor comprising such a thermal compressor, a first double-acting cylinder, comprising a first piston separating a first small chamber from a first large chamber, a fourth pipe connecting the lower sealed enclosure in part high with the first small chamber, a third solenoid valve selectively interrupting the fourth pipe, a fifth pipe connecting the first large chamber with the high sealed enclosure in the upper part, a sixth pipe connecting the first small chamber with the first large chamber, a fourth solenoid valve interrupting the sixth line, a right limit switch detecting the presence of the first piston at the bottom of the first large chamber and a left limit switch detecting the presence of the first piston at the bottom of the first small chamber, detection by the end of right stroke controlling the closing of the third solenoid valve and the opening of the fourth solenoid valve and detection by the left limit switch controlling the opening of the third solenoid valve and the closing of the fourth solenoid valve. Particular characteristics or embodiments, usable alone or in combination, are:

- the engine further comprises a second double-acting cylinder comprising a second rod secured to a first rod of the first cylinder, a second piston separating a second small chamber from a second large chamber, the second small chamber being connected by a seventh pipe to a pumping inlet, the second large chamber being connected by an eighth pipe to a pumping outlet, the second piston comprising at least one first non-return valve allowing the passage of a fluid from the second large chamber to the second small chamber,

- the motor further comprises a rotary hydraulic motor comprising an inlet connected to the pumping inlet and an outlet connected to the pumping outlet, an accumulator connected to the seventh pipe, a tank connected to the eighth pipe and a second non-return valve arranged on the eighth pipe so as to only allow flow from the tank to the second cylinder.

Brief description of the drawings

The invention will be better understood on reading the description which follows, given solely by way of example, and with reference to the appended figures in which:

[Fig. 1] shows, in schematic view, the principle of the thermal compressor according to the invention,

[Fig. 2] shows, in perspective view, a detail of the neck of a waterproof enclosure,

[Fig. 3] shows, in sectioned view along a vertical plane, a high waterproof enclosure,

[Fig. 4] shows, in schematic view, an application to the production of movement, according to a first embodiment,

[Fig. 5] shows, in schematic view, an application to the production of movement, according to another embodiment.

Description of embodiments With reference to Figure 1, the invention relates to a thermal compressor 100. This thermal compressor 100 comprises, according to a characteristic of the invention, a lower sealed enclosure 1 and a upper sealed enclosure 12.

The lower sealed enclosure 1 is filled with refrigerant in phase equilibrium, i.e. at a pressure and a temperature such that the two phases, liquid and gaseous, coexist in the lower sealed enclosure 1. The first sealed enclosure 1 is equipped with an exchanger 4. This exchanger 4 includes a closed circuit and allows the circulation of a hot medium. This circuit is mainly immersed in a sealed manner and separated from the refrigerant in the interior of the first sealed enclosure 1, so as to make it possible to increase the temperature, and consequently the pressure, of the refrigerant contained in the enclosure. waterproof low 1.

The exchanger 4 is illustrated internal to the lower sealed enclosure 1 in order to allow optimal exchange efficiency. However, it would be possible to arrange the exchanger 4 outside, for example in the form of a serpentine winding around the lower sealed enclosure 1.

The upper sealed enclosure 12 is filled with refrigerant in phase equilibrium, i.e. at a pressure and a temperature such that the two phases, liquid and gaseous, coexist in the upper sealed enclosure 12.

The high waterproof enclosure 12 is located higher than the low waterproof enclosure 1.

In the present application, the term connection in the upper part means a connection to a waterproof enclosure 1, 12, 11 in its upper part. Such a connection allows the connected pipe to open into the gaseous sky of the sealed enclosure 1, 12, 11, and allows this pipe to draw or fill gas. Alternatively, by connection in the lower part we mean a connection to a waterproof enclosure 1, 12, 11 in its lower part. Such a connection allows the connected pipe to open into the liquid bottom of the sealed enclosure 1, 12, 11, and allows this pipe to draw or fill liquid.

The lower sealed enclosure 1 and the upper sealed enclosure 12 are connected by a first pipe 18 in the upper parts. The first pipe 18 is connected to the upper part of the lower waterproof enclosure 1, and to the upper part of the waterproof enclosure high 12. The first pipe 18 is equipped with a first solenoid valve 14, making it possible to selectively connect or interrupt the connection between the gaseous skies of the two sealed enclosures 1, 12.

The lower sealed enclosure 1 and the upper sealed enclosure 12 are still connected by a second pipe 19 in the lower parts. The second pipe 19 is connected in the lower part of the lower sealed enclosure 1, and in the lower part of the upper sealed enclosure 12. The second pipe 19 is equipped with a second solenoid valve 15, making it possible to selectively connect or interrupt the connection between the liquid bottoms of the two waterproof enclosures 1, 12.

As detailed in Figure 3, the high waterproof enclosure 12 also includes a liquid level detector 10. This level detector 10 is used to control the first solenoid valve 14 and the second solenoid valve 15. On detection of a high level, the two solenoid valves 14, 15 are controlled in the open position. On detection of a low level, the two solenoid valves 14, 15 are controlled to the closed position.

According to another characteristic, the high waterproof enclosure 12 is located so that its lowest point is approximately halfway up the low waterproof enclosure 1. This difference in relative altitude allows, when the solenoid valve 15 is open, the liquid present in the upper sealed enclosure 12 to flow by gravity towards the lower sealed enclosure 1, until the levels 2, 3 are equalized.

In order to initialize the thermal compressor 100, the closed circuit constituted by the sealed enclosures 1, 12, 11 is filled with refrigerating fluid in such a way that the two lower 1 and upper 12 sealed enclosures contain refrigerating fluid in liquid form. Thus, at ambient temperature, as an indication 20 to 25°C, a pressure of 57 bars is used for a refrigerating fluid composed of carbon dioxide CO ₂ .

The thermal compressor 100 previously described operates in the following manner. Its operation is cyclical. Also, the description of the cycle can be done from any event. Operation is based on a cycle materialized by transfers of refrigerant from a low sealed enclosure 1, in which high pressure prevails, to a high sealed enclosure 12, in which the pressure is lower.

Let us assume that we start the description of the operating cycle with the opening of the solenoid valves 14, 15.

A liquid is substantially incompressible. Also, the fact that the solenoid valve 15 is open causes the liquid contained in the two sealed enclosures 1, 12 to flow from one to the other, by communicating vessel effect, until level 2 in the The low waterproof enclosure 1 is equal to level 3 in the high waterproof enclosure 12, as illustrated in Figure 1.

Although level 2 is equal to level 3 in absolute terms, the high waterproof enclosure 12 being located at a higher altitude than the lower waterproof enclosure 1, the relative level, i.e. the filling level, is even more important in the lower sealed enclosure 1 than in the upper sealed enclosure 12.

The fact that the first solenoid valve 14 is open causes the gas pressures to balance between the two sealed enclosures 1, 12. The gas pressure in the lower sealed enclosure 1 is thus equal to the gas pressure in the enclosure high sealed 12. This equalization of pressures still causes significant cooling in the low sealed enclosure 1, which was at high pressure, which is beneficial for the rest of the cycle.

When balancing the gas pressures by opening the first solenoid valve 14, the pressure is such that, at ambient temperature, the refrigerant is in the liquid phase in the two sealed enclosures, the lower sealed enclosure 1 and the enclosure waterproof high 12.

The flow of liquid via the solenoid valve 15 generally takes place from the upper sealed enclosure 12 towards the lower sealed enclosure 1. The drop in the liquid level makes it possible to reach a low level of liquid filling of the upper sealed enclosure 12. This low level is detected by the level detector 10 which consequently controls a closing of the two solenoid valves 14, 15.

When the solenoid valves 14, 15 are closed, the lower sealed enclosure 1 is filled with refrigerant mainly in liquid form and having a high density, advantageously between 0.8 and 0.9 g per cm ³ . The high density refrigerant is all the more sensitive to even a slight rise in temperature, which produces a very high pressure, due to the insulation of the low sealed enclosure 1.

The refrigerant contained in the lower sealed enclosure 1, now isolated from the upper sealed enclosure 12 by the closing of the first solenoid valve 14 and the second solenoid valve 15, is heated by contact with the hot medium circulating in the exchanger 4.

Under the effect of this heating, the pressure in the lower sealed enclosure 1 increases significantly. An increase in temperature of a few degrees Celsius causes, at the density where the refrigerant is located, a significant increase in pressure at the level of the gaseous head of the lower sealed enclosure 1.

This pressure will be taken advantage of by the invention. The refrigerant in gaseous form under high pressure is advantageously used by an application. This application recovers the refrigerant under high pressure by drawing it from the lower sealed enclosure 1. After use, the refrigerant previously drawn is returned to the high sealed enclosure 12.

Thus, the refrigerant in gaseous form joins the upper sealed enclosure 12 via the outlet 9. When it reaches the upper sealed enclosure 12, said refrigerant joins the gaseous sky of the upper sealed enclosure 12 which is located at a density and at lower pressure. Lowering the temperature in the high sealed enclosure 12 allows the liquefaction of the refrigerant. Also, the liquid level in the high sealed enclosure 12 increases accordingly. This increase in the liquid level does not have a significant effect on the gas pressure, because the density of the refrigerant is very low in the high sealed enclosure 12. The liquid level increases until it reaches a high liquid level. . This high liquid level is detected by the level detector 10 which then controls the opening of the first and second solenoid valves 14, 15.

The cycle is complete here. It then reproduces itself, essentially identically. In order to separate the opening event of the solenoid valves 14, 15 and the closing event of the solenoid valves 14, 15, according to another characteristic, the liquid level detector 10 includes a hysteresis in order to move the high level away from the low level.

According to another characteristic, the level detector 10 is based on a float placed in the high sealed enclosure 12 in order to float on the surface of the liquid. For this, you! as illustrated in Figure 3, the level detector 10, 301 comprises a float 310 capable of floating on the surface of the refrigerant liquid. This float 310 is integral with a magnetic element 313 and drives it in its vertical movement when it rises or falls with the liquid level. This magnetic element 313 is able to be magnetized and detected by a magnetic sensor 314. This magnetic sensor 314 is advantageously arranged outside the high waterproof enclosure 12.

Advantageously, the float 310 is made of flexible material in order to allow its deformation to allow it to pass through the neck 303 of the high sealed enclosure 12, this deformation being reversible in order to allow it to then return to its initial shape.

According to another characteristic, the hysteresis is carried out by means of a rod 312, secured to one of the elements among the magnetic element 313 or the float 310, sliding with distant stops in a sheath 311 secured to the other of the elements among the float 310 and the magnetic element 313.

Thus, when the float 310 rises with the liquid level, it takes with it the body 307, the sheath 311 and the rod 312 in the folded position in the sheath 311. The rod 312 is at the bottom stop, its proximal end resting against the body 307.

When the magnetic element 313, carried by the distal end of the rod 312, comes into contact with the roof of the high waterproof enclosure 12, it is magnetized and is detected by the magnetic sensor 314. This corresponds to the high level of liquid.

This configuration controls the opening of the solenoid valves 14, 15, which stops the rise in the liquid level and causes said level to fall, by gravity flow.

When the liquid level drops, float 310 goes back down. It carries with it the body 307 and the sheath 311 secured to the body 307. The rod 312 always magnetized remains in the high position in contact with the roof of the high waterproof enclosure 12. It remains magnetized to the roof and unfolds out of the sheath 311 until the rod 312 comes to a high stop, its proximal end in contact against the part distal of the sheath 311 which attracts it downwards and stops the magnetization, when the float 310 arrives at the low liquid level.

The distance between the two stops, i.e. approximately the length of the rod 312, determines the extent of the hysteresis and the distance between the low level and the high level.

According to another characteristic, more particularly illustrated in Figure 1, the thermal compressor 100 also comprises an additional sealed enclosure 11. This additional waterproof enclosure 11 is located at least as high as the high waterproof enclosure 12 and is connected by a third pipe 13 in the upper part of the high waterproof enclosure 12. This connection is advantageously permanent. The connection of the third pipe 13 is arranged to the right of the solenoid valve 14.

This additional sealed enclosure 11 is intended to accommodate gas only. It serves as an extension to the high watertight enclosure 12. It makes it possible to increase the volume capable of accommodating gas. This makes it possible to reduce the density of the refrigerant and thus promotes the liquefaction of the refrigerant when it returns to gaseous form.

According to another characteristic, the additional waterproof enclosure 11 is located so that its lowest point is approximately halfway up the high waterproof enclosure 12.

The sealed enclosures 1, 12, 11 can be made by any means from any material capable of holding pressure. They can thus be made of composite material, metallic material or even concrete.

According to another characteristic, at least one of the sealed enclosures 1, 12, 11, and advantageously all, are bottles capable of withstanding the pressure. Each bottle advantageously includes a single neck 303. This neck 303 is arranged downwards. A connection in the lower part is then made at the neck 303. Such a connection then makes it possible to draw/fill liquid. A connection at the top could be made by a second neck placed at the top of the sealed enclosure, as illustrated in Figure 5.

However, in order to limit the necks and advantageously reuse existing bottles or tanks, on the contrary, a connection in the upper part is made passing through the single neck 303, by means of a tube passing through the neck 303 and going up towards the top of the bottle. Such a connection allows you to draw/fill gas.

Advantageously, these bottles reuse diving bottles, capable of withstanding a pressure of 300 bars, typically made of aluminum.

As detailed in Figure 2, detailed view of the neck of the lower sealed enclosure 1, the exchanger 4 comprises a plurality of capillary tubes 204. These capillary tubes 204 pass through the neck 303. They are looped by connection two by two in order to allow circulation in the volume of the lower sealed enclosure 1 from a pump placed outside the lower sealed enclosure 1.

The capillary tubes 5, 204, 205 are advantageously made of a material with high thermal conductivity, such as copper, Cu or aluminum, Al.

According to another characteristic, the refrigerant is carbon dioxide, CO ₂ . This refrigerant is advantageous in that it presents physical characteristics and in particular change of state particularly suited to the operation of the present thermal compressor 100. In addition, CO ₂ advantageously presents characteristics among the least harmful in terms of effect gas greenhouse, GHG.

According to another characteristic, the hot medium which provides its caloric energy to the refrigerant in exchanger 4, is heated by a solar water heater. This heating of the refrigerant being the only external energy supply to the thermal compressor 100 useful for operating it, such substantially free caloric energy advantageously makes it possible to produce compression substantially free of charge. Solar heating is a possibility. Alternatively, while retaining the advantage of being free, the heat can be provided by a naturally hot source, heat recovery from an industrial process, for example from a nuclear power plant or even geothermal energy.

Furthermore, neither the heating of the hot medium nor the operation of the compression means of the invention produces noise. Also the thermal compressor 100 is advantageously silent.

The hot medium can be any heat transfer fluid. For example, it may be glycol water or glycol. The hot medium is preferably water.

According to another characteristic, the low waterproof enclosure 1 also includes a temperature sensor and/or a pressure sensor 7.

According to another characteristic, the temperature sensor is a thermocouple advantageously placed in a blind capillary 5, 205, solitary and arranged across the neck 303 like the capillaries 204 of the second exchanger 4. As illustrated in Figure 1 , this capillary 5 is advantageously arcuate, as visible in Figure 1, so as to distance the thermocouple from the other capillaries 204 where the hot medium circulates and not to disturb the measurement by the heat provided by the hot medium via the exchanger 4 .

As illustrated in Figure 5, the pressure sensor 7 can be placed on a pipe 25 connected to the lower waterproof enclosure 1 in the upper part.

The temperature or pressure sensor 7 is advantageously used to secure the thermal compressor 100 by preventing the refrigerant from reaching a predetermined temperature or pressure.

It is possible for the refrigerant to pass into the transcritical phase. This advantageously makes it possible to obtain very high pressures and thus provide increased driving power. When exhausting the engine towards the high sealed enclosure 12, the pressure may be lower than the critical pressure, 73 bars for CO ₂ , and the temperature may be lower than the critical temperature, 31 ° C for CO ₂ . The refrigerant liquefies in the high sealed enclosure 12. Also, as soon as critical conditions are approached, and preferably before, the exchanger 4 is used to cool the refrigerant. For this the hot medium is replaced by a cold medium.

This cold medium can typically come from the network water supply which generally has a temperature below 20°C and can allow cooling in order to safeguard the thermal compressor 100.

The pressure sensor 7 can be used to secure the thermal compressor 100 so that the critical pressure is not exceeded, as described previously.

The pressure sensor 7 can also be used to trigger a cycle reset and a balancing of the liquid levels 2, 3 and the pressures between the lower sealed enclosure 1 and the upper sealed enclosure 12. In this case this pressure sensor 7 observes the pressure and when the pressure becomes lower than a predetermined threshold value, the opening of the solenoid valves 14, 15 is controlled. In this case, the pressure sensor 7 replaces the level detector 10 for the detection of a high level. The closing of the solenoid valves 14, 15 remains controlled by the detection of a low liquid level by means of the level detector 10. The predetermined pressure threshold value is determined from a pressure relationship produced as a function of the heating time, for a value beyond which the quantity of heat to be supplied by the exchanger 4 becomes too great, leading to a lower efficiency of the thermal compressor 100.

The thermal compressor 100 previously described can advantageously be used in numerous applications. In any application, the pressure produced at the level of the lower sealed chamber 1 is taken from the lower sealed enclosure 1 by a user means, either in the upper part in the form of gaseous refrigerant, or in the lower part in the form of liquid refrigerant. . The refrigerant, after use by the engine 300, is returned to the upper sealed enclosure 12. This addition into the upper sealed enclosure 12 causes a gradual rise in the liquid level 3, until a reset, by opening the solenoid valves. 14, 15. This reset is controlled by the level detector 10 detecting a high level or by the pressure sensor 7. With reference to Figure 4 or 5, according to a first application, the thermal compressor 100 can be used to produce a motor 200 producing reciprocating rectilinear movement.

For this, the engine 200 includes a thermal compressor 100 as described previously. The motor 200 also includes a first cylinder 20. This cylinder 20 is double-acting. It comprises a first piston 23. This first piston 23 separates two first chambers 21, 22. A first chamber 21, arranged on the side of a first rod 24, sees a section of the first piston 23 smaller, since reduced by the section of the first rod 24. It is therefore called small. It is still qualified as first since it relates to the first cylinder 20. Another first chamber 22, arranged on the side opposite the first rod 24, sees a larger section of the first piston 23, since corresponding to the total section of the first piston 23. It is therefore called large. It is still qualified as first since it relates to the first cylinder 20.

The first large chamber 22 is permanently connected with the high waterproof enclosure 12 in the upper part via a fifth pipe 26. The first small chamber 21 is connected with the low waterproof enclosure 1 in the upper part via a fourth pipe 25. This fourth pipe 25 is selectively interrupted by a third solenoid valve 16. This third solenoid valve 16 is thus capable of selectively connecting and/or isolating the lower sealed enclosure 1 in the upper part with the first small chamber 21. A fourth solenoid valve 17 selectively interrupts a sixth pipe 29. This sixth pipe 29 connects the first small chamber 21 with the first large chamber 22 and therefore with the high waterproof enclosure 12 in the upper part.

Two limit switches 27, 28 make it possible to control the third solenoid valve 16 and the fourth solenoid valve 17. From these limit switches, we can distinguish a right limit switch 27 detecting the presence of the first piston 23 at the bottom of the first large chamber 22 , either when the first piston 23 is all the way to the right in Figure 4 or 5, and a left limit switch 28 detecting the presence of the first piston 23 at the bottom of the first small chamber 21, or when the first piston 23 is all the way left in Figure 4 or 5. The third solenoid valve 16 and fourth solenoid valve 17 are controlled in phase opposition: when one is open the other is closed and vice versa. Exceptionally, the third solenoid valve 16 and fourth solenoid valve 17 are simultaneously closed, when the thermal compressor 100 performs balancing or resetting, i.e. when the first solenoid valve 14 and the second solenoid valve 15 are open.

The third solenoid valve 16 and fourth solenoid valve 17 are controlled by the limit switches 27, 28 in the following manner: detection by the right limit switch 27 controls the closing of the third solenoid valve 16 and the opening of the fourth solenoid valve 17. Conversely, detection by the left limit switch 28 controls the opening of the third solenoid valve 16 and the closing of the fourth solenoid valve 17.

The operation of the first cylinder 20 is as follows. Operation follows a cycle, so it is possible to start the description at any time. It is assumed, to start the cycle, that the third solenoid valve 16 is open and that the fourth solenoid valve 17 is closed.

The thermal compressor 100 constantly produces pressure at the level of the lower sealed enclosure 1. This pressure is recovered by drawing refrigerant in gaseous form, from the lower sealed enclosure 1 in the upper part, via the fourth pipe 25. It is transmitted, via the third open solenoid valve 16 and the sixth pipe 29, to the first small chamber 21 of the first cylinder 20. The first large chamber 22 is connected, via the fifth pipe 26 to the upper sealed enclosure 12 which has a low pressure. Also, the significantly higher pressure transmitted to the first small chamber 21 has the effect of pushing the first piston 23 towards the right in Figure 4 or 5.

This continues until this movement to the right of the first piston 23 and the first associated rod 24 is detected by the right limit switch 27. Detection by the right limit switch 27 results in closing of the third solenoid valve 16 and an opening of the fourth solenoid valve 17. Closing the third solenoid valve 16 isolates the high pressure source. The opening of the fourth solenoid valve 17 places the first two chambers 21, 22 of the first cylinder 20 in communication with each other and with the upper sealed enclosure 12. This implementation communication equalizes the pressures in the first two chambers 21, 22. This same pressure on either side of the first piston 23 produces a greater force on the side of the first large chamber 22 than that applied on the side of the first small chamber 21, due to the upper bearing surface of the first piston 23, on the right side relative to the left side.

This has the effect of pushing the first piston 23 towards the left of Figure 4 or 5. This continues until this movement towards the left of the first piston 23 and the first associated rod 24 is detected by the end of left stroke 28. Detection by the left limit switch 28 causes the third solenoid valve 16 to open and the fourth solenoid valve 17 to close.

This returns the motor 200 to the start state of cycle description. The cycle repeats itself again, and as long as the thermal compressor 100 produces pressure.

Such an arrangement produces, as shown, an alternating rectilinear movement. This movement is transmitted by the first rod 24 of the first cylinder 20.

With reference to Figure 4 or 5, according to another application, the thermal compressor 100 can be used to produce a motor 200 capable of pumping a liquid.

For this, it is added to the previous arrangement, comprising a thermal compressor 100 and a first cylinder 20, a second double-acting cylinder 30. This second cylinder 30 comprises a second coaxial rod 34, integral in translation along the common axis of the rods 24, 34, of the first rod 24 of the first cylinder 20.

This second cylinder 30 is double-acting. It comprises a second piston 33. This second piston 33 separates a second small chamber 31 from a second large chamber 32. The second small chamber 31, arranged on the side of the second rod 34, sees a smaller section of the second piston 33, since reduced by the section of the second rod 34. It is therefore called small. It is still qualified as second since it relates to the second cylinder 30. The other second chamber 32, arranged on the side opposite the second rod 34, sees a larger section of the second piston 33, since corresponding to the section total of the second piston 33. It is therefore called large. It is still qualified as second since it relates to the second cylinder 30.

The second small chamber 31 is connected by a seventh pipe 35 to a pumping inlet 38. The second large chamber 32 is connected by an eighth pipe 36 to a pumping outlet 39. The second piston 33 comprises at least one first non-return valve 37 This first non-return valve 37 is such that it allows the passage of a fluid from the second large chamber 32 to the second small chamber 31, through the second piston 33. A non-return valve 37 in the other direction is also possible. , the pumping taking place in the opposite direction, i.e. by reversing the pumping inlet 38 and the pumping outlet 39.

Such an arrangement allows pumping of liquid, sucking at the pumping inlet 38 and pushing back at the pumping outlet 39. It can also be applied to desalination by reverse osmosis.

With reference to Figure 4 or 5, according to another application, the thermal compressor 100 can be used to produce a motor 200 producing a rotary movement.

For this, it is added to the previous arrangement, comprising a thermal compressor 100, a first cylinder 20 and a second cylinder 30, a rotary hydraulic motor 40. A hydraulic motor 40 comprises an input 41 which is then connected to the pumping inlet 38 and an output 42 which is then connected to the pumping output 39. Such an arrangement makes it possible to produce a rotary movement at the level of the shaft output of the hydraulic motor 40.

Due to the alternative origin of the movement initiated by the first cylinder 20, the rotary movement may present jerks. Also, an accumulator 43 is advantageously added. This accumulator 43, conventionally of the oleo-pneumatic type, comprising a gas pocket separated from the fluid pumped by a sealed elastic membrane, is advantageously connected on the side of the pumping inlet 38, connected to the seventh line 35, via a branch connection. This accumulator 43 makes it possible to smooth out the reciprocating movements and thus obtain a more continuous rotation. In order to balance the fluid levels, a reservoir 44 is still advantageously connected on the side of the pumping outlet 39, connected to the eighth pipe 36, by a branch connection. This tank 44 is advantageously arranged above the eighth pipe 36 in order to ensure its filling by gravity.

A second non-return valve 45 is also advantageously arranged, on the side of the tank 44, on the eighth pipe 35 so as to only allow the flow of the tank 44 towards the second cylinder 30.

When a hydraulic motor 40 is added, the circuit comprising the second cylinder 30, the motor 40, the seventh and eighth lines 35, 36, the accumulator 43 and the tank 44 is a closed circuit. It is advantageously filled with hydraulic oil.

Figure 5 substantially reproduces the embodiment and the characteristics of Figure 4. The characteristics which differ from Figure 4 to Figure 5 mainly concern variants of the thermal compressor part.

The first pipe 18 which connects the gaseous skies of the upper sealed enclosure 12 and the additional sealed enclosure 11, as well as the gaseous skies of the lower sealed enclosure 1 and the upper sealed enclosure 12 via the solenoid valve 14 is for Figure 5 connected by additional necks in the upper part of the waterproof enclosures 1, 11, 12.

The additional waterproof enclosure 11 must be arranged at least at the same level as the high waterproof enclosure 12 as shown in Figure 4. It can be arranged significantly higher, as illustrated in Figure 5.

The pressure sensor 7 is only shown in Figure 5. It can be used in the embodiment of Figure 4.

The invention has been illustrated and described in detail in the drawings and the preceding description. This should be considered as illustrative and given by way of example and not as limiting the invention to this description alone. Numerous embodiment variants are possible.

List of reference signs 1: low waterproof enclosure,

2, 3: liquid level,

4: exchanger,

5: temperature sensor tube,

7: pressure sensor,

9: outlet,

10: level detector,

11: additional waterproof enclosure,

12: high waterproof enclosure,

13: third conduct,

14: first solenoid valve,

15: second solenoid valve,

16: third solenoid valve,

17: fourth solenoid valve,

18: first conduct,

19: second line,

20: first cylinder,

21: first small bedroom,

22: first large bedroom,

23: first piston,

24: first stem,

25: fourth conduct,

26: fifth conduct,

27: right limit switch,

28: left limit switch,

29: sixth conduct,

30: second cylinder,

31: second small bedroom,

32: second large bedroom,

33: second piston,

34: second stem,

35: seventh conduct,

36: eighth conduct, 37: first non-return valve,

38: pumping inlet,

39: pumping outlet,

40: rotary hydraulic motor,

41: entry,

42: exit,

43: accumulator,

44: tank,

45: second check valve, 100: thermal compressor, 200: motor,

204, 205: capillary tubes,

301: level detector,

302: high waterproof enclosure,

303: bottleneck,

304: sliding tube,

305, 306: tube,

307: body,

308: vent,

309: support,

310: float, 311: sheath,

312: stem,

313: magnetic element,

314: magnetic sensor. |

Claims

[Claim 1] Thermal compressor (100) characterized in that it comprises a low sealed enclosure (1) filled with refrigerant in phase equilibrium and an exchanger (4) allowing the circulation of a hot medium, in order to increase the temperature and pressure of the refrigerant contained in the lower sealed enclosure (1), a upper sealed enclosure (12) filled with refrigerant in phase equilibrium, located higher than the lower sealed enclosure (1), the lower sealed enclosure (1) and the upper sealed enclosure (12) being connected in the upper parts by a first pipe (18), selectively interruptible by means of a first solenoid valve (14), the lower sealed enclosure (1) and the upper waterproof enclosure (12) being connected in the lower parts by a second pipe (19), selectively interruptible by means of a second solenoid valve (15) and the upper waterproof enclosure (12) further comprising a level detector (10 ) of liquid capable of controlling the first solenoid valve (14) and the second solenoid valve (15) open for a high level and closed for a low level.

[Claim 2] Thermal compressor (100) according to claim 1, where the upper sealed enclosure (12) is located so that its lowest point is substantially halfway up the lower sealed enclosure (1). ).

[Claim 3] A thermal compressor (100) according to any one of the preceding claims, wherein the liquid level detector (10) includes hysteresis to move the high level away from the low level.

[Claim 4] Thermal compressor (100) according to any one of the preceding claims, where the liquid level detector (10) comprises a float (310) disposed in the upper sealed enclosure (12) so as to float on the surface of the liquid, secured to a magnetic element (313) capable of being magnetized and detected by a magnetic sensor (314) placed outside the upper sealed enclosure (12).

[Claim 5] Thermal compressor (100) according to any one of the two preceding claims, where the hysteresis is produced by means of a rod (312), integral with the magnetic element (313), respectively with the float (310). ), sliding with distant stops in a sheath (311) secured to the float (310), respectively of the magnetic element (313), the distance between the stops determining the extent of the hysteresis.

[Claim 6] Thermal compressor (100) according to any one of the preceding claims, further comprising an additional sealed enclosure (11), located at least as high as the upper sealed enclosure (12) and connected by a third pipe (13). ) in the upper part of the upper waterproof enclosure (12).

[Claim 7] Thermal compressor (100) according to any one of the preceding claims, where the sealed enclosures (1, 12, 11) are bottles comprising a single neck (303), arranged downwards, a connection in the lower part being made at the neck (303), in order to draw/fill liquid, and a connection at the top being made by a tube passing through the neck (303) and going up to the top of the bottle, in order to draw/fill liquid. gas.

[Claim 8] Thermal compressor (100) according to any one of the preceding claims, where the exchanger (4) comprises a plurality of capillary tubes forming loops plunging into the lower sealed enclosure (1) and opening out through a bottleneck (303).

[Claim 9] Thermal compressor (100) according to any one of the preceding claims, wherein the refrigerant is carbon dioxide, CO ₂ .

[Claim 10] Thermal compressor (100) according to any one of the preceding claims, where the hot medium is heated by a solar water heater and is preferably water.

[Claim 11] Thermal compressor (100) according to any one of the preceding claims, where the lower sealed enclosure (1) further comprises a temperature sensor and/or a pressure sensor and where the hot medium is replaced by a cold medium in order to cool the refrigerant when the refrigerant is likely to exceed its critical temperature or pressure.

[Claim 12] Engine (200) characterized in that it comprises a thermal compressor (100) according to any one of the preceding claims, a first double-acting cylinder (20), comprising a first piston (23) separating a first small chamber (21) of a first large chamber (22), a fourth pipe (25) connecting the lower waterproof enclosure (1) in the upper part with the first small chamber (21), a third solenoid valve (16) selectively interrupting the fourth pipe (25), a fifth pipe (26) connecting the first large chamber (22) with the upper sealed enclosure (12) in the upper part , a sixth pipe (29) connecting the first small chamber (21) with the first large chamber (22), a fourth solenoid valve (17) selectively interrupting the sixth pipe (29), a right limit switch (27) detecting the presence of the first piston (23) at the bottom of the first large chamber (22) and a left limit switch (28) detecting the presence of the first piston (23) at the bottom of the first small chamber (21), detection by the end right stroke (27) controlling the closing of the third solenoid valve (16) and the opening of the fourth solenoid valve (17) and detection by the left limit switch (28) controlling the opening of the third solenoid valve (16) and closing the fourth solenoid valve (17).

[Claim 13] Motor (200) according to the preceding claim, further comprising a second double-acting cylinder (30) comprising a second rod (34) secured to a first rod (24) of the first cylinder (20), a second piston ( 33) separating a second small chamber (31) from a second large chamber (32), the second small chamber (31) being connected by a seventh pipe (35) to a pumping inlet (38), the second large chamber ( 32) being connected by an eighth pipe (36) to a pumping outlet (39), the second piston (33) comprising at least a first non-return valve (37) allowing the passage of a fluid from the second large chamber (32) ) towards the second small bedroom (31).

[Claim 14] Motor (200) according to the preceding claim, further comprising a rotary hydraulic motor (40) comprising an inlet (41) connected to the pumping inlet (38) and an outlet (42) connected to the pumping outlet (39), an accumulator (43) connected to the seventh pipe (35), a tank (44) connected to the eighth pipe (36) and a second check valve (45) arranged on the eighth pipe (36) so as to only allow flow from the reservoir (44) to the second cylinder (30).