Classifications

• • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure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 thermal machines.
• Publication W084/00399A1 discloses an example of mechanical decoupling between the positions of the displacer and the positions of the working piston for a Stirling engine supplied with heat by external combustion.
• the system works with an additional hydraulic piston to the working piston, which complicates the engine and the control of the assembly, especially since a pump is integrated between the pistons to compress the air before mixing it with the combustible.
• ORC Organic Rankine Cycle
• the present invention aims to overcome at least one of these drawbacks and aims to provide an alternative thermal machine solution.
• the invention relates to a thermal machine capable and intended to perform at least one conversion of thermal energy into mechanical energy comprising at least one thermodynamic fluid and capable and intended to implement a thermodynamic cycle comprising at least an isochoric heating phase, optionally an isobaric heating phase, an expansion phase and an isobaric cooling phase,
• the thermal machine comprising at least:
• a first heat source at a first temperature configured to contain and transmit thermal energy to at least one heat transfer fluid
• a second heat source at a second temperature configured to contain and transmit thermal energy to at least one heat transfer fluid, the first and second temperatures being different
• said at least one module comprising at least the cold part
• said at least one module comprising a first heat transfer fluid supply circuit connected to the first heat source and to the cold part,
• said at least one module comprising at least the hot part
• said at least one module comprising a second heat transfer fluid supply circuit connected to the second heat source and to the hot part,
• said at least one module comprising at least one chamber suitable and intended to contain said at least one thermodynamic fluid, preferably at high pressure and in the supercritical state, and which is connected to at least one outlet thermodynamic fluid supply at a first pressure or to a hydraulic fluid supply outlet at a second pressure,
• thermodynamic fluid supply outlet at least a first unit for converting a pressure difference of the thermodynamic fluid into mechanical energy
• at least one circuit which comprises at least mechanical conversion means, preferably a motor, said first conversion unit being connected at the thermodynamic fluid supply outlet or at the hydraulic fluid supply outlet,
• said thermal machine is characterized in that
• said at least one module further comprises at least one movable mover in said chamber alternately between the cold part and the hot part,
• said chamber being suitable and intended to contain said at least one high-pressure thermodynamic fluid exhibiting pressures of between 50 bars and 300 bars and in the supercritical state,
• thermodynamic cycle in that it comprises at least a first control unit arranged at least in part in the first conversion unit arranged at least to control the phase in which the thermodynamic cycle is located in said at least one module,
• figure 1 represents an overall diagram representative of the thermal machine according to the type of module
• figure 2 represents the Temperature T- Entropy S diagram of a thermodynamic cycle of the thermal machine for carbon dioxide
• FIG. 3 represents a schematic view of a thermal machine according to a first variant of the invention illustrating the first control unit
• FIG. 4 represents a schematic view of a thermal machine according to a second variant of the invention illustrating the first control unit
• FIG. 5 represents a schematic view of a module for a thermal machine illustrating a second control unit according to a first possibility
• FIG. 6 figure 6 represents a schematic view of a module for a thermal machine illustrating the second control unit according to a second possibility
• figure 7 represents a schematic view of a thermal machine module illustrating the second control unit
• FIG. 8 figure 8 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to a first example
• figure 9 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to a second example
• figure 10 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to a third example
• figure 11 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to a fourth example
• FIG. 12 figure 12 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to the third example and illustrates its operation
• FIG. 13 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to the third example and illustrates its operation
• figure 14 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to the third example and illustrates its operation
• FIG. 15 figure 15 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to the third example and illustrates its operation
• FIG. 16 figure 16 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to the third example and illustrates its operation
• figure 17 represents a schematic view of a thermal machine with a so-called anti-phase architecture according to the third example and illustrates its operation
• FIG. 18 figure 18 represents a schematic view of a thermal machine according to the first variant of the invention in which the pressure limiter is replaced by an additional pressure accumulator,
• Figure 19 shows a sectional view of a module comprising a cartridge.
• a thermal machine is suitable and intended to carry out at least one conversion of thermal energy into mechanical energy comprising at least one thermodynamic fluid and suitable and intended to implement a thermodynamic cycle comprising at least one isochoric heating phase 1- 2, optionally an isobaric heating phase 2-3, an expansion phase 3-4 and an isobaric cooling phase 4-1 (FIG. 2).
• the thermal machine comprises at least:
• a first heat source 1 at a first temperature T1 configured to contain and transmit thermal energy to at least one heat transfer fluid (Figure 1),
• a second heat source 2 at a second temperature T2 configured to contain and transmit thermal energy to at least one heat transfer fluid, the first and second temperatures T1 and T2 being different (figure 1),
• said at least one module 3, 3' comprising at least the cold part 4,
• said at least one module 3, 3 ' comprising a first circuit for supplying the heat transfer fluid A, B connected to the first heat source 1 and to the cold part 4,
• said at least one module 3, 3′ comprising at least the hot part 5
• said at least one module 3, 3′ comprising a second supply circuit for the heat transfer fluid C, D connected to the second heat source 2 and to the hot part 5,
• said at least one module 3, 3' comprising at least one chamber suitable and intended to contain said at least one thermodynamic fluid and which is connected to at least one thermodynamic fluid supply outlet G at a first pressure P1 or at a hydraulic fluid supply outlet E at a second pressure P2,
• At least a first unit 6 for converting a thermodynamic fluid pressure difference into mechanical energy comprising at least one circuit 7 which comprises at least mechanical conversion means, preferably a motor 8, said first conversion unit 6 being connected to the thermodynamic fluid supply outlet G (FIGS. 4 and 11) or to the hydraulic fluid supply outlet E (FIGS. 3, 8 to 10).
• the thermal machine is characterized in that said at least one module 3, 3′ further comprises at least one movable mover in said chamber alternately between the cold part 4 and the hot part 5,
• said chamber being suitable and intended to contain said at least one high-pressure thermodynamic fluid having pressures of between 50 bars and 300 bars and in the supercritical state,
• thermodynamic cycle in that it comprises at least a first control unit at least partially disposed in the first conversion unit 6 arranged at least to control the phase in which the thermodynamic cycle is located in said at least one module 3, 3',
• the thermal machine allows the conversion of heat, preferably at low temperature, that is to say for first and second heat sources 1, 2 whose temperature T1, T2 does not exceed 150 degrees Celsius, in mechanical energy.
• This conversion takes place according to a closed thermodynamic cycle using a thermodynamic fluid preferably in the supercritical phase alternately heated and cooled via the first heat source 1 and the second heat source 2. As illustrated in FIG.
• the thermodynamic cycle comprises at least one isochoric heating phase 1-2, optionally an isobaric heating phase 2-3, a preferably polytropic expansion phase 3-4 and an isobaric cooling phase 4-1.
• the supercritical thermodynamic cycle contains isochoric 1-2 heating which is completed by isobaric 2-3 heating if the pressure during heating exceeds a determined limit value between 100 bars and 200 bars.
• the thermodynamic fluid is carbon dioxide
• the pressure ranges of the thermodynamic fluid are typically between 74 bars and 350 bars, preferably 74 bars and 250 bars and the temperature ranges are between 0 degrees Celsius and 150 degrees Celsius, preferably between 10 degrees Celsius and 100 degrees Celsius.
• the first conversion unit 6 advantageously allows the conversion of the pressure of the thermodynamic fluid at the thermodynamic fluid supply outlet G or of the hydraulic fluid at the hydraulic fluid supply outlet E into mechanical movement.
• the recovery of energy by the first conversion unit 6 can thus be done using a hydraulic fluid different from the thermodynamic fluid (FIGS. 3, 8 to 10) or directly with the thermodynamic fluid (FIGS. 4 and 11).
• the first control unit allows the control of the state of completion of each phase of thermodynamic transformation and therefore of the thermodynamic cycle, in particular by the detection of the points of the thermodynamic cycle for example by the detection of pressure and / or flow as described below.
• the second control unit makes it possible to alternately move the thermodynamic fluid in the chamber from the cold part 4 to the hot part 5 and to modulate the heat input of the module 3, 3'.
• the second control unit allows the management of the pressure and/or the flow coming from the first and second heat sources 1, 2 as described below. As a result, the efficiency of the thermal machine and its average power density can consequently be modulated at will, by offering the possibility of optimizing one or the other according to the availability of the first and second heat sources 1 , 2.
• the displacer is one or more mechanical parts.
• the expansion 3, 4 is polytropic, that is to say it is neither isothermal nor adiabatic.
• the expansion is variable and can approximate either a 3.4' isothermal expansion or a 3.4' adiabatic expansion (figure 2).
• the isochoric heating phase 1-2 does not correspond to an ideal/theoretical isochoric heating, but the heating phase approaches this ideal or theoretical isochorus with a deviation value which is preferably between 0 and 20 percent.
• the 2-3 isobar heating phase and/or the 4-1 cooling phase do not correspond to ideal/theoretical isobars, but approach them with a deviation value which is preferably between 0 and 20 percent.
• the module 3 comprises at least one chamber suitable and intended to contain only a thermodynamic fluid preferably at high pressure, that is to say for pressures preferably between 50 bars and 300 bars preferably between 80 bars and 250 bars, and in the supercritical state and which is connected to the thermodynamic fluid supply outlet G, this module 3 is said to be basic. This is particularly the case for modules 3 described in Figures 4 and 11.
• module 3′ further comprises a hydraulic piston 36 connected to the hydraulic fluid supply outlet E
• this module 3′ is said to be hybrid. This is particularly the case for the 3' modules described in figures 3, 8 to 10.
• the so-called basic module 3 can be connected to a hydraulic piston 36 which is outside the module 3.
• Each module 3 or association of basic modules 3 can be coupled to one or more high pressure hydraulic piston(s) 36 outside the module(s) 3 and maintained at temperature by one of the first/second heat sources 1, 2.
• the hydraulic piston 36 thus makes it possible to transmit the pressure of the supercritical fluid to a hydraulic fluid.
• a hydraulic reduction ratio can also be achieved within the hydraulic piston 36 so as to modify the characteristics of the pressure and of the volume of oil displaced. This may have some advantage in certain cases to facilitate the sizing of the charging system, in particular to adapt to the pressure/flow characteristics of the hydraulic motor 12.
• the hydraulic piston 36 may be in the form of a so-called “liquid” piston, that is to say without a solid interface between the two fluids provided that they are immiscible and insoluble with each other. This makes it possible to avoid losses by friction of joints.
• said first conversion unit 6 comprises at least one hydraulic pressure accumulator 11 connected downstream of the mechanical conversion means, preferably of the engine 8, which is a hydraulic motor 12, said pressure accumulator 11 being able and intended to maintain the pressure of circuit 7 greater than or equal to the critical pressure of the thermodynamic fluid.
• the pressure accumulator 11 ensures that the pressure of the hydraulic fluid in the circuit 7 is maintained above or equal to the critical pressure of the thermodynamic fluid for the entire thermodynamic cycle and in particular during the isobaric cooling phase.
• this critical pressure is substantially equal to 73.77 bars. Consequently, the precharged pressure of the pressure accumulator 11 is preferably between 73 and 85 bars, preferably equal to 80 bars.
• the thermodynamic fluid contained in one or more so-called hybrid module(s) 3' is alternately heated, then cooled and works against an almost constant assimilated pressure of the pressure accumulator 11. The pressure differences of the thermodynamic fluid, then hydraulic fluid is converted into mechanical energy by the hydraulic motor 12.
• said first conversion unit 6 comprises at least one pressure accumulator 11 connected downstream of the mechanical conversion means, preferably of the motor 8 which is a thermodynamic fluid turbine 14 preferably in the supercritical state, said pressure accumulator 11 being able and intended to maintain the pressure of the circuit 7 higher or equal to the critical pressure of the thermodynamic fluid.
• the pressure accumulator 11 ensures that the pressure of the thermodynamic fluid in the circuit 7 is maintained above or equal to the critical pressure of the thermodynamic fluid for the entire thermodynamic cycle and in particular during the isobaric cooling phase.
• this critical pressure is substantially equal to 73.77 bars. Consequently, the precharged pressure of the pressure accumulator 11 is preferably between 73 and 85 bars, preferably equal to 80 bars.
• the thermodynamic fluid contained in one or more so-called basic module(s) 3 is alternately heated then cooled and works against an almost constant assimilated pressure of the pressure accumulator 11. The only pressure differences of the thermodynamic fluid are converted into mechanical energy by the thermodynamic fluid turbine 14.
• said first control unit comprises at least one pressure and/or flow measurement device 9 arranged to control the phase in which the thermodynamic cycle is located and in particular to determine the completion of each phase of the cycle.
• Said pressure and/or flow measurement member 9 is preferably arranged between the chamber and said pressure accumulator 11 .
• said first control unit makes it possible, thanks to at least one pressure and/or flow measurement device 9 arranged in the circuit 7 or in the chamber, to follow the evolution of the different phases of the thermodynamic cycle thanks to the measurement of the pressure of the thermodynamic or hydraulic fluid in the chamber or in the circuit 7 and/or thanks to the measurement of the flow rate of the hydraulic fluid in the circuit 7.
• This pressure and/or flow measurement device 9 is arranged upstream of the engine 8 or at the level of the engine 8. This configuration allows the control of the state of completion of each thermodynamic transformation and therefore of the thermodynamic cycle, in particular by the detection cycle points by detection and monitoring of pressure and/or flow rate of the thermodynamic fluid or of the hydraulic fluid.
• said first control unit comprises two pressure and/or flow measurement devices 9 circuit 7 in the form of a pressure sensor 90 and a speed sensor 10.
• the rotational speed sensor 10 is arranged at the level of the motor 8 and allows an indirect measurement of the flow in the circuit 7.
• the rotational speed sensor 10 can allow via the measurement of the hydraulic fluid flow in the circuit 7 to conclude that at the end of the isobaric heating phase, the system is in equilibrium.
• the pressure sensor 90 allows a direct measurement of the pressure of the hydraulic fluid in the circuit 7 (FIG. 3) or a direct measurement of the pressure of the thermodynamic fluid in the circuit 7 (FIG. 4).
• said pressure and/or flow measurement device 9 is arranged between the hydraulic fluid supply outlet E and said pressure accumulator 11. Said measurement device pressure and/or flow rate 9 is placed in the circuit 7.
• said pressure and/or flow measurement device 9 is arranged between the thermodynamic fluid supply outlet G and said pressure accumulator 11. Said measurement device pressure and/or flow rate 9 is placed in the circuit 7.
• said first control unit comprises at least one pressure and / or flow control element 13 of circuit 7 arranged at least to control / control the heating phase isobaric and/or the expansion phase of the thermodynamic cycle, said at least one pressure and/or flow rate regulating element 13 being arranged between the thermodynamic fluid supply outlet G or at the hydraulic fluid supply outlet E and said pressure accumulator 11.
• said first control unit makes it possible in particular, thanks to at least one pressure and/or flow control element 13, to supply the motor 8 or not.
• Said first control unit also makes it possible, thanks to at least one pressure and/or flow control element 13 to control the movement of the thermodynamic fluid (FIG. 4) or of the hydraulic fluid (FIG. 3) in the circuit 7 to control/control the isobaric heating phase and/or the expansion phase of the thermodynamic cycle
• said at least one pressure and/or flow control element 13 is chosen from among a pressure limiter 16 (FIG. 3) and/or a flow regulator, and/or a hydraulic valve 15 (FIG. 3) and/or an adjustable flow restrictor and/or a variable throttle orifice 17 (FIG. 4) or an additional pressure accumulator 30 (FIG. 18).
• said at least one pressure and/or flow rate regulating element 13 is arranged between the hydraulic fluid supply outlet E and said pressure accumulator 11.
• said first control unit comprises two pressure and/or flow control elements 13 in the form of an adjustable pressure limiter 16 and a hydraulic valve 15.
• the adjustable pressure limiter 16 ensures the transition from the isochoric heating phase to the isobaric heating phase at a determined pressure.
• the hydraulic valve 15 is opened to perform the polytropic expansion then the cooling of the fluid after inversion of the displacers in the module(s) 3'.
• the adjustable pressure limiter 16 can be replaced by an additional pressure accumulator 30 preferably precharged to the isobaric heating pressure.
• thermodynamic fluid supply outlet G is arranged between the thermodynamic fluid supply outlet G and said pressure accumulator 11.
• said first control unit comprises a pressure and/or flow rate regulating element 13 in the form of a variable throttle orifice 17.
• the adjustable pressure limiter 16 and the hydraulic valve 15 of the first variant can be replaced by a single variable throttle orifice 17 so as to be able to actively control the isobaric heating phase and the cooling phase. preferably polytropic relaxation.
• the circuit 7 may comprise one or more preferably heat-insulated pipes and which make it possible in particular to connect the thermodynamic fluid supply outlet G or to the hydraulic fluid supply outlet E to the pressure accumulator 11 and/or to the pressure and/or flow rate measuring device 9 and/or to the pressure and/or flow rate regulating element 13 and/or to the motor 8.
• the machine further comprises a second unit 18 for converting mechanical energy into electrical energy connected to said first conversion unit 6 downstream of said motor 8.
• the second conversion unit 18 makes it possible to convert the mechanical energy coming from the motor 8 into electrical energy.
• the second conversion unit 18 comprises at least one inertia 19 connected on the one hand to a coupling 20 and on the other hand to a generator 21.
• the module 3, 3' comprises at least one piston (not shown) contained in a cylinder (not shown) connected to a working fluid supply circuit J, H by a first end and a second end of the cylinder to control the displacement of the movable piston in the cylinder and the displacer and the piston are coupled to each other.
• the displacement of the piston causes the displacement of the displacer in the chamber between the hot part 5 and the cold part 4.
• the coupling between the displacer and the piston is preferably a magnetic coupling in order to limit friction losses in particular.
• the second control unit comprises at least a first pressure regulating member and / or flow at the first end of the cylinder and at least a second pressure and/or flow control member at the second end of the cylinder to maintain or vary a pressure difference between the first end and the second end so as to alternately move said at least one displacer between the hot part 5 and the cold part 4.
• the second control unit allows the management of the position of the thermodynamic fluid between the hot part 5 and the cold part 4 in at least one module 3, 3′.
• Each module 3, 3' contains a certain mass of thermodynamic fluid, preferably in the supercritical phase, which is alternately brought into contact with the first heat source 1 then the second heat source 2 via one or more displacers ( s).
• This or these displacer(s) operate as free pistons whose stop type position is determined solely by the pressure difference between the first end of the cylinder and the second end of the cylinder.
• the working fluid supply circuit J, H is independent of the pressure regulation of said first heat transfer fluid supply circuit A, B and of said second heat transfer fluid supply circuit C, D.
• the working fluid supply circuit J, H is formed from said first supply circuit for the heat transfer fluid A, B and from said second supply circuit for the coolant C,D.
• the second control unit comprises at least a first member for regulating the pressure and/or the flow rate of the first heat source 1 and a second member for regulating the pressure and /or the flow rate of the second heat source 2, the first pressure and/or flow rate regulating member and the second pressure and/or flow rate regulating member being configured to maintain or vary a pressure difference between the first heat source 1 and the second heat source 2 so as to alternately move said at least one displacer between the cold part 4 and the hot part 5.
• the first heat source 1 comprises at least one preferably hydraulic pump, which forms the first pressure and/or flow control member and the second heat source 2 comprises a second preferably hydraulic pump, which forms the second pressure and/or flow control member.
• the control of the displacement of the preferably supercritical hydraulic fluid in the module 3, 3' is therefore achieved as simply as possible by an adequate regulation of the preferably hydraulic pumps (not shown) of the first and second heat sources 1, 2 in order to create/maintain the differential pressure between the first and second supply circuits of the heat transfer fluid A, B and C, D required for the movement of the displacer(s).
• the second control unit comprises at least a third member for regulating the pressure and/or the flow rate of the first supply circuit A, B and a fourth member for regulating the pressure and/or the flow rate of the second supply circuit C, D, the third member for regulating the pressure and/or the flow rate and the fourth member for regulating the pressure and/or the flow rate being configured to maintain or vary a pressure difference between the first supply circuit A, B and the second supply circuit C, D so as to alternately move said at least one displacer between the cold part 4 and the hot part 5 .
• the second control unit allows the management of the position of the thermodynamic fluid between the hot part 5 and the cold part 4 in at least one module 3, 3'.
• Each module 3, 3' contains a certain mass of thermodynamic fluid, preferably in the supercritical phase, which is alternately brought into contact with the first heat source 1 then the second heat source 2 via one or more displacers ( s).
• This or these displacer(s) operate(s) as free pistons whose stop-type position is determined solely by the pressure difference between the first and second supply circuits of the heat transfer fluid A, B and C, D.
• said first pressure and/or flow regulating member and/or said second pressure and/or flow regulating member and/or said third pressure and/or flow regulating member flow rate of the first heat transfer fluid supply circuit A, B and/or the fourth member for regulating the pressure of the second heat transfer fluid supply circuit C, D is chosen from among a pressure limiter 26, 27 and/or a flow regulator 28, 29 and/or a hydraulic valve and/or an adjustable flow limiter and/or a variable throttle orifice or an additional pressure accumulator.
• the second control unit preferably comprises at least one pressure sensor 22, 23, 24, 25.
• the pressure sensor 22, 23 can be connected to the working fluid supply circuit J, H.
• the pressure sensor 24.25 can be connected to the first supply circuit A, B or to the second supply circuit C, D.
• the second control unit can also comprise a temperature sensor 37, 38 which can be connected to the first supply circuit A, B or to the second supply circuit C, D.
• said thermal machine comprises at least a first module 3, 3 'and a second module 3, 3', which are connected in series to each other. at their thermodynamic fluid supply outlet G or their hydraulic fluid supply outlet E using a first interconnection pipe 31 , which are connected in series to each other at the level of their first supply circuit A, B, and which are connected in series to each other at the level of their second supply circuit C, D.
• said first control unit is arranged at least to centrally control the phase in which the cycle is located. thermodynamics in said first module 3, 3' and in said second module 3, 3'.
• said second control unit is common to the first module 3, 3' and to the second module 3, 3' and is arranged to centrally control said at least one mover of the first module 3, 3' and said at least one mover of the second module 3, 3'.
• said thermal machine comprises at least a first module 32 and at least a second module 33, which are each connected to the first conversion unit 6 by their fluid supply outlet thermodynamics G or by their hydraulic fluid supply outlet E and the first module 32 and the second module 33 are arranged so that when said at least one mover of the first module 32 is in the cold part 4 then said at least one mover of the second module 33 is in the hot part 5.
• this configuration is said to be in phase opposition.
• the examples illustrated below in figures 8 to 11 are distinguished by the management of the energy resulting from the isobaric heating phase 2-3. This management depends on the conversion system installed (hydraulic motor mapping, inertia size). It is thus advantageous to be able to modulate this energy in order to supply the hydraulic motor 12 in its zone of best efficiency.
• the first conversion unit 6 and the second conversion unit 18 are substantially identical to those of the first variant embodiment illustrated in FIG. at least a first module 32 forming an assembly A while cooling at least a second module 33 forming an assembly B to avoid working with hydraulic pressure accumulators 11 of too large dimensions.
• the hydraulic fluid thus passes from said at least one first module 32 to said at least one second module 33.
• the pressure accumulator 11 then only plays a buffer storage role, the thermodynamic fluid not necessarily contracting at the same rate that it expands on the opposite side.
• the equilibrium detection of said at least one second module 33 is carried out for example using a flowmeter 34.
• Four non-return valves 35 form a passive flow management system between said at least one first module 32 and said at least one second module 33.
• the energy of the isobaric heating phase 2-3 is not stored and supplies the hydraulic motor 12 directly to the opening of the adjustable pressure limiter 16 at the cycle point 2 pressure. There is no hydraulic motor feed flow control 12.
• the addition of an additional pressure accumulator 30 in the high pressure part after the hydraulic valve 15 can make it possible to smooth the flow of fluid supplying the motor 8 during the expansion polytropic in order to operate the latter in its field of best performance.
• the pressure accumulator 11 is precharged to at least the critical pressure of the thermodynamic fluid.
• the energy of the isobaric heating phase 2-3 is partially stored in an additional pressure accumulator 30 in order to smooth the flow rate supplying the hydraulic motor 12 during this phase.
• an additional pressure accumulator 30 sized to be able to store all of the energy during the isobaric heating phase 2-3 is selected, in this case it is possible to simplify by placing the additional pressure accumulator 30 before the hydraulic valve 15 which makes it possible to eliminate the adjustable pressure limiter 16. polytropic is then restored. Inertia 19 then determines the time of relaxation.
• the non-return valves 35 can be simple (FIGS. 8 and 9) or calibrated (FIG. 10).
• the energy of the isobaric heating phase 2-3 is entirely stored in an additional pressure accumulator 30 then restored at the start of the expansion phase 3-4.
• This management of the energy resulting from the 2-3 isobaric phase is an important advantage.
• the energy of the thermodynamic cycle is recovered during two phases, the isobaric heating phase and the preferably polytropic expansion.
• the times of these two phases can be very different, the expansion phase being faster than the isobaric heating phase.
• the flow rates supplying the motor 8 can therefore be very variable from one phase to another.
• the hydraulic motors 12 maintain good efficiency in defined ranges of flow rates which may be less than the actual flow rate variations of the cycle.
• thermodynamic cycle varies greatly depending on the temperature difference between the first and second heat sources 1, 2 but is between a few seconds and a few tens of seconds.
• the thermodynamic cycle is carried out without a mechanical compressor.
• a distributor 36 4/2 can also fulfill the role of flow management between the different sets A and B but requires be controlled (active system), unlike the four non-return valves 35 described above.
• said at least one first module 32 of assembly A is heated in the isobaric heating phase 2-3 and said at least one second module 33 of assembly B is cooled in the expansion phase 4- 1.
• the hydraulic valve 15 is closed.
• the additional pressure accumulator 30 is open and stores the energy from the isobaric heating phase 2-3.
• the flowmeter 341 allows detection of the end of this heating phase.
• said at least one first module 32 of assembly A is in the 3-4 expansion phase and said at least one second module 33 of assembly B is cooled in the phase relaxing 4-1.
• the hydraulic valve 15 is open.
• the additional pressure accumulator 30 restores the stored energy.
• the rotation speed sensor 10 makes it possible to detect the end of the expansion phase.
• the flow meter 342 allows the detection of the end of this cooling phase.
• the coupling 20 is coupled and the mechanical energy is transformed into electricity.
• the hydraulic valve 15 is closed and said at least one displacer of said at least one first module 32 and said at least one displacer of said at least one second module 33 are reversed by differential pressure inversion, such as as previously described using the second control module.
• said at least one first module 32 of assembly A is cooled in the expansion phase 4-1 and said at least one second module 33 of assembly B is heated in the isochoric heating phase 1-2.
• the hydraulic valve 15 is closed.
• Coupling 20 is uncoupled.
• the additional pressure accumulator 30 is closed as long as the pressure is lower than the precharge pressure of the additional pressure accumulator 30. This phase is completed when the pressure in said at least one second module 33 of assembly B is equal to the precharge pressure of the additional pressure accumulator 30.
• said at least one first module 32 of assembly A is cooled in the expansion phase 4-1 and said at least one second module 33 of assembly B is heated in the heating phase isobaric 2-3.
• the hydraulic valve 15 is closed.
• the additional pressure accumulator 30 is open and stores the energy coming from the isobaric heating phase 2-3.
• the flowmeter 341 allows detection of the end of this heating phase.
• said at least one first module 32 of assembly A is cooled in the expansion phase 4-1 and said at least one second module 33 of assembly B is in the phase relaxation 3-4.
• the hydraulic valve 15 is open.
• the additional pressure accumulator 30 restores the stored energy.
• the rotation speed sensor 10 and/or the pressure sensor 9, 90 associated with assembly B makes it possible to detect the end of the expansion phase.
• the flow meter 342 and/or the pressure sensor 9, 90 associated with assembly A allows detection of the end of this cooling phase.
• the coupling 20 is coupled and the mechanical energy is transformed into electricity.
• the hydraulic valve 15 is closed and said at least one displacer of said at least one first module 32 and said at least one displacer of said at least one second module 33 are reversed by differential pressure inversion, such as as previously described using the second control module.
• a certain number of elements have a “passive” operation, thus simplifying the control of the heat engine as much as possible.
• the non-return valves 35 make it possible to supply the hydraulic motor 12 always in the same direction by forming a circuit managed solely by the induced pressure differences.
• the coupling 20, ideally of the freewheel type does not require any particular action and transmits energy to the inertia only in the direction of rotation of the hydraulic motor 12, while remaining decoupled if the hydraulic motor 12 rotates slower than the inertia 19.
• the additional pressure accumulator 30 is calibrated at an opening pressure of point 2 of the cycle, allowing isochoric heating as long as the pressure is lower than the pressure at point 2 of the cycle.
• the first control unit only requires the use of two flowmeters 34, 341, 342 and/or two pressure sensors 9, 90 in order to determine the end of the heating and cooling phases.
• a set A, B can chain the first three phases of the cycle [1 -2, 2-3, 3-4] independently of the other set B, A which is only in the cooling phase [4-1]
• the inversion of the movers only occurs when the two sequences are finished, [1-2, 2-3, 3-4 ] on one side and [4-1] on the other, but it is not determined that the cooling [4-1] is systematically longer or shorter than the succession of phases [1-2, 2- 3, 3-4]
• the order of magnitude of the time necessary for the two sequences is however quite close in the range of temperature and pressure targeted, which avoids downtime in the use of the machine.
• FIG. 19 represents an example of a module 3 according to the invention for moving a thermodynamic fluid alternately between a cold part 4 connected to a first heat source 1 and a hot part 5 connected to a second heat source. 2 for thermal machine with thermodynamic cycle.
• This module 3 generally comprises at least one cartridge 101 or a plurality of cartridges 101, in the example of Figure 19, a single cartridge 101 described below is included, and further comprises:
• the first heat transfer fluid supply circuit A, B connected to first circulation means 103 of said at least one cartridge 101 by at least one first supply orifice 135 and at least one second supply orifice 136 first means of circulation 103, [0134] a second heat transfer fluid supply circuit C, D connected to second circulation means 109 of said at least one cartridge 101 by at least one third supply orifice 137 and at least one fourth supply orifice 138 second circulation means 109,
• junction plate 139 comprising at least junction means 114 of the cartridge 1,
• a working fluid supply circuit H, J connected to a third profile 115 of said at least one cartridge 101 by at least a fifth supply orifice 140 that comprises the third profile 115 and at least a sixth supply orifice 141 that comprises the third section 115, arranged to control the movement of the piston 126,
• thermodynamic fluid supply outlet G connected to the chamber 124 of said at least one cartridge 101 or a hydraulic fluid supply outlet E connected to a first filling space 121 or to a second filling space filling 123 of said chamber 124.
• 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 module 3 comprises a first insulating enclosure 143 which comprises at least a first compartment 144 into which opens said at least one first supply orifice 135 of the first circulation means 103 and at least one second compartment 145 into which opens said at least one second supply orifice 136 of the first circulation means 103.
• the module 3 comprises a second insulating enclosure 143' which comprises at least one third compartment 146 into which opens said at least one third supply orifice 137 of the second circulation means 109 and at least one fourth compartment 147 into which said at least one fourth supply orifice 138 of the second circulation means 109 opens.
• the first compartment 144 and the second compartment 145 are preferably delimited by at least one first dividing wall 148.
• the third compartment 146 and the fourth compartment 147 are preferably delimited by at least one second dividing wall 149.
• a cartridge 101 for moving a thermodynamic fluid between a cold part 4 connected to a first heat source 1 and a hot part 5 connected to a second heat source 2 for machine heat with thermodynamic cycle includes at least:
• a first exchanger forming a so-called cold part 4, comprising a first hollow section 102 comprising first circulation means 103 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 section 102 comprising an internal wall and an external wall,
• a second exchanger forming a so-called hot part, comprising a second hollow section 8 comprising second circulation means 109 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 profile 108 comprising an internal wall and an external wall,
• a third hollow section 115 adapted and intended to be connected to at least one circuit for supplying at least one working fluid J, H, said third section 115 being arranged inside the first section 102 and the second section 108, said third section 115 comprising an internal wall and an external wall,
• At least a part of the internal wall of the second profile 108 and a second part of the external wall of the third profile 115 being spaced apart and located facing each other so as to form a second filling space 123 , at least one chamber 124 able and intended to contain at least one thermodynamic fluid, preferably at high pressure and in the supercritical state, said chamber 124 comprising at least the first filling space 121 and the second filling space 123 which are communicators,
• At least one displacer 125 arranged inside said chamber 124 and mounted to slide relative to the outer wall of said third section 115 and movable between a first position and a second position, and configured to alternately displace said at least one fluid thermodynamics between the first filling space 121 and the second filling space 123,
• a piston 126 arranged inside said third profile 115 and mounted to slide relative to the internal wall of said third profile 115 and movable between the first position and the second position, the piston 126 being able and intended to be moved by said at least one working fluid J, H between the first position and the second position,
• the third profile 115 is preferably made of non-magnetic material and the displacer 125 and the piston 126 are magnetically coupled to each other through the third profile 115 by magnetic connection means 127.
• this configuration allows control of the displacer 125 from the outside of the chamber 124 by means of a magnetic coupling between the piston 126 and the displacer 125.
• This magnetic coupling makes it possible to transmit radial forces to the displacer 125 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.
• said third profile 115, said first profile 102 and said second profile 108, the displacer 125 and the piston 126 are coaxial.
• the invention is not limited to the embodiments described and shown in the accompanying drawings. Modifications remain possible, in particular from the point of view of the constitution of the various elements or by substitution of technical equivalents, without thereby departing from the scope of protection of the invention.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
• Wind Motors (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=75539624

Family Applications (1)

Country Status (6)

Family Cites Families (9)

• 2021
  • 2021-03-17 FR FR2102659A patent/FR3120922A1/fr active Pending
• 2022
  • 2022-03-15 WO PCT/EP2022/056726 patent/WO2022194878A1/fr active Application Filing
  • 2022-03-15 JP JP2023555777A patent/JP2024511960A/ja active Pending
  • 2022-03-15 EP EP22714863.2A patent/EP4308801A1/de active Pending
  • 2022-03-15 CN CN202280020752.7A patent/CN116964303A/zh active Pending
  • 2022-03-15 US US18/550,218 patent/US20240218812A1/en active Pending

Also Published As

Similar Documents

Legal Events