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EP2574738A1 - Installation de stockage d'énergie thermique - Google Patents

Installation de stockage d'énergie thermique Download PDF

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Publication number
EP2574738A1
EP2574738A1 EP11183267A EP11183267A EP2574738A1 EP 2574738 A1 EP2574738 A1 EP 2574738A1 EP 11183267 A EP11183267 A EP 11183267A EP 11183267 A EP11183267 A EP 11183267A EP 2574738 A1 EP2574738 A1 EP 2574738A1
Authority
EP
European Patent Office
Prior art keywords
fluid energy
energy machine
thermal fluid
working gas
machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11183267A
Other languages
German (de)
English (en)
Inventor
Daniel Reznik
Henrik Stiesdal
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to EP11183267A priority Critical patent/EP2574738A1/fr
Priority to PCT/EP2012/068858 priority patent/WO2013045437A1/fr
Priority to CN201280048050.6A priority patent/CN103842623A/zh
Priority to EP12769071.7A priority patent/EP2748435A1/fr
Priority to US14/346,729 priority patent/US20140338329A1/en
Publication of EP2574738A1 publication Critical patent/EP2574738A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
    • 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas

Definitions

  • the invention relates to a system for storing thermal energy having a circuit for a working gas.
  • This circuit can be designed to be open, so that it sucks air as working gas from the environment and blows them back into the environment; that is, the environment belongs to the cycle. It is also possible a closed circuit in which any working gas (including air) can be used.
  • the following units are connected in the order indicated by a working gas line: a cold storage, a first thermal fluid energy machine, a heat storage, and a second thermal fluid energy machine. In the flow direction of the working gas seen from the cold storage to the heat storage while the first thermal fluid energy machine is connected as a working machine and the second thermal fluid energy machine as an engine.
  • thermal fluid energy machine used as a work machine is thus operated as a compressor or as a compressor.
  • an engine performs work, wherein a thermal fluid energy machine for performing the work converts the thermal energy available in the working gas.
  • the thermal fluid energy machine is thus operated as a motor.
  • thermal fluid energy machine forms a generic term for machines that can draw thermal energy from or supply thermal energy to a working fluid, in the context of this application, a working gas.
  • thermal energy is meant both thermal energy and cold energy.
  • Thermal fluid energy machines Also referred to below as fluid energy machines in the following
  • hydrodynamic thermal fluid energy machines can be used, the wheels allow a continuous flow of the working gas.
  • axially acting turbines or compressors are used.
  • the object of the invention is to provide a system for storing thermal energy of the type specified (for example, conversion of mechanical energy into thermal energy with subsequent storage or conversion of the stored thermal energy into mechanical energy), with or with the high efficiency at the same time reasonable expense of the units used is possible.
  • the moistening unit is understood to mean a device through which the working gas can flow, in which steam is supplied to the working gas.
  • the air should be moistened to at most the saturation limit of water vapor.
  • a humidification of the working gas eg air
  • the cycle of the system according to the invention for storing thermal energy is used with its moistening unit to convert the energy stored in the heat storage and cold storage on the second thermal fluid energy machine into mechanical energy. This can be used, for example, for driving an electric generator.
  • the stored thermal energy is then used in times of great demand for electrical energy to make these available by means of the system.
  • the system for storing thermal energy can be used to convert the electrical energy into mechanical energy, for example via an electric motor, and into thermal energy via the fluid energy machines.
  • reversing the process does not use the humidification tower. This must therefore be bypassed for example by means of suitable bypass lines.
  • Another possibility is to provide for the charging process of the cold storage and the heat storage in the system a separate circuit. This can also be equipped with additional fluid energy machines.
  • bypass lines they must be suitable for this, the first thermal fluid energy machine and to switch the second thermal fluid energy machine so that the heat storage is in the flow direction of the working gas in front of the cold storage. This can be achieved by reversing the flow direction in the piping system.
  • bypass lines in each case directly in front of or behind the heat storage or cold storage in the circuit open, so that only within the thermal storage, the flow direction of the working gas is reversed. It is important to reverse the flow direction in the thermal storage (cold storage or heat storage), so that the cold-warm front is moved in the storage medium of the thermal storage during charging or discharging the thermal storage in the opposite direction.
  • an additional circuit is used for charging the thermal storage, it also passes through the same heat storage and cold storage. Suitable valve mechanisms ensure that only the circuit for charging or the circuit for discharging is connected to the thermal storage. Another possibility is that in the thermal storage each two conduit systems are included for two circuits. In this case, a changeover is not required and it can be done in principle even a simultaneous charging and discharging of the thermal storage.
  • the charging of the heat accumulator and the cold accumulator in the system is achieved in that the heat accumulator can be connected via a second line between a third thermal fluid energy machine and a fourth thermal fluid energy machine, wherein in the direction of flow of the working gas from the third fluid thermal energy machine for the fourth thermal fluid energy machine seen the third thermal fluid energy machine as a working machine and the fourth thermal fluid energy machine is connected as an engine.
  • the cold storage can be provided in the second line, which is then fed by the emerging from the fourth fluid energy machine working gas and can absorb the stored in the working gas cooling energy.
  • a water separator is arranged in the line.
  • the water separator By relaxation and cooling of the working gas and the absorption capacity of the same for water vapor decreases so that it condenses.
  • This can then be collected in said water, wherein the separated water still has a temperature of about 50 ° C. This temperature level is thus still above the ambient temperature, so that the stored in the collected water thermal energy can be recycled to the process. If the water vapor were blown into the environment and instead use feed water for the moistening tower from the environment, this thermal energy would be lost to the process.
  • the water separator thus serves to increase the efficiency of the realized by the inventive system process.
  • the water separator is connected to the moistening unit via a feed line.
  • the leading away from the second fluid energy machine line leads through a first heat exchanger located in the evaporator.
  • the working gas which leads away from the second fluid energy machine, has temperatures of about 200 ° C.
  • This heat can be used to provide the humidification tower with thermal energy necessary for the evaporation of the water in the humidification tower.
  • This heat energy is the Process therefore advantageously provided again and thus does not escape into the environment unused. This advantageously further increases the efficiency of the process realized by the plant.
  • a downstream water separator can operate more effectively, since the water can be more easily separated from the cooled working gas.
  • Yet another embodiment of the invention provides that an additional heat storage is provided in a branch line, wherein the leading away from the additional heat storage branch line leads through a second heat exchanger located in the evaporator.
  • the stored energy in the additional heat storage can thus additionally support the process of evaporation of water in the humidification unit.
  • the thermal energy input which takes place indirectly via the additional heat storage, thus advantageously leads to a further increase in the humidity in the humidification unit. This leads to the already described increase in the efficiency of the realized by the inventive system process.
  • the additional heat storage as well as the heat storage and the cold storage can be powered by external heat and cold sources.
  • the additional heat storage and the heat storage and the cold storage are charged by various heat pump processes.
  • the additional heat accumulator can advantageously be connected via an additional line between a fifth thermal fluid energy machine and a sixth thermal fluid energy machine, the fifth thermal fluid energy being seen in the direction of flow of the working gas from the fifth thermal fluid energy machine to the sixth thermal fluid energy machine Machine is connected as a working machine and the sixth thermal fluid energy machine as an engine.
  • the fifth and sixth fluid energy machine can be optimized for the temperatures to be generated in the additional heat storage.
  • the supplemental heat storage may also be charged by the first or by the third fluid energy machine, if an appropriate interconnection via lines or bypass lines is made possible. It is always necessary to weigh up the costs of components compared to increasing the efficiency for the individual processes. In this weighing economic considerations are in the foreground.
  • the working gas can be fed either in a closed or an open circuit.
  • An open circuit always uses the ambient air as working gas. This is sucked from the environment and released at the end of the process also in this, so that the environment closes the open circuit.
  • a closed circuit also allows the use of a different working gas than ambient air. This working gas is guided in the closed circuit. Since a relaxation in the environment with simultaneous adjustment of the ambient pressure and the ambient temperature is eliminated, the working gas in the case of a closed circuit must be passed through a heat exchanger, which allows a release of heat of the working gas to the environment.
  • the circuit for the storage of thermal energy in the cold storage and the heat storage is designed as an open circuit and there works as a motor engine thermal fluid energy machine is constructed of two stages, wherein between the steps a water separator for the working gas is provided. This takes into account the fact that humidity is contained in the ambient air. By a relaxation of the working gas in a single stage, it may happen that the humidity due to the strong cooling of the working gas to eg - 100 ° C freezes and in this case the thermal fluid energy machine damaged. In particular, turbine blades can be permanently damaged by icing.
  • a relaxation of the working gas in two steps makes it possible to separate condensed water in a water separator behind the first stage, for example at 5 ° C, so that it is already dehumidified in a further cooling of the working gas in the second turbine stage and prevents or at least reduces ice formation can be.
  • the risk of damaging the second fluid energy machine is thereby reduced.
  • a closed circuit is used and, as already described, a heat exchanger installed in the circuit, the use of a water separator and a two-stage fluid energy machine as an engine can be omitted.
  • a working gas for example, dehumidified ambient air can be used, the humidification is excluded by the closed nature of the circuit. But other working gases can be used.
  • the additional heat storage can serve in addition to the heating of the humidifying another task.
  • the use of the additional heat accumulator has the following advantages. If the system is used to store the thermal energy, the additional heat storage is passed before passing in this case as a working machine (compressor) working first / third fluid energy machine. As a result, the working gas is already warmed above ambient temperature.
  • the working machine has to absorb less power in order to achieve the required temperature of the working gas.
  • the heat storage to be heated to over 500 ° C which is advantageous subsequent to the preheating of the working gas can also be done with commercially available thermodynamic compressors that allow a compression of the working gas to 15 bar.
  • the working gas in the additional heat storage to a temperature between 60 ° C and 100 ° C, particularly advantageously heated to a temperature of 80 ° C.
  • heating of the working gas to about 190 ° C is particularly advantageous for the supply of heat in the humidification tower.
  • the working gas in the cycle of the heat storage and cold storage can be compressed to 15 bar, which can reach temperatures of the working degree of up to 550 ° C.
  • a heat exchanger is provided in the line, which is fed as a coolant with water for the moistening.
  • a heat exchanger is provided in the line, which is fed as a coolant with water for the moistening.
  • this energy is made available to the process again, whereby its efficiency advantageously further increases.
  • the humidification needs comparatively much feed water, since the water is at least partially discharged into the environment after passing through the circuit. But even in a closed circuit leaks in the circuit or the drying of the channels in the heat storage and the cold storage when switching from unloading to charging mode can lead to new feed water must be entered into the humidification.
  • a plant for storing thermal energy has a conduit 11, with which a plurality of units are connected to each other such that they can be traversed by a working gas in an open circuit.
  • the working gas is drawn in through a valve A from the environment and flows through a first thermal fluid energy machine 13, which is designed as a hydrodynamic compressor.
  • the line then leads via a valve B to a heat accumulator 14.
  • This is connected via the line 11 via a valve C with a second thermal fluid energy machine 15, which is designed as a hydrodynamic turbine.
  • the line 11 leads via a valve D to a cold storage 16. From the cold storage 16, the line opens into the environment. In the described operating state, the valves A to D are thus opened. Valves E to H are closed (more on that below)
  • the first and second fluid energy machines 13 and 15 are mechanically coupled to each other via a shaft 21 and are driven by an electric motor M fed by a wind power plant 22 as long as the generated electrical energy in the power grid is not in demand.
  • an electric motor M fed by a wind power plant 22 as long as the generated electrical energy in the power grid is not in demand.
  • the system supports the power generation in another operating state by the heat accumulator 14 and the cold storage 16 are discharged and the shaft 21 by the fluid energy machines 18 and 19, a generator G is driven.
  • the valves A to D are closed and opened for the valves E to H.
  • portions of the conduit 11 are no longer flowed through, but instead open bypass lines 19, which change the flow of the working gas.
  • the working gas flows through the cold storage 16 and passes through a bypass line 19 via the valve E to the first fluid energy machine (compressor). After leaving the compressor, the working gas is passed through a valve F through a humidifying unit 18, which is provided in a further bypass line 19 and leads to the heat accumulator 14. Therefore, the heat accumulator 14 is already supplied with humidified air, which leaves the heat accumulator 14 via the bypass line 19 through a valve G and the second fluid energy machine 15 (turbine) is supplied. Here, the mechanical energy for driving the first fluid energy machine 13 (compressor) and the generator is obtained. About the bypass line 19 through a valve H, the working gas returns to the environment, previously the working gas is dehumidified via a water separator 17.
  • the separated, about 50 ° C warm water is supplied via a feed pump 23 a of the humidifying 18.
  • heat can be introduced into the humidification unit, which is derived, for example, as district heating from a power plant. This is in FIG. 1 indicated by a heat exchanger 33a.
  • the structure of the heat accumulator 14 and the cold accumulator 16 (also the additional heat accumulator according to FIG. 3 ) in the system according to FIG. 1 is equal in each case and is explained in greater detail by an enlarged detail on the basis of the cold accumulator 16.
  • a container whose wall 24 is provided with an insulating material 25 having large pores 26.
  • Inside the container concrete 27 is provided, which acts as a heat storage or cold storage.
  • pipes 28 are laid parallel running through which the working gas flows and thereby emits heat or absorbs heat (depending on the mode and storage).
  • FIG. 2 First, a two-stage charging process is shown, which works on the principle of a heat pump. Shown in the Figures 2 and 3 an open circuit, however, as indicated by dash-dotted lines, using an optional heat exchanger 17a, 17b could be closed.
  • the states in the working gas, which in the embodiment of the Figures 2 and 3 consists of air, are each shown on the lines 30, 31, 32 in circles. At the top left is the pressure in bar. Top right, the enthalpy is given in KJ / Kg. Bottom left is the temperature in ° C and bottom right is the mass flow in kg / s. The direction of flow of the gas is indicated by arrows in the relevant line.
  • the isentropic efficiency ⁇ c can be assumed to be a compressor with 0.85.
  • the heated working gas now passes through the heat storage 14, where the majority of the available thermal energy is stored.
  • the working gas cools to 20 ° C, while the pressure (apart from flow-related pressure losses) is maintained at 15 bar.
  • the working gas is expanded in two series-connected stages 35a, 35b of a fourth fluid energy machine 35 so that it arrives at a pressure level of 1 bar.
  • the working gas cools to 5 ° C after the first stage and to -100 ° C after the second stage.
  • the basis for this calculation is also the formula given above.
  • a water separator 29 is additionally provided in the part of the line 31, which connects the two stages of the fourth fluid energy machine 35a, 35b in the form of a high-pressure turbine and a low-pressure turbine. This allows for a first relaxation, a drying of the air, so that the humidity contained in this second stage 35b of the fourth fluid energy machine 35 does not lead to icing of the turbine blades.
  • the relaxed and therefore cooled working gas withdraws heat from the cold storage 16 and is thereby heated to 0 ° C.
  • cold energy is stored in the cold storage 16, which can be used in a subsequent energy production.
  • the heat exchanger 17b must be provided.
  • the working gas can be reheated to an ambient temperature of 20 ° C, whereby the environment heat is removed, which is provided to the process.
  • such a measure can be omitted if the working gas is sucked directly from the environment, since this already has ambient temperature.
  • the additional heat storage 12 when passing through the circuit of the second line 31, a preheating can be done by the additional heat storage 12, an additional circuit is realized by an additional line 30, with which the additional heat storage 12 can be charged.
  • the additional heat storage 12 must therefore be connected to both the circuit of the second line 31 and to the circuit of the additional line 30.
  • a connection to the second line 31 takes place through the valves I, while a connection to the additional line 30 is ensured by opening the valves K.
  • the air is first passed through a fifth fluid energy machine 36, which operates as a compressor.
  • the compressed air is passed through the additional heat storage 12, wherein the flow direction corresponding to the indicated arrows runs exactly opposite to the circuit formed by the second conduit 31.
  • the circuits of the second line 31 and the additional line 30 are set independently. Therefore, the third and fourth fluid energy machines are mechanically coupled via the shaft 21 to a motor M1 and the fifth and sixth fluid energy machines via the other shaft 21 to a motor M2. With overcapacities of the wind turbine 22, the electrical energy can first drive the motor M2 to charge the additional heat storage 12. Subsequently, by operation of the motor M1 and simultaneous discharge of the additional heat accumulator 12, the heat accumulator 14 and the cold accumulator 16 can be charged. Subsequently, by the operation of the motor M2 and the additional heat storage 12 can be recharged. When all accumulators are fully charged, an effective discharge cycle can be initiated to generate electrical energy (cf. FIG. 3 ). However, should the excess capacity of the wind power plant 22 end without the additional heat storage 12 could be charged, the energy available in this can be replaced by other heat sources (see. FIG. 3 ).
  • an additional heat accumulator 12 which can be supplied by separate line systems for the second line 31 and the additional line 30. This would create two independent circuits without valves I and K being used. In this way, the auxiliary heat storage 12 could be simultaneously charged and discharged. It is therefore conceivable in this case, a simultaneous operation of the motors M1, M2.
  • This operating regime has two advantages. On the one hand, even larger overcapacities of the wind power plant 22 can be absorbed by simultaneous operation of the motors M1, M2 at full load, resulting in greater flexibility of the system. In addition, could through To ensure simultaneous operation of both motors that the three thermal storage 12, 14, 16 are always filled simultaneously and not one after the other. Thus, the charging process can be stopped at any time at full operability of the discharge process, if no excess capacity in the electrical network are no longer available and instead creates a need for additional electrical energy.
  • the discharge cycle of the heat accumulator 14 and the cold accumulator 16 can be followed, wherein the generator G electrical energy is generated.
  • the first fluid energy machine 13 and the second fluid energy machine 15 are available, which are described in the charging processes described above (see FIG FIG. 2 ) were not used.
  • This allows the optimization of the efficiency of the fluid energy machines, but also leads to higher investment costs for the purchase of the system. Therefore, the higher investment cost of using additional fluid power machines versus the gain in efficiency achieved by optimizing each to the appropriate operating condition using four fluid power machines is to be weighed.
  • the heat storage 14, the cold storage 16 and the additional heat storage 12 are the same as in FIG. 2 and are flowed through only in the opposite direction. In the Figures 2 and 3 Thus, the same system is shown, for reasons of clarity, only the system components and lines involved in the running process are shown. Furthermore, the alternative of a closed circuit is shown in phantom.
  • the compressed working gas first passes through the moistening unit 18 and then the heat accumulator 14 and is thereby heated in the moistening unit to 145 ° C. and in the heat accumulator 14 to 530 ° C.
  • the working gas is expanded by the second fluid energy machine 15, which thus operates in this operating state as a turbine.
  • the working gas can still be passed through a heat exchanger 33b in the evaporation unit to emit heat there for the evaporation of the water.
  • the water separator 17 it is possible to deposit at least part of the air humidity via the water separator 17.
  • the separated water still has a temperature of about 50 ° C and is pumped via a feed pump 23b back into the humidification unit.
  • the dehumidified air leaves the circuit and is blown into the environment.
  • a closed circuit is realized by the line 32.
  • a heat exchanger 17a ensures that the working gas, which still has a temperature of 50 ° C, is cooled to ambient temperature (20 ° C).
  • the heat exchanger can also be used to warm up fresh water, which can be pumped via a feed pump 23c into the humidification unit.
  • the heat exchanger 33 a are connected to an external heat source. This can be, for example, district heating. But it is also advantageous to use the charged additional heat storage 12.
  • a branch line 38 is provided, which branches off from the line 32 before the cold storage 16. This goes through the additional heat storage 12 and then a heat exchanger 33c in the humidification unit, so that the heat energy stored in the additional heat storage 12 can also be supplied to the humidification unit.
  • the branch line 38 opens behind the heat exchanger 33c in the line 32 behind the heat exchanger 33b. The mass flow of working gas is thus split at the branch line 38, 8.3 Kg / s are passed through the branch line 38 and 4.8 Kg / s through the cold storage 16 humidifying unit 18 and the heat storage 14 are passed.

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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)
EP11183267A 2011-09-29 2011-09-29 Installation de stockage d'énergie thermique Withdrawn EP2574738A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP11183267A EP2574738A1 (fr) 2011-09-29 2011-09-29 Installation de stockage d'énergie thermique
PCT/EP2012/068858 WO2013045437A1 (fr) 2011-09-29 2012-09-25 Installation de stockage d'énergie thermique
CN201280048050.6A CN103842623A (zh) 2011-09-29 2012-09-25 用于存储热能的设备
EP12769071.7A EP2748435A1 (fr) 2011-09-29 2012-09-25 Installation de stockage d'énergie thermique
US14/346,729 US20140338329A1 (en) 2011-09-29 2012-09-25 Installation for storing thermal energy

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11183267A EP2574738A1 (fr) 2011-09-29 2011-09-29 Installation de stockage d'énergie thermique

Publications (1)

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EP2574738A1 true EP2574738A1 (fr) 2013-04-03

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EP11183267A Withdrawn EP2574738A1 (fr) 2011-09-29 2011-09-29 Installation de stockage d'énergie thermique
EP12769071.7A Withdrawn EP2748435A1 (fr) 2011-09-29 2012-09-25 Installation de stockage d'énergie thermique

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EP12769071.7A Withdrawn EP2748435A1 (fr) 2011-09-29 2012-09-25 Installation de stockage d'énergie thermique

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US (1) US20140338329A1 (fr)
EP (2) EP2574738A1 (fr)
CN (1) CN103842623A (fr)
WO (1) WO2013045437A1 (fr)

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IT201900015770A1 (it) * 2019-09-06 2021-03-06 Ivar Spa Nuovo ciclo combinato seol
IT201900015776A1 (it) * 2019-09-06 2021-03-06 Ivar Spa Macchina termica configurata per realizzare cicli termici e metodo per realizzare cicli termici
WO2021044338A3 (fr) * 2019-09-06 2021-05-27 I.V.A.R. S.P.A. Nouveau cycle thermodynamique combiné à haute récupération d'énergie

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CN106256995A (zh) * 2015-06-16 2016-12-28 熵零股份有限公司 一种蓄能系统
WO2019104156A1 (fr) 2017-11-21 2019-05-31 Aestus Energy Storage, LLC Charge de système de stockage thermique

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Publication number Priority date Publication date Assignee Title
IT201900015770A1 (it) * 2019-09-06 2021-03-06 Ivar Spa Nuovo ciclo combinato seol
IT201900015776A1 (it) * 2019-09-06 2021-03-06 Ivar Spa Macchina termica configurata per realizzare cicli termici e metodo per realizzare cicli termici
WO2021044338A3 (fr) * 2019-09-06 2021-05-27 I.V.A.R. S.P.A. Nouveau cycle thermodynamique combiné à haute récupération d'énergie
US12078085B2 (en) 2019-09-06 2024-09-03 I.V.A.R. S.P.A. Combined thermodynamic cycle with high energy recovery

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EP2748435A1 (fr) 2014-07-02

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