EP3320189B1 - Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé - Google Patents

Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé Download PDF

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EP3320189B1
EP3320189B1 EP16723930.0A EP16723930A EP3320189B1 EP 3320189 B1 EP3320189 B1 EP 3320189B1 EP 16723930 A EP16723930 A EP 16723930A EP 3320189 B1 EP3320189 B1 EP 3320189B1
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working
heat
piston
pressure
cylinder
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EP3320189A1 (fr
EP3320189C0 (fr
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Jan Trzcionka
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Nexus GmbH
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Nexus GmbH
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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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines using steam of critical or overcritical pressure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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/02—Use of accumulators and specific engine types; Control thereof

Definitions

  • the invention relates to a cycle for a heat engine with external heat input and a heat engine with external heat input that operates according to the inventive cycle. More specifically, the invention relates to supercritical cycles and further to heat engines designed with isothermal expansion, with or without phase change.
  • the currently used heat engines in the lower power range up to 150kW mainly use hot gas processes without phase change with internal or external heat supply, whereby the maximum working pressure is usually below 150 bar.
  • the Clausius-Rankine process as a high-pressure process with phase change is now used almost exclusively in large, multi-stage water or ORC steam turbines in the upper power range.
  • Hot gas process with internal combustion very good heat input at high speed, high compression work, no recuperation, 5 high cooling losses, high pressure and temperature difference, wear and corrosion very high (e.g. internal combustion engines);
  • Hot gas process with external combustion poor heat input, therefore high heater temperatures at high speeds of 300 to 3500 rpm, little or no compression work, good recuperation, low cooling losses, average pressure and temperature difference, low wear and corrosion, sealing problems of the working medium (e.g. Stirling engines, gas turbines);
  • Clausius Rankine process water or ORC: good heat input and no compression work in the liquid phase, very poor recuperation only in the event of overheating (economizer), large cooling losses at the lowest temperature level, high pressure and low temperature difference, highest possible speeds (turbines with a multi-stage structure therefore very expensive), low wear and high corrosion (steam turbines, steam engines).
  • the patent application EP 2 441 925 A1 relates to a low-temperature process for recovering waste heat in a thermodynamic Brayton cycle using a thermal storage medium (e.g. water).
  • a thermal storage medium e.g. water
  • Supercritical CO 2 is proposed as the working medium.
  • the patent application DE 34 27 219 A1 relates to a supercritical steam engine cycle, in which a hot or cold gas serving as a working substance, obtained directly from the liquid phase in the supercritical temperature and pressure range and further overheated at constant supercritical pressure, is fed to a gas turbine, in which it expands adiabatically or polytropically to near the critical point of the working substance and the cooling of the Gas is taken to its complete liquefaction by means of a heat pump and / or expansion chamber in front of 5.
  • the patent application US 2013/0 152 576 A1 relates to a closed loop waste heat recovery system comprising a heat exchanger that transfers heat from an external heat source into a working fluid, an expander in fluid communication with an outlet of the heat exchanger and configured to expand the working fluid and produce mechanical energy , a recuperator in fluid communication with an outlet of the expander and configured to remove heat from the working fluid, a condensing unit in fluid communication with an outlet of the recuperator and configured to condense the working fluid, and a pump that is in fluid communication with an outlet of the condensing unit and configured to pump the condensed working fluid back into the recuperator, the recuperator being in fluid communication with the heat exchanger such that the working fluid follows a closed path.
  • the patent U.S. 8,783,034 B2 refers to a thermodynamic cycle for hot days, in which a pump drives a working medium through a heat exchanger, where it is heated and expanded via a turbine. It is then cooled to ambient temperature and liquefied by a multi-stage intercooled compressor.
  • the patent U.S. 8,006,496 B2 relates to an engine with working fluid in a closed circuit with at least one pump for the pressure build-up in the fluid and for the further pressure build-up during the recuperative heat absorption, as well as a heating device to bring the fluid above its critical temperature to its maximum working temperature.
  • At the outlet follows an expansion device for mechanical energy conversion with return flow to the recuperative heat exchanger.
  • the patent U.S. 4,077,214A relates to a heat engine for condensable wet steam as the working medium, consisting of a cylinder and a piston.
  • the heat input is matched to a specific dead space volume that is as small as possible.
  • the object of the invention is to improve the thermodynamic efficiency of the cyclic process while at the same time avoiding the main disadvantages and utilizing certain advantages of the methods mentioned at the outset.
  • the aim is still to increase longevity, low production costs and flexibility with regard to the heat source.
  • a main problem of high-compression Stirling engines is the sealing of the working medium to the outside and the subsequent energy extraction.
  • the external supply of heat energy takes place during the isothermal expansion and all process steps with the exception of the isothermal expansion are made possible by recuperation of the heat energy using the intermediate heat storage device.
  • the difference between the predetermined upper working temperature and the predetermined lower working temperature is greater than 150 Kelvin, in particular several 100 Kelvin, and the lower working pressure is at least above the critical pressure of the working medium and the difference between the upper working pressure and the lower working pressure is more than 50 bar, in particular several hundred bar and where the expansion rate is more than seven times the liquefied working volume.
  • a cold pole is maintained through heat bridges to the heat pole through the removal of heat from the outside of the working space.
  • Hydraulic areas are advantageously provided which are under the same pressure as the working medium in the working space and transmit a change in volume of the working medium to the outside of the working space and ensure an additional hermetic seal of the working space.
  • the heat engine can have: a master drive in the form of a cam disc or a linear actuator for actuating the control piston and a slave drive in the form of a linear gear or linear actuator, which is synchronized with the master drive and is axially connected to the oscillator piston, and wherein the master drive and the slave drive are either fully or partially within the hydraulic regions for the purpose of differential pressure equalization.
  • the heat engine can have: in each case a pressure chamber-externally driven magnetic coupling, which is magnetically coupled to the oscillator piston from the outside and a pressure chamber-externally driven magnetic coupling, which is magnetically coupled to the control piston from the outside.
  • the heat engine can comprise a static regenerator and heat sink or a movable regenerator connected to the control piston.
  • the contraction cylinder can be dimensioned in such a way that it can accommodate the entire liquefied working medium.
  • cooling devices can be arranged on the contraction cylinder.
  • the working piston can be designed as an extended free piston and media separating piston between the working space and the hydraulic area, which has piston seals on the side of the cold pole outside the hot working space, with the cold pole being able to be provided with a cooling device.
  • control piston can be designed either with piston seals as a media separating piston between the cold area of the working chamber and the hydraulic area, or within the cold area of the working medium as a displacer without piston seals.
  • the heating device can be designed as a combustion head with heat exchanger ribs or as an insulated heating jacket which is filled with a heat transfer medium.
  • the entire machine can be designed as a low-speed machine with a high maximum working pressure and a high expansion rate.
  • the invention thus relates to a cyclic process that enables an almost complete conversion of heat into mechanical energy and the reciprocating piston device to convert this.
  • This fully supercritical cycle with isothermal expansion enables a very high recuperation rate despite the phase change, since every energy change in the working medium in the upper and lower isobars is associated with a non-latent temperature change at approximately the same level.
  • the isothermal expansion also enables the greatest possible expansion ratio of the working medium within the scope of this cyclic process. It exceeds that of pure, externally heated hot gas machines by a maximum of 1:3 many times over. Since the pressure build-up (see point 3 to point 4 in 1 ) takes place, the mechanical pre-compaction work is also eliminated.
  • the device according to the invention is provided with hydraulic energy conversion.
  • the isothermal expansion (1-2) of the gaseous working medium is achieved by supplying heat via the cylinder wall and an oscillator piston with turbulator slots, which oscillates linearly in the expanding working chamber.
  • the working piston is designed as a hollow free piston with sealing rings at the cold end and, like the oscillator piston drive, follows the stroke of the control piston, which is driven by the external master drive. All external piston drives are operated largely force-neutrally with hydraulic pressure equalization and, due to the process, require only little mechanical energy supply. Due to the stretched design, the device has a high thermal resistance in the direction of the hydraulic pressure chambers or cold poles and, due to the process, requires relatively little external cooling.
  • the machine according to the invention uses a working medium with an upper working pressure of several 100 bar, high specific density and therefore high thermal conductivity due to the supercritical cycle process. Since this cyclic process always runs above the critical pressure of the wet steam curve, all heat exchange processes are non-latent, ie associated with a temperature gradient. In principle, this enables heat recovery in the area of isobaric expansion or contraction in a countercurrent heat exchanger or recuperator and is already being used in hot gas processes. What is special about the supercritical cycle, however, is that a phase transformation takes place at the same time if the lowest process temperature Tu is below the critical temperature of the working medium.
  • the two-cylinder variant with a 180° phase offset is selected as the basic version in order to achieve the most even hydraulic energy decoupling possible.
  • the number of cylinders can be projected from two to more, whereby a pressure accumulator and a leakage oil pump should be used to ensure the lower working pressure pu.
  • Serial parts from 220 to 700 bar can be used as hydraulic components, including hydraulic motor, hydraulic seals, valves and hoses.
  • the system is very stretched in order to maximize the thermal resistance (similar to ohmic resistance) from the hot working chamber zone to the cold zones at both ends of the cylinder, thus minimizing cooling losses.
  • FIG. 12 is an idealized log-ph diagram of the supercritical isothermal (Tp-vp) cycle according to which this system operates in accordance with the invention.
  • the idealized cyclic process runs clockwise through corner points 1 to 4 using the example of the working medium CO2. It is completely above the critical pressure and goes just below the critical temperature of the working medium in order to achieve a phase change from the liquid to the supercritical gas state.
  • the temperature range of the heat source is therefore decisive for the choice of the working medium (e.g. CO2, NH3, other refrigerants, water, etc.). Due to the phase change and the isothermal external heat supply, an expansion ratio > 10 can be achieved despite the high process pressures. In pure hot gas processes (Ericsson, Stirling, etc.) with maximum working pressures of around 40 to 100 bar, this is usually between 2 and 3.
  • the isothermal expansion (1-4) achieves a very high degree of recuperation during the isobaric expansion (4-1) or contraction (2-3) with minimal cooling water requirements. Due to the isochoric pressure build-up with the addition of heat (3-4) in the liquid phase, an extremely high working pressure po can also be achieved without the addition of mechanical energy. Theoretically, all of this leads to an almost complete conversion of the externally supplied heat into mechanical energy.
  • the practical efficiencies with CO2 from a working temperature To of 450°C are 60% far above that of pure hot gas processes without phase change or above that of the Clausius-Rankine steam process or ORC process with their large cooling losses.
  • an idealized isothermal expansion takes place, during which the entire external heat supply takes place.
  • This external heat supply corresponds to the enthalpy difference between point 2 and point 2* on the x-axis in kJ/kg, based on the working medium.
  • a maximum volume expansion of the working medium up to the lower isobars is possible as a result. Since the isotherms in the hot zone are almost vertical, there is the possibility of almost complete energy recuperation on the x-axis after the isobaric expansion is complete.
  • the isobaric expansion takes place by adding more heat from the recuperator (or a counterflow heat exchanger if heat is extracted from point 2 to point 3).
  • the constant upper working pressure po during this process is independent of the working medium and is solely determined by the generator counter-torque. The higher the difference between the upper and lower working pressure, the higher the power turnover.
  • Fig.2 shows the circuit diagram for the hydraulic energy conversion of the translation into a continuous rotation with translation to generator speed.
  • Generator 20 is connected to hydraulic motor 22 and flywheel 21 via a clutch.
  • the high-pressure side HD is alternately filled by the check valves 25.1 via the respective high-pressure lines 26.1 of the working cylinder. Possible pressure peaks are smoothed out with the pressure control valve 24.1.
  • the low-pressure side ND allows the oil to flow back from the hydraulic motor 22 into the working cylinder via the check valves 25.2 and the respective low-pressure lines 26.2 of the working cylinder.
  • the pressure level on the low-pressure side ND is maintained with the pressure control valve 24.2, the pressure accumulator 28 and the leakage oil pump 29.
  • the lines 27 are bypass lines to allow the pressure equalization between both ends of the working cylinder.
  • Fig.3 the preferred structure is shown in a two-cylinder arrangement with a 180° phase offset with mechanical control, as is the case at burner temperatures of up to 1200°C for the supercritical cycle process according to claims 1-4 ( Fig.1 ) but can also be used with real hot gas (e.g. air, helium, etc.) with the same process sequence.
  • real hot gas e.g. air, helium, etc.
  • the work cycle in the upper cylinder begins with the isothermal expansion stroke of the working piston 3 after the control piston 1 has been extended to the maximum using the common master cam drive 1b-1d.
  • the working piston 3 is a differential free piston, which always strives for the pressure balance on both sides and is moved by the smallest pressure differences. It is designed as an insulating hollow piston with an inner tube and seals near the cold pole at HR1.
  • the gaseous working medium in the working chamber AR is evenly reheated with the help of the oscillator piston 5, which is heated via the outer wall of the working cylinder 4. This oscillates back and forth between the fixed liquefaction cylinder 2 and the working piston 3 during the expansion with increasing amplitude.
  • the respective oscillator piston is moved by a linear slave servo drive 5.b, which is synchronized with the master drive 1b-1d.
  • the oscillator piston 5 has fine slits on the circumference in the axial direction, through which the working gas is turbulently pressed and then swirled. This ensures that during the expansion as much as possible each molecule of the working gas with the hot oscillator piston 5 and the cylinder wall 4 comes into contact again and again and is thus reheated.
  • the working pressure drops continuously, while the temperature of the working gas and the surrounding components around the working space AR remain approximately constant due to the external supply of heat. This prevents AC cracks and temperature fluctuations from occurring in this highly stressed cylinder area 4 .
  • the reverse contraction or reliquefaction in AR takes place over the entire path continuously and simultaneously with the retraction movement of the control piston 1.
  • the oscillator piston is in contact with the working piston 3 and is moved passively by it.
  • the reverse contraction or reliquefaction takes place isobaric, with the lower system pressure pu being kept stable via a pressure control valve, a leakage oil pump and a pressure accumulator. Almost the entire heat extraction can, according to the cyclic process in Fig.1 take place non-latently via an intermediate heat storage device 7 .
  • regenerator compared to a counterflow heat exchanger is that it consists of, for example, pressure-resistant, fine steel wire and therefore enables the greatest possible surface area and turbulence of the working medium even at the highest working pressures.
  • the regenerator requires a cyclically changing flow of a coordinated quantity of the working medium and is therefore not used, for example, in turbines, despite its advantages.
  • the regenerator can be oversized with regard to the heat storage capacity per stroke in order to ensure the greatest possible heat exchange.
  • Heat sink insert 6, contraction cylinder 2 and hydraulic section HR1 are adequately cooled by a water cooling jacket or air cooler 8.
  • the optional water cooling jacket or air cooler 9 should also prevent heating in the direction of HR2. This heat dissipation is primarily dependent on the thermal resistance of the thermal bridges from AR to HR1 and HR2 and is not (as is usually the case) due to the cyclic process. At the same time, it serves to maintain the temperature gradient between the hot pole in AR and the cold poles in HR1 and HR2 and requires comparatively small amounts of cooling water.
  • preheated fresh water or heating water can also be used for cooling.
  • the following isochoric pressure build-up is realized instantaneously by the control piston pushing out a small portion of the contracted or liquid working medium via recuperative heat supply.
  • the associated gradual pressure equalization is only possible with cyclic work processes and not with continuous processes (e.g. turbines with boiler feed pumps). It reduces the work required to build up the working pressure to the dynamic pressure of the working medium. Because of the external rod drive 1.a, the differential piston work (stroke x rod cross-section) of the control piston is added here.
  • the control piston 1 When the upper working pressure po is reached, the further extension of the control piston 1 leads to an isobaric expansion or gasification of the following working medium with the aid of the heat energy and temperature To previously stored in the heat storage device 7 .
  • the stroke of the working piston 3 in relation to the control piston 1 is determined by the temperature-dependent specific expansion rate of the working medium and the upper working pressure po.
  • the oscillator piston 5 is not moved during the entire isobaric expansion and remains in the left-hand position shown in dashed lines.
  • the upper working pressure po is determined by the working medium and the regulated load torque of the generator. Under these circumstances, it can be maintained as long as the control piston moves out continuously and still pushes working medium into the hot working chamber AR. When the control piston has reached the heat sink insert 6 (UT), the working pressure inevitably drops.
  • the insulated combustion chamber 10 has the task of conducting the combustion gases in such a way that they optimally transfer the heat of the combustion gases to the cylinder ribs of the working cylinder 4 .
  • the exhaust gases which are still hot (just above To), are then used via a separate countercurrent heat exchanger either to preheat the burner air or to heat the heating or service water.
  • Fig.4 provides a hermetic control variant in comparison to Fig.3
  • the control pistons as well as the oscillator pistons are moved by linear drives or hydraulic cylinders. You are within the hydraulic fluid in HR 1 and HR 2 in complete differential pressure equalization.
  • the drive motors can also be arranged outside of the pressure chambers HR 1 and HR 2 via rotary feedthroughs. Apart from the more complex servo or proportional control for each individual cylinder, the mechanical structure is simpler and wear-resistant. This version is therefore useful for larger, cost-intensive systems where service life and reliability are of primary importance.
  • Fig.5 represents a modification to the design Fig.3 which is particularly useful for low-temperature applications.
  • the entire system is hermetically sealed and the actuators are moved with magnetic couplings and differential pressure compensation.
  • the control piston is designed here as a purely sealless displacer 1 with a magnet ring 1.a and an integral recuperator 1.c as one assembly. It is completely within the working medium and is moved via the magnetic ring 1.b. Under certain circumstances, low-temperature use requires a working medium whose critical temperature is below the ambient temperature. The condensation temperature around the displacer 1 must be at least 10 K below this critical temperature. This can be achieved, for example, with a small external heat pump. Since hydraulic oil becomes viscous at these degrees of cold or falls below its pour point and seals become brittle, this version was equipped with a displacement piston 1 without seals. The thermal resistance is here compared to the version in Fig.3 however lower, which results in higher cooling losses in the HR1 area.
  • insulated heating sleeves 4 with heating water or heat transfer oil occur here.
  • the oscillator piston 5 is moved here with a hollow magnetic rod 5.a via a magnetic ring 5.b.
  • the hydraulic oil in HR2 is able to flow around and through the magnet rod, ensuring full pressure equalization and minimal flow resistance. Cooling on this side can be omitted if the working temperature of the working medium does not exceed the limit temperature of the hydraulic oil in room HR2.
  • the entire arrangement should be insulated as best as possible (10 and 11), since the cold pole in area HR1 may be below and the hot pole in work area AR above ambient temperature, and these are negatively influenced in both cases.
  • Fig.6 shows the path-time control diagram for the three actuators: working piston, oscillator piston and control piston.
  • the control points 1 to 4 relate to the cycle process according to the invention Fig.1 , but can also be used for a normal hot gas process, although the working pressure and the expansion rate should be lower here.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Claims (12)

  1. Cycle supercritique à transformation de phase pour moteurs thermiques à apport de chaleur extérieur à la zone de travail caractérisé en ce que
    un milieu de travail est détendu isothermiquement supercritiquement à une température de travail supérieure prédéfinie (Tu) dans une zone de travail avec un apport de chaleur extérieur à la zone de travail (1-2),
    puis reliquéfié de manière isobare supercritique à une pression de travail inférieure prédéterminée (pl) à une température de travail inférieure prédéfinie (TI), la température de travail inférieure prédéfinie (TI) étant inférieure à la température critique pour le milieu de travail, dans lequel l'énergie thermique ainsi libérée est temporairement stockée dans un dispositif de stockage temporaire de chaleur (7) (2-3),
    la montée en pression isochore est réalisée à partir de la phase fluide avec apport de chaleur du dispositif de stockage temporaire de chaleur (7, 1c) (3-4),
    est encore détendu de manière isobare supercritique à une pression de travail supérieure prédéfinie (pu) à la température de travail supérieure prédéfinie (Tu) avec un apport de chaleur provenant du dispositif de stockage de chaleur temporaire (4-1),
    dans cycle a toujours lieu au-dessus de la pression critique sur la courbe de vapeur humide pour le fluide de travail.
  2. Cycle selon la revendication 1, dans lequel la totalité de l'apport d'énergie thermique externe se produit presque entièrement pendant l'expansion isotherme (1-2) et dans lequel toutes les étapes du processus à l'exception de l'expansion isotherme (1-2) sont rendues possibles par la régénération de l'énergie thermique à l'aide du dispositif de stockage temporaire de chaleur (7).
  3. Cycle selon les revendications 1 et 2, dans lequel la différence entre la température de travail supérieure prédéfinie (Tu) et la température de travail inférieure prédéfinie (TI) est supérieure à 150 Kelvin, en particulier plusieurs 100 Kelvin, et dans lequel la pression de travail inférieure est supérieure à la pression critique du fluide de travail et la différence entre la pression de travail supérieure (pu) et la pression de travail inférieure (pl) est supérieure à 50 bars, en particulier plusieurs centaines de bars, et dans lequel la dilatation le taux est plus de sept fois le volume de travail liquéfié.
  4. Cycle selon l'une quelconque des revendications précédentes, dans lequel un pôle froid est maintenu sur des ponts thermiques vers un pôle chaud par extraction de chaleur à l'extérieur de la zone de travail.
  5. Un moteur thermique à apport thermique extérieur et découplage de l'énergie hydraulique pour la mise en oeuvre d'un cycle thermodynamique à détente isotherme, mise en pression isochore et expansion isobare du volume de travail et contraction du volume de travail, selon l'une quelconque des revendications précédentes, caractérisé en ce que
    au moins un cylindre de travail (4) et un cylindre de contraction (2) sont présents, dans lequel un piston de travail (3) pouvant se déplacer en va-et-vient est disposé dans le cylindre de travail (4) qui définit une zone de travail (WA) dans laquelle un fluide de travail peut être périodiquement contracté et dilaté,
    dans lequel un piston de commande (1) mobile en va-et-vient étant disposé dans le cylindre de contraction (2),
    dans lequel un dispositif de stockage de chaleur temporaire (7) étant également disposé dans le cylindre de contraction (2),
    dans lequel le dispositif de stockage de chaleur temporaire (7) stocke de l'énergie thermique pendant la contraction du volume de travail et fournit l'énergie thermique stockée pour l'établissement ultérieur de la pression isochore et pour la poursuite de la dilatation isobare,
    un dispositif de chauffage pour fournir de la chaleur à l'extérieur de la zone de travail est disposé sur le cylindre de travail (4) au moyen duquel le fluide de travail peut être chauffé de manière isotherme dans le cylindre de travail (4),
    dans lequel un piston oscillant thermiquement conducteur (5) qui peut se déplacer d'avant en arrière dans la zone de travail élargie (WA) du cylindre de travail (4) et qui est conçu pour transférer la chaleur fournie de l'extérieur à travers la paroi extérieure du cylindre de travail (4) dans le milieu de travail est également disposé dans le cylindre de travail (4),
    dans lequel le piston oscillateur (5) présente dans sa direction axiale des ouvertures dimensionnées de telle sorte que le fluide de travail est poussé à travers de manière turbulente et tourbillonne dans le cylindre de travail (4) après s'être échappé du piston oscillateur (5).
  6. Moteur thermique selon la revendication précédente, dans lequel des secteurs hydrauliques (HS1, HS2) sont prévus, qui sont sous la même pression que le fluide de travail dans la zone de travail (WA) et transfèrent une modification du volume du fluide de travail à l'extérieur de la zone de travail (WA) et assurent un joint hermétique supplémentaire sur la zone de travail.
  7. Moteur thermique selon la revendication 6, dans lequel il y a un entraînement maître sous la forme d'un disque à cames ou d'un actionneur linéaire pour actionner le piston de commande (1) et un entraînement esclave sous la forme d'une tête linéaire ou d'un actionneur linéaire, qui est relié axialement au piston oscillateur (5 ), qui est synchronisé avec l'entraînement maître du piston de commande (1) et dans lequel l'entraînement maître et l'entraînement esclave sont situés partiellement ou complètement à l'intérieur des secteurs hydrauliques (HS1, HS2) aux fins d'équilibrage de pression différentielle.
  8. Moteur thermique selon l'une quelconque des revendications 5 à 7, dans lequel il y a un accouplement magnétique entraîné à l'extérieur de la chambre de pression qui est couplé magnétiquement au piston oscillateur (5) et est mobile depuis l'extérieur, et un accouplement magnétique entraîné à l'extérieur de la chambre de pression qui est couplé magnétiquement au piston de commande (1 ) et est mobile de l'extérieur, respectivement
  9. Moteur thermique selon l'une quelconque des revendications 5 à 8, dans lequel le dispositif de stockage thermique temporaire (7) comprend un régénérateur statique et un dissipateur thermique (6) ou un régénérateur intégré, relié au piston de commande (1)
  10. Moteur thermique selon l'une quelconque des revendications 5 à 9, dans lequel le cylindre de contraction (2) est dimensionné de telle sorte qu'il peut recevoir tout le milieu de travail contracté et dans lequel des dispositifs de refroidissement (6, 8) sont agencés sur le cylindre de contraction (2).
  11. Moteur thermique selon l'une quelconque des revendications 6 à 10, dans lequel le piston de travail (3) étant réalisé sous la forme d'un piston libre étendu et d'un piston de séparation de fluide entre la zone de travail (WA) et le secteur hydraulique (HS2) avec des joints de piston sur le côté d'un pôle froid, à l'extérieur de la zone de travail chaude (WA ), le pôle froid pouvant être équipé d'un dispositif de refroidissement (9).
  12. Moteur thermique selon l'une quelconque des revendications 6 à 11, dans lequel le piston de commande (1) est réalisé soit avec des joints de piston en tant que piston de séparation de fluide entre le secteur froid de la zone de travail (WA) et le secteur hydraulique (HS1), soit dans le secteur froid du fluide de travail (WA) en tant que plongeur sans joints de piston.
EP16723930.0A 2015-04-17 2016-04-08 Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé Active EP3320189B1 (fr)

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DE102015105878.2A DE102015105878B3 (de) 2015-04-17 2015-04-17 Überkritischer Kreisprozess mit isothermer Expansion und Freikolben-Wärmekraftmaschine mit hydraulischer Energieauskopplung für diesen Kreisprozess
PCT/DE2016/100166 WO2016165687A1 (fr) 2015-04-17 2016-04-08 Procédé à cycle fermé supercritique à détente isotherme et machine thermique à piston libre à découplage énergétique hydraulique pour ce procédé à cycle fermé

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PL426295A1 (pl) * 2018-07-10 2020-01-13 Prosperitos Spółka Z Ograniczoną Odpowiedzialnością Sposób zasilania parą wodną o parametrach ultra-nadkrytycznych tłokowych silników parowych i zawór do zasilania parą wodną o parametrach ultra-nadkrytycznych tłokowych silników parowych
BR102018015325A2 (pt) * 2018-07-26 2020-02-04 Finco Saulo motor de combustão interna integrado formado por uma unidade principal a turbina e uma unidade secundária a pistões e processo de controle para o ciclo termodinâmico do motor.
FR3120916B1 (fr) 2021-03-17 2023-03-17 Berthelemy Pierre Yves Cartouche pour machine thermique à cycle thermodynamique et module pour machine thermique associé

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EP3320189A1 (fr) 2018-05-16
WO2016165687A1 (fr) 2016-10-20
DE112016001781A5 (de) 2018-01-25
DE102015105878B3 (de) 2016-06-23
EP3320189C0 (fr) 2023-06-07
CN107636261B (zh) 2019-07-12
CN107636261A (zh) 2018-01-26

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