Cartridges for heat engines with thermodynamic cycles and related heat engines

Abstract

The present invention relates to a cartridge (1) for transferring a thermodynamic fluid for a heat engine, the cartridge (1) comprising a first profile section (2) with first circulation means (3) for circulating a heat transfer fluid, a second profile section (8) with second circulation means (9) for circulating a heat transfer fluid and a third profile section (15) that is connectable and intended to be connected to at least one supply circuit of at least one working fluid (J, H), the third profile section (15) being arranged inside the first profile section (2) and the second profile section (8). 5), a chamber (24) for accommodating a thermodynamic fluid, a displacer (25) arranged in the chamber (24) and mounted so as to be slidable relative to the outer wall (17) of the third profile section (15), and a piston (26) arranged inside the third profile section (15) and mounted so as to be slidable relative to the inner wall (16) of the third profile section (15), the piston (26) being movable and intended to be moved by at least one working fluid (J, H), the displacer (25) and the piston (26) being connected to each other.

Description

Technical Field

[0001] The present invention relates to the field of thermodynamic cycle heat engine cartridges and related thermodynamic cycle heat engine modules.

[0002] The current energy transition poses challenges in many fields, including reducing primary energy consumption. The industrial sector generates large amounts of thermal energy, most of which is still being wasted in the form of waste heat. This waste heat represents a vast energy source that is directly available and already paid for, and its recovery is a strategic issue for the industry. Waste heat can be recovered by direct supply to a heat network, by temporary storage, or by conversion to electricity for internal or external use. For low-temperature waste heat, i.e., waste heat below 100 degrees Celsius, there are currently no commercially viable machines for conversion to electricity due to the lack of economic viability, and use in a heat network is the only possible option. However, there are some constraints in implementation, especially the need to be close to the end use.

[0003] Therefore, current developments in machines with external heat input are limited to temperatures where the heat reservoir is ultimately not very important.

[0004] Other natural heat sources, such as low-temperature geothermal energy or solar thermal energy, are readily available. Today, these renewable resources are only used in heat networks.

[0005] Machines with an external heat supply and a closed-cycle working fluid without phase change are generally called Stirling engines. In particular, beta-type or gamma-type Stirling engines have working pistons and displacers for alternately transferring the working fluid from a high-temperature side to a low-temperature side. In this type of motor, the working pistons and displacers are mechanically coupled. These motors are characterized by very low power density and difficult power control, as the rotational speed depends mainly on the temperature difference between the supply sources. Therefore, the few machines on the market require a large temperature difference between the heat sources, often several hundred degrees Celsius, to compensate for the low thermal conductivity of the working gas used, the small heat exchange surface, and the dead volume of the regenerator.

[0006] To improve power density, we know from International Publication No. 2018 / 062627(A1) that certain Stirling engines have been developed that operate with pressurized gases or even supercritical fluids such as carbon dioxide. However, the extremely high pressures required, combined with high motor rotational speeds typically around 3,000 rpm, result in problematic losses due to friction and pumping of the working fluid. In the case of the working piston, the ability of the dynamic seal to withstand high pressure and high temperature also remains a challenge to ensure a certain lifespan for the engine and to avoid leaks.

[0007] Another concept in this category of machines utilizing the properties of near-critical carbon dioxide is proposed in International Publication No. 02 / 01052(A2), in which the working fluid is not moved, but the heat source is alternately brought into contact with the fluid via a movable heat shield. This system is structurally complex to implement due to the alternating high-temperature and low-temperature sources incorporated into each cylinder. This configuration generates significant heat loss, particularly through a heat screen that is continuously in contact with a heat source that does not directly contribute to heating or cooling the fluid, as in conventional regenerators.

[0008] International Publication No. 2016 / 165687(A1) also describes a heat conversion process with a supercritical cycle using carbon dioxide, in which expansion is isothermal thanks to an oscillator system. An oscillating piston, which must be controlled according to the stroke of the working piston, acts as an active agitator of the supercritical fluid during expansion to increase convective heat transfer. The structural complexity resulting from the integration of the oscillator, regenerator, piston, and displacer in the cylinder makes this concept unattractive for large-scale installations and production. In addition, the improvement of heat transfer by increasing convection within the cylinder is limited by the small contact area of ​​the cylinder with the heat source. Therefore, this concept is designed to operate with temperature differences exceeding 150 degrees Celsius.

[0009] The development of so-called free-piston Stirling engines (FPSEs) has led to attempts to limit heat loss between high-temperature and low-temperature sources in order to increase motor efficiency. International Publication No. 2005 / 042958 proposes integrating a regenerator into a low-thermal-conductivity ceramic section connecting the high-temperature and low-temperature sections. However, this configuration does not allow for the control of the displacer, and a generator must be incorporated into each piston, which poses a problem for high-power equipment requiring several cylinders.

[0010] International Publication No. 02088536 proposes a multi-cylinder external heat transfer engine architecture. The “liquid” displacer technology used and the series connection of pistons for transferring thermodynamic fluid from one piston chamber to another do not allow for control of the position of the thermodynamic fluid independent of the working fluid, and therefore do not allow for the optimization of the thermodynamic cycle to be achieved.

[0011] In conventional Stirling engines, the mechanical coupling between the displacer and the working piston, due to continuous rotation, does not allow for precise thermodynamic transformation, thus significantly reducing the actual efficiency of this type of engine. The pressure chamber cannot be properly sealed at high pressure (>10 bar) due to high rotational speeds, resulting in high friction losses. Heat transfer is very low at low temperatures, leading to very low power density.

[0012] As described in current technology, mechanically disengaging the displacer from the working piston to allow for better control of thermodynamic conversion in order to improve efficiency requires the addition of an additional external actuator system, as the displacer is no longer driven by engine rotation in current solutions. In the case of multi-cylinder engines, each displacer in each cylinder requires an actuator, so these systems become very complex and costly to implement.

[0013] The object of the present invention is to provide an expandable, modular solution for operating a heat source at temperatures below 150 degrees Celsius.

[0014] For this purpose, the present invention provides a cartridge for transferring a thermodynamic fluid between a low-temperature portion connected to a first heat source and a high-temperature portion connected to a second heat source for a thermodynamic cycle heat engine, comprising at least, A first heat exchanger forming a so-called low-temperature section, comprising a first hollow profile including a first means for circulating at least one heat transfer fluid adapted and intended to be connected to a first heat transfer fluid supply circuit connected to a first heat source, wherein the first profile comprises an inner wall and an outer wall, A second heat exchanger forming a so-called high-temperature portion, comprising a second hollow section suitable for connection to a second heat transfer fluid supply circuit connected to a second heat source and equipped with a second means for circulating at least one heat transfer fluid intended for connection, wherein the second section comprises an inner wall and an outer wall, A third hollow section suitable for and intended for connection to at least one supply circuit for at least one working fluid, wherein the third section is located inside the first and second sections, and the third section comprises an inner wall and an outer wall, At least a portion of the inner wall of the first section and the first portion of the outer wall of the third section are spaced apart from each other and facing each other, forming a first filling space. A third hollow section, where at least a portion of the inner wall of the second profile and a second portion of the outer wall of the third profile are spaced apart from each other and facing each other, forming a second filling space, At least one chamber adapted and designed to accommodate at least one thermodynamic fluid, preferably under high pressure and supercritical conditions, wherein the chamber comprises at least a first and second filling space that are in communication with each other. Displacers positioned inside a chamber, slidably mounted to the outer wall of a third profile, and movable between a first position and a second position, comprising at least one displacer configured to alternately displace at least one thermodynamic fluid between a first filling space and a second filling space, A piston is positioned inside a third profile, slidably mounted against the inner wall of the third profile, and movable between a first position and a second position, wherein the piston is adapted and intended to move between the first and second positions by at least one working fluid.

[0015] The displacer and piston are coupled to each other.

[0016] The present invention also relates to a module for a thermodynamic cycle heat engine for alternating the movement of a thermodynamic fluid between a low-temperature portion connected to a first heat source and a high-temperature portion connected to a second heat source, comprising at least one or more cartridges according to the present invention. A first heat transfer fluid supply circuit connected to the first circulation means of at least one cartridge via at least one first supply port and at least one second supply port of the first circulation means, A second heat transfer fluid supply circuit connected to the second circulation means of at least one cartridge via at least one third supply port and at least one fourth supply port of the second circulation means, A bonding plate having at least a cartridge bonding means, A working fluid supply circuit is connected to the third profile of at least one cartridge by at least one fifth supply port included in the third profile and at least one sixth supply port included in the third profile, and is arranged to guide the displacement of the piston, The device is characterized by comprising a thermodynamic fluid supply outlet connected to the chamber of at least one cartridge, or a hydraulic fluid supply outlet connected to a first or second filling space of the chamber. [Brief explanation of the drawing]

[0017] The present invention will be better understood from the following description, which refers to several preferred embodiments given as non-limiting examples and described with reference to the attached schematic diagrams. [Figure 1] A cross-sectional view of the cartridge according to the present invention is shown. [Figure 2] Figure 1 shows a cross-sectional view of the cartridge. [Figure 3] A cross-sectional view of a cartridge according to the first embodiment of the present invention is shown. [Figure 4] A cross-sectional view of a cartridge according to a second embodiment of the present invention is shown. [Figure 5] A perspective view of a part of the cartridge according to the first embodiment of the present invention is shown. [Figure 6] A perspective view of a part of the cartridge according to the first embodiment of the present invention is shown. [Figure 7]A cross-sectional view of a cartridge according to the present invention showing a circulation means in the form of a circular cross-section channel is represented. [Figure 8] A cross-sectional view of a cartridge according to the present invention showing a circulation means in the form of a trapezoidal cross-section channel is shown. [Figure 9] A cross-sectional view of a cartridge according to the present invention having a circulation means in the form of an open groove is shown. [Figure 10] A cross-sectional view of a so-called hybrid cartridge in the third embodiment of the present invention is shown. [Figure 11] A cross-sectional view of the cartridge according to FIG. 1 connected to a hydraulic piston according to the fourth modification of the present invention is shown. [Figure 12] A cross-sectional view of a module including the cartridge shown in FIG. 1 is shown. [Figure 13] A cross-sectional view of a module including the so-called hybrid cartridge shown in FIG. 10 is shown. [Figure 14] A cross-sectional view of a module including the cartridge according to FIG. 1 and the so-called hybrid cartridge according to FIG. 10 is shown. [Figure 15] A joining plate is shown. [Figure 16] A cross-sectional view of a module including four cartridges according to FIG. 4 and two so-called hybrid cartridges according to the present invention is shown. [Figure 17] A perspective view of the module shown in FIG. 16 is shown. [Figure 18] A cross-sectional view of a module including six cartridges as shown in FIG. 3 is shown. [Figure 19] A perspective view of the module shown in FIG. 18 is shown.

[0018] According to the present invention, particularly as illustrated in FIGS. 1 to 9, cartridges 1, 1' for moving a thermodynamic fluid between a low-temperature portion connected to a first heat source and a high-temperature portion connected to a second heat source for a thermodynamic cycle heat engine are at least A first exchanger forming a so-called low-temperature section, comprising a first hollow section 2 including a first circulation means 3 for at least one heat transfer fluid adapted and intended to be connected to first heat transfer fluid supply circuits A and B connected to a first heat source, wherein the first section 2 comprises an inner wall 4 and an outer wall 5, A second heat exchanger forming a so-called high-temperature portion, comprising a second hollow section 8 suitable for connection to second heat transfer fluid supply circuits C and D connected to a second heat source, and comprising a second means 9 for circulating at least one heat transfer fluid intended for connection, wherein the second section 8 comprises an inner wall 10 and an outer wall 11, A third hollow section 15 suitable for and intended for connection to at least one supply circuit for at least one working fluid J, H, wherein the third section 15 is located inside the first section 2 and the second section 8, and the third section 15 comprises an inner wall 16 and an outer wall 17. At least a portion of the inner wall 4 of the first section 2 and the first portion 20 of the outer wall 17 of the third section 15 are spaced apart from each other and facing each other to form a first filling space 21. At least a portion of the inner wall 10 of the second section 8 and the second portion 22 of the outer wall 17 of the third section 15 are spaced apart from each other and facing each other, forming a second filling space 23, a third hollow section, At least one chamber 24 adapted and designed to accommodate at least one thermodynamic fluid, preferably under high pressure and supercritical conditions, wherein the chamber 24 comprises at least a first packed space 21 and a second packed space 23 that are in communication with each other. Displaced inside the chamber 24, slidably mounted to the outer wall 17 of the third section 15, and movable between a first position P1 and a second position P2, the displacer 25 is configured to alternately displace at least one thermodynamic fluid between a first filling space 21 and a second filling space 23, and The present invention comprises a piston 26 positioned inside the third profile 15, slidably mounted against the inner wall 16 of the third profile 15, and movable between a first position P1 and a second position P2, wherein the piston 26 is adapted and intended to move between the first position P1 and the second position P2 by at least one working fluid J, H.

[0019] The displacer 25 and the piston 26 are coupled to each other.

[0020] Advantageously, the cartridge configurations 1, 1' provide a modular and expandable solution. In addition, the first profile 2 and the second profile 8 provide large internal and external exchange surfaces that contribute to the efficiency of heat transfer between the heat transfer fluid and the thermodynamic fluid. Furthermore, the first profile 2 and the second profile 8 can be manufactured at very low cost. Preferably under a pressure of 50 to 300 bar, preferably 80 to 250 bar, the chamber 24 housing the displacer 25 is isolated from the low-pressure environment. The low-pressure environment corresponds to a pressure of preferably 0 to 50 bar, preferably 0 to 10 bar. Thus, the displacer 25 is controlled from outside the chamber 24 via the displacement of the piston 26. Since the thermodynamic fluid flows around the displacer 25 during the displacement between a first position P1 and a second position P2, in addition to its thermodynamic fluid displacement function, the displacer 25 can also act as a regenerator. In addition, the displacer 25 can be heated or cooled solely by the heat transfer fluid when stationary at the first position P1 or the second position P2.

[0021] As shown in Figure 1, the first heat transfer fluid supply circuits A and B and the second heat transfer fluid supply circuits C and D supply the external heat necessary to operate the heat engine, preferably by ensuring a temperature difference between the low-temperature and high-temperature sections. Figure 1 shows cartridge 1 with the displacer 25 and piston 26 in a first position P1. In this configuration, the thermodynamic fluid is confined between the first section 2 and the third section 15, and therefore in the first filling space 21, and in contact with the temperature of the first heat transfer fluid supply circuits A and B. The dotted line indicates the second position P2 of the displacer 25 and piston 26, where the thermodynamic fluid is confined between the second section 8 and the third section 15, and therefore in the second filling space 23, and in contact with the temperature of the second heat transfer fluid supply circuits C and D. The change from a first position P1 to a second position P2, or vice versa, is controlled by the piston 26, preferably using the relative pressure between points H and J, thus allowing the thermodynamic fluid to move between the first and second filling spaces 21 and 23. Preferably, a thermodynamic fluid supply outlet G connected to the chamber 24 of at least one cartridge 1 allows the high pressure difference generated inside the cartridge 1 to be utilized for energy.

[0022] Chamber 24 accommodates a thermodynamic fluid under a pressure, for example, greater than 10 bar, but ideally above its critical pressure, so that it has significantly improved convective heat transfer compared to a gas at near atmospheric pressure. This improvement is typically 10 [W / m]. 2 Instead of .K, use a magnitude of 1-2 digits, i.e., 100-1000 [W / m]. 2The temperature is [.K]. As shown in Figure 2, a second packed space 23 for accommodating a high-pressure thermodynamic fluid is located between the third profile 15 and the second profile 8. In this second packed space 23, the thermodynamic fluid is preferably maintained in a supercritical state. The thermodynamic fluid may be carbon dioxide, but this example is not limiting. As illustrated in Figures 7, 8 and 9, a first packed space 21 is located between the third profile 15 and the first profile 2, and this first packed space 21 allows the thermodynamic fluid to be accommodated under high pressure, i.e., at a pressure of preferably 50 bar to 300 bar, preferably 80 bar to 250 bar. In this first packed space 21, the thermodynamic fluid is preferably maintained in a supercritical state.

[0023] Preferably, the first profile 2 and / or the second profile 8 are made of a material having high thermal conductivity, preferably 100 watts / meter·Kelvin to 400 watts / meter·Kelvin, such as an aluminum alloy or a copper alloy.

[0024] Advantageously, this property of the first profile 2 and / or the second profile 8 contributes to the efficiency of heat transfer between the heat transfer fluid and the thermodynamic fluid.

[0025] Preferably, the third section 15 is made of a non-magnetic material, and the displacer 25 and piston 26 are magnetically coupled to each other via the third section 15 by magnetic coupling means 27.

[0026] Advantageously, this configuration allows the displacer 25 to be controlled from outside the chamber 24 via a magnetic coupling between the piston 26 and the displacer 25. This magnetic coupling allows axial forces to be transmitted to the displacer 25 without mechanical contact, and therefore without friction. Thus, frictional losses and wear are avoided. This arrangement also helps to limit losses.

[0027] Non-magnetic refers to a material that either does not possess magnetic properties or has a low magnetic permeability, i.e., close to 1, generally less than 50.

[0028] For example, the third part 15 is made of stainless steel.

[0029] For example, the piston 26 is equipped with one or more permanent magnets 32, the displacer 25 is equipped with one or more permanent magnets 33, and the permanent magnets 32 and 33 form a magnetic connection means 27.

[0030] Preferably, as illustrated in Figures 1, 3, and 4, the first profile 2 extends longitudinally along axis A1 over a first length L1, and the second profile 8 extends longitudinally along axis A1 over a second length L2.

[0031] Preferably, the second section 8 is an extension of the first section 2 in the direction of axis A1.

[0032] For example, the first length L1 is equal to the second length L2, as illustrated in Figures 1, 3, and 4, in order to enable the symmetry of the cartridge by the joining means 14 described later.

[0033] Preferably, the first section 2 comprises a first end 6 and a second joining end 7, and the second section 8 comprises a first end 12 and a second joining end 13, and the first section 2 and the second section 8 are joined to each other by joining means 14 at their respective second joining ends 7 and 13.

[0034] Advantageously, the first profile 2 and the second profile 8 are separate from each other but connected by a connecting means 14 to avoid heat transfer. As a result, the first and second exchangers are mounted facing each other on the connecting means 14.

[0035] In the first embodiment of the present invention illustrated in Figure 3 and the second embodiment of the present invention illustrated in Figure 4, the second joining ends 7, 13 are configured on the one hand to enable joining with the joining means 14 and on the other hand to have at least one opening leading to the first / second circulation means 3, 9.

[0036] Preferably, the joining means 14 has a thermal conductivity lower than that of the first profile 2 and / or the second profile 8.

[0037] Advantageously, the joining means 14 allows for thermal separation between the first section 2 and the second section 8.

[0038] Preferably, the joining means 14 includes at least one thermal insulating material arranged to thermally insulate the first section 2 from the second section 8, and vice versa.

[0039] Advantageously, this configuration provides better insulation between the so-called low-temperature portion and the so-called high-temperature portion of cartridge 1, 1'.

[0040] For example, as shown in Figure 15, the joining means 14 may consist of a joining plate 39, which may be covered on both sides with a layer of insulating material.

[0041] Preferably, as illustrated in Figures 2, 7, 8, and 9, the third section 15, the first section 2, the second section 8, the displacer 25, and the piston 26 are coaxial along axis A1.

[0042] Advantageously, this configuration defines an annular chamber 24. Thus, the third portion 15 is arranged concentrically with a smaller diameter than the first portion 2 and the second portion 8.

[0043] Preferably, the third section 15 extends longitudinally along axis A1 over a third length L3, the third length L3 being greater than the first length L1 or the second length L2, preferably greater than or equal to the sum of the first length L1 and the second length L2.

[0044] Advantageously, in this configuration, the third profile 15 intersects with the so-called low-temperature portion and the so-called high-temperature portion of cartridge 1, 1' over a length L3 as defined above. As a result, the displacer 25 can alternately move between the so-called low-temperature portion and the so-called high-temperature portion by sliding over at least a portion of the third length L3 of the third profile 15.

[0045] For example, the third section 15 is a cylindrical hollow tube.

[0046] Preferably, the third section 15 comprises a first end 18 and a second end 19, the first end 6 of the first section 2 and the first end 18 of the third section 15 are joined by connecting means, and the first end 12 of the second section 8 and the second end 19 of the third section 15 are joined by connecting means.

[0047] In the first embodiment of the present invention shown in Figure 3 and the second embodiment of the present invention shown in Figure 4, the first end 6 of the first section 2 and the first end 18 of the third section 15 are attached to each other, for example, by crimping, soldering, joining, or by one or more additional elements. The first end 6 of the first section 2 has a conical shape, but this example is not limiting. Similarly, the first end 12 of the second section 8 and the second end 19 of the third section 15 are attached to each other, for example, by crimping, brazing, joining, or by one or more additional elements. The first end 12 of the second section 8 has a conical shape, but this example is not limiting.

[0048] Preferably, cartridges 1, 1' include a first radial and / or axial stress reinforcement portion 28 to which the first profile 2 is clamped, and a second radial and / or axial stress reinforcement portion 29 to which the second profile 8 is clamped.

[0049] The first reinforcement 28 and the second reinforcement 29 absorb radial and / or axial pressure, thereby minimizing the first thickness E1 of the first profile 2 and the second thickness E2 of the second profile 8, bringing the heat transfer fluid as close as possible to the thermodynamic fluid. These pressures are due to the pressure of the thermodynamic fluid contained within the chamber 24 and are applied to the first and second profiles 2 and 8.

[0050] The first reinforcing portion 28 can be joined to the first profile 2, and the second reinforcing portion 29 can be joined to the second profile 8, using a joining method that ensures a radial clearance of 0 between the two portions, i.e., pressing / hardening / bonding / forming the tube by rolling or swaging.

[0051] Figure 2 illustrates how the second reinforcement 29 absorbs radial forces in order to minimize the second thickness E2 of the second section 8.

[0052] Figures 7, 8, and 9 illustrate how radial forces are absorbed by the first reinforcement 28 in order to minimize the first thickness E1 of the first section 2.

[0053] As shown in the first embodiment illustrated in Figure 3 and the second embodiment illustrated in Figure 4, the first reinforcing portion 28 or the second reinforcing portion 29 may be equipped with a strap. Preferably, the first reinforcing portion 28 and the second reinforcing portion 29 have a hollow cylindrical shape.

[0054] Advantageously, the first profile 2 and the second profile 8 are assembled without any play within the strap. Radial forces are absorbed by the strap.

[0055] The strap itself can be attached on one side to the first ends 6, 12 of the first / second profiles 2, 8, and on the other side to the connecting means 14.

[0056] As shown in the second embodiment in Figure 4, the first reinforcing piece 28 or the second reinforcing piece 29 may include a flange 51 held to the first / second profiles 2,8 by fastening means 52, in addition to the strap.

[0057] The axial force is absorbed by the flange, which is particularly important for cartridge 1,1', whose diameter is preferably 20 mm to 120 mm.

[0058] The flange 51 can also form first / second dividing walls 48, 49, as described below.

[0059] In the first embodiment shown in Figure 3, the first reinforcement 28 or the second reinforcement 29 consists only of a strap, and the axial force is absorbed by the first / second profiles 2, 8 and the third profile 15.

[0060] Preferably, generally speaking, the first reinforcement 28 and / or the second reinforcement 29 and / or the first section 2 and / or the second section 8 and / or the third section 15 are designed to absorb axial forces.

[0061] For example, the first thickness E1 of the first profile 2 and / or the second thickness E2 of the second profile 8 is 1 mm to 15 mm, preferably 2 mm to 6 mm.

[0062] Preferably, the inner wall 4 of the first profile 2 and / or the inner wall 10 of the second profile 8 have a serrated surface (Figures 7, 8, and 9) and / or a smooth surface (Figure 2).

[0063] As shown in Figure 2, the smooth contact surface between the second profile 8 and the thermodynamic fluid has the simplest tubular shape.

[0064] Advantageously, when the inner walls 4 and / or 10 have a serrated surface (Figures 7, 8, and 9), the surface area increases compared to a smooth surface (Figure 2), improving heat exchange. Thus, the exchange surface is extended at the interface between the first profile 2 and / or the second profile 8 and the thermodynamic fluid.

[0065] Preferably, the first profile 2 has a first thickness E1 between the inner wall 4 and the outer wall 5, and the first profile 2 comprises at least one channel 30 and / or at least one groove 31 that form the first circulation means 3 within its first thickness E1, the at least one channel 30 and / or at least one groove 31 extending over a length L4 in the longitudinal direction parallel to the axis A1.

[0066] Advantageously, at least one channel 30 and / or at least one groove 31 allow for the circulation of the heat transfer fluid within the first exchanger. The channel 30 provides a substantial exchange surface between the heat transfer fluid and the first profile 2. This configuration helps to maximize heat transfer.

[0067] Preferably, the second profile 8 has a second thickness E2 between the inner wall 10 and the outer wall 11, and the second profile 8 comprises at least one channel 30 and / or at least one groove 31 that form the second circulation means 9 in its second thickness E2, the at least one channel 30 and / or at least one groove 31 extending over a length L5 in the longitudinal direction parallel to axis A.

[0068] Advantageously, at least one channel 30 and / or at least one groove 31 allow for the circulation of the heat transfer fluid within the second exchanger. The channel 30 provides a substantial exchange surface between the heat transfer fluid and the second profile 8, thereby maximizing heat transfer.

[0069] Preferably, at least one channel 30 has a square, rectangular, trapezoidal (Figure 8), or circular (Figure 7) cross-section.

[0070] At least one groove 31 can be opened (Figures 2 and 3).

[0071] At least one channel 30 and / or at least one groove 31 may be linear or helical.

[0072] Preferably, according to the first possibility, the cross-section of the displacer 25 is smaller than the cross-section of the chamber 24 so as to form a clearance J1 between the displacer 25 and the inner wall 4 of the first section 2 or a clearance J2 between the displacer 25 and the inner wall 10 of the second section 8 (Figures 2, 7, 8, and 9).

[0073] Advantageously, these clearances J1 and J2 ensure the passage of the thermodynamic fluid as the displacer 25 moves. Each time the thermodynamic fluid passes through, some of its heat is transferred to the displacer 25 to perform its regeneration function.

[0074] Preferably, the clearances J1 and J2 are 0.05 mm to 5 mm, preferably 0.1 mm to 1 mm.

[0075] According to the second possibility, the cross-section of the displacer 25 is equal to the cross-section of the chamber 24, and the displacer 25 is made of a porous material, at least partially.

[0076] The porosity of the displacer 25 favorably ensures the passage of thermodynamic fluid during the displacement of the displacer 25. Each time the thermodynamic fluid passes through, some of its heat is transferred to the displacer to perform its regeneration function.

[0077] Preferably, the cross-section of the chamber 24 is annular, and the cross-section of the displacer 25 is annular (Figure 2).

[0078] In this way, the cross-sections of the chamber 24 and the displacer 25 are identical, minimizing dead volume.

[0079] Preferably, the displacer 25 conforms to the shape of the inner wall 4 of the first section 2 and / or the inner wall 10 of the second section 8 (Figures 7 and 8).

[0080] Preferably, the piston 26 is a low-pressure piston. The low-pressure environment preferably corresponds to a pressure of 0 to 50 bar, preferably 0 to 10 bar.

[0081] According to a third embodiment of the present invention shown in Figure 10, the cartridge 1' is called a hybrid and further comprises a hydraulic piston 34 located inside a first filling space 21 or a second filling space 23 of a chamber 24, the first filling space 21 or the second filling space 23 being fitted and designed to accommodate at least one hydraulic fluid and to be fitted and designed to be connected to a hydraulic fluid supply outlet E, the hydraulic piston 34 being slidably mounted in the direction of axis A1 relative to the outer wall 17 of the third profile 15 and movable inside the first filling space 21 or the second filling space 23 between a first position P3 and a second position P4, and configured to be displaced on the one hand by at least one thermodynamic fluid and on the other hand to alternately displace at least one hydraulic fluid in the first filling space 21 or the second filling space 23.

[0082] Advantageously, as illustrated in Figure 10, it is possible to associate the hydraulic piston 34 with the geometric shape of the cartridge 1 described above in order to maintain a certain degree of symmetry with respect to the connecting plate 39.

[0083] A special feature of this configuration is that the displacer 25 follows the position of the hydraulic piston 34 while being in contact with and held against the hydraulic piston 34 during the cooling phase. The hydraulic piston 34 moves in only one of the two thermal sections, either the so-called high-temperature section or the so-called low-temperature section. The hydraulic piston 34 represents the physical interface between the thermodynamic fluid and the hydraulic fluid and does not need to be completely sealed, for example, if the fluids are immiscible and insoluble. This configuration simplifies the integration of the hydraulic piston 34 when the system is used in a module, as detailed below.

[0084] According to a fourth alternative embodiment of the present invention illustrated in Figure 11, the chamber 24 of the cartridge 1 is adapted and intended to be connected to a hydraulic piston 34 adapted and intended to be connected to a supply circuit for a hydraulic fluid E. Preferably, at least one thermodynamic fluid supply outlet G connected to the chamber 24 of the cartridge 1 can be connected to the hydraulic piston 34, which ensures the transfer of pressure from the thermodynamic fluid to the hydraulic fluid, such as oil or water or equivalent. The hydraulic piston 34 is preferably housed in a tube or cylinder. The hydraulic piston 34 is ideally maintained at a temperature by being supplied by a first / second heat source, for example, via first / second supply circuits A, B / C, D. Advantageously, the thermodynamic fluid leaving the cartridge 1 is kept cooled or heated depending on whether the first / second heat source is supplied to the hydraulic piston 34. Advantageously, the working fluid for the energy recovery system can be different from the thermodynamic fluid, avoiding the use of turbines operating with supercritical phase thermodynamic fluids. Similarly, one or more cartridges 1 may be connected to one or more hydraulic pistons 34. The hydraulic pistons 34 may be located outside the module described below or inside the module described below in order to concentrate the heat supply.

[0085] The present invention also relates to a module for a thermodynamic cycle heat engine for alternating the movement of a thermodynamic fluid between a low-temperature portion connected to a first heat source and a high-temperature portion connected to a second heat source, comprising at least one cartridge 1, 1' or a plurality of cartridges 1, 1' as described above according to the present invention, First heat transfer fluid supply circuits A and B are connected to the first circulation means 3 of at least one cartridge 1, 1' via at least one first supply port 35 and at least one second supply port 36 of the first circulation means 3. A second heat transfer fluid supply circuit C, D is connected to the second circulation means 9 of at least one cartridge 1 via at least one third supply port 37 and at least one fourth supply port 38 of the second circulation means 9, A bonding plate 39 having at least one cartridge bonding means 14, A working fluid supply circuit H, J is connected to the third section 15 of at least one cartridge 1 by at least one fifth supply port 40 included in the third section 15 and at least one sixth supply port 41 included in the third section 15, and is arranged to guide the displacement of the piston 26. It comprises a thermodynamic fluid supply outlet G connected to the chamber 24 of at least one cartridge 1, or a hydraulic fluid supply outlet E connected to the first filling space 21 or the second filling space 23 of the chamber 24.

[0086] Advantageously, the module can comprise one or more cartridges 1,1' depending on the desired heat engine output. The size of the module can be adapted to the number of cartridges 1,1' incorporated for the target output of the heat engine.

[0087] In the example shown in Figure 12, the module comprises a single cartridge 1.

[0088] In the examples shown in Figures 18 and 19, the module comprises six cartridges 1.

[0089] Preferably, the module comprises at least one of the aforementioned hybrid cartridges 1' having a hydraulic piston 34 located inside a first filling space 21 or a second filling space 23 of the chamber 24.

[0090] In the example shown in Figure 13, the module comprises a single hybrid cartridge 1'. However, compared to the module shown in Figure 12, which does not have a hydraulic piston, the replacement surface is no longer symmetrical between the high-temperature and low-temperature portions.

[0091] In the example shown in Figure 14, the module comprises cartridge 1 and a so-called hybrid cartridge 1'. However, compared to the module shown in Figure 12, which does not have a hydraulic piston, the replacement surface is no longer symmetrical between the high-temperature and low-temperature portions. This lack of symmetry can be partially compensated in the multi-cartridge module 1, 1' by using a ratio in which the so-called hydride cartridge 1' is combined with several basic cartridges 1 that do not have a hydraulic piston 34. Then, the hydraulic piston 34 of the so-called hybrid cartridge 1' takes over the expansion of some cartridges 1 without the hydraulic piston 34.

[0092] For example, as shown in Figures 16 and 17, the module integrates six cartridges 1, 1' in a ratio of two cartridges 1 without a hydraulic piston 34 to one so-called hybrid cartridge 1'.

[0093] Preferably, the module comprises two insulating casings separated by a bonding plate 39 and housing at least one cartridge 1, 1' or at least a portion of a plurality of cartridges 1, 1'.

[0094] Two insulating casings can be separated by one or more casings.

[0095] Advantageously, each insulating casing is directly connected to a first or second heat source, which allows the heat transfer fluid to be supplied from a central source to at least one cartridge 1, 1' or more cartridges 1, 1', instead of having to supply each cartridge 1, 1' individually.

[0096] The sizes of the two insulating casings can be adapted to the number of cartridges 1, 1' incorporated for the target heat engine output.

[0097] Preferably, the working fluid supply circuits H and J are formed by first heat transfer fluid supply circuits A and B and second heat transfer fluid supply circuits C and D.

[0098] In this case, the working fluid supply sources H and J at the fifth supply port 40 are the same as those of the first heat transfer fluid supply circuits A and B, and similarly, the working fluid supply source at the sixth supply port 41 is the same as those of the second heat transfer fluid supply circuits C and D. As a result, the piston 26 can be actuated by the relative pressure difference between the first heat transfer fluid supply circuits A and B and the second heat transfer fluid supply circuits C and D.

[0099] Preferably, and alternatively, the working fluid supply circuits H and J are separate from the first heat transfer fluid supply circuits A and B and the second heat transfer fluid supply circuits C and D (Figures 18 and 19).

[0100] Preferably, the connecting plate 39 has a thermal conductivity lower than that of the first profile 2 and / or the second profile 8.

[0101] Advantageously, the bonding plate 39 has a thermal separation function.

[0102] Preferably, the connecting plate 39 is made of a steel-type metal.

[0103] Preferably, the first reinforcing piece 28 and the second reinforcing piece 29 are attached to the connecting plate 39, respectively.

[0104] Preferably, as shown in Figures 12, 13, and 14, the module comprises a first insulating casing 43 including at least one first compartment 44 leading to at least one first supply port 35 of the first circulation means 3, and at least one second compartment 45 leading to at least one second supply port 36 of the first circulation means 3.

[0105] Preferably, additionally or alternatively, as illustrated in Figures 12, 13, and 14, the module comprises a second insulating casing 43' comprising at least one third compartment 46 leading to at least one third supply port 37 of the second circulation means 9, and at least one fourth compartment 47 leading to at least one fourth supply port 38 of the second circulation means 9.

[0106] Preferably, the second reinforcing portion 29 includes the third supply port 37 and the fourth supply port 38 of the second circulation means 9.

[0107] As a result, the first insulating casing 43 is designed to house the so-called low-temperature portion of cartridges 1, 1' and to receive the heat transfer fluid coming from the first heat source to supply to the first heat transfer fluid supply circuits A, B. As a result, the second insulating casing 43' is designed to house the so-called high-temperature portion of cartridges 1, 1' and to receive the heat transfer fluid coming from the second heat source to supply to the second heat transfer fluid supply circuits C, D.

[0108] Preferably, the joining plate 39 separates the first casing 43 from the second casing 43'.

[0109] Preferably, the first reinforcing piece 28 includes a first supply port 35 and a second supply port 36 of the first circulation means 3.

[0110] This configuration allows the first / second reinforcing members 28, 29 and the first / second profiles 2, 8 to be immersed in the heat transfer fluid.

[0111] The first section 44 and the second section 45 are preferably separated by at least one first separation wall 48.

[0112] The third section 46 and the fourth section 47 are preferably separated by at least one second dividing wall 49.

[0113] The first dividing wall 48 and / or the second dividing wall 49 act as hydraulic shutters and preferably do not withstand high mechanical stress.

[0114] The first dividing wall 48 and / or the second dividing wall 49 are preferably made of plastic or elastomer material, but these examples are not limiting.

[0115] The first supply port 35 and the second supply port 36 are located on either side of the first separation wall 48, thereby ensuring that the flow of heat transfer fluid between A and B occurs between the first reinforcement 28 and the first profile 2, inside the first reinforcement 28, rather than outside the first reinforcement 28.

[0116] The third supply port 37 and the fourth supply port 38 are located on either side of the first separation wall 48, thereby ensuring that the flow of heat transfer fluid between C and D occurs between the second reinforcement 29 and the second profile 8, rather than outside the second reinforcement 29.

[0117] Preferably, at least one fifth supply port 40 of the H, J working fluid supply circuit leads to the first compartment 44, and at least one sixth supply port 41 of the H, J working fluid supply circuit leads to the third compartment 46.

[0118] In this case, the working fluid supply sources H and J in the fifth supply port 40 are the same as those in the first heat transfer fluid supply circuits A and B, and similarly, the working fluid supply source in the sixth supply port 41 is the same as those in the second heat transfer fluid supply circuits C and D.

[0119] As shown in Figure 14, the module may comprise at least two cartridges 1, 1', the chambers 24 of each cartridge 1 being interconnected by at least one interconnection line 50 preferably located on at least one connecting plate 39, and the module's thermodynamic fluid supply outlet G or the module's hydraulic fluid supply outlet E preferably located on the connecting plate 39.

[0120] Advantageously, at least one interconnection duct 50 allows for the interconnection of each chamber 24 of each cartridge 1, 1'.

[0121] The present invention also relates to a heat engine adapted and intended to perform at least one conversion of thermal energy to mechanical energy, preferably comprising at least one thermodynamic fluid in a supercritical state, and adapted and intended to implement a thermodynamic cycle comprising at least one isococcal heating stage, optionally an isobaric heating stage, an expansion stage, and an isobaric cooling stage, wherein the heat engine comprises at least one module according to the present invention as described above.

[0122] Naturally, the present invention is not limited to the embodiments described and shown in the accompanying drawings. However, modifications remain possible without departing from the scope of protection of the present invention, particularly with respect to the configuration of various elements, or by substitution of technical equivalents.

Claims

1. A cartridge (1, 1') for transferring a thermodynamic fluid between a low-temperature portion connected to a first heat source and a high-temperature portion connected to a second heat source for a thermodynamic cycle heat engine, comprising at least, - A first exchanger forming a "low temperature" section, comprising a hollow first section (2) suitable for connection to a first heat transfer fluid supply circuit (A, B) connected to a first heat source and equipped with a first means (3) for circulating at least one heat transfer fluid intended for connection, wherein the first section (2) comprises an inner wall (4) and an outer wall (5), - A second heat exchanger forming a so-called high-temperature section, comprising a hollow second section (8) including a second means (9) for circulating at least one heat transfer fluid, which is adapted and designed to be connected to a second heat transfer fluid supply circuit (C, D) connected to a second heat source, wherein the second section (8) comprises an inner wall (10) and an outer wall (11), - A hollow third section (15) adapted and intended to be connected to at least one supply circuit for at least one working fluid (J, H), wherein the third section (15) is disposed inside the first section (2) and the second section (8), and the third section (15) comprises an inner wall (16) and an outer wall (17), wherein at least a portion of the inner wall (4) of the first section (2) and a first portion (20) of the outer wall (17) of the third section (15) are spaced apart and facing each other to form a first filling space (21), and at least a portion of the inner wall (10) of the second section (8) and a second portion (22) of the outer wall (17) of the third section (15) are spaced apart and facing each other to form a second filling space (23), - At least one chamber (24) suitable for and designed to contain at least one thermodynamic fluid, preferably under high pressure and supercritical conditions, wherein the chamber (24) comprises at least one first packed space (21) and a second packed space (23) that are in communication with each other, - A displacer (25) positioned inside the chamber (24), slidably mounted against the outer wall (17) of the third section (15), and movable between a first position (P1) and a second position (P2), wherein at least one displacer (25) is configured to alternately displace the at least one thermodynamic fluid between the first filling space (21) and the second filling space (23), A cartridge comprising: a piston (26) located inside the third section (15), slidably mounted against the inner wall (16) of the third section (15), and movable between a first position (P1) and a second position (P2), wherein the piston (26) is adapted and designed to be displaced between the first position (P1) and the second position (P2) by the at least one working fluid (J, H), and the displacer (25) and the piston (26) are coupled to each other.

2. The cartridge according to claim 1, characterized in that the third section (15) is preferably made of a non-magnetic material, and the displacer (25) and the piston (26) are magnetically coupled to each other via the third section (15) by magnetic coupling means (27).

3. The cartridge according to claim 1 or 2, characterized in that the first section (2) extends longitudinally along the axis A1 over a first length L1, and the second section (8) extends longitudinally along the axis A1 over a second length L2.

4. The cartridge according to claim 3, characterized in that the third section (15) extends longitudinally along the axis A1 over a third length L3, and the third length L3 is greater than the first length L1 or the second length L2, preferably greater than or equal to the sum of the first length L1 and the second length L2.

5. The cartridge according to any one of claims 1 to 4, characterized in that the second section (8) is an extension of the first section (2) in the direction of axis A1.

6. The cartridge according to any one of claims 1 to 5, characterized in that the first section (2) comprises a first end (6) and a second joining end (7), the second section (8) comprises a first end (12) and a second joining end (13), and the first section (2) and the second section (8) are joined to each other at their respective second joining ends (7, 13) by joining means (14).

7. The cartridge according to claim 6, wherein the third section (15) comprises a first end (18) and a second end (19), the first end (6) of the first section (2) and the first end (18) of the third section (15) are joined by connecting means, and the first end (12) of the second section (8) and the second end (19) of the third section (15) are joined by connecting means.

8. The cartridge according to any one of claims 1 to 7, characterized in that the third section (15), the first section (2), the second section (8), the displacer (25), and the piston (26) are coaxial along the axis A1.

9. The cartridge according to any one of claims 1 to 8, comprising a first radial and / or axial stress reinforcing portion (28) to which the first section (2) is connected, and a second radial and / or axial stress reinforcing portion (29) to which the second section (8) is connected.

10. The cartridge according to any one of claims 6 to 9, characterized in that the joining means (14) has a thermal conductivity lower than that of the first section (2) and / or the second section (8).

11. The cartridge according to any one of claims 1 to 10, characterized in that the inner wall (4) of the first section (2) and / or the inner wall (10) of the second section (8) have a serrated surface and / or a smooth surface.

12. The first section (2) has a first thickness E1 between the inner wall (4) and the outer wall (5), and the first section (2) comprises at least one channel (30) and / or at least one groove (31) in its first thickness E1 that form the first circulation means (3), the at least one channel (30) and / or at least one groove (31) extending over a length L4 in a longitudinal direction parallel to the axis A1, and / or the second section (8) The cartridge according to any one of claims 1 to 11, wherein the inner wall (10) and the outer wall (11) have a second thickness E2, and the second section (8) comprises at least one channel (30) and / or at least one groove (31) in the second thickness E2 that form the second circulation means (9), and the at least one channel (30) and / or at least one groove (31) extends over a length L5 in a longitudinal direction parallel to the axis A1.

13. The cartridge according to any one of claims 1 to 12, wherein the cartridge (1') is called a hybrid and comprises a hydraulic piston (34) disposed inside the first filling space (21) or the second filling space (23) of the chamber (24), the first filling space (21) or the second filling space (23) being fitted and designed to accommodate at least one hydraulic fluid and to be fitted and designed to be connected to a hydraulic fluid supply outlet (E), the hydraulic piston (34) being mounted to slide against the outer wall (17) of the third section (15) in the direction of axis A1, and being movable within the first filling space (21) or the second filling space (23) between a first position (P3) and a second position (P4), and being displaced on the one hand by the at least one thermodynamic fluid, and on the other hand alternatingly displacing the at least one hydraulic fluid in the first filling space (21) or the second filling space (23).

14. The cartridge according to any one of claims 1 to 13, characterized in that the first section (2) and / or the second section (8) are made of a material having a high thermal conductivity, preferably 100 watts / meter Kelvin to 400 watts / meter Kelvin, for example, aluminum or a copper alloy.

15. The cartridge according to claim 9, characterized in that the first radial and / or axial stress reinforcing portion (28) and / or the second radial and / or axial stress reinforcing portion (29), and / or the first section (5) and / or the second section (8) and / or the third section (15) are arranged to absorb axial forces.

16. A module for alternating the movement of a thermodynamic fluid between a low-temperature portion connected to a first heat source and a high-temperature portion connected to a second heat source for a thermodynamic cycle heat engine, comprising at least one cartridge (1, 1') or a plurality of cartridges (1, 1') as described in any one of claims 1 to 15, - A first heat transfer fluid supply circuit (A, B) connected to the first circulation means (3) of at least one cartridge (1, 1') by at least one first supply port (35) and at least one second supply port (36) of the first circulation means (3), - A second heat transfer fluid supply circuit (C, D) connected to the second circulation means (9) of at least one cartridge (1) by at least one third supply port (37) and at least one fourth supply port (38) of the second circulation means (9), - At least the joining plate (39) having the joining means (14) of the cartridge (1), - A working fluid supply circuit (H, J) is connected to the third section (15) of the at least one cartridge (1) by at least one fifth supply port (40) included in the third section (15) and at least one sixth supply port (41) included in the third section (15), and is arranged to guide the displacement of the piston (26), A module comprising: a thermodynamic fluid supply outlet (G) connected to the chamber (24) of at least one cartridge (1), or a hydraulic fluid supply outlet (E) connected to the first filling space (21) or the second filling space (23) of the chamber (24).

17. The module according to claim 16, comprising at least one cartridge (1') as described in claim 13, wherein the so-called hybrid cartridge comprises a hydraulic piston (34) disposed inside the first filling space (21) or the second filling space (23) of the chamber (24).

18. The module according to claim 16 or 17, characterized in that the working fluid supply circuit (H, J) is formed from the first heat transfer fluid supply circuit (A, B) and the second heat transfer fluid supply circuit (C, D).

19. The module according to any one of claims 16 to 18, characterized in that the bonding plate (39) has a thermal conductivity lower than that of the first section (2) and / or the second section (8).

20. The module according to any one of claims 16 to 19, characterized in that the first insulating casing (43) comprises at least one first compartment (44) leading to at least one first supply port (35) of the first circulation means (3) and at least one second compartment (45) leading to at least one second supply port (36) of the first circulation means (3), and / or the second insulating casing (43') comprises at least one third compartment (46) leading to at least one third supply port (37) of the second circulation means (9) and at least one fourth compartment (47) leading to at least one fourth supply port (38) of the second circulation means (9).

21. The module according to claims 17 and 20, characterized in that at least one fifth supply port (40) of the working fluid supply circuit (H, J) leads to the first compartment (44), and at least one sixth supply port (41) of the working fluid supply circuit (H, J) leads to the third compartment (46).

22. The module according to any one of claims 17 to 21, wherein the module comprises at least two cartridges (1, 1'), the chambers (24) of each cartridge (1) are interconnected by at least one interconnecting pipe (50), and the thermodynamic fluid supply outlet (G) or the hydraulic fluid supply outlet (E) of the module is preferably located within the joining plate (39).

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