WO2022194877A1 - Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé - Google Patents
Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé Download PDFInfo
- Publication number
- WO2022194877A1 WO2022194877A1 PCT/EP2022/056723 EP2022056723W WO2022194877A1 WO 2022194877 A1 WO2022194877 A1 WO 2022194877A1 EP 2022056723 W EP2022056723 W EP 2022056723W WO 2022194877 A1 WO2022194877 A1 WO 2022194877A1
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- WIPO (PCT)
- Prior art keywords
- section
- profile
- cartridge
- filling space
- piston
- Prior art date
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- 239000012530 fluid Substances 0.000 claims abstract description 101
- 239000013529 heat transfer fluid Substances 0.000 claims abstract description 50
- 230000003014 reinforcing effect Effects 0.000 claims description 29
- 238000005304 joining Methods 0.000 claims description 5
- 239000000463 material Substances 0.000 claims description 4
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 2
- 239000000696 magnetic material Substances 0.000 claims description 2
- 239000002826 coolant Substances 0.000 claims 2
- 229910000838 Al alloy Inorganic materials 0.000 claims 1
- 229910000881 Cu alloy Inorganic materials 0.000 claims 1
- 238000006073 displacement reaction Methods 0.000 abstract description 5
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 5
- 229910002092 carbon dioxide Inorganic materials 0.000 description 4
- 239000001569 carbon dioxide Substances 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 239000002918 waste heat Substances 0.000 description 3
- 238000005219 brazing Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000002788 crimping Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 239000000945 filler Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000011810 insulating material Substances 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000008929 regeneration Effects 0.000 description 2
- 238000011069 regeneration method Methods 0.000 description 2
- 230000002787 reinforcement Effects 0.000 description 2
- 230000009466 transformation Effects 0.000 description 2
- 238000000844 transformation Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000011031 large-scale manufacturing process Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000000135 prohibitive effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000002436 steel type Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/32—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/103—Carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G1/00—Hot gas positive-displacement engine plants
- F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
- F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
- F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
Definitions
- the present invention relates to the field of cartridges for thermal machine thermodynamic cycle and modules for thermal machine associated thermodynamic cycle.
- waste heat constitutes an enormous source of energy, directly available and already paid for, the recovery of which constitutes a strategic challenge for the industry.
- the recovery of waste heat can be done either by directly feeding heat networks or be temporarily stored, or be converted into electricity for internal or external use.
- Machines with external heat input and exploiting a working fluid in a closed cycle without phase change are generally called motors.
- Stirling More particularly, so-called beta or gamma type Stirling engines comprise a working piston and a displacer serving to transfer the working fluid alternately from the hot side to the cold side. In this type of engine, the engine piston and the displacer are mechanically linked.
- These motors are characterized by a very low power density and difficult power control because the speed of rotation depends mainly on the temperature difference of the sources.
- the rare machines on the market therefore require a large temperature difference between the heat sources, often of the order of several hundred degrees Celsius, to compensate for the low thermal conductivities of the working gases used, the low heat exchange surfaces heat and dead volumes of the regenerator.
- Publication WO2016/165687A1 also describes a heat conversion process with a supercritical cycle using carbon dioxide, in which the expansion takes place isothermally using an oscillator system.
- the piston oscillating which must be driven according to the stroke of the working piston, functions as an active agitator of the supercritical fluid during expansion to increase heat transfer by convection.
- the complexity of the construction due to the integration in each cylinder of the oscillator, a regenerator, pistons and a displacer makes this concept unattractive for large installations and large-scale production.
- the improvement in heat transfer by increasing convection in the cylinder is limited by the low contact surface of the cylinder with the heat sources. The concept is thus designed to operate with a temperature difference greater than 150 degrees Celsius.
- thermodynamic cycle A multi-cylinder external heat supply engine architecture is proposed in the publication WO02088536.
- the technique of "liquid" displacers implemented and the series connection of the pistons for the transfer of the thermodynamic fluid from one piston chamber to the other do not allow management of the position of the thermodynamic fluid independent of the working fluid, and therefore does not make it possible to optimize the thermodynamic cycle carried out.
- the present invention aims to provide a scalable and modular solution allowing the exploitation of heat sources whose temperature is less than 150 degrees Celsius.
- the invention relates to a cartridge 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 thermal machine with a thermodynamic cycle characterized in what it includes at least:
- a first exchanger forming a so-called cold part, comprising a first hollow profile comprising first means for circulating 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 exchanger forming a so-called hot part, comprising a second hollow profile comprising second means for circulation of 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 section suitable and intended to be connected to at least one circuit for supplying at least one working fluid, said third section being arranged inside the first section and the second section, said third section comprising an inner wall and an outer wall, [0018] at least a part of the internal wall of the first profile and a first part of the external wall of the third profile being spaced apart and located facing each other so as to form a first filling space,
- At least one displacer disposed inside said chamber and mounted to slide relative to the outer wall of said third section 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 internal wall of said third profile and movable between the first position and the second position, the piston being able and intended to be moved by said at least one fluid working between the first position and the second position,
- the invention also relates to a 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 thermal machine with a thermodynamic cycle characterized in that 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 orifice and at least one second supply orifice 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 orifice and at least one fourth supply orifice of the second circulation means
- a junction plate comprising at least said cartridge junction means
- a working fluid supply circuit connected to said third section of said at least one cartridge by at least one fifth supply orifice which comprises the third section and at least one sixth supply orifice which comprises the third profiled, arranged to control the movement of the piston,
- thermodynamic fluid supply outlet connected to the chamber of said at least one cartridge or a hydraulic fluid supply outlet connected to the first filling space or to the second filling space of said chamber.
- Figure 1 shows a sectional view of a cartridge according to the invention
- Figure 2 shows a cross-sectional view of the cartridge of Figure 1
- Figure 3 shows a sectional view of a cartridge according to a first variant embodiment of the invention
- Figure 4 shows a sectional view of a cartridge according to a second variant embodiment of the invention
- Figure 5 shows a perspective view of part of the cartridge according to the first embodiment of the invention
- FIG. 6 represents a perspective view of part of the cartridge according to the first variant embodiment of the invention
- FIG. 7 shows a cross-sectional view of the cartridge according to the invention showing circulation means in the form of channels of circular section,
- FIG. 8 shows a cross-sectional view of the cartridge according to the invention showing circulation means in the form of channels of trapezoidal section,
- Figure 9 shows a cross-sectional view of the cartridge according to the invention showing circulation means in the form of open grooves
- FIG. 10 represents a sectional view of a so-called hybrid cartridge in a third embodiment variant according to the invention
- FIG. 11 shows a sectional view of a cartridge according to figure 1 connected to a hydraulic piston according to a fourth variant of the invention
- Figure 12 shows a sectional view of a module comprising a cartridge according to Figure 1,
- figure 13 shows a sectional view of a module comprising a so-called hybrid cartridge according to figure 10,
- Figure 14 shows a sectional view of a module comprising a cartridge according to Figure 1 and a so-called hybrid cartridge according to Figure 10,
- figure 15 shows a junction plate
- FIG. 16 shows a sectional view of a module comprising four cartridges according to Figure 4 and two so-called hybrid cartridges according to the invention
- figure 17 shows a perspective view of the module of figure 16.
- FIG. 18 shows a sectional view of a module comprising six cartridges according to Figure 3,
- a 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 thermal machine with a thermodynamic cycle comprises at least:
- a first exchanger forming a so-called cold part, comprising a first hollow section 2 comprising first circulation means 3 of at least one heat transfer fluid suitable and 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 exchanger forming a so-called hot part, comprising a second hollow section 8 comprising second circulation means 9 of at least one heat-transfer fluid suitable and intended to be connected to a second heat-transfer fluid supply circuit C , D connected to a second heat source, 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 arranged inside the first section 2 and the second section 8, said third section 15 comprising an internal wall 16 and an external wall 17,
- At least one chamber 24 suitable and intended 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 communicators, [0057] at least one mover 25 disposed inside said chamber 24 and slidably mounted relative to the outer wall 17 of said third section 15 and movable between a first position P1 and a second position P2, and configured to alternately move said au least one thermodynamic fluid between the first filling space 21 and the second filling space 23,
- a piston 26 arranged 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 able 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 configuration in the form of a cartridge 1, 1′ makes it possible to provide a modular and scalable solution.
- the first section 2 and the second section 8 provide large internal and external exchange surfaces which contribute to the efficiency of heat transfer between the heat transfer fluid and the thermodynamic fluid.
- the first profile 2 and the second profile 8 can be produced at very low cost.
- the chamber 24 which is under pressure, for pressures preferably between 50 bars and 300 bars preferably between 80 bars and 250 bars and which contains the displacer 25 is closed with respect to the low pressure environment.
- the low pressure environment corresponds to pressures preferably between 0 bar and 50 bars and preferably between 0 bar and 10 bars.
- the control of the displacer 25 is thus done from outside the chamber 24, by means of the displacement of the piston 26.
- the displacer 25 can perform, in addition to its function of displacing the thermodynamic fluid, a function of regenerator since the fluid thermodynamic flows around the displacer 25 during the displacement between the first position P1 and the second position P2.
- the displacer 25 can be heated or cooled by means of the heat transfer fluid alone, when it is static in the first position P1 or in the second position P2.
- the first heat transfer fluid supply circuit A, B and the second heat transfer fluid supply circuit C, D make it possible to supply the external heat necessary for the operation of the thermal machine, preferably by providing a temperature difference between the so-called cold part and the so-called hot part.
- Figure 1 shows the cartridge 1 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 then in the first filling space 21, in contact with the temperature of the first heat transfer fluid supply circuit A, B.
- thermodynamic fluid is confined between the second section 2 and the third section 15 and is then 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 the points H and J which allows thus moving the thermodynamic fluid between the first filling space 21 and the second filling space 23.
- a thermal fluid supply outlet odynamic G connected to the chamber 24 of said at least one cartridge 1 makes it possible to exploit the high pressure differences generated inside the cartridge 1 to exploit the energy thereof.
- the chamber 24 makes it possible to receive a thermodynamic fluid which is under pressure, for example greater than 10 bars, but ideally above or equal to its critical pressure, so as to have a convective heat transfer greatly improved in comparison with a gas close to atmospheric pressure.
- the improvement is typically one to two orders of magnitude, namely 100 to 1000 [W/m 2 .K] instead of 10 [W/m 2 .K]
- the second space filling 23 which makes it possible to contain the thermodynamic fluid under high pressure is located between the third section 15 and the second section 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.
- the first filling space 21 which makes it possible to contain the thermodynamic fluid under high pressure, that is to say for pressures preferably between 50 bars and 300 bars preferably included between 80 bar and 250 bars, is located between the third section 15 and the first section 2.
- the thermodynamic fluid is preferably maintained in a supercritical state.
- 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 alloy of aluminum or copper.
- this property of the first profile 2 and/or of the second profile 8 contributes to the efficiency of heat transfer between the heat transfer fluid and the thermodynamic fluid.
- 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 connection means 27.
- this configuration allows control of the displacer 25 from the outside of the chamber 24 by means of a magnetic coupling between the piston 26 and the displacer 25.
- This magnetic coupling makes it possible to transmit radial forces to the displacer 25 without mechanical contact and therefore without friction. This avoids causing losses and prohibitive wear by friction. This arrangement thus contributes to limiting losses.
- non-magnetic is meant a material which does not have magnetic properties or whose magnetic permeability is low, i.e. for example close to 1 and generally less than 50.
- the third section 15 is made of stainless steel.
- the piston 26 comprises one or more permanent magnets 32 and the displacer 25 comprises one or more permanent magnets 33, said permanent magnets 32, 33 forming said magnetic connection means 27.
- said first section 2 extends longitudinally over a first length L1 along an axis A1 and said second section 8 extends longitudinally along axis A1 on a second length L2.
- said second section 8 is in the extension of the first section 2 in the direction of the axis A1.
- 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 in Figures 1, 3 and 4.
- said first section 2 comprises a first end 12 and a second junction end 13
- said second section 8 comprises a first end 6 and a second junction end 7, 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, 13.
- the first section 2 and the second section 8 are separate from each other to avoid heat transfer, while being connected to each other by the junction means 14. This results that the first exchanger and the second exchanger are mounted facing each other on the junction means 14.
- the second junction ends 7, 13 on the one hand are configured to allow the junction with the junction means 14 and on the other hand comprise at least one opening leading to the first/second circulation means 3, 9.
- the junction means 14 have a lower thermal conductivity than the thermal conductivity of said first profile 2 and/or second profile 8.
- junction means 14 make it possible to thermally separate the first profile 2 and the second profile 8.
- the junction means 14 comprise at least one heat insulating material arranged at least to thermally insulate said first profile 2 from said second profile 8 or vice versa.
- the junction means 14 may consist of a junction plate 39 which may be covered on each side with a layer of insulating material.
- 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.
- this configuration makes it possible to define a chamber 24 of annular shape.
- the third profile 15 is thus arranged concentrically on a diameter smaller than the first profile 2 and the second profile 8.
- the third section 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.
- the third section 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 above. 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 over part of the third length L3 of the third section 15.
- the third section 15 is a hollow tube of cylindrical shape.
- 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.
- the first end 6 of the first section 2 and the first end 18 of the third profile 15 are fixed to one another, for example, by crimping, brazing, jointing or by one or more additional elements.
- the first end 6 of the first section 2 has a conical shape, this example is not limiting.
- the first end 12 of the second section 8 and the second end 19 of the third profile 15 are fixed to one another, for example, by crimping, brazing, jointing or by one or more additional elements.
- the first end 12 of the second section 8 has a conical shape, this example is not limiting.
- the cartridge 1, 1 comprises a first reinforcing part 28 of radial and/or axial stresses in which the first section 2 is clamped and a second reinforcing part 29 of radial and/or axial stresses in which the second section 8 is clamped.
- the first reinforcing part 28 and the second reinforcing part 29 make it possible to absorb the radial and/or axial pressure forces, which makes it possible to minimize 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 are exerted on the first and second sections 2, 8.
- the assembly of the first reinforcing part 28 to the first profile 2 and the assembly of the second reinforcing part 29 to the second profile 8 can be done by an assembly process which ensures zero radial play between the two parts: pressing/shrinking/bonding/forming the tube by rolling or shrinking.
- Figure 2 illustrates the take-up of radial forces by the second reinforcing part 29 in order to minimize the second thickness E2 of the second profile 8.
- Figures 7, 8 and 9 illustrate the absorption of radial forces by the first reinforcing part 28 in order to minimize the first thickness E1 of the first section 2.
- the first reinforcing part 28 or the second reinforcing part 29 may comprise strapping.
- the first reinforcing part 28 and the second reinforcing part 29 have a hollow cylindrical shape.
- first profile 2 and the second profile 8 are each assembled without play in the strapping.
- the radial forces are taken up by the strapping.
- the strapping can itself be fixed on one side to the first end 6, 18 of the first/second section 2, 8 and on the other side be fixed to the joining means 14.
- the first reinforcing part 28 or the second reinforcing part 29 may, in addition to the strapping, comprise a flange 51 held by fastening means 52 to the first/second profile 2, 8.
- the axial forces are taken up by the flange which is particularly important for a cartridge 1, 1 'whose diameter is preferably between 20 millimeters and 120 millimeters.
- the flange 51 can also form a first/second dividing wall 48, 49 described below.
- the first reinforcing part 28 or the second reinforcing part 29 comprises only the strapping and the axial forces are taken up by the first / second section 2, 8 and the third section 15.
- the first reinforcing part 28 and/or the second reinforcing part 29 and/or the first profile 2 and/or the second profile 8 and/or the third profile 15 is arranged to axial forces.
- 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.
- the internal wall 4 of the first section 2 and/or the internal wall 10 of the second section 8 has a crenellated surface (FIGS. 7, 8 and 9) and/or a smooth surface (FIG. 2).
- the smooth contact surface between the second section 8 and the thermodynamic fluid is at its simplest with a tubular geometry.
- said first section 2 has a first thickness E1 between the internal wall 4 and the external wall 5 and the first section 2 comprises in its first thickness E1 at least one channel 30 and/or at least one groove 31 forming said first circulation means 3, said at least one channel 30 and/or at least one groove 31 extending along a longitudinal direction parallel to axis A1 and over a length L4.
- said at least one channel 30 and/or said at least one groove 31 allows the circulation of the heat transfer fluid in the first exchanger.
- said second profile 8 has a second thickness E2 between the internal wall 10 and the external wall 11 and the second profile 8 comprises in its second thickness E2 at least one channel 30 and/or at least one groove
- said at least one channel 30 and/or at least one groove 31 extending in a longitudinal direction parallel to axis A and over a length L5.
- said at least one channel 30 and/or said at least one groove 31 allows the circulation of the heat transfer fluid in the second exchanger.
- the channel 30 has a substantial exchange surface between the heat transfer fluid and the second section 8. This configuration contributes to maximizing heat transfer.
- said at least one channel 30 has a square or rectangular or trapezoidal section (Figure 8) or circular ( Figure 7).
- Said at least one groove 31 can be opened (FIGS. 2 and 3).
- Said at least one channel 30 and/or at least one groove 31 can be rectilinear or helical.
- the section of the displacer 25 is smaller than the section of the chamber 24 so as to provide a clearance respectively J1 between the displacer 25 and the internal wall 4 of the first section 2 or a clearance J2 between the displacer 25 and the internal wall 10 of the second section 8 (FIGS. 2, 7, 8 and 9).
- This clearance J1, J2 advantageously makes it possible to ensure the passage of the thermodynamic fluid during the displacement of the displacer 25. Each time the thermodynamic fluid passes, part of the heat of the latter is transferred to the displacer 25 to perform the function of regeneration.
- said clearance J1, J2 is between 0.05 millimeters and 5 millimeters, preferably between 0.1 millimeter and 1 millimeter.
- the section of the displacer 25 is equal to the section of the chamber 24 and the displacer 25 is at least partly in a porous material.
- the porosity of the displacer 25 advantageously makes it possible to ensure the passage of the thermodynamic fluid during the displacement of the displacer 25. Each time the thermodynamic fluid passes, part of the heat of the latter is transferred to the displacer to carry out the regeneration function. .
- the section of the chamber 24 is of annular shape and the section of the displacer 25 is of annular shape (FIG. 2).
- the displacer 25 follows the shape of the internal wall 4 of the first section 2 and/or the internal wall 10 of the second section 8 (FIGS. 7 and 8).
- the piston 26 is a low pressure piston.
- the low pressure environment corresponds to pressures preferably between 0 bar and 50 bars and preferably between 0 bar and 10 bars
- said cartridge 1′ is said to be hybrid and further comprises a hydraulic piston 34 arranged inside the first filling space 21 or the second filling space. filling 23 of said chamber 24, the first filling space 21 or the second filling space 23 being able and intended to contain at least one hydraulic fluid and being able and intended to be connected to a hydraulic fluid supply outlet E and said hydraulic piston 34 is mounted sliding in the direction of the axis A1 relative to the outer wall 17 of said third section 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.
- the particularity of this configuration is that the displacer 25 then follows the position of the hydraulic piston 34 while being held in abutment against the latter during the cooling phases.
- the hydraulic piston 34 only moves in one of the two thermal parts, either in the so-called hot part or in the so-called cold part.
- the hydraulic piston 34 represents the physical interface between the thermodynamic fluid and the hydraulic fluid and does not have to be completely sealed if, for example, the fluids are immiscible and not soluble with each other.
- This configuration makes it possible to simplify the integration of the hydraulic piston(s) 34 when the system is used in a module as detailed below.
- the chamber 24 of the cartridge 1 is suitable and intended to be connected to a hydraulic piston 34 suitable and intended to be connected to a supply circuit of a hydraulic fluid E.
- a thermodynamic fluid supply outlet G connected to the chamber 24 of said at least one cartridge 1 can be connected to the hydraulic piston 34 which ensures the transmission of pressure from the thermodynamic fluid to a hydraulic fluid for example oil or water or the like.
- the hydraulic piston 34 is preferably contained in a tube or cylinder This hydraulic piston 34 is ideally maintained at temperature by being supplied by the first/second heat source, for example via the first/second supply circuit A, B / C, D
- the thermodynamic fluid leaving the cartridge 1 continues to be cooled or heated, depending on whether the hydraulic piston 34 is supplied with a first/second heat source.
- the working fluid for the energy recovery system can be different from the thermodynamic fluid avoiding the use of a turbine operating with a thermodynamic fluid in the supercritical phase.
- one or more cartridge(s) 1 can(wind) be connected to one or more hydraulic piston(s) 34.
- the hydraulic piston(s) 34 can(wind) be outside the module described below or inside the module described below in order to centralize the heat supply.
- the invention also relates to a 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 thermal machine with a thermodynamic cycle characterized in that that it comprises at least one cartridge 1, 1' or a plurality of cartridges 1, 1' according to the invention and described previously, 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 orifice 35 and at least one second supply 36 of the first means of circulation 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 orifice 37 and at least one fourth supply orifice 38 of the second means of circulation 9,
- junction plate 39 comprising at least said junction means 14 of the 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 a fifth supply orifice 40 that comprises the third profile 15 and at least a sixth orifice supply 41 that comprises the third section 15, arranged to control the movement of the piston 26,
- the module may comprise one or more cartridges 1, 1' depending on the power of the desired thermal machine.
- the size of the module can be adapted to the number of cartridges 1, 1' to be integrated for a targeted power of the thermal machine.
- the module comprises a single cartridge 1.
- the module comprises six cartridges 1.
- the module comprises 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.
- the module comprises a single so-called 1' hybrid cartridge.
- the exchange surface is no longer symmetrical between the hot part and the cold part.
- the module comprises a cartridge 1 and a so-called hybrid cartridge 1'.
- the exchange surface is no longer symmetrical between the hot part and the cold part. This lack of symmetry can be partially compensated for in the 1.1′ multiple cartridge module by using a ratio of a so-called 1′ hybrid cartridge combined with multiple 1′ cartridges without a basic 34 hydraulic piston.
- the hydraulic piston 34 of the so-called hybrid cartridge 1' then takes over the expansion of several cartridges 1 without hydraulic piston 34.
- the module incorporates six cartridges 1, 1' with a ratio of two cartridges 1 without hydraulic piston 34 for a so-called hybrid cartridge 1'.
- the module comprises two insulating enclosures separated by junction plate 39 and receiving at least partly said at least one cartridge 1, 1' or a plurality of cartridges 1, 1'.
- the two insulating enclosures can be delimited by one or more casings.
- each insulating enclosure is directly powered by the first or the second heat source, which makes it possible to centrally supply said at least one cartridge 1, 1′ or a plurality of cartridges 1, 1′ with heat transfer fluid instead of having to supply each cartridge 1, 1' individually.
- the size of the two insulating enclosures can be adapted to the number of cartridges 1, 1' to be integrated for a targeted power of the thermal machine.
- the working fluid supply circuit H, J is formed from said first heat transfer fluid supply circuit A, B and from said second heat transfer fluid supply circuit C, D.
- the working fluid supply source H, J at the level of the fifth supply orifice 40 is identical to that of the first heat transfer fluid supply circuit A, B, as well as the source working fluid supply 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 supply circuit in heat transfer fluid A, B and the second heat transfer fluid supply circuit C, D makes it possible to actuate the piston 26.
- the working fluid supply circuit H, J is separate from said first heat transfer fluid supply circuit A, B and from said second heat transfer fluid supply circuit C, D ( figures 18 and 19).
- the junction plate 39 has a lower thermal conductivity than the thermal conductivity of said first profile 2 and/or second profile 8.
- the junction plate 39 has a thermal separation function.
- the junction plate 39 is made of steel type metal. [0148] Preferably, the first reinforcing part 28 and the second reinforcing part 29 are fixed respectively to the junction plate 39.
- the module comprises a first insulating enclosure 43 which comprises at least a first compartment 44 into which opens said at least one first supply orifice 35 of the first means circulation 3 and at least one second compartment 45 into which opens said at least second supply orifice 36 of the first circulation means 3
- the module comprises a second insulating enclosure 43' which comprises at least one third compartment 46 into which the said at least one third supply orifice opens. 37 of the second circulation means 9 and at least one fourth compartment 47 into which the said at least one fourth supply orifice 38 of the second circulation means 9 opens.
- the second reinforcing piece 29 comprises said third supply orifice 37 and said fourth supply orifice 38 of the second circulation means 9.
- the first insulating enclosure 43 comprises a so-called cold part of the cartridge 1, 1 'and is provided to receive the heat transfer fluid from the first heat source to supply the first supply circuit with heat transfer fluid A, B.
- the second insulating enclosure 43′ comprises a so-called hot part of the cartridge 1, 1′ and is provided to receive the heat transfer fluid coming from the second heat source to supply the second power supply circuit with heat transfer fluid C, D.
- junction plate 39 separates first enclosure 43 from second enclosure 43'.
- the first reinforcement piece 28 comprises said first supply orifice 35 and said second supply orifice 36 of the first circulation means 3.
- the first compartment 44 and the second compartment 45 are preferably delimited by at least one first dividing wall 48.
- the third compartment 46 and the fourth compartment 47 are preferably delimited by at least one second dividing wall 49.
- the first dividing wall 48 and/or the second dividing wall 49 act as hydraulic shutters and preferably do not withstand high mechanical stresses.
- the first dividing wall 48 and/or the second dividing wall 49 are preferably made of plastic or elastomeric materials, these examples are not limiting.
- the first supply orifice 35 and the second supply orifice 36 are arranged on either side of the first dividing wall 48, which ensures that the flow of heat transfer fluid between A and B takes place at inside the first reinforcing part 28 between the latter and the first section 2, and not outside the first reinforcing part 28.
- the third supply orifice 37 and the fourth supply orifice 38 are arranged on either side of the first dividing wall 48, which ensures that the flow of heat transfer fluid between C and D takes place at inside the second reinforcing part 29 between the latter and the second section 8, and not outside the second reinforcing part 29.
- said at least one fifth supply orifice 40 of the working fluid supply circuit H, J opens into the first compartment 44 and said at least one sixth supply orifice 41 of the supply circuit in working fluid H, J opens into the third compartment 46.
- the working fluid supply source H, J at the level of the fifth supply orifice 40 is identical to that of the first heat transfer fluid supply circuit A, B, as well as the source working fluid supply at the sixth supply port 41 is identical to that of the second heat transfer fluid supply circuit C, D.
- the module may include at least two cartridges 1, 1 'and the chambers 24 of each cartridge 1 are interconnected by at least one interconnection pipe 50, preferably arranged 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 arranged in said junction plate 39.
- said at least one interconnection line 50 allows interconnection of each chamber 24 of each cartridge 1, 1'.
- the invention also relates to a thermal machine capable of and intended for carrying out at least one conversion of thermal energy into mechanical energy comprising at least one thermodynamic fluid, preferably in the supercritical state and capable and intended of implementing a cycle thermodynamics comprising at least one isochoric heating phase, optionally an isobaric heating phase, an expansion phase and an isobaric cooling phase, the heat engine comprising at least one module according to the invention described above.
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
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Abstract
Description
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Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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CN202280020747.6A CN117043450A (zh) | 2021-03-17 | 2022-03-15 | 用于具有热力学循环的热机的盒和相关联热机 |
EP22715581.9A EP4308802A1 (fr) | 2021-03-17 | 2022-03-15 | Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé |
JP2023555710A JP2024511582A (ja) | 2021-03-17 | 2022-03-15 | 熱力学サイクルを有する熱機関及び関連する熱機関のためのカートリッジ |
Applications Claiming Priority (2)
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FRFR2102658 | 2021-03-17 | ||
FR2102658A FR3120916B1 (fr) | 2021-03-17 | 2021-03-17 | Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé |
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WO2022194877A1 true WO2022194877A1 (fr) | 2022-09-22 |
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PCT/EP2022/056723 WO2022194877A1 (fr) | 2021-03-17 | 2022-03-15 | Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé |
Country Status (5)
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EP (1) | EP4308802A1 (fr) |
JP (1) | JP2024511582A (fr) |
CN (1) | CN117043450A (fr) |
FR (1) | FR3120916B1 (fr) |
WO (1) | WO2022194877A1 (fr) |
Citations (11)
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DE19938023A1 (de) * | 1999-08-11 | 2000-04-27 | Enerlyt Potsdam Gmbh En Umwelt | Heißgasmotor mit einem Arbeitskolben, der sich innerhalb eines Verdrängerkolbens bewegt |
WO2002001052A2 (fr) | 2000-06-30 | 2002-01-03 | Leonello Acquaviva | Moteur thermique a combustion externe et a basse temperature |
WO2002088536A1 (fr) | 2001-05-02 | 2002-11-07 | Stirling Advantage, Inc. | Moteur a piston fluidique |
EP1411235A1 (fr) * | 2002-10-15 | 2004-04-21 | Enerlyt Potsdam GmbH | Moteur à gaz chaud à deux temps avec deux parties mobiles |
WO2005042958A1 (fr) | 2003-10-30 | 2005-05-12 | Japan Aerospace Exploration Agency | Moteur stirling |
DE102009020417A1 (de) * | 2009-05-08 | 2010-11-11 | Bayerische Motoren Werke Aktiengesellschaft | Thermoelektrischer Wandler sowie Verfahren zum Betreiben desselben |
DE102013114159A1 (de) * | 2013-04-12 | 2014-10-16 | Arvid Rauchschwalbe | Verfahren und Vorrichtungen zur Nutzung von thermischer Energie und zur Erzeugung von Temperaturniveaudifferenzen |
WO2014187558A2 (fr) * | 2013-05-21 | 2014-11-27 | Richter, Berta | Procédé et moteur thermique pour exploiter des dégagement de chaleur ou de l'énergie géothermique |
WO2016165687A1 (fr) | 2015-04-17 | 2016-10-20 | Nexus Gmbh | Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé |
WO2018062627A1 (fr) | 2016-09-29 | 2018-04-05 | 한국과학기술원 | Moteur stirling utilisant un fluide supercritique |
WO2019143520A1 (fr) * | 2018-01-18 | 2019-07-25 | Thermal Tech Holdings | Ensemble piston à tête flottante |
-
2021
- 2021-03-17 FR FR2102658A patent/FR3120916B1/fr active Active
-
2022
- 2022-03-15 WO PCT/EP2022/056723 patent/WO2022194877A1/fr active Application Filing
- 2022-03-15 EP EP22715581.9A patent/EP4308802A1/fr active Pending
- 2022-03-15 JP JP2023555710A patent/JP2024511582A/ja active Pending
- 2022-03-15 CN CN202280020747.6A patent/CN117043450A/zh active Pending
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
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DE19938023A1 (de) * | 1999-08-11 | 2000-04-27 | Enerlyt Potsdam Gmbh En Umwelt | Heißgasmotor mit einem Arbeitskolben, der sich innerhalb eines Verdrängerkolbens bewegt |
WO2002001052A2 (fr) | 2000-06-30 | 2002-01-03 | Leonello Acquaviva | Moteur thermique a combustion externe et a basse temperature |
WO2002088536A1 (fr) | 2001-05-02 | 2002-11-07 | Stirling Advantage, Inc. | Moteur a piston fluidique |
EP1411235A1 (fr) * | 2002-10-15 | 2004-04-21 | Enerlyt Potsdam GmbH | Moteur à gaz chaud à deux temps avec deux parties mobiles |
WO2005042958A1 (fr) | 2003-10-30 | 2005-05-12 | Japan Aerospace Exploration Agency | Moteur stirling |
DE102009020417A1 (de) * | 2009-05-08 | 2010-11-11 | Bayerische Motoren Werke Aktiengesellschaft | Thermoelektrischer Wandler sowie Verfahren zum Betreiben desselben |
DE102013114159A1 (de) * | 2013-04-12 | 2014-10-16 | Arvid Rauchschwalbe | Verfahren und Vorrichtungen zur Nutzung von thermischer Energie und zur Erzeugung von Temperaturniveaudifferenzen |
WO2014187558A2 (fr) * | 2013-05-21 | 2014-11-27 | Richter, Berta | Procédé et moteur thermique pour exploiter des dégagement de chaleur ou de l'énergie géothermique |
WO2016165687A1 (fr) | 2015-04-17 | 2016-10-20 | Nexus Gmbh | Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé |
WO2018062627A1 (fr) | 2016-09-29 | 2018-04-05 | 한국과학기술원 | Moteur stirling utilisant un fluide supercritique |
WO2019143520A1 (fr) * | 2018-01-18 | 2019-07-25 | Thermal Tech Holdings | Ensemble piston à tête flottante |
Also Published As
Publication number | Publication date |
---|---|
JP2024511582A (ja) | 2024-03-14 |
FR3120916B1 (fr) | 2023-03-17 |
EP4308802A1 (fr) | 2024-01-24 |
FR3120916A1 (fr) | 2022-09-23 |
CN117043450A (zh) | 2023-11-10 |
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