Cartridge for a heat engine having a thermodynamic cycle and associated heat engine

Abstract

The invention relates to a cartridge (1) for the displacement of a thermodynamic fluid for a heat engine, the cartridge being characterised in that it comprises: a first profile section (2) comprising first circulation means (3) for circulating a heat transfer fluid; a second profile section (8) comprising second circulating means (9) for circulating a heat-transfer fluid; a third profile section (15) being able and intended to be connected to at least one supply circuit of at least one working fluid (J, H), said third profile section (15) being placed inside the first profile section (2) and the second profile section (8); a chamber (24) for containing a thermodynamic fluid; a displacer (25) placed within said chamber (24) and mounted so as to be capable of sliding relative to the outer wall (17) of said third profile section (15); a piston (26) placed inside said third profile section (15) and mounted so as to be capable of sliding relative to the inner wall (16) of said third profile section (15), the piston (26) being able and intended to be moved by said at least one working fluid (J, H), the displacer (25) and the piston (26) being coupled to each other.

Description

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

[0002] The current energy transition presents challenges in numerous areas, notably through the reduction of primary energy consumption. In this regard, the industrial sector produces large quantities of thermal energy, a significant portion of which is still currently wasted as waste heat. This lost heat represents a vast energy resource, readily available and already paid for, the recovery of which is a strategic imperative for industry. Waste heat can be recovered either by directly supplying district heating networks, by temporarily storing it, or by converting it into electricity for internal or external use.For low-temperature emissions, i.e., below 100 degrees Celsius, there is currently no commercially viable machine for converting them into electricity, due to a lack of economic viability; use in a district heating network is the only possible alternative. However, this presents numerous implementation constraints, particularly regarding the mandatory proximity of the end user.

[0003] Current developments in external heat supply machines are therefore limited for temperatures where the resource is ultimately less significant.

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

[0005] Machines with external heat input that utilize a working fluid in a closed cycle without phase change are generally called Stirling engines. More specifically, so-called beta or gamma Stirling engines have a working piston and a displacer used to alternately transfer the working fluid from the hot side to the cold side. In this type of engine, the working piston and the displacer are mechanically linked. These engines are characterized by very low power density and difficult power control because the rotational speed depends primarily on the temperature difference between the heat sources. The few commercially available machines therefore require a large temperature difference between the heat sources, often on the order of several hundred degrees Celsius, to compensate for the low thermal conductivities of the working gases used, the small heat exchange surfaces, and the dead volumes of the regenerator.

[0006] To improve power density, we know from publication WO2018062627A1 of certain Stirling engines developed to operate with pressurized gas or even with a supercritical fluid such as carbon dioxide. However, the very high pressures required, combined with the engine's high rotational speeds, typically around 3000 rpm, lead to problematic losses due to friction and pumping of the working fluid. At the working piston level, the durability of the dynamic seals under high pressure and high temperature also remains a challenge to ensure engine longevity and prevent leaks.

[0007] Another concept in this machine category, utilizing the properties of carbon dioxide near its critical point, is proposed in publication WO02 / 01 052A2. In this design, the working fluid is not displaced, but rather the heat sources are alternately brought into contact with the fluid via movable thermal screens. This system is constructionally complex due to the need to integrate alternating hot and cold sources within each cylinder. This configuration generates significant heat losses, particularly through the thermal screens, which are successively brought into contact with the heat sources and do not directly contribute to heating or cooling the fluid like a conventional regenerator.

[0008] Publication WO2016 / 165687A1 also describes a supercritical cycle heat conversion process using carbon dioxide, in which expansion is achieved isothermally by means of an oscillator system. The 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 enhance heat transfer by convection. The complexity of the construction, due to the integration of the oscillator, a regenerator, pistons, and a displacer within each cylinder, makes this concept unattractive for large-scale installations and production. Furthermore, the improvement in heat transfer through increased convection within the cylinder is limited by the small contact area between the cylinder and the heat sources. The concept is therefore designed to operate with a temperature difference exceeding 150 degrees Celsius.

[0009] Developments, particularly concerning so-called free piston Stirling engines (FPSE), have led to attempts to limit heat losses between the hot and cold sources to increase engine efficiency. Publication WO2005 / 042958 proposes integrating the regenerator into a low-thermal-conductivity ceramic component connecting the hot and cold sections. However, this configuration does not allow for displacer control, and the electric generator must be integrated into each piston, which becomes problematic for high-power installations requiring multiple cylinders.

[0010] A multi-cylinder external heat-supply engine architecture is proposed in publication WO02088536. The "liquid" displacer technique implemented and the series connection of the pistons for the transfer of the thermodynamic fluid from one piston chamber to another does not allow for management of the position of the thermodynamic fluid independent of the working fluid, and therefore does not allow for optimization of the thermodynamic cycle performed.

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

[0012] The mechanical decoupling of the displacers and working pistons, which, as explained in the state of the art, allows for better control of thermodynamic transformations to improve efficiency, requires, however, in current solutions, the addition of extra external actuator systems, as the displacers are no longer driven by the engine's rotation. In the case of multi-cylinder engines, these systems become very complex and expensive to implement, since each displacer in each cylinder then requires an actuator.

[0013] The present invention aims to provide an evolving and modular solution enabling the exploitation of heat sources with a temperature below 150 degrees Celsius.

[0014] To this end, the invention relates to a cartridge for the movement of a thermodynamic fluid between a cold part connected to a first heat source and a hot part connected to a second heat source for a thermodynamic cycle heat engine, characterized in that it comprises at least: a first heat exchanger, forming a so-called cold part, comprising a first hollow profile including first circulation means for at least one heat transfer fluid suitable and intended to be connected to a first heat transfer fluid supply circuit connected to a first heat source, said first profile comprising an internal wall and an external wall, a second heat exchanger, forming a so-called hot part, comprising a second hollow profile including second circulation means for at least one heat transfer fluid suitable and intended to be connected to a second heat transfer fluid supply circuit connected to a second heat source, said second profile comprising an internal wall and an external wall, a third hollow profile suitable and intended to be connected to at least one supply circuit for at least one working fluid, said third profile being disposed inside the first profile and the second profile,said third profile comprising an inner wall and an outer wall, at least a portion of the inner wall of the first profile and a first portion of the outer wall of the third profile being spaced apart and situated opposite each other so as to form a first filling space, at least a portion of the inner wall of the second profile and a second portion of the outer wall of the third profile being spaced apart and situated opposite each other so as to form a second filling space, at least one chamber suitable and intended to contain at least one thermodynamic fluid preferably at high pressure and in a supercritical state, said chamber comprising at least the first filling space and the second filling space which are communicating,at least one displacer disposed inside said chamber and mounted to slide relative to the outer wall of said third profile and movable between a first position and a second position, and configured to alternately displace said at least one thermodynamic fluid between the first filling space and the second filling space, a piston disposed inside said third profile and mounted to slide relative to the inner wall of said third profile and movable between the first position and the second position, the piston being suitable and intended to be moved by said at least one working fluid between the first position and the second position, the displacer and the piston being coupled to each other.

[0015] The invention also relates to a module for the movement of a thermodynamic fluid alternately between a cold part connected to a first heat source and a hot part connected to a second heat source for a thermodynamic cycle heat engine, characterized in that it comprises at least one cartridge or a plurality of cartridges according to the invention, and in that it comprises: a first heat transfer fluid supply circuit connected to said first circulation means of said at least one cartridge by 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 said second circulation means of said at least one cartridge by at least one third supply port and at least one fourth supply port of the second circulation means, a junction plate comprising at least said cartridge junction means, a working fluid supply circuit, connected to said third profile of said at least one cartridge by at least one fifth supply port comprising the third profile and at least one sixth supply port comprising the third profile, arranged to control the movement of the piston,a thermodynamic fluid supply outlet connected to the chamber of said chamber, and at least one cartridge or hydraulic fluid supply outlet connected to the first or second filling space of said chamber.

[0016] The invention will be better understood from the following description, which relates to several preferred embodiments, given by way of non-limiting examples, and explained with reference to the accompanying schematic drawings, in which [ Fig. 1 ] there figure 1 represents a cross-sectional view of a cartridge according to the invention, [ Fig. 2 ] there figure 2 represents a cross-sectional view of the cartridge of the figure 1 , [ Fig. 3 ] there figure 3 represents a cross-sectional view of a cartridge according to a first embodiment of the invention, [ Fig. 4 ] there figure 4 represents a cross-sectional view of a cartridge according to a second embodiment of the invention, [ Fig. 5 ] there figure 5 represents a perspective view of part of the cartridge according to the first embodiment of the invention, [ Fig. 6 ] there figure 6 represents a perspective view of part of the cartridge according to the first embodiment of the invention, [ Fig. 7 ] there figure 7 represents a cross-sectional view of the cartridge according to the invention showing circulation means in the form of channels with a circular cross-section, [ Fig. 8 ] there figure 8 represents a cross-sectional view of the cartridge according to the invention showing circulation means in the form of trapezoidal cross-section channels, [ Fig. 9 ] there figure 9 represents a cross-sectional view of the cartridge according to the invention showing circulation means in the form of open grooves, [ Fig. 10 ] there figure 10 represents a cross-sectional view of a so-called hybrid cartridge in a third embodiment according to the invention [ Fig. 11 ] there figure 11 represents a cross-sectional view of a cartridge according to the figure 1 connected to a hydraulic piston according to a fourth variant of the invention, [ Fig. 12 ] there figure 12 represents a cross-sectional view of a module including a cartridge according to the figure 1 , [ Fig. 13 ] there figure 13 represents a cross-sectional view of a module including a cartridge known as a hybrid cartridge according to the figure 10 , [ Fig. 14 ] there figure 14 represents a cross-sectional view of a module including a cartridge according to the figure 1 and a so-called hybrid cartridge according to the figure 10 , [ Fig. 15 ] there figure 15 represents a junction plate, [ Fig. 16 ] there figure 16 represents a cross-sectional view of a module comprising four cartridges according to the figure 4 and two so-called hybrid cartridges according to the invention, [ Fig. 17 ] there figure 17 represents a perspective view of the module of the figure 16 . Fig. 18 ] there figure 18 represents a cross-sectional view of a module comprising six cartridges according to the figure 3 , [ Fig. 19 ] there figure 19 represents a perspective view of the module of the figure

[0017] In accordance with the invention and as illustrated in particular by the figures 1 à 9 , a cartridge 1, 1' for the movement of a thermodynamic fluid between a cold part connected to a first heat source and a hot part connected to a second heat source for a thermodynamic cycle heat engine comprises at least: a first heat exchanger, forming a so-called cold part, comprising a first hollow profile 2 including first circulation means 3 of at least one suitable heat transfer fluid intended to be connected to a first heat transfer fluid supply circuit A, B connected to a first heat source, said first profile 2 comprising an internal wall 4 and an external wall 5, a second heat exchanger, forming a so-called hot part, comprising a second hollow profile 8 including second circulation means 9 of at least one suitable heat transfer fluid intended to be connected to a second heat transfer fluid supply circuit C, D connected to a second heat source, said second profile 8 comprising an internal wall 10 and an external wall 11, a third hollow profile 15 suitable and intended to be connected to at least one supply circuit of at least one working fluid J, H,said third profile 15 being disposed inside the first profile 2 and the second profile 8, said third profile 15 comprising an internal wall 16 and an external wall 17, at least a part of the internal wall 4 of the first profile 2 and a first part 20 of the external wall 17 of the third profile 15 being spaced and situated opposite each other so as to form a first filling space 21, at least a part of the internal wall 10 of the second profile 8 and a second part 22 of the external wall 17 of the third profile 15 being spaced and situated opposite each other so as to form a second filling space 23, at least one chamber 24 suitable and intended to contain at least one thermodynamic fluid preferably at high pressure and in a supercritical state, said chamber 24 comprising at least the first filling space 21 and the second filling space 23 which are communicating,at least one displacer 25 disposed inside said chamber 24 and mounted to slide relative to the external wall 17 of said third profile 15 and movable between a first position P1 and a second position P2, and configured to alternately displace said at least one thermodynamic fluid between the first filling space 21 and the second filling space 23, a piston 26 disposed inside said third profile 15 and mounted to slide relative to the internal wall 16 of said third profile 15 and movable between the first position P1 and the second position P2, the piston 26 being suitable and intended to be moved by said at least one working fluid J, H between the first position P1 and the second position P2, the displacer 25 and the piston 26 being coupled to each other.

[0018] Advantageously, the cartridge configuration 1, 1' provides a modular and scalable solution. Furthermore, the first profile 2 and the second profile 8 provide large internal and external heat exchange surfaces, contributing to the efficiency of heat transfer between the heat transfer fluid and the thermodynamic fluid. In addition, the first profile 2 and the second profile 8 can be produced at very low cost. The chamber 24, which is pressurized for pressures preferably between 50 bar and 300 bar, and preferably between 80 bar and 250 bar, and which contains the displacer 25, is closed to the low-pressure environment. The low-pressure environment corresponds to pressures preferably between 0 bar and 50 bar, and preferably between 0 bar and 10 bar. The displacer 25 is thus controlled from outside the chamber 24, via the movement of the piston 26.In addition to its function of displacing the thermodynamic fluid, the displacer 25 can also perform a regenerator function, since the thermodynamic fluid flows around the displacer 25 during its movement between the first position P1 and the second position P2. Furthermore, the displacer 25 can be heated or cooled by the heat transfer fluid alone when it is stationary in the first position P1 or the second position P2.

[0019] As illustrated in particular by the figure 1 The first heat transfer fluid supply circuit A, B and the second heat transfer fluid supply circuit C, D provide the external heat necessary for the operation of the heat engine, preferably by ensuring a temperature difference between the so-called cold part and the so-called hot part. figure 1 Figure 1 represents the cartridge with the displacer 25 and the piston 26 in the first position P1. In this configuration, the thermodynamic fluid is confined between the first profile 2 and the third profile 15 and is therefore located in the first filling space 21, in contact with the temperature of the first heat transfer fluid supply circuit A, B. The second position P2 of the displacer 25 and the piston 26 is represented by a dashed line, in which the thermodynamic fluid is confined between the second profile 8 and the third profile 15 and is therefore located in the second filling space 23, in contact with the temperature of the second heat transfer fluid supply circuit C, D.The change from the first position P1 to the second position P2 or vice versa, is controlled by the piston 26 preferably by means of a relative pressure between points H and J which allows the thermodynamic fluid to be moved between the first filling space 21 and the second filling space 23. Preferably, a thermodynamic fluid supply outlet G connected to the chamber 24 of said at least one cartridge 1 allows the strong pressure differences generated inside the cartridge 1 to be exploited for their energy.

[0020] Chamber 24 allows for the reception of a thermodynamic fluid under pressure, for example, greater than 10 bar, but ideally above or equal to its critical pressure, so as to have a greatly improved convective heat transfer compared to a gas near atmospheric pressure. The improvement is typically one to two orders of magnitude, namely 100 to 1000 [W / m².K] instead of 10 [W / m².K]. As illustrated by the figure 2 The second filling space 23, which contains the thermodynamic fluid under high pressure, is located between the third profile 15 and the second profile 8. In this second filling space 23, the thermodynamic fluid is preferably maintained in a supercritical state. The thermodynamic fluid can be carbon dioxide; this example is not limiting. As illustrated by the figures 7 , 8 And 9, the first filling space 21 which allows the thermodynamic fluid to be contained under high pressure, that is to say for pressures preferably between 50 bars and 300 bars preferably between 80 bars and 250 bars, is located between the third profile 15 and the first profile 2. In this first filling space 21 the thermodynamic fluid is preferably maintained in a supercritical state.

[0021] Preferably, the first profile 2 and / or the second profile 8 is made of a material with high thermal conductivity, preferably between 100 Watts per meter-Kelvin and 400 Watts per meter-Kelvin, for example an aluminum or copper alloy.

[0022] Advantageously, this property of the first profile 2 and / or the second profile 8 contributes to the efficiency of heat transfers between the heat transfer fluid and the thermodynamic fluid.

[0023] Preferably, the third profile 15 is preferably made of non-magnetic material and the displacer 25 and the piston 26 are magnetically coupled to each other through the third profile 15 by magnetic linkage means 27.

[0024] Advantageously, this configuration allows control of the displacer 25 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. This avoids prohibitive losses and wear due to friction. This arrangement thus helps to limit losses.

[0025] Non-magnetic means a material that does not have magnetic properties or whose magnetic permeability is low, i.e. for example close to 1 and generally less than 50.

[0026] For example, the third profile 15 is made of stainless steel.

[0027] For example, the piston 26 includes one or more permanent magnets 32 and the displacer 25 includes one or more permanent magnets 33, said permanent magnets 32, 33 forming said magnetic bonding means 27.

[0028] Preferably, and as illustrated by the figures 1 , 3 And 4 , said first profile 2 extends longitudinally over a first length L1 along an axis A1 and said second profile 8 extends longitudinally along the axis A1 over a second length L2.

[0029] Preferably, said second profile 8 is in line with the first profile 2 along the direction of axis A1.

[0030] For example, the first length L1 is equal to the second length L2, so as to allow symmetry of the cartridge according to the joining means 14 described below, as illustrated by the figures 1 ,3 And 4 .

[0031] Preferably, said first profile 2 comprises a first end 6 and a second joining end 7, said second profile 8 comprises a first end 12 and a second joining end 13, and the first profile 2 and the second profile 8 are joined to each other by joining means 14 at their respective second joining ends 7, 13.

[0032] Advantageously, the first profile 2 and the second profile 8 are distinct from each other to avoid heat transfers, while being connected to each other by the joining means 14. It results that the first exchanger and the second exchanger are mounted opposite each other on the joining means 14.

[0033] In a first embodiment of the invention illustrated in the figure 3 and in a second embodiment of the invention illustrated in the figure 4 , the second junction ends 7, 13 on the one hand are configured to allow junction with junction means 14 and on the other hand include at least one opening leading to the first / second means of circulation 3, 9.

[0034] Preferably, the joining means 14 have a thermal conductivity lower than the thermal conductivity of said first profile 2 and / or second profile 8.

[0035] Advantageously, the joining means 14 allow the first profile 2 and the second profile 8 to be thermally separated.

[0036] Preferably, the joining means 14 comprise at least one thermal insulating material arranged at least to thermally insulate said first profile 2 from said second profile 8 or vice versa.

[0037] Advantageously, this configuration allows for better insulation between the so-called cold part and the so-called hot part of cartridge 1, 1'.

[0038] For example, and as illustrated by the figure 15 , the joining means 14 may consist of a joining plate 39 which may be covered on each face with a layer of insulating material.

[0039] Preferably, and as illustrated by the figures 2 , 7 , 8 And 9 , said third profile 15, said first profile 2 and said second profile 8, the displacer 25 and the piston 26 are coaxial along said axis A1.

[0040] Advantageously, this configuration allows for the definition of an annular chamber 24. The third profile 15 is thus arranged concentrically on a diameter smaller than the first profile 2 and the second profile 8.

[0041] Preferably, the third profile 15 extends longitudinally along said axis A1 over a third length L3, said third length L3 being greater than the first length L1 or the second length L2 and preferably greater than or equal to the sum of the first length L1 and the second length L2.

[0042] Advantageously, in this arrangement, the third profile 15 passes through the so-called cold part and the so-called hot part of the cartridge 1, 1' over a length L3 as defined previously. It follows that the displacer 25 can be moved alternately between the so-called cold part and the so-called hot part by sliding at least along a portion of the third length L3 of the third profile 15.

[0043] For example, the third profile 15 is a hollow tube of cylindrical shape.

[0044] Preferably, the third profile 15 comprises a first end 18 and a second end 19, the first end 6 of the first profile 2 and the first end 18 of the third profile 15 are joined by connecting means, and the first end 12 of the second profile 8 and the second end 19 of the third profile 15 are joined by connecting means.

[0045] In the first embodiment of the invention illustrated in the figure 3 and in the second embodiment of the invention illustrated in the figure 4 The first end 6 of the first profile 2 and the first end 18 of the third profile 15 are fixed to each other, for example, by crimping, brazing, joining, or by one or more additional elements. The first end 6 of the first profile 2 has a conical shape; this example is not limiting. Similarly, the first end 12 of the second profile 8 and the second end 19 of the third profile 15 are fixed to each other, for example, by crimping, brazing, joining, or by one or more additional elements. The first end 12 of the second profile 8 has a conical shape; this example is not limiting.

[0046] Preferably, the cartridge 1, 1' comprises a first radial and / or axial stress reinforcement piece 28 in which the first profile 2 is clamped and a second radial and / or axial stress reinforcement piece 29 in which the second profile 8 is clamped.

[0047] The first reinforcing piece 28 and the second reinforcing piece 29 allow for the absorption of radial and / or axial pressure forces, thereby minimizing the first thickness E1 of the first profile 2 and the second thickness E2 of the second profile 8 in order to bring the heat transfer fluid as close as possible to the thermodynamic fluid. These pressure forces are due to the pressure of the thermodynamic fluid contained in the chamber 24, which is exerted on the first and second profiles 2 and 8.

[0048] The assembly of the first reinforcement piece 28 to the first profile 2 and the assembly of the second reinforcement piece 29 to the second profile 8 can be done by an assembly process which ensures zero radial play between the two pieces: pressing / shrunking / gluing / forming the tube by rolling or shrinking.

[0049] There figure 2 illustrates the transfer of radial forces by the second reinforcement piece 29 in order to minimize the second thickness E2 of the second profile 8.

[0050] Figures 7, 8 and 9 illustrate the transfer of radial forces by the first reinforcing piece 28 in order to minimize the first thickness E1 of the first profile 2.

[0051] As shown in the first variant of the embodiment illustrated in the figure 3 and the second variant of the implementation illustrated at the figure 4 The first reinforcing piece 28 or the second reinforcing piece 29 may include a band. Preferably, the first reinforcing piece 28 and the second reinforcing piece 29 have a hollow cylindrical shape.

[0052] Advantageously, the first profile 2 and the second profile 8 are each assembled without play in the band. The radial forces are absorbed by the band.

[0053] The band can itself be fixed on one side to the first end 6, 12 of the first / second profile 2, 8 and on the other side be fixed to the joining means 14.

[0054] As shown in the second variant of the embodiment illustrated in the figure 4 , the first reinforcement piece 28 or the second reinforcement piece 29 may in addition to the banding include a flange 51 held by fastening means 52 to the first / second profile 2, 8.

[0055] The axial forces are taken up by the flange, which is particularly important for a 1,1' cartridge whose diameter is preferably between 20 millimeters and 120 millimeters.

[0056] The flange 51 can also form a first / second separating wall 48, 49 described below.

[0057] In the case of the first variant of the implementation of the figure 3 , the first reinforcement piece 28 or the second reinforcement piece 29 includes only the band and the axial forces are taken up by the first / second profile 2, 8 and the third profile 15.

[0058] Preferably and generally, the first reinforcing piece 28 and / or the second reinforcing piece 29 and / or the first profile 2 and / or the second profile 8 and / or the third profile 15 is arranged to take up axial forces.

[0059] For example, the first thickness E1 of the first profile 2 and / or the second thickness E2 of the second profile 8 is between 1 millimeter and 15 millimeters, preferably between 2 millimeters and 6 millimeters.

[0060] Preferably, the internal wall 4 of the first profile 2 and / or the internal wall 10 of the second profile 8 has a serrated surface ( figures 7 , 8 And 9 ) and / or a smooth surface ( figure 2 ).

[0061] As illustrated by the figure 2 , the smooth contact surface between the second profile 8 and the thermodynamic fluid is at its simplest with a tubular geometry.

[0062] Advantageously, when the inner wall 4 and / or the inner wall 10 has a crenellated surface ( figure 7 , 8 And 9 ) then the surface area is increased compared to a smooth surface ( figure 2 ) and heat exchange is improved. Thus, at the interface between the first profile 2 and / or the second profile 8 and the thermodynamic fluid, the exchange surface is extended.

[0063] Preferably, said first profile 2 has a first thickness E1 between the inner wall 4 and the outer wall 5 and the first profile 2 includes in its first thickness E1 at least one channel 30 and / or at least one groove 31 forming said first means of circulation 3, said at least one channel 30 and / or at least one groove 31 extending in a longitudinal direction parallel to the axis A1 and over a length L4.

[0064] Advantageously, at least one channel 30 and / or at least one groove 31 allows the heat transfer fluid to circulate in the first heat exchanger. Channel 30 provides a substantial exchange surface between the heat transfer fluid and the first profile 2. This configuration helps to maximize heat transfer.

[0065] Preferably, said second profile 8 has a second thickness E2 between the inner wall 10 and the outer wall 11 and the second profile 8 includes in its second thickness E2 at least one channel 30 and / or at least one groove 31 forming said second means of circulation 9, said at least one channel 30 and / or at least one groove 31 extending in a longitudinal direction parallel to the axis A and over a length L5.

[0066] Advantageously, at least one channel 30 and / or at least one groove 31 allows the heat transfer fluid to circulate in the second heat exchanger. Channel 30 provides a substantial exchange surface between the heat transfer fluid and the second profile 8. This configuration helps to maximize heat transfer.

[0067] Preferably, said at least one channel 30 has a square, rectangular, or trapezoidal cross-section ( figure 8 ) or circular ( figure 7 ).

[0068] Said at least one groove 31 can be opened ( figures 2 And 3 ).

[0069] Said at least one channel 30 and / or at least one groove 31 may be straight or helical.

[0070] Preferably, according to a first possibility, the cross-section of the displacer 25 is smaller than the cross-section of the chamber 24 so as to provide respectively a clearance J1 between the displacer 25 and the internal wall 4 of the first profile 2 or a clearance J2 between the displacer 25 and the internal wall 10 of the second profile 8 ( figures 2 , 7 , 8 And 9 ).

[0071] This J1, J2 set advantageously ensures the passage of the thermodynamic fluid during the movement of the displacer 25. At each passage of the thermodynamic fluid, a part of the heat of the latter is transferred to the displacer 25 to perform the regeneration function.

[0072] Preferably, said J1, J2 clearance is between 0.05 millimeters and 5 millimeters, preferably between 0.1 millimeters and 1 millimeter.

[0073] According to a second possibility, the cross-section of the displacer 25 is equal to the cross-section of the chamber 24 and the displacer 25 is at least partly in a porous material.

[0074] The porosity of the displacer 25 advantageously ensures the passage of the thermodynamic fluid during the movement of the displacer 25. With each passage of the thermodynamic fluid, a part of the heat of the latter is transferred to the displacer to perform the regeneration function.

[0075] Preferably, the section of chamber 24 is annular in shape and the section of displacer 25 is annular in shape ( figure 2 ).

[0076] Thus the section of chamber 24 and the section of displacer 25 are identical and dead volumes are thus minimized.

[0077] Preferably, the displacer 25 conforms to the shape of the internal wall 4 of the first profile 2 and / or the internal wall 10 of the second profile 8 ( figures 7 And 8 ).

[0078] Preferably, piston 26 is a low-pressure piston. The low-pressure environment corresponds to pressures preferably between 0 bar and 50 bar, and preferably between 0 bar and 10 bar.

[0079] According to a third embodiment of the invention illustrated in the figure 10 said cartridge 1' is said to be hybrid and further comprises a hydraulic piston 34 disposed inside the first filling space 21 or the second filling space 23 of said chamber 24, the first filling space 21 or the second filling space 23 being suitable and intended to contain at least one hydraulic fluid and being suitable and intended to be connected to a supply outlet of a hydraulic fluid E and said hydraulic piston 34 is mounted sliding along the direction of the axis A1 relative to the external wall 17 of said 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 on the one hand to be moved by said at least one thermodynamic fluid and to alternately move said at least one hydraulic fluid in the first filling space 21 or the second filling space 23.

[0080] Advantageously, as illustrated by the figure 10 , it is possible to associate a hydraulic piston 34 with a cartridge geometry 1 described previously in order to maintain a certain symmetry with respect to the junction plate 39.

[0081] The distinctive feature of this configuration is that the displacer 25 follows the position of the hydraulic piston 34 while being held against it during the cooling phases. The hydraulic piston 34 moves only within one of the two thermal zones, either the hot zone or the cold zone. The hydraulic piston 34 represents the physical interface between the thermodynamic fluid and the hydraulic fluid and does not need to be completely sealed if, for example, the fluids are immiscible and insoluble. This configuration simplifies the integration of the hydraulic piston(s) 34 when the system is used in a module as detailed below.

[0082] According to a fourth alternative variant of the invention illustrated in the figure 11 The chamber 24 of the cartridge 1 is suitable and intended to be connected to a hydraulic piston 34, which is itself suitable and intended to be connected to a hydraulic fluid supply circuit E. Preferably, a thermodynamic fluid supply outlet G connected to the chamber 24 of at least one cartridge 1 can be connected to the hydraulic piston 34, which ensures the pressure transmission of the thermodynamic fluid to a hydraulic fluid, for example, oil, water, or an equivalent. The hydraulic piston 34 is preferably contained within a tube or cylinder. This hydraulic piston 34 is ideally kept at temperature by being supplied by the first / second heat source, for example, via the first / second supply circuit A, B / C, D. Advantageously, the thermodynamic fluid exiting the cartridge 1 continues to be cooled or heated, depending on whether the hydraulic piston 34 is supplied with a first / second heat source.Advantageously, the working fluid for the energy recovery system can be different from the thermodynamic fluid, thus avoiding the use of a turbine operating with a thermodynamic fluid in the supercritical phase. Similarly, one or more cartridges 1 can be connected to one or more hydraulic pistons 34. The hydraulic piston(s) 34 can be located outside or inside the module described below in order to centralize the heat supply.

[0083] The invention also relates to a module for the movement of a thermodynamic fluid alternately between a cold part connected to a first heat source and a hot part connected to a second heat source for a thermodynamic cycle heat engine, characterized in that it comprises at least one cartridge 1, 1' or a plurality of cartridges 1, 1' according to the invention and described above, and in that it comprises:a first heat transfer fluid supply circuit A, B connected to said first circulation means 3 of said 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 said second circulation means 9 of said 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, a junction plate 39 comprising at least said junction means 14 of cartridge 1, a working fluid supply circuit H, J, connected to said third profile 15 of said at least one cartridge 1 by at least one fifth supply port 40 comprising the third profile 15 and at least one sixth supply port 41 comprising the third profile 15,arranged to control the movement of the piston 26, a thermodynamic fluid supply outlet G connected to the chamber 24 of said at least one cartridge 1 or a hydraulic fluid supply outlet E connected to the first filling space 21 or to the second filling space 23 of said chamber 24. ,

[0084] Advantageously, the module can include one or more 1.1" cartridges depending on the desired power output of the thermal machine. The module size can be adapted to the number of 1.1" cartridges to be integrated for a target thermal machine power output.

[0085] In the example illustrated in the figure 12 The module includes a single cartridge 1.

[0086] In the example illustrated in figures 18 And 19 The module includes six cartridges 1.

[0087] Preferably, the module includes at least one cartridge 1' described above, called hybrid, comprising a hydraulic piston 34 disposed inside the first filling space 21 or the second filling space 23 of said chamber 24.

[0088] In the example illustrated in the figure 13 The module includes a single cartridge, known as a hybrid 1'. Compared to the module of the figure 12 Without a hydraulic piston, the exchange surface is no longer symmetrical between the hot and cold parts.

[0089] In the example illustrated in the figure 14 The module includes a cartridge 1 and a so-called hybrid cartridge 1'. Compared to the module of the figure 12 Without a hydraulic piston, the heat exchange surface is no longer symmetrical between the hot and cold parts. This lack of symmetry can be partially compensated for in the multi-cartridge module 1, 1' by using a ratio of one so-called hybrid cartridge 1' combined with several basic cartridges 1 without a hydraulic piston 34. The hydraulic piston 34 of the so-called hybrid cartridge 1' then takes over the expansion of several cartridges 1 without a hydraulic piston 34.

[0090] For example, and as shown by figures 16 And 17 , the module integrates six 1, 1' cartridges with a ratio of two 1 cartridges without hydraulic piston 34 for one 1' cartridge called hybrid.

[0091] Preferably, the module comprises two insulating enclosures separated by the junction plate 39 and receiving at least part of said at least one cartridge 1, 1' or a plurality of cartridges 1, 1'.

[0092] The two insulating enclosures can be delimited by one or more casings.

[0093] Advantageously, each insulating enclosure is directly supplied by the first or second heat source, which allows the said at least one cartridge 1,1' or a plurality of cartridges 1,1' to be supplied in a central manner with heat transfer fluid instead of having to supply each cartridge 1,1' individually.

[0094] The size of the two insulating enclosures can be adapted to the number of 1, 1' cartridges to be integrated for a targeted power of the thermal machine.

[0095] Preferably, the working fluid supply circuit H, J is formed by said first heat transfer fluid supply circuit A, B and said second heat transfer fluid supply circuit C, D.

[0096] In this case, the working fluid supply source H, J at the fifth supply port 40 is identical to that of the first heat transfer fluid supply circuit A, B, just as the working fluid supply source at the sixth supply port 41 is identical to that of the second heat transfer fluid supply circuit C, D. It follows that the relative pressure difference between the first heat transfer fluid supply circuit A, B and the second heat transfer fluid supply circuit C, D allows the piston 26 to be actuated.

[0097] Preferably and alternatively, the working fluid supply circuit H, J is separate from said first heat transfer fluid supply circuit A, B and said second heat transfer fluid supply circuit C, D ( figures 18 And 19 ).

[0098] Preferably, the junction plate 39 has a thermal conductivity lower than the thermal conductivity of said first profile 2 and / or second profile 8.

[0099] Advantageously, the junction plate 39 has a thermal separation function.

[0100] Preferably, the junction plate 39 is made of steel-type metal.

[0101] Preferably, the first reinforcement piece 28 and the second reinforcement piece 29 are fixed respectively to the junction plate 39.

[0102] Preferably, and as illustrated by the figures 12 , 13 And 14The module comprises a first insulating enclosure 43 which includes at least a first compartment 44 into which opens said at least a first supply port 35 of the first circulation means 3 and at least a second compartment 45 into which opens said at least a second supply port 36 of the first circulation means 3

[0103] Preferably additionally or alternatively, and as illustrated by the figures 12 , 13 And 14 , the module includes a second insulating enclosure 43' which includes at least a third compartment 46 into which opens said at least a third supply port 37 of the second means of circulation 9 and at least a fourth compartment 47 into which opens said at least a fourth supply port 38 of the second means of circulation 9.

[0104] Preferably, the second reinforcement piece 29 includes said third supply port 37 and said fourth supply port 38 of the second means of circulation 9.

[0105] It follows that the first insulating enclosure 43 includes a so-called cold part of the cartridge 1, 1' and is intended to receive the heat transfer fluid from the first heat source to supply the first heat transfer fluid supply circuit A, B. It follows that the second insulating enclosure 43' includes a so-called hot part of the cartridge 1, 1' and is intended to receive the heat transfer fluid from the second heat source to supply the second heat transfer fluid supply circuit C, D.

[0106] Preferably, the junction plate 39 separates the first speaker 43 from the second speaker 43'.

[0107] Preferably, the first reinforcement piece 28 includes said first supply port 35 and said second supply port 36 of the first means of circulation 3.

[0108] This configuration allows the first / second reinforcement piece 28, 29 and the first / second profile 2, 8 to be immersed in the heat transfer fluid.

[0109] The first compartment 44 and the second compartment 45 are preferably delimited by at least one first separating wall 48.

[0110] The third compartment 46 and the fourth compartment 47 are preferably delimited by at least a second separating wall 49.

[0111] The first separating wall 48 and / or the second separating wall 49 act as hydraulic seals and preferentially do not support high mechanical stresses.

[0112] The first separating wall 48 and / or the second separating wall 49 are preferably made of plastic or elastomer materials, these examples are not limiting.

[0113] The first supply port 35 and the second supply port 36 are arranged on either side of the first separating wall 48, which ensures that the flow of the heat transfer fluid between A and B takes place inside the first reinforcing piece 28 between it and the first profile 2, and not outside the first reinforcing piece 28.

[0114] The third supply port 37 and the fourth supply port 38 are arranged on either side of the first separating wall 48, which ensures that the flow of the heat transfer fluid between C and D takes place inside the second reinforcing piece 29 between it and the second profile 8, and not outside the second reinforcing piece 29.

[0115] Preferably, said at least one fifth supply port 40 of the working fluid supply circuit H, J opens into the first compartment 44 and said at least one sixth supply port 41 of the working fluid supply circuit H, J opens into the third compartment 46.

[0116] In this case, the working fluid supply source H, J at the fifth supply port 40 is identical to that of the first heat transfer fluid supply circuit A, B, just as the working fluid supply source at the sixth supply port 41 is identical to that of the second heat transfer fluid supply circuit C, D.

[0117] As illustrated by the figure 14, the module may comprise at least two cartridges 1, 1' and the chambers 24 of each cartridge 1 are connected to each other by at least one interconnecting conduit 50, preferably disposed in said at least one junction plate 39 and the thermodynamic fluid supply outlet G of the module or the hydraulic fluid supply outlet E of the module is preferably disposed in said junction plate 39.

[0118] Advantageously, said at least one interconnecting conduit 50 allows interconnection of each chamber 24 of each cartridge 1, 1'.

[0119] The invention also relates to a suitable heat engine intended to carry out at least one conversion of thermal energy into mechanical energy comprising at least one thermodynamic fluid preferably in the supercritical state and suitable for implementing a thermodynamic cycle comprising at least one isochoric heating phase, optionally one isobaric heating phase, one expansion phase and one isobaric cooling phase, the heat engine comprising at least one module according to the invention described above.

[0120] Of course, the invention is not limited to the embodiments described and shown in the accompanying drawings. Modifications remain possible, particularly with regard to the composition of the various elements or by substitution of technical equivalents, without departing from the scope of protection of the invention as defined by the claims.

Claims

1. Cartridge (1, 1') for moving a thermodynamic fluid between a cold part connected to a first heat source and a hot part connected to a second heat source for a thermodynamic cycle thermal machine, characterised in that it comprises at least : - a first exchanger, forming a so-called cold part, comprising a first hollow section (2) comprising first means (3) for circulating at least one heat transfer fluid, which means are suitable for and intended to be connected to a first heat transfer fluid supply circuit (A, B) connected to a first heat source, said first section (2) comprising an internal wall (4) and an external wall (5), - a second exchanger, forming a so-called hot part, comprising a second hollow section (8) comprising second means (9) for circulating at least one heat transfer fluid, suitable and intended for connection to a second heat transfer fluid supply circuit (C, D) connected to a second heat source, the said second section (8) comprising an inner wall (10) and an outer wall (11), - a third hollow section (15) adapted and intended to be connected to at least one circuit for supplying at least one working fluid (J, H), said third section (15) being disposed inside the first section (2) and the second section (8), said third section (15) comprising an inner wall (16) and an outer wall (17), at least part of the inner wall (4) of the first profile (2) and a first part (20) of the outer wall (17) of the third profile (15) being spaced apart and facing each other so as to form a first filling space (21), at least part of the inner wall (10) of the second profile (8) and a second part (22) of the outer wall (17) of the third profile (15) being spaced apart and facing each other so as to form a second filling space (23), - at least one chamber (24) adapted and designed to contain at least one thermodynamic fluid preferably at high pressure and in the supercritical state, said chamber (24) comprising at least the first filling space (21) and the second filling space (23) which are in communication, - at least one displacer (25) disposed inside said chamber (24) and slidably mounted relative to the outer wall (17) of said third profile (15) and movable between a first position (P1) and a second position (P2), and configured to displace said at least one thermodynamic fluid alternately between the first filling space (21) and the second filling space (23), - a piston (26) disposed inside said third profile (15) and slidably mounted relative to the inner wall (16) of said third profile (15) and movable between the first position (P1) and the second position (P2), the piston (26) being adapted and intended to be displaced by said at least one working fluid (J, H) between the first position (P1) and the second position (P2), the displacer (25) and the piston (26) being coupled to each other.

2. Cartridge according to claim 1, characterized in that the third profile (15) is preferably made of non-magnetic material and in that the displacer (25) and the piston (26) are magnetically coupled to one another through the third profile (15) by magnetic connection means (27).

3. Cartridge according to any one of claims 1 to 2, characterized in that the said first profile (2) extends longitudinally over a first length L1 along an axis A1 and in that the said second profile (8) extends longitudinally along the axis A1 over a second length L2, and the said second profile (8) is in the prolongation of the first profile (2) in the direction of the axis A1.

4. Cartridge according to claim 3, characterised in that the third profile (15) extends longitudinally along said axis A1 over a third length L3, said third length L3 being greater than the first length L1 or the second length L2 and preferably greater than or equal to the sum of the first length L1 and the second length L2.

5. Cartridge according to any one of claims 1 to 4, characterized in that the said first profile (2) comprises a first end (6) and a second joining end (7), in that the said second profile (8) comprises a first end (12) and a second joining end (13), and in that the first profile (2) and the second profile (8) are joined to each other by joining means (14) at their respective second joining end (7, 13).

6. Cartridge according to the preceding claim, characterised in that said third profile (15) comprises a first end (18) and a second end (19), in that the first end (6) of the first profile (2) and the first end (18) of the third profile (15) are joined by connecting means, and in that the first end (12) of the second profile (8) and the second end (19) of the third profile (15) are joined by connecting means.

7. Cartridge according to any one of claims 1 to 6, characterised in that said third profile (15), said first profile (2) and said second profile (8), the displacer (25) and the piston (26) are coaxial along said axis A1.

8. Cartridge according to any one of claims 1 to 7, characterised in that it comprises a first radial and / or axial stress-reinforcing part (28) in which the first profile (2) is clamped and a second radial and / or axial stress-reinforcing part (29) in which the second profile (8) is clamped.

9. Cartridge according to any one of claims 5 to 8, characterised in that the joining means (14) have a thermal conductivity lower than the thermal conductivity of the said first profile (2) and / or of the second profile (8).

10. Cartridge according to any one of claims 1 to 9, characterized in that the said cartridge (1') is called hybrid and comprises a hydraulic piston (34) arranged inside the first filling space (21) or the second filling space (23) of the said chamber (24), the first filling space (21) or the second filling space (23) being capable of and intended to contain at least one hydraulic fluid and being capable of and intended to be connected to a hydraulic fluid supply outlet (E), and in that the said hydraulic piston (34) is mounted so as to slide in the direction of the axis A1 relative to the outer wall (17) of the said 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 firstly to be displaced by said at least one thermodynamic fluid and secondly to displace alternately said at least one hydraulic fluid in the first filling space (21) or the second filling space (23).

11. Cartridge according to any one of claims 1 to 10, characterised in that the first profile (2) and / or the second profile (8) is made of a material with high thermal conductivity, preferably between 100 Watts per metre-Kelvin and 400 Watts per metre-Kelvin, for example an aluminium or copper alloy.

12. Module for moving a thermodynamic fluid alternately between a cold part connected to a first heat source and a hot part connected to a second heat source for a thermodynamic cycle thermal machine, characterised in that it comprises at least one cartridge (1, 1') or a plurality of cartridges (1, 1') according to any one of claims 1 to 11, and in that it comprises : - a first heat transfer fluid supply circuit (A, B) connected to said first circulation means (3) of said at least one cartridge (1, 1') via at least one first supply orifice (35) and at least one second supply orifice (36) of the first circulation means (3), - a second heat transfer fluid supply circuit (C, D) connected to said second circulation means (9) of said at least one cartridge (1) via at least one third supply orifice (37) and at least one fourth supply orifice (38) of the second circulation means (9), - a connection plate (39) comprising at least the said connection means (14) for the cartridge (1), - a working fluid supply circuit (H, J), connected to said third section (15) of said at least one cartridge (1) by at least one fifth supply orifice (40) which the third section (15) comprises and at least one sixth supply orifice (41) which the third section (15) comprises, arranged to pilot the movement of the piston (26), - a thermodynamic fluid supply outlet (G) connected to the chamber (24) of said at least one cartridge (1) or a hydraulic fluid supply outlet (E) connected to the first filling space (21) or to the second filling space (23) of said chamber (24).

13. Module according to the preceding claim, characterised in that a first insulating enclosure (43) comprises at least one first compartment (44) into which opens said at least one first supply orifice (35) of the first circulation means (3) and at least one second compartment (45) into which opens said at least one second supply orifice (36) of the first circulation means (3) and / or in that a second insulating enclosure (43') comprises at least one third compartment (46) into which opens said at least one third supply orifice (37) of the second circulation means (9) and at least one fourth compartment (47) into which opens said at least one fourth supply orifice (38) of the second circulation means (9), and in that the said at least one fifth supply orifice (40) of the working fluid supply circuit (H, J) opens into the first compartment (44) and in that the said at least one sixth supply orifice (41) of the working fluid supply circuit (H, J) opens into the third compartment (46).

14. Module according to any one of claims 12 to 13, characterised in that the junction plate (39) has a lower thermal conductivity than the thermal conductivity of said first profile (2) and / or of the second profile (8).

15. Module according to any one of claims 12 to 14, characterised in that the module comprises at least two cartridges (1, 1') and in that the chambers (24) of each cartridge (1) are connected together by at least one interconnecting pipe (50).

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