EP1017933B1 - Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique - Google Patents

Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique Download PDF

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Publication number
EP1017933B1
EP1017933B1 EP98955343A EP98955343A EP1017933B1 EP 1017933 B1 EP1017933 B1 EP 1017933B1 EP 98955343 A EP98955343 A EP 98955343A EP 98955343 A EP98955343 A EP 98955343A EP 1017933 B1 EP1017933 B1 EP 1017933B1
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Prior art keywords
volume
working
gas
working fluid
working volume
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EP98955343A
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German (de)
English (en)
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EP1017933A1 (fr
Inventor
Thomas Ertle
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SOLISOLAR ENERGY GMBH
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SoliSolar Energy GmbH
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Priority claimed from DE1997142660 external-priority patent/DE19742660A1/de
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    • 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
    • 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
    • F02G1/02—Hot gas positive-displacement engine plants of open-cycle type
    • 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
    • F02G2270/00—Constructional features
    • F02G2270/70—Liquid pistons

Definitions

  • thermodynamic cycle processes previously used are each coupled to two heating baths with a constant temperature.
  • energy can only be transported optically (with parabolic mirrors or light guides) or via a material flow with a phase transition (heat pipe). Due to the desired isothermal exchange of thermal energy, the thermal energy can only be stored in chemical stores or in latent heat stores. As a result, the effort for concentrating the energy by the collector, transport and storage that is desirable for many applications is too often too great. If, for example, a direct supply of cold or compressed air is desired with the least possible equipment outlay, in many known systems the route via the interface of electrical current must be chosen.
  • the entire cyclic process in a working volume can be assigned several circular processes running in parallel between two heat reservoirs with constant temperatures, if justifiable idealization is considered.
  • Each heat reservoir of these cycle processes can be assigned to a partial volume of the working volume which is filled with working fluid and as defined above.
  • At least one substance of a continuous or periodically increasing and decreasing mass flow is heated or cooled either by the absorption or release of thermal energy at a lower temperature difference relative to the overall temperature change when it comes into contact with the hotter or colder heat reservoirs of these cycles, whereby the phase or can transform chemical composition.
  • At least one substance is used continuously to use solar energy or periodically rising and falling mass flow thermal energy with sliding Temperature or multiple temperature levels supplied.
  • the cited patent does not list a physical (phase) and / or chemical change due to thermal energy transformation over a wide temperature range, although these problems can be attributed to the same core problem:
  • thermal energy In order to liquefy part of a gas mixture, thermal energy usually has to be extracted over a temperature interval due to the changeable ratio of the partial pressures. Accordingly, when a gas mixture is vaporized, thermal energy must be supplied over a temperature interval or at several temperatures.
  • the mechanical work supplied (consumed) or given (won) during a period of the entire cycle to balance the energy balance is largely directly from a storage space during the transfer of at least a certain amount of at least one fluid substance moved to another storage space with different pressure.
  • Direct use of the pressure change e.g. by replacing a mechanically driven compressor or Decoupling the movements in the working volume from the driving shaft of a turbine or a compressor or the like. which is driven by or generates the pressure difference of the substance flowing (in the closed circuit).
  • a generator can be driven at the usual angular velocity and a flow velocity of the working fluid in the order of 1 m / s against the heat transfer surfaces and a correspondingly small temperature difference during heat transfer can be achieved, which has a positive effect on the efficiency and the accelerations occurring on the control system as well as the flow losses are reduced.
  • This enables a large-volume construction in which the pressure in the working volume is in the range of the atmospheric pressure and air is used as the working fluid, which alleviates many problems with regard to tightness and makes interesting applications possible. (see application examples)
  • the cited patent is limited to a cooling or heating of a heating or cooling medium through the thermal contact with heat exchangers of a regenerative work or heat engine compared to the more abstract formulation of the task chosen above.
  • This eliminates a reduction in the structural or technological outlay for heat exchangers or regenerators, which is achieved according to the invention if the heat is added to the working volume by the heating medium being taken up, for example, as hot gas in the working volume by valves and at a lower temperature again by valve ( e) is emitted, whereby the dead volume of the working volume can also be reduced, which experience has shown that it is just as favorable for achieving good efficiency as a functional replacement of the relatively small heat transfer surface of the heat exchanger by the much larger one of the regenerator.
  • Fresh air can flow into the working volume through one of the valves at atmospheric pressure, which can achieve decisive synergy effects in some applications.
  • hot air can be taken up in a working volume and blown out as cooler air into a room with higher pressure, with some of the heat energy released when the air is cooled being taken up by the cooler. If the hot fresh air has been heated at atmospheric pressure by exhaust gases from an internal combustion engine and the cooler air with higher pressure is used to charge the internal combustion engine, great synergy effects are used.
  • the device shown in Figure 1 can be used, among other things, as a thermal device Gas compressors (with the integrated effect as an engine) work and form due to the simple structure and the relatively easy theoretical Description of the cycle a good starting point for understanding the more complex machines also based on the principle of the invention, Devices or processes.
  • a working volume filled with gas as the working fluid is largely enclosed by a working cylinder as the pressure housing 1, a slidingly sealed piston 2, inlet and outlet valves 3 and 4, respectively.
  • a frame 6 is slidably sealed against the cylinder wall 5, on which a heat exchanger 7 and a regenerator 8 which is unchangeable in structure or size are mounted such that the gas must flow through them.
  • a resilient spacer 9 is between this regenerator 8 and a structure 11 surrounded by a bellows 10 with a reversible, acting and acting as a regenerator structure 11, which consists of a fine (40 - 80 ppi) foam or comes close to this in terms of homogeneity or gaps , (e.g.
  • a flow channel 12 is formed over the entire cylinder surface, through which the gas passes the structure 11 through the opened outlet valve 4 of the volume and part 13 of the piping system to the fan 14 can reach.
  • This gas can flow from the fan through part 15 of the piping system and a regenerator 16 to be flowed through into a reserve space 17 which is enclosed by a bellows. From the fan 14 or from this reserve space 17, the gas can reach the working volume after being heated in a (countercurrent) heat exchanger 18 through part of the piping system 19 through the inlet valves 3.
  • a pressure tank 20 is connected to the pipe system at 13 in front of the fan (turbine) 14.
  • the piston 2 and the frame 6 are moved periodically by hydraulic pistons 21, 22, 23 as is characterized in FIG. 4, FIG. 5, FIG. 6 or the subsequent description of the cycle.
  • the piston 2 is stabilized in the orientation with regard to the stroke direction.
  • the drive tube 24 of the frame 6 is guided by the piston 2 in the stroke direction through seals from the working volume. Two tubes for the cooling water run in this drive tube and are sealed against the inner wall of the drive tube in such a way that no gas exchange which interferes with the cycle can take place between the working volume and the environment.
  • Movable hoses 25, 26 connect these pipes to fixed connections 27, 28 of a cooled water reservoir, so that the cooling water can circulate in a closed circuit.
  • the liquid in the heat exchanger 7 should always have a lower pressure than the working volume, so that no liquid is pressed into the working volume, which could lead to dangerous sudden steam development, but the liquid in the heat exchanger is displaced by the inflowing working fluid. If the hot gas to be cooled is introduced directly into the pipeline system of the entropy transfer device (see FIG. 1) at 19 and is removed again at 15, the losses and the structural outlay of the heat exchanger 18 can be eliminated.
  • the hydraulic pistons 21, 22 and 23 exchange mechanical power via a controlled valve system 29 of the control system via a hydraulic pump 30 with a flywheel 31 and a component 32 acting as an electric motor and / or generator.
  • Working fluid can be exchanged from the part of the pipeline system 19 to the flow channel 12 by a valve 33, optionally driven by a fan 34 or not by a further valve 35.
  • the valve 33 remains closed for the time being.
  • the justifiable, simplifying assumption is made that the working fluid as the ideal gas in the coolest partial volume always has the temperature T k , ie only isothermal processes take place there.
  • the sequence of movements is determined by the control system and is rough and sufficient for the following analysis in Fig.4, Fig.5, Fig.6 I.
  • the mean temperature T mg of which is significantly higher than the cooler temperature T k this gives directly the temporal profile of the mean temperature in the working volume T m (t) and is shown qualitatively in Fig.4, Fig.5, Fig.6 II.
  • the pressure P 0 in the part of the piping system 19 in front of the inlet valves corresponds to atmospheric pressure.
  • the fan 14 is to work in such a way that the pressure P 1 in the space 13 of the pipeline system adjacent to the outlet valve 4 is changed only slightly relative to the pressure difference P 1 - P 2 .
  • the valves 3 and 4 are opened or closed by the (flow) pressure of the gas.
  • the pressure is increased since the inlet valves 3 and outlet valves 4 due to the higher pressure P relative to P 0 but lower relative to P 1 (t) are closed in the work volume.
  • the cool gas in the working volume at the temperature T k the thermal energy delivered to the cooler.
  • the work W abc -Q abc must be performed on the piston by the control system in this period.
  • T 2 is independent of m
  • a W nutz C p * m A * (T 1 - T 2 ) * ⁇ ges
  • Each volume V can be divided into partial volumes V i by a corresponding, possibly very small, division be divided so that V i can be applied without an effective falsification of the thermodynamic description:
  • P * V i N i * k B * T i ;
  • N i P * 1 k B * 1 T i * V i ;
  • k B Boltzmann constant;
  • T i temperature in V i ; N i ⁇ number of gas molecules in V i
  • the working volume is increased by the piston movement.
  • the gas should not flow relative to the heat transfer surfaces which are necessary for the thermodynamic cycle. Since the gas in the entire working volume is in direct contact with heat transfer areas during this period of time to large thermal capacities, which are necessary for the thermodynamic cycle and due to their special movement, the gas is not moved relative to it, this period of the cycle can be described by an isothermal expansion the same formulas apply to the exchanged thermal energy or work as for the time period abc. This makes it possible to store this energy in a vibrating system and to release it again for compression (e.g. by a vibrating water column in a U-shaped tube, possibly with a cavity acting as an air spring as a limitation.
  • the largely homogeneous regenerator structure 11 fills the entire working volume with the heat capacity that is very large in relation to the gas, hereinafter assumed to be infinite, and largely the entire working volume expanded by the displacement of the piston. Due to the special movement, only isothermal processes take place in the arity volume.
  • the working volume be divided into sub-volumes of equal size by E - 1 planes arranged perpendicular to the stroke. Due to the symmetry, the temperature is ideally constant at these levels.
  • the regenerator structure 11 is effectively supplied with energy by the cooling of the hot gas quantity of the mass m A flowing through the inlet valves 3 at each period, since as a result a larger quantity of gas flows from the hot part into the colder part of the regenerator structure 11 than in the reverse flow direction.
  • the exchanged and cooled gas quantity m A is thereby increased by m B and the regenerator system 11 is supplied with a larger quantity of thermal energy during a period.
  • This greater thermal energy is partially withdrawn from the regenerator system 11 in the time period efg during the effectively isothermal expansion of the gas from P 1 to P 0 , a larger pressure ratio P 1 / P 0 being able to be achieved and thus more energy being converted per period overall, whereby the total heat energy exchanged at the regenerator 8 or at the regenerator system 11 as well as the associated thermal losses are increased in a much lower ratio.
  • the mass flow through the adjustable fan can be set in 3 stages (off, medium, large) and the large stage is always switched on by a thermostat when the temperature falls below a certain temperature, the temperature T 2 can thus be sufficient at a relatively low cost Value to be stabilized.
  • the device shown in FIG. 1 can also be operated as a refrigerator, which cools a quantity of gas over a large temperature interval.
  • the then driven fan (turbine) 14 must press the gas from the part of the piping system 19 with the pressure P 0 into the part 13 with P 1 .
  • the direction of flow of the gas is reversed (everywhere in the working volume), the structure of the device and the speed of movement remain as in Fig. 1 and Fig. 4. Fig.5, Fig.6 obtained.
  • the outlet valve 4 becomes an inlet valve in that it is kept open against the flow pressure with an unchanged stop direction in the time period cde, for example by an attacking spring connected to the control system.
  • the gas then flowing in with the pressure P 1 releases thermal energy to the regenerator system 11 during cooling.
  • the regenerator is efg during the time period in which effective isothermal expansion of the gas (such as front, home gas compressor; engine) from P 1 to P 0 withdrawn heat energy.
  • a temperature field T (r) which is linear in the stroke direction is also formed in the regenerator structure 11 in the refrigeration machine by the interaction of the sub-processes in the time periods cde and efg, the mean temperature T m of which in the refrigeration machine is below the Radiator temperature T k is.
  • the average temperature in the working volume when the regenerator system 11 is pushed together is increased in the time period gha.
  • the inlet valves of the engine 3 can act as outlet valves in the refrigerator if they are kept open against the flow pressure in this time period gha, for example by an attacking spring connected to the control system, and gas due to the increase in the mean temperature in the constant working volume at a constant pressure Pressure P 0 flows out into the part of the piping system 19. Before this gas is compressed again by the fan (turbine), it absorbs the heat energy from the cooling of the other gas stream in the heat exchanger 18. If the gas to be cooled is introduced directly into the pipeline system of the refrigeration machine at 15 (cf. FIG.
  • the device shown in FIG. 1 and already described as an engine can, as already largely shown at the front, also be operated as a refrigerator.
  • a greater temperature difference in the amount of gas of the mass m A taken up and given off by the working volume can be achieved if in the period gha a gas amount of the mass m H by in this case at the same stop as Exhaust valve acting valve 35 flows into space 15, which is kept open during this period gha by the control system against the flow pressure.
  • the motor machine shown in FIG. 1 can also be operated as a refrigeration machine, as already shown above. If, as with the engine, a larger pressure difference P 1 -P 0 is also to be used for the cooling machine for a certain cooling, this can be achieved if, in the period gha, the gas quantity of the mass m B is passed through a further (controlled) inlet valve 35 is blown into the flow channel 12 from the room 15 with a fan 34.
  • thermal energy is supplied to the regenerator system 11 during the isothermal compression (with closed valves) of the gas from P 0 to P 1 .
  • the valve T is taken up by the turbine gas at the temperature T H of the working volume at the pressure P 1 , since the mean temperature is lowered.
  • this construction can do the same operated that lukewarm gas at a higher pressure through a turbine in the Working volume pressed and thereby the flow direction but not the periodic movement sequence (see Fig.4, Fig.5, Fig.6) is changed and from the Flush out working volume of hot and cold gas at lower pressure.
  • gas can be cooled below the cooling water temperature T k by an entropy transformer with 2 working volumes.
  • the driven fan 14 is replaced by one of the devices described above with the effect of a gas compressor; the hot gas is taken up by the working volume, which can be assigned to the gas compressor, and is discharged at higher pressure through the outlet valve 4 of this working volume into a space of the piping system, to which a buffering pressure vessel can be connected and from where the gas may be after a previous cooling to about T k flows through the valve 4 acting as an inlet valve into the working volume, which can be assigned to the refrigerator.
  • the gas cooled under T k flows out through the valves 3 and possibly 35.
  • the periodic flow through the valves 35 of the two unit volumes can be set accordingly (as shown above). If the movements shown in FIG. 4, FIG. 5, FIG. 6 I run simultaneously in a work volume, the buffering pressure vessel can be dimensioned smaller or can be omitted. It is also interesting to use this combination as a heat pump for liquids. Other interesting combinations serve to increase the heating number to a value above 1.
  • a hot and cold gas quantity is absorbed by a first working volume as described above and released again as a cool gas quantity at higher pressure, and absorbed by a second working volume which it releases as a warm gas quantity at the outlet pressure. The liquid of a heat exchanger or an additional amount of gas was cooled in the second working volume.
  • FIG. 8 part of a gas compressor (engine)
  • the working volume of an entropy transformer shown in FIG. 8, FIG. 9 or FIG. 10 shows, for example, as part of an engine in comparison with the two that are decisive for thermodynamics in comparison with FIG. 1 or FIG. 4, FIG Differences in:
  • First the work volume is not changed in size.
  • the regenerators are made of a lower V2A perforated plate with as little metal surface as possible, with U-profiles made of V2A welded on for reinforcement and open parallel to the perforated plate, in which metal fibers are sheathed with V2A fabric (wire diameter approx. 0.1 mm) (center of gravity of the diameter at 40 micrometers ) are inserted, which are clamped and enclosed by another perforated plate.
  • the two perforated sheets are held together by a wire winding where the perforated sheets have been deformed in such a way that the outer surfaces of these regenerators have no local elevation despite the wire winding.
  • the perforated plate turns into a plate without holes, whereby the seals are held and sealed to the metal fibers so that they flow through.
  • a working volume filled with gas as working fluid is largely enclosed by a pressure housing 47, inlet 48 and outlet valves 49.
  • the gas can flow through the inlet valves from a space of the piping system corresponding to FIG. 1 in FIG. 1 into the partial volume between the cylinder cover and the regenerator 36 and from a space between the regenerators 39 and 40 through
  • the heat exchanger is in a closed circuit with Liquid from the elements with the reference number 45, 46, 102-106.
  • grating planes 108 to be flowed through by the gas and arranged perpendicular to the direction of rotation are characterized by the control system as in FIG. 9 I, so that they move to this regenerator 41 or the neighboring one , either move the grating plane that is already moving, maintain a certain distance (e.g. 20% of the total stroke) or remain as close as possible to the boundary surface of the pressure vessel.
  • the control system as in FIG. 9 I
  • valves 49 and 48 are opened and / or closed by the (flow) pressure of the gas.
  • the gas has its lowest mean temperature T m (t) in the working volume cf. Fig.9 I reached at time a.
  • the inlet valve is closed by the flow pressure of gas flowing from the working volume due to the increase in the average gas temperature T m in the working volume.
  • the pressure in the time period abc increases from P 0 to P 1 :
  • the compressed gas emits thermal energy to the cooler.
  • the gas in the working volume has reached the highest average temperature T m (t).
  • the outlet valve is closed again by the pressure in the working volume which is lower than that of P 1 .
  • the pressure in the working volume is still too great for the inlet valves to open, so that the reduction in T m (t) leads to a reduction in the pressure P (t) in the working volume.
  • 37 - 40 heat energy is taken from the regenerators; (cf. Q efg ) because the gas flowing through it is expanded again between two regenerators.
  • the maximum average temperature of the gas in the aridity volume is reached.
  • the mass of the gas in the working volume is smaller than in the time period abc.
  • the pressure difference from P 1 - P 0 is already reached after a smaller decrease in T m (t).
  • the amount of gas that flows in is cooled by the release of thermal energy to the regenerators 36-40 and by mixing with cooler gas.
  • a partial volume divided by the components characterized in claim 1 from the working volume is withdrawn from thermal energy during a full period if it is (significantly) smaller during the time period of the pressure increase than during that of the pressure decrease. If all valves on this machine are suddenly closed while the equilibrium is in operation, a process takes place that comes very close to that of a Vuilleumier heat pump. In this case, thermal energy is taken from the partial volumes of the working volume between the regenerators 36-40 and partially released to the cooler.
  • This partial cycle process drives a second partial cycle process which pumps from the partial volume of the working volume, which is only delimited by regenerator 41, into the partial volume which is only delimited from the working volume by regenerator 36.
  • a valve that is controlled by the temperature of the endangered sub-volume can prevent that this process is not started unintentionally by a sticking valve and that it is destroyed by overheating, which valve causes a constant pressure in the working volume in an emergency.
  • the outlet valve is opened by a correspondingly lower selection of the pressure P 1 a small fraction of the time period abc after the point in time a at which the lowest average gas temperature prevails in the working volume, the pressure in the working volume is increased in this cycle process in particular , if the partial volume delimited only by regenerator 41 and the partial volume adjacent to the cooler largely have the maximum size and the partial volume only delimited by regenerator 36 and the partial volumes between two regenerators largely have their minimum size. The other extreme size ratio prevails while the pressure in the working volume is reduced. As a result, the thermal energy with respect to these partial volumes is converted in the opposite direction through this entire cycle process than with closed valves (see above)
  • the pressure P 1 can be selected such that on average no heat energy is removed or supplied to the partial volume of the working volume which is only delimited by the regenerator 36 by the cyclic process.
  • the thermal energy which is supplied to the partial volume of the working volume, which is only delimited by the regenerator 41, due to irreversibilities such as the shuttle effect, heat conduction and the unfavorable efficiency of the regenerator, is at this pressure P 1 by the special one shown in FIG Movement sequence of the regenerator 41 withdrawn and fed to the cooler.
  • the movement sequence characterized in FIG. 10 has the advantage that the flow channels for gas exchange are covered to a lesser extent by the moving regenerators or are better designed.
  • the lower lifting frame 90 must be connected to the lowest regenerator 41.
  • the pressure P1 can be set so that an analog one for the corresponding partial volumes Thermal energy balance results.
  • the partial volume of the working volume between two of the regenerators 36-40 is reduced by the fact that the gas flowing through is further expanded in the time period efg between two regenerators.
  • These partial volumes are supplied with thermal energy during a period by virtue of the fact that, due to the gas quantity of the mass m A, which is hotly taken up into the working volume by the inlet valve 48 and coolly discharged through the outlet valves 49, the regenerators 36-39 flow through the hottest side with one around them Gas quantity of mass m A larger gas volume is flowed through than from the cooler side.
  • a temperature profile with a larger gradient in the flow direction is formed on the cooler side of one of these homogeneously assumed regenerators.
  • one of the partial volumes defined above is supplied with more thermal energy than is extracted by the periodic flow.
  • the heat energy given off during the cooling of the gas quantity m A flowing into the working volume, which flows periodically hot and cooler again, is absorbed in part by the circular processes running parallel between the partial volumes with largely isothermal heat energy absorption and delivery.
  • a linear temperature profile is formed in the working volume, as generally shown in the front of Fig. 4, Fig. 5, Fig. 6.
  • the average temperatures of adjacent partial volumes of the working volume range between two? the regenerators 36-40 with the same size and temporal order of magnitude the same difference as shown in the front to Fig.4, Fig.5, Fig.6 generally.
  • the losses at regenerators 36-39 are partially reduced by W_. Due to the irreversibility, such as heat conduction or the losses of the regenerators, only a smaller pressure ratio P 1 / P 2 is achieved and the gas quantity m A must enter the working volume with a temperature greater than T, especially in a device constructed as in FIG 1 is.
  • One of the valves 49 in FIG. 8 can be used like the valve 35 in FIG. 1 in order to achieve the described changes in the temperature differences when cooling or heating a portion of the exchanged gas at the same ratio of the pressures P 1 / P 0 .
  • the system described above which acts as an engine and has the working volume shown in FIG. 8, can, after a few changes, also be operated as a refrigeration machine which cools a gas quantity over a large temperature interval.
  • the then driven fan (turbine) 14 must press the gas from the part of the piping system 15 with the pressure P 0 into the part 13 with P 1 .
  • the movement sequence shown qualitatively in FIG. 9 I or FIG. 10 I is carried out in the reverse chronological order.
  • the outlet valve 49 becomes an inlet valve in that it is kept open by the control system against the flow pressure in the time period ahg with the stop direction unchanged. In this time period ahg, the partial volumes between these regenerators are increased and the average temperature of the gas in the working volume is lowered from the maximum value.
  • the gas then flowing in with the pressure P 1 releases thermal energy to the regenerators 36 to 39 during cooling.
  • Thermal energy is withdrawn from these regenerators during the subsequent period of time by the expansion of the gas between two regenerators (cf. front: engines). With closed valves, the pressure in the working volume is reduced due to the lowering of the average temperature of the gas to the minimum value by a shift at constant relative distances of the regenerators 36 to 41.
  • a linearly stepped temperature field T (r) is formed in the regenerators 36 to 39, whose average temperature T m at the Chiller is below the cooler temperature T k .
  • the temporal development of T m (t) corresponds to the reversal of the chronological sequence and the replacement of max.
  • the average temperature of the gas in the working volume is increased when the regenerators 36 to 39 are pushed together in the subsequent time period edc.
  • the inlet valve 48 of the engine in FIG. 8 acts as an outlet valve in the refrigerator if it is kept open by the control system against the flow pressure during this period of time edc with the stop direction unchanged and gas and, inter alia, due to the increase in the mean temperature in the constant working volume at constant pressure P. 0 flows out into the part of the piping system 15. Before this gas is compressed again by the fan (turbine), it absorbs the heat energy from the cooling of the other gas stream in the heat exchanger 18.
  • the gas to be cooled is introduced directly into the piping system of the refrigeration machine at 15 (cf. FIG. 1) and is removed again at 15, the losses and the structural outlay of the heat exchanger 18 can be eliminated.
  • the average temperature of the gas in the working volume is increased to the maximum value by the displacement of the regenerators 36 to 39, which leads to a pressure increase and the closing of the cycle due to the closed valves.
  • thermal energy is removed by opening the valve 48 or a valve acting in parallel with it with a smaller cross-sectional area before the pressure difference is completely equalized.
  • the partial volume of the working volume, which is only delimited by regenerator 41 is supplied with thermal energy in that a valve acting in parallel with one of the valves 49 is already opened before the pressure difference is completely equalized.
  • a greater temperature difference in the amount of gas of mass m A taken up and given off by the working volume can be achieved in the device shown in FIG. 1 if, in the time period edc, a gas amount of mass m H is in this case relative to Fig. 8 modified stop as an outlet valve as valve 35 in Fig. 1 acting valve 49 flows into space 15, which is kept open in this time period edc by the control system against the flow pressure.
  • regenerator 208 which is temporarily applied to the regenerator 207 with the regenerator 38 which is occasionally applied to the regenerator 39
  • the regenerator 209 which is occasionally applied to the regenerator 208 with the regenerator 37 which is occasionally applied to the regenerator 38
  • the regenerator 210 which is occasionally applied to the regenerator 209 with the temporarily Regenerator 37 adjacent regenerator 36 firmly connected.
  • the air exchange through the air guide tubes 205 and 211 takes place predominantly simultaneously, as does the air exchange through the air guide tubes 50 and 212.
  • One of the valves 49 or one of the valves 213, through which the air flows out of or into the air guide tube 212, is used with a changed stop direction like the valve 35 in FIG. 1.
  • This construction can also be operated in such a way that lukewarm gas at higher pressure is periodically pressed into the working volume by a turbine and hot and cold gas periodically flow out of the working volume at a lower pressure. Both the cycle shown at the front of the heat pump and the one at the chiller can be used.
  • the respective temperature differences can additionally with a valve that like that Valve 35 acts to be adjusted.
  • gas can be cooled below the cooling water temperature T k by an entropy transformer with 2 working volumes.
  • the driven fan 14 is replaced by an engine described above, the hot gas being taken up by the working volume which can be assigned to the engine and, at higher pressure, through the outlet valve 49 or 4 into a space of the piping system is delivered, to which a buffering pressure vessel can be connected and from where the gas, possibly after a previous cooling to approx. T k, flows through the valve 49 acting as an inlet valve into the working volume which can be assigned to the refrigerator. From this working volume, the gas cooled under T k flows out through valves 48 and possibly valve 49, which acts like valve 35.
  • the periodic flow through these valves of the two working volumes can be set accordingly. If the movements shown in Fig. 4, Fig. 5, Fig. 6 I occur simultaneously in a working volume, the buffering pressure vessel can be dimensioned smaller or can be omitted.
  • This combination can also be used as a heat pump to heat a liquid be used.
  • a hot and cold gas quantity is absorbed by a first working volume as described above and released again as a cool gas quantity at higher pressure, and absorbed by a second working volume which it releases as a warm gas quantity at the outlet pressure.
  • the liquid of a heat exchanger or an additional amount of gas was cooled in the second working volume.
  • the gas temperature is changed only relatively slightly, since the gas volume flowing through in one period is significantly larger compared to the size of the partial volume of the working volume between two regenerators. This reduces the irreversibility of gas and heat transfer surfaces of the regenerators.
  • the working volume largely enclosed by a cylinder as the pressure housing 110, the valves 111, 112 and the slidingly sealed piston 113 is divided into partial volumes by cylindrical displacers 114:
  • the working fluid can flow around these displacers 114, the gap between the displacer and the cylinder wall acting as a regenerator, in the direction of the cylinder axis they are 3 to 10 times larger than their maximum length of movement against the pressure housing.
  • cooling lines 115 cool outside the pressure housing.
  • a single displacer 114 acts like one of the corresponding regenerators 36-40 in FIG. 8.
  • the argumentation to Fig. 9 can be adopted directly with a transferable movement sequence.
  • Valves 111 and 112 correspond to valves 49 and 48, respectively.
  • the displacers 114 are driven by a bundle of concentric tubes 109, the tube with the largest diameter slidingly sealing against the piston 113 and any other tube to the two tubes with the next smaller or next larger diameter becomes.
  • the drive can then take place with only a relatively small change in the working volume (up to 10%) by means of the piston 113 by means of a lever construction 117 as in FIG.
  • the corresponding connecting rods of the chain drive described in FIG. 8 can act directly on the corresponding tubes of the tube bundle 109.
  • This machine can also be used for operation with a liquid as a working fluid Working volume can be designed.
  • the working volumes of the entropy transformers in Fig. 22 can be described thermodynamically by the same models that can be connected to Fig. 4, Fig. 5, Fig. 6 or Fig. 9.
  • the working volume is largely delimited by a pressure housing 128, inlet and outlet valves 130 and 129a, b.
  • the regenerators 131-136 which are stationary relative to the pressure housing, the partition walls 137-141 connected to the regenerators 131-135, walls of the pressure housing and displacers 142-146 slidingly sealed on these walls, delimit partial volumes.
  • the periodic change in size of these partial volumes corresponds to the periodically changed stroke difference of the corresponding regenerators in FIG.
  • the displacers 142-145 can be periodically moved simultaneously.
  • the racks 146-149 attached to these displacers are driven by gears on a shaft 150a.
  • This shaft is sealed by the pressure housing out of the working volume and on it the ends of a chain 150 are wound up or unwound, which is stretched over two sprockets 151 and on which the connecting rod 152 engages such a chain transmission control, which in FIG Regenerator 36 drives.
  • this chain transmission through the shaft 154 driven by an electric motor, another similar chain transmission 155, which moves the displacer 146 in the same way, is connected in such a way that there is a phase shift of approximately a quarter period with the movement of the other displacers.
  • each of the displacers 142-145 in FIG. 22 adjoins one of the partial volumes between two of the regenerators 131-135 and the partial volume adjacent to the cooler 156.
  • the displacers 142-145 may practically no longer be flowed around, otherwise the desired balance will not be formed.
  • the displacers have slots in the region which is inserted between two regenerators, from one regenerator to the other and in the stroke direction , The resulting dead volume can have a very unfavorable effect in some applications.
  • Another valve 129 can be used like valve 35 in FIG.
  • FIG. 22 As shown in FIG. 8, the construction of FIG. 22 as an engine, Chiller, heat pump, ... are trained or used.
  • the construction shown in Fig. 22 is modified as shown in Fig. 23.
  • the displacement pistons are designed as a vibrating liquid column with a float in a U-shaped container.
  • the movement of the liquid displacement piston is controlled and driven by a belt 159 which is tensioned on a shaft 158 and which is attached to the float 157. Since the liquid displacement pistons perform largely the same periodic movements, as explained for FIG. 22 with FIG. 9, several of the liquid displacement pistons corresponding to the displacement pistons 142-145 can also be driven from a shaft 158 corresponding to 150 a in the operating state with this construction.
  • the periodic movement of this shaft 158 can be controlled and / or driven as described in FIG. 22.
  • each of the regenerators 131-134 in FIG. 22 must be provided with a heat exchanger on the same side with regard to the flow as in regenerator 135. The liquid can then flow through these heat exchangers in sequence and thereby exchange thermal energy at several temperature levels (see Fig. 3).
  • the thermal energy given off by the exhaust gas of a gasoline or diesel engine during cooling can be used to generate additional mechanical or electrical energy or to charge the engine with filtered fresh air at a higher pressure, thereby avoiding the need to use mechanical energy for a turbocharger or compressor. whereby, compared to an engine without this supercharging, a better output volume and in any case a better efficiency can be achieved. Compared to an engine without charging, a cheaper engine power volume with an improved efficiency is possible, since when the engine is charged by a compressor or turbocharger, the compression of the air takes place with a less efficient efficiency. Further synergy effects are achieved in that no turbine and no additional generator are required to convert the energy of the compressed air into electrical energy.
  • the thermal energy emitted by the exhaust gas of a gas turbine during cooling can be used to supply the cool gas with filtered, cool fresh air at higher pressure.
  • the compressor of the gas turbine used can be designed so that it requires less drive energy with unchanged pressure in the combustion chamber and with unchanged gas flow, which leads directly to a greater useful output with the same fuel consumption and better efficiency.
  • the efficiency in this case is greater due to a synergy effect than the sum of the efficiency of the original gas turbine and the efficiency of the thermal compressor (gas compressor), since the power applied by the thermal compressor for gas partial compression from the original compressor of the gas turbine only with less favorable Efficiency can be achieved, driven by the branching of mechanical shaft power. Possibly. it is also possible to use a conventional gas turbine.
  • a relative pressure increase in the gas turbine can then be expected, which decreases continuously from the fresh air inlet to the exhaust gas outlet, as a result of which the power density and efficiency are increased.
  • the area of the regenerators 274 - 277 through which flow is required must be increased accordingly.
  • the stationary regenerators 274-277 are folded several times at a substantially constant distance along parallels 278 and enclose at least one disk-shaped displacer element 279, which is periodically moved parallel to it, up to the area of the central axis of the displacer element parallel to the folded edges on both sides.
  • the other half of the displacement element is surrounded by the adjacent regenerator.
  • the folded edges of the regenerator are accordingly on concentric circles.
  • At least one of the regenerators is optionally available with one in the stroke direction movable hydraulic or pneumatic pistons or diaphragm bellows connected by Liquid or gas from the room around the corresponding work area removed liquid surface of the coupled vibrating liquid column is filled or filled via control valves.
  • two-part displacement structure is necessary to be able to realize the movement either by means of a rod or a tensioned tension element (such as a rope or chain) a flexible connection from an endless traction element like a closed chain or toothed belt, tapped, which non-positively over several, with relative even angular speed rotating wheels is so tense that the angle between the two elements in time periods of the operating state in which the driven element in the working space (regenerator, displacer) only slightly should be moved about 90 ° and the smaller the faster the movement of the driven element in the work space.
  • a tensioned tension element such as a rope or chain
  • a pipeline system with negative pressure like the boiler via a heater is coupled to the inlet valve of a heat engine according to the invention. This system is used as a vacuum cleaner.
  • each regenerator is connected to a sheet metal cylinder jacket 285 or a comparable jacket of a pointed truncated cone, which is continuously immersed in a liquid 286 at the lower end and thus prevents flow around the regenerator during stroke movements parallel to the cylinder axis of the sheet metal jacket.
  • Truncated cones which become narrower at the top, are favorable and unproblematic as a shape for the sealing element 285 immersed in the liquid and the side housing 280, since the upper region is expanded due to the temperature increase.
  • the cone-obtuse angle must be relatively acute so that the gap between two sealing elements 285 does not widen too much when they are moved apart, since irreversible processes take place in this gap due to the heat transfer.
  • Concentric tubes 286 are used to drive and guide the regenerators and sealing cylinders, which are guided on an unmoved tube 287 on the common axis of the cylinders and are connected to the regenerators 281-285 in the region of the cone tips.
  • the tubes 286 are provided with at least one slot in the axial direction, through which the internal tubes are connected to the corresponding regenerators 281-284.
  • the tubes 287 protrude decisively upwards over the uppermost regenerator 281 into a special bulge 288 of the work space enclosed by the housing and are slidably guided there on an unmoved tube 287.
  • Below the liquid surface 288, the cylinders 285 are also each connected to one of the tubes 286, which are also slidably guided in this area.
  • the space between the liquid surface 288 and the lowermost regenerator 284 at its lowest position in the operating state is largely filled by an at least two-part displacer structure 289, which is moved apart during an upward movement and releases flow channels for the working gas at the separating surfaces which run at an angle to the direction of movement.
  • This displacer structure 289 is also guided in the region of the cylinder axis and either moved via a separate drive or by springs between the regenerator 284 and individual displacement elements and a spring-loaded stop for the stop at the liquid interface 288. If, alternatively, this displacer 289 is permanently connected in one piece form to the lowest regenerator 284, then two parts have to be moved less.
  • the heat exchanger 290 is either attached directly below the lowermost regenerator 284 and flows through a heat exchange medium, or it is attached to the cylinder 285 and / or the corresponding pipe 286 with the lowest regenerator 284 and immersed in the lowest position in the liquid 286, whereby the heat energy is exchanged, which is compensated for in continuous operation by a stationary heat exchanger, which is connected, for example, to the hot water supply of the building.
  • Working gas is exchanged periodically by at least one valve 291 in the housing above the uppermost regenerator 281.
  • This exchange is compensated for by the exchange of working gas, which takes place from the partial space above the lowermost regenerator 284 through at least one piercing tube attached directly to one end in the stroke direction, which is always immersed in the liquid 286.
  • a tube 293, which projects beyond the liquid level 288 and from which the gas exchange takes place through at least one valve 294, is arranged in a concentric manner in a sealed manner with the housing.
  • Intermediate levers are movably attached to a plurality of regenerators 281 - 284 or elements rigidly connected to them, which are each movably connected at the other end to different locations of at least one further main lever, which is movably connected either directly or via a lever to the housing.
  • the top regenerator 281 directly or indirectly movably engages the main lever at a location that is closest to the location where the direct or indirect movable connection to the housing occurs.
  • the mirror symmetry of this lifting arrangement to a plane in which the stroke direction lies also means that no lateral forces are transmitted to the regenerator structure, in particular if the lever arrangement takes place below the centroids.
  • One of the lowest regenerators is movably connected via connecting rods 298 to two driven crankshafts 299, which are arranged and moved mirror-symmetrically to a plane in which the stationary guide element 287 lies in the stroke direction.
  • Lower regenerative forces relative to the stroke direction which would have to be absorbed by the guides 300 and lead to additional wear, are transmitted to the regenerator arrangement 281-285, in particular if the connecting rods 298 run below the center of gravity of the regenerators 281-284 Masses are attached to the crankshaft 299 opposite the connecting rod bearing, which at least partially compensate for the weight of the regenerator arrangement due to their weight.
  • regenerators are at least each movably connected to one of the connecting rods, which are supported at the other ends on axles of at least one crankshaft, all of which can be cut by a line through the axis of rotation of the crankshaft parallel to it, whereby the bearing for a connecting rod of the lowest regenerator is furthest from the axis of rotation of the crankshaft and the bearing of the highest regenerator is closest.
  • At least one regenerator is driven with a phase shift of a quarter (25%) of a period in relation to the change in volume.
  • work area work volume
  • the periodic intake takes place and when operating as a heat pump or refrigeration machine, the working fluid is periodically released through a valve 291, which is activated in the work area adjoins a partial space 301 with constant volume, which is completely enclosed by two regenerators 302-303, one of these regenerators 302 being relatively directly adjacent to the housing.
  • At least one guide element in the stroke direction 287 is at least partially designed as a threaded rod or recirculating ball screw, and by means of an element engaging therein, at least one regenerator connected to it is moved in the lifting direction by rotating the threaded rod or Kubelumlspindel.
  • the threaded rod or ball screw has areas with different pitches, in which the connecting elements of the regenerators moving at different speeds engage, so that when the threaded rod or ball screw rotates at different speeds they are moved in the stroke direction, so the number of movable Parts can be significantly reduced.
  • a heat engine according to the invention can thus be constructed with only five moving parts and the necessary valves.
  • the regenerators are periodically moved up and down in the direction of stroke when the ball screw rotates at a constant speed, or at least one threaded rod or ball screw is rotated periodically in different directions by using a cube screw and interlocking connecting elements, each with a closed, intersecting threaded path either by a mechanical control system or directly by an appropriately controlled motor
  • the bottom regenerator engages in a ball screw with a closed path and at least a part of the other regenerators in rather ordinary thread paths whose paths are not closed. This prevents the bottom regenerator from hitting the liquid surface.
  • the guide tube is flowed through periodically or continuously in the middle of working gas from the coolest part.
  • a radial fan is connected to the pipe with thread or ball screw and the pipe in this area is opened laterally as well as in the coolest part on the other side of the pipe center.
  • a separate pipeline for working gas leads from the space adjacent to one opening of the guide tube to the space adjacent to the other opening in the area of the liquid surface.
  • a tube 306 is stirred in the stroke direction with an opening above the liquid surface 288 from the housing 280.
  • the other end of the coupled pipe 304 of the periodically resonating liquid column 305 is connected to a pressure vessel 306.
  • a valve 312 is attached to the connection from the working space to the tube with the vibrating liquid column, which has a stop in the flow direction to the working space, against which the valve plate 313 is pressed in a sealed manner as soon as the liquid column has moved too far in the direction of the working space.
  • this valve is closed, the excess pressure which builds up in front of it can pass through a pressure relief valve leading from this space 308 to the pipe system of the vibrating water column and a special pipe (into the pressure vessel) to the other end 309 of the vibrating liquid column 305.
  • Another pressure relief valve 315 coupled to the same space 308, leads to an external container 316 instead of the pressure vessel 309.
  • the liquid level in this container is kept constant at the highest possible level. It is connected to a further check valve with one end of the pipe system around the vibrating water column, through which a small amount of the liquid can flow back again in certain time periods.
  • a tube 295a extending in the stroke direction is fastened to the lowest periodically moving regenerator, into which gas can flow in and out unhindered from the part space above it and the bottom end of which is always immersed in the liquid.
  • a pipe 295b is arranged concentrically in this pipe 295a, sealingly connected to the housing, the upper edge of which corresponds to the height of the maximum liquid surface 288 applied to the sealing cylinder 285 of the regenerator and that in an area in the working space above the safety valve 313 at the access to the vibrating water column 305 leads from which the possibly overflowing liquid reaches the liquid of the vibrating liquid column 305.
  • a tube 299, the upper edge of which ends in the lowermost subspace at the level of the desired liquid surface 288 in the working space, is connected as far as possible to the previously described tube 295, which leads to the vibrating liquid column 305.
  • a porous structure 297 is integrated from the confluence into the previously described pipe system, which cannot be flowed around.
  • a valve supplies the machine with a certain amount (eg 3l) of liquid each time the machine is rigid. The rest of the management of the different amounts of liquid in the machine is done automatically with the construction described above and the functional relationships.
  • the pressure vessel can optionally be replaced by another work space, in which the thermodynamic cycle with an identical period by half Period is staggered
  • a bulk material storage works well thermodynamically and becomes bearable Effort built up by flowing through the heat transfer medium (e.g. air) Bulk material 348 through at least one insulating, non-flowable intermediate layer 349 in concentric shells with cylindrical mantle with vertical axis and after outside vaulted floor and top surfaces is divided and the flowable Transitions 350 from an inner, filled with Schürgut to the adjacent outer shell through openings in the insulating cylinder jacket 349, which are arranged on both sides in the area of a plane through the cylinder axis and the flow through non-flow bores running in the area of this plane Connections are made so that the shells only in one direction of rotation can flow through the vertical cylinder axis.
  • the heat transfer medium e.g. air
  • a transition between two half-shells filled with bulk material is only possible when flowing through a vertical shaft 351, via which the heat transfer medium can also be exchanged.
  • the flow can be controlled by reducing the inflow channel in places so that only heat transfer medium flows in a narrow temperature range in the shaft.
  • One of the outermost insulation layers 352 becomes a bed layer flowed through others. This creates a decisive curvature of the Temperature profile out, which due to the smaller slope on the cooler Side only a lower loss of heat energy flow than without the flow through the temperature gradient occurs.
  • the bulk material storage becomes hot when it cools down Incoming and coolly flowing air heated to well over 100 ° C and the Bulk storage is removed a few weeks later by air, which flows into the outer storage area at approx. 50 ° C and through one of the Air channels at 120 ° C - 150 ° C is removed and then cooled by a heat exchanger, which heats water from approx. 40 ° C to 100 ° C isolated water storage in the lower area and in the upper area is fed.
  • the waste heat from the heat engine operated as a hot gas engine is used in houses to supply energy for heating and hot water.
  • a memory is interposed to decouple the operation of the machine from the heat requirement.
  • a high synergy effect is achieved if the storage is not filled with pure water, but with organic waste and faeces. Especially when seasonal heat storage is sought, the faeces in the summer are too hot for decomposition reactions or the generation of biogas to take place to a significant extent. This effect is used in a similar way when preserving fruit. If this storage facility is cooled in late autumn or winter, biogas production can begin. This not only saves heat energy seasonally, it also indirectly stores biogas

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Claims (26)

  1. Procédé pour le transfert d'entropie à l'aide d'un cycle thermodynamique périodique ouvert avec
    au moins un volume de travail qui est rempli d'un fluide de travail et
    au moins un volume partiel central dans le volume de travail, qui se trouve entre deux surfaces isothermes et dont la taille peut être modifiée périodiquement,
    le volume partiel central étant traversé par le fluide de travail d'une surface isotherme à l'autre,
    un échange de fluide de travail ayant lieu à différents niveaux de pression et à différentes périodes de temps (c-d-e, g-h-a) depuis le volume de travail vers au moins un volume à pression largement constante et/ou depuis au moins un volume à pression largement constante vers le volume de travail,
    la modification périodique de la taille de l'au moins un volume partiel central contribuant à provoquer une modification de la température du fluide de travail, dont la moyenne a été faite par l'intermédiaire du volume de travail,
    la taille d'au moins un volume partiel central étant modifiée lors de l'échange de fluide de travail à pression largement constante,
    l'au moins un volume partiel central étant maintenu largement constant dans sa taille ou dans son rapport de taille en fonction du volume de travail lorsque durant (a-b-c, e-f-g), sans échange de fluide de travail, la pression dans le volume de travail est modifiée,
    de la chaleur étant injectée dans la zone des au moins deux surfaces isothermes et/ou éjectée de cette zone,
    un autre volume partiel étant respectivement adjacent des surfaces isothermes traversées par le flux et entourant l'au moins un volume partiel central, le fluide de travail ayant des températures différentes dans les volumes partiels et la taille des volumes partiels étant modifiée périodiquement et
    soit une absorption d'énergie thermique par le fluide de travail soit une restitution d'énergie thermique au fluide de travail dans le volume de travail par au moins une substance d'au moins un flux de masse s'accroissant et décroissant continuellement ou périodiquement sous une température changeante ou sous plusieurs niveaux de température ayant lieu lors d'un intervalle de temps beaucoup plus long par rapport à la durée des périodes du cycle.
  2. Procédé selon la revendication 1, caractérisé en ce que l'absorption de fluide de travail dans le volume de travail et la restitution de fluide de travail par le volume de travail ont lieu respectivement à partir de volumes partiels, qui ont une température différente et qui sont séparés par une des surfaces isothermes, dans la zone desquelles le fluide de travail absorbe et/ou prélève de l'énergie thermique.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce qu'un autre échange de fluide de travail a lieu lors de mêmes périodes de temps et à des niveaux de pression qui sont approximativement les mêmes.
  4. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la taille de l'au moins un volume de travail est modifiée périodiquement.
  5. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la taille de l'au moins un volume de travail est modifiée périodiquement principalement lors des périodes de temps (a-b-c, e-f-g, voir les figures 4-6), lors desquelles il n'y a pas d'absorption de fluide de travail par le volume de travail ou de restitution de fluide de travail dans le volume de travail.
  6. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une substance est le fluide de travail.
  7. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que le cycle ouvert périodique est entraíné à l'aide d'énergie solaire, de géothermie, d'énergie issue de la combustion, en particulier issue de matières brutes qui repoussent, de chaleur dissipée ou d'énergie nucléaire.
  8. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'énergie d'entraínement fait l'objet d'un stockage intermédiaire dans un lieu de stockage traversé par la substance et ayant en particulier la forme d'un remblai.
  9. Dispositif pour la réalisation du procédé selon l'une quelconque des revendications précédentes
    avec au moins un volume de travail (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) rempli d'un fluide de travail (301, 310) se trouvant dans un réservoir sous pression (1, 128, 302, 288, 107),
    avec au moins deux dispositifs (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) pouvant être traversés par le fluide de travail pour inclure dans le volume de travail au moins un volume partiel central (11, 36-41, 131-135, 207-210, 281-284, 275-277) dont la taille peut être modifiée périodiquement,
    avec au moins un moyen (21-24, 29-32, 55-91, 117, 150-155, 298-300) pour la modification périodique de la taille de l'au moins un volume partiel central, de sorte qu'une contribution à la modification de la température du fluide de travail, dont la moyenne a été faite par l'intermédiaire du volume de travail, est ainsi apportée lors de l'échange de fluide de travail à pression largement constante et que l'au moins un volume partiel central est maintenu largement constant dans sa taille ou dans son rapport de taille en fonction du volume de travail lorsque, sans échange de fluide de travail, la pression dans le volume de travail est modifiée,
    avec au moins un moyen (146, 2, 22, 29-32, 113, 304-316, 11, 36-41, 131-135, 207-210, 281-284, 275-277) pour la modification de la pression dans le volume de travail et
    avec au moins un moyen (18, 8, 11, 36-41, 131-135, 207-210, 281-284, 275-277, 7, 43, 115, 156, 290) pour une absorption d'énergie thermique par le fluide de travail ou une restitution d'énergie thermique au fluide de travail dans le volume de travail par au moins une substance d'au moins un flux de masse s'accroissant et décroissant continuellement ou périodiquement sous une température changeante ou sous plusieurs niveaux de température lors d'un intervalle de temps beaucoup plus long par rapport à la durée des périodes du cycle,
    au moins une vanne (3, 4, 48, 49, 111, 112, 130, 129a, 129b, 291, 294) étant ouverte pour l'échange de fluide de travail à différents niveaux de pression pour l'absorption de fluide de travail à partir d'au moins un volume à pression sensiblement constante (13, 20, 19, 17) ou pour la restitution de fluide de travail dans au moins un tel volume,
    le fluide de travail absorbant et/ou restituant de l'énergie thermique et des surfaces respectivement isothermes, qui sont reliées entre elles par des moyens d'étanchéité (285, 288, 101, voir la figure 13) ou par la limitation du volume de travail (1, 44), s'étendant dans la zone des au moins deux dispositifs (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) pouvant être traversés par le flux et
    respectivement un volume partiel à température différente, dont la taille peut être modifiée périodiquement, étant adjacent sur le côté des surfaces isothermes opposé au volume partiel central dans la zone des dispositifs (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) pouvant être traversés par le flux.
  10. Dispositif selon la revendication 9, caractérisé en ce que dans la zone de la surface isotherme, à l'endroit où a lieu l'échange d'énergie thermique, est disposé un régénérateur (8, 11, 36-41, 131-135, 207-210, 281-284, 275-277).
  11. Dispositif selon l'une quelconque des revendications précédentes 9 à 10, caractérisé en ce que dans la zone de la surface isotherme, à l'endroit où a lieu l'échange d'énergie thermique, est disposé un échangeur de chaleur (7, 43, 115, 156, 290).
  12. Dispositif selon l'une quelconque des revendications précédentes 9 à 11, caractérisé par un système de commande (21-24, 29-32, 55-91, 117, 150-155, 298-300) pour une mise en mouvement périodique les uns par rapport aux autres des au moins deux dispositifs traversés par le flux (11, 8, 36-41, 43, 114, 207-210, 281-284) afin de réduire pendant au moins une période de temps jusqu'au volume inerte le volume partiel central entre les dispositifs traversés par le flux (11, 8, 36-41, 43, 114, 207-210, 281-284).
  13. Dispositif selon l'une quelconque des revendications précédentes 9 à 12, caractérisé en ce que les au moins deux dispositifs traversés par le flux (114, 131-135, 156, 274-277) sont montés de manière fixe dans le compartiment de travail et en ce que le volume partiel central situé entre eux est réduit pendant au moins une période de temps jusqu'au volume inerte par au moins un élément de refoulement (279, 114, 142-145) introduit périodiquement entre eux par le système de commande (117, 150-155).
  14. Dispositif selon l'une quelconque des revendications précédentes 9 à 12, caractérisé en ce que les au moins deux dispositifs pouvant être traversés par le flux sont configurés comme pistons de refoulement (114) pouvant être déplacés l'un contre l'autre, le volume partiel central se trouvant entre respectivement deux pistons de refoulement (114).
  15. Dispositif selon l'une quelconque des revendications précédentes 9 à 14, caractérisé par un dispositif de compression (2, 22, 29-32, 113, 304-316) pour la modification périodique de la taille du volume de travail.
  16. Dispositif selon la revendication 15, caractérisé en ce que le dispositif de compression comprend au moins une colonne de liquide mobile (304).
  17. Dispositif selon la revendication 15 ou 16, caractérisé en ce que dispositif de compression pour la modification périodique de la taille du volume de travail est un système oscillant résonnant (304-316) accordé avec les autres mouvements périodiques.
  18. Dispositif selon l'une quelconque des revendications 15 à 17, caractérisé en ce que le système de commande est conçu pour la commande et la régulation du dispositif de compression (2, 22, 29-32, 113).
  19. Dispositif selon l'une quelconque des revendications précédentes 9 à 18, caractérisé en ce que les dispositifs pouvant être traversés par le flux (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) servent à la séparation, au nettoyage ou à la modification physique ou chimique d'au moins une substance contenue dans le fluide de travail et agissent en particulier comme catalyseurs.
  20. Dispositif selon l'une quelconque des revendications précédentes 12 à 19, caractérisé en ce que la direction de déplacement et l'axe de symétrie des dispositifs pouvant être traversés par le flux (11, 8, 36-41, 43, 114, 207-210, 281-284) sont verticaux et en ce qu'en particulier les dispositifs pouvant être traversés par le flux ont une forme de cône.
  21. Dispositif selon l'une quelconque des revendications précédentes 12 à 20, caractérisé en ce que respectivement deux des dispositifs pouvant être traversés par le flux (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277), qui ne sont pas directement voisins, sont reliés entre eux en direction de déplacement et avec un espacement fixe par des éléments et en ce que respectivement deux dispositifs pouvant être traversés par le flux directement voisins se déplacent périodiquement l'un vers l'autre et s'éloignent de nouveau périodiquement l'un de l'autre.
  22. Dispositif selon l'une quelconque des revendications précédentes 9 à 21, caractérisé par une turbine (14), qui est reliée à deux compartiments (13, 15) dans lesquels règnent des pressions différentes, les deux compartiments (13, 15) étant reliés avec le volume de travail par l'au moins une vanne (3, 4, 48, 49, 111, 112, 130, 129a, 129b, 291, 294).
  23. Dispositif caractérisé par une disposition en série d'une pluralité de dispositifs selon l'une quelconque des revendications précédentes 9 à 22.
  24. Dispositif caractérisé par une disposition en parallèle d'une pluralité de dispositifs selon l'une quelconque des revendications précédentes 9 à 22.
  25. Dispositif selon l'une quelconque des revendications 15 à 24, caractérisé en ce qu'au moins un des dispositifs pouvant être traversés par le flux (11, 8, 36-41, 43, 114, 131-135, 156, 207-210, 281-284, 275-277) est entraíné avec un décalage de phase d'un quart (25%) par rapport au dispositif de compression (2, 22, 29-32, 113, 304-316).
  26. Dispositif selon l'une quelconque des revendications précédentes 9 à 25, caractérisé par son utilisation dans le cadre d'un couplage force-chaleur, en particulier dans des réseaux thermiques locaux et distants.
EP98955343A 1997-09-26 1998-09-23 Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique Expired - Lifetime EP1017933B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19742520 1997-09-26
DE19742660 1997-09-26
DE1997142660 DE19742660A1 (de) 1997-09-26 1997-09-26 Verfahren und Vorrichtung zur Nutzung von Sonnenenergie oder Wärmequellen zur Transformation von Entropie
DE19742520 1997-09-26
PCT/DE1998/002827 WO1999017011A1 (fr) 1997-09-26 1998-09-23 Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique

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EP1017933A1 EP1017933A1 (fr) 2000-07-12
EP1017933B1 true EP1017933B1 (fr) 2003-08-20

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US (1) US6470679B1 (fr)
EP (1) EP1017933B1 (fr)
JP (1) JP2001518592A (fr)
KR (1) KR20010082498A (fr)
CN (1) CN1273623A (fr)
AP (1) AP2000001794A0 (fr)
AT (1) ATE247773T1 (fr)
AU (1) AU753000B2 (fr)
BR (1) BR9812554A (fr)
CA (1) CA2304570A1 (fr)
DE (2) DE19881421D2 (fr)
EA (1) EA200000257A1 (fr)
IL (1) IL135136A0 (fr)
NZ (1) NZ503628A (fr)
OA (1) OA11343A (fr)
TR (1) TR200001624T2 (fr)
WO (1) WO1999017011A1 (fr)

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Also Published As

Publication number Publication date
BR9812554A (pt) 2000-07-25
IL135136A0 (en) 2001-05-20
DE19881421D2 (de) 1999-10-28
TR200001624T2 (tr) 2000-10-23
EA200000257A1 (ru) 2000-12-25
AU753000B2 (en) 2002-10-03
EP1017933A1 (fr) 2000-07-12
WO1999017011A1 (fr) 1999-04-08
ATE247773T1 (de) 2003-09-15
US6470679B1 (en) 2002-10-29
CN1273623A (zh) 2000-11-15
AP2000001794A0 (en) 2000-06-30
NZ503628A (en) 2003-05-30
OA11343A (en) 2003-12-10
KR20010082498A (ko) 2001-08-30
JP2001518592A (ja) 2001-10-16
CA2304570A1 (fr) 1999-04-08
AU1223599A (en) 1999-04-23
DE59809356D1 (de) 2003-09-25

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