OA20837A - Energy storage plant process - Google Patents

Abstract

An energy storage plant (1) comprises a casing (5) for the storage of a working fluid other than atmospheric air, in a gaseous phase and in equilibrium of pressure with the atmosphere; a tank (9) for the storage of said working fluid in a liquid or supercritical phase with a temperature close to the critical temperature; wherein said critical temperature is close to the ambient temperature. The plant (1) is configured to carry out a closed thermodynamic cyclic transformation (TTC), first in one direction in a charge configuration and then in the opposite direction in a discharge configuration, between said casing (5) and said tank (9); wherein in the charge configuration the plant (1) stores heat and pressure and in the discharge configuration generates energy.

Description

Energy storage plant and process

DESCRIPTION

Field of the invention

Object of the présent invention is a plant and a process for the storage of electrical energy. More precisely, object of the présent invention is a System able to absorb/use electrical energy from a network or a System when an excess of availability and/or scarcity of consomption is manifested, able to maintain in the time the stored energy and able to transform it back into electrical energy and to put it back in the network when saîd electrical energy is demanded. In details, this invention is related to a System of storage of electrical energy in the form of potential energy (pressure) and thermal/thermodynamic energy. The présent invention is part of medium and large scale energy storage Systems, for both terrestrial and marine applications, typically with powers from hundreds of kW up to tens of MW (e.g. 20-25MW), but also hundreds of MW, and with storage capacity from a few hundred kWh, up to hundreds of MWh and even up to several GWh. The présent invention can also be placed in the field of small· scale energy storage Systems, for domestic and commercial applications, both terrestrial and marine, typically with powers from a few kW up to a few hundred kW and with storage capacity from a few kWh, up to hundreds of kWh.

Définitions

The following définitions will be used in the présent description and in the accompanying daims.

• Thermodynamic cycle (CT): thermodynamic transformation from a point X to a point Y, where X coïncides with Y; the CT, unlike the TTC (Thermodynamic Cyclic Transformation) below, has no mass accumulations (significant for energy purposes) within the cycle, while the TTC typically works between two storages ofworkîng fluid, one initial and the other final;

• Thermodynamic Cyclic Transformation (TTC): thermodynamic transformation from a point X to a point Y and from a point Y to a point X, without necessarily passing through the same intermediate points;

• Closed CT and/or TTC: with. no mass exchange (significant for energy purposes) with the atmosphère;

-120837 • Open CT and/or TTC: with mass exchange (significant for energy purposes) with the atmosphère.

Backqround of the invention

Recently, due to the ever-increasing diffusion of Systems for the production of energy from renewable sources and in particular from wind and photovoltaic sources, which are characterized by production variabilîty and unpredictability, electric energy storage Systems are becoming încreasîngly important.

The electrical energy storage Systems may perform various fondamental functions for the networks, both îsolated and interconnected, including the adjustment of frequency/supply of dynamic inertia, the supply of flexible ramping Systems, i.e. allowing the start of emergency production Systems, energy shifting from hours of greater production and less demand to hours which, on the other hand, présent greater demand and/or lack of production, seasonal compensations, etc..

In addition to Systems that operate according to electrochemical principles (Batteries) that typically hâve high costs and limited useful life, mechanical (flywheel) suitable only for small amounts of stored energy, the Systems currently in use or under development or otherwise known include the foilowing.

The Systems mainly in use are the hydroelectric pumping storage Systems (PUMPED HYDRO STORAGE - PHS), which currently cover more than 90% of the globally installed storage capacity. These Systems are suitable for both long and short term storage, are quite compétitive in terms of costs, but hâve the disadvantage of being able to be built only in places that hâve particular geo-morphological conditions. Said PHS System can be counted among the energy storage Systems in potential form and in particular gravitational. Also the System disclosed in document GB 2518125 A is in the family of gravitational Systems.

A second System in use is the so-called CAES System (Compressed Air Energy Storage), which consists of an Open TTC that accumulâtes through transformation into potential energy (pressure) and (possibly) thermal energy. This CAES System is known both in the basic (non-adiabatic) configuration and in the more advanced AA-CAES (Advanced Adiabatic CAES; see US 4,147,205 - Compressed Air Storage Installation) configuration. These Systems are suitable for both long and short term storage, are quite compétitive in terms of costs, are less efficient than PHS Systems in terms of

-220837 'Round Trip Efficiency', and they also hâve the disadvantage of being able to be built only in places with particular geo-morphological conditions.

CAES Systems also hâve an additional disadvantage in that the pressure of the tank/cave varies with the charge level of the same. This affects both the efficiency of the TTC and the efficiency of the turbomachines that perform it.

Systems are also known to remedy the absence of underground caves for CAES Systems. In particular, solutions are known that seek to make it economically viable to store energy in over-ground tanks, without the need for underground caves. An example is in US2011/0204064 A1 of LIGHTSAIL where tanks of spécial construction are praposed in order to try to contain costs of over-ground storage tanks that vice versa would make the costs of said CAES over ground Systems unprofîtable. These solutions also belong to the Systems that work according to an Open TTC.

Systems that combine the two previous Systems are also known (see US 7,663,255 B2), in which the combination of CAES and PHS also allows the CAES System to operate at constant compression pressure. These Systems too work according to an Open TTC.

The document 'Novel concept of compressed air energy storage and thermos-electric energy storage' - THESE N.5525 (2012) - Ecole Polytechnique Federale de Lousanne, discloses ail types of CAES energy storage Systems. Among others, the CAES Systems diabatic, adiabatic, isothermal and combined with PHS to allow a constant compression pressure, are disclosed, this System is called Constant Pressure-CAES combined with PHS. These too are Systems working according to an Open TTC.

The same document also discloses the so-called TEES (Thermo Electric Energy Storage) proposed by ABB Corporate Research Center (see also EP 2532843 A1 and EP 2698506 A1). This is one of the Systems that work according to a Closed CT, and can be counted among the PHES Systems. PHES Systems (pumped heat electrical storage) are Systems for storing electrical/mechanical energy by converting it into thermal energy using, for example, Rankine, Brayton or Kalina CT.

In addition to the Systems described above that use trans-critical and super-critical CO₂ cycles or other fluid cycles and therefore réversible tra ns-su per-critical Rankine cycles, PHES Systems with Brayton cycle are known, typically using Argon but also air (see Isoentropic EP 2220343 B1 and US 2010/0257862 A1 and Laughlin US 2016/0298455 A1. This is one of the Systems that work according to a Closed CT, and can be counted among the PHES Systems).

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Another System that can be counted among the PHES/TEES Systems is the Siemens Gamesa System (see US 2014/0223910 A1 and US 8,991,183 B2 and US 8,966,902 B2) which combines two different cycles for the charging and discharging phase, and in particular provides for a Brayton cycle or simple dissipation with electrical résistances for the charging phase of the high-temperature heat storage tank and a steam Rankine cycle for the discharge/production phase of electrical energy. This type of solution is one of the PHES Systems. It is carried out by means of several Open and/or Closed CT. it should be noted that ail PHES Systems, also called TEES, are based on a 'closed' and réversible thermodynamic cycle principle. Depending on the different proposed solutions, they can be 'closed' Rankine or Brayton cycles, but in any case the working fluid of the motor/heat pump, which is almost réversible, performs transformations according to a 'closed' thermodynamic cycle in which there are no intermediate accumulations sized according to the required storage capacity.

Ail CAES Systems, of ail types, are instead Systems that carry out transformations, first in one direction and then in the other according to an 'open' thermodynamic cycle, that is, taking and returning airto the atmosphère.

Another known method of energy storage is the so-called LAES System (Liquid Air Energy Storage, see US2009/0282840 A1). The LAES method involves transformations according to an 'open' thermodynamic transformation, i.e. taking and returning air to the atmosphère. Moreover, this System works at cryogénie températures, close to -200°C, with high technical difficulties. This too belongs to the Systems that work according to an Open TTC.

In 'Analysis of the exergy efficiency of a super-critical compressed carbon dioxide energy-storage System based on the orthogonal method' by Qing He, Yinping Hao, Hui Liu, Wenyi Liu, the use of CO₂ as working fluid for energy storage Systems was also proposed. The proposed System (called SC-CCES (Super Critical - Compressed Carbon dioxide Energy Storage), uses as specified two saline aquifers as storage réservoirs. In this SC-CCES System, CO₂ from the compressor delivery is sent directly to the réservoir without the interposition of any heat exchanger and/or thermal energy storage System. Moreover, during the discharge cycle, the CO₂ discharged from the turbine heats up through a recuperator the same CO₂ entering the turbine. This solution belongs to Systems that work according to a Closed TTC, i.e. between two closed tanks. Also document 'Green Energy Storage: The Potential Use of compressed Liquid CO2 and Large Sub-Terrain Cavities to Help Maintain a Constant Electricity Supply -420837

Dalgaard JZ, talks (both in the titie and abstract, and in the body of the document) about the use of CO2 in underground cavities.

Summary

The applicant pointed oui that the current electrical energy storage Systems do not hâve characteristics that allow them to be used economically in different situations.

In particular, in some cases (e.g. PHS and CAES) the Systems require very particular geo-morphological situations that are difficult to find. In some cases (e.g. PHS) the implémentation of such Systems requires the manufacture of réservoirs with heavy environmental impact.

In other cases (AA-CAES) the realization of thermal energy storage Systems présents problems that are difficult to solve at low cost and, moreover, there is still the need to identify suitable underground caves. The above also leads to difficulties in achieving satisfactory Round Trip Efficiency (RTE). In any case, the problem of working with variable pressures in the storage tank remains, unless the CAES System is combined with the PHS System, with obvious additional cost complications and to identify the correct geological conditions.

The applicant further observed that attempts to build surface CAES Systems hâve corne up against the practical impossibility of building pressurized air storage tanks at a compétitive cost to enable the Systems themselves to be built.

The applicant further observed that the attempts to build LAES Systems hâve not at the moment allowed to develop economically viable Systems also because of the problems inhérent in working in cryogénie conditions. The problems of storing cryogénie energy in double layer tanks with vacuum between layers, and other expensive devices, makes the technology difficult to optimize in terms of costs.

The applicant further observed that the attempts to build PHES Systems with almost réversible Rankine cycles present considérable difficulties in achieving satisfactory Round Trip Efficiency (RTE) (i.e. above 60%) and at the same time with reasonable costs, the RTE being linked to température différences in the equipment.

Similarly, PHES Systems based on the Brayton cycle hâve to contend with the fact that these Systems use a compressor and a turbine for each cycle, both for charging and for discharging. This entails higher investment costs, but also greater irreversibility that can be compensated for obtaining high TENs only by maintaining very high température différences between hot and cold storage.

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In this context, the Applicant has set itself the objective of designing and implementing an energy storage process and plant, i.e. an energy storage System, that is:

capable of being done in different geo-morphologicaî situations, which do not require particular geographical or territorial conditions to be realized and that can eventually in certain sizes also be used for marine/off-shore applications;

• able to obtain hîgh RTE and in any case higher than 70% and up to 75% and up to even 80% and more;

• capable of working with adjustable storage tank pressures, thorugh various Systems described below;

simple and economical, preferably with the target of having a construction cost of less than 100 USD/kWh and, in particular, that allows storage under pressure and with high energy density (in terms of m³ _storage / kWh_stored);

able to ïncrease its RTE by using the variations of Ambient Température;

safe and environmentally friendly, e.g. that it does not use particularly hazardous fluids;

modular;

compact;

lasting or having an increased useful life of 30 years;

flexible and able to get into operation quickly;

easily and economically maintainable;

corrosion résistant (especially for marine applications);

having low levels of vibrations and noise.

The applicant has found that the above objectives and others can be achieved through an Energy Storage System operating by means of thermodynamic cyclic transformations (TTC), first in one direction and then in the opposite direction, between two accumulations of a working fluid in two distinct tanks, one of which (the one with the lowest pressure) is atmospheric, but which is not atmospheric air but another gas in pressure equilibrium with the atmosphère. This System is also characterized by the fact that it stores energy transforming the working fluid from an initial gaseous/steam State to a final liquid or supercritical State with a température close to critical température (for example less than 1.2 fîmes the critical température in Kelvin, preferably between 0.5 and 1.2 fîmes). It is also characterized by the fact that this critical température is preferably not far from ambient température, preferably close to ambient température (preferably between 0°C and 200°C, more preferably between 0° and 100°C).

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The working fluid is preferably carbon dioxide (CO₂), but in order to improve the performance of the system, also in relation to the particular environmental conditions in which ît opérâtes, a mixture of CO₂ and other substances could be used in order to correct the critical température T_c of the fluid. Other fiuids, such as SF₆, N₂O, etc. can be used, always pure or mixed with others.

In the system proposed in this invention, a storage of heat recovered from the delivery of a compresser is présent. Both high and low pressure tanks work at constant pressures or in any case adjusted within certain well-defined ranges, both when the system opérâtes in subcritical and supercritical conditions, possibly with different control strategies.

In particular, the stated objectives and others are substantially achieved by a plant and a process for energy storage of the type claimed in the attached daims and/or described in the following aspects.

In an independent aspect, the présent invention concerns an energy storage plant (energy storage system).

Preferably, the plant comprises:

a casing for the storage of a working fluid other than atmospheric air, in a gaseous phase and in equilibrium of pressure with the atmosphère;

a tank for the storage of said working fluid in liquid or supercritical phase with a température close to the critical température (for example less than 1.2 times the critical température in Kelvin 0.5 -1.2); wherein said critical température is between 0°C and 200°C, more preferably between 0°C and 100°C, preferably close to the ambient température;

wherein the plant is configured to carry out a closed cyclic thermodynamic transformation (TTC), first in one direction into a charge configuration/phase and then in the opposite direction into a discharge configuration/phase, between said casing and said tank; wherein in the charge configuration the system accumulâtes heat and pressure and in the discharge configuration itgenerates energy.

Preferably, the working fluid has the following chemical-physical properties: critical température between 0°C and 100°C, density at 25°C between 0.5 and 10 Kg/m³, preferably between 1 and 2 Kg/m³.

Preferably, the working fluid is chosen in the group including: CO₂, SF₆, N₂O, or a mixture of the same, or even a mixture of the same with other components that act as

-7 20837 additives, for example mainly to modify the parameters of critical Température of the resulting mixture in orderto optimize the performance of the System.

Preferably, the energy storage plant comprises:

a compresser and a motor mechanically connected to each other;

a turbine and a generator mechanically connected to each other;

said casing externally in contact with the atmosphère and delimiting inside a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric pressure, wherein said volume is selectively in communication with an inlet of the compresser or with an outlet of the turbine; a primary heat exchanger (or even a plurality of primary heat exchangers that may also operate with different fluids on their secondary side) selectively in fluid communication with an outlet of the compressor or with an inlet of the turbine;

said tank in fluid communication with the primary heat exchanger to accumulate the working fluid;

a secondary heat exchanger operationally active between the primary heat exchanger and the tank or in the tank.

This plant is configured to operate in a charge or in a discharge configuration.

In the charge configuration, the casing is in fluid communication with the inlet of the compressor and the primary heat exchanger is in fluid communication with the outlet of the compressor, the turbine is at rest, the motor is operating and drives the compressor to compress the working fluid coming from the casing, the primary heat exchanger works as a cooler to remove heat from the compressed working fluid, cool it and store thermal energy, the secondary heat exchanger works as a cooler to remove additional heat from the compressed working fluid and store additional thermal energy, the tank receives and stores the compressed and cooled working fluid, wherein the working fluid stored in the tank ha s a température close to its own critical température (e.g. between 0.5 and 1.2 of the critical Température in Kelvin).

In the discharge configuration, the casing is in fluid communication with the outlet of the turbine and the primary heat exchanger is in fluid communication with the inlet of the turbine, the compressor is at rest, the secondary heat exchanger works as a heater to release heat to the working fluid coming from the tank, the primary heat exchanger works as a heater to release further heat to the working fluid and heat it, the turbine is

-820837 rotated by the heated working fiuid and drives the generator generating energy, the working fluid returns in the casing to atmospheric pressure or substantially atmospheric. In an independent aspect, the présent invention relates to an energy storage process, optionally implemented with the plant according to the previous aspect or according to at least one of the foilowîng aspects.

Preferably, the process comprises: carrying out a closed thermodynamic cyclic transformation (TTC), first in one direction in a charge configuration/phase and then in an opposite direction in a discharge configuration/phase, between a casing for the storage of a working fluid other than atmospheric air, in a gaseous phase and in equilibrium of pressure with the atmosphère, and a tank for the storage of said working fluid in a liquid or super-critical phase with a température close to the criticai température (for example between 0.5 and 1.2 of the Criticai Température in Kelvin); whereîn said criticai température is close to the ambient température, preferably between 0°C and 100°C, but also up to 200°C; whereîn the process accumulâtes heat and pressure in the charge phase and generates energy in the discharge phase.

Preferably, said working fluid has the foilowîng chemical-physical properties: criticai température between 0°C and 200°C, more preferably between 0°C and 100°C, preferably close to ambient température.

Preferably, this working fluid is chosen in the group including: CO2, SF_6i N₂O, or a mixture of the same, or even a mixture of the same with other components that act as additives, for example mainly to modify the parameters of criticai Température of the resulting mixture in order to optimize the performance of the System.

Preferably, the process comprises a phase of energy charge and a phase of discharge and génération of energy.

The charge phase comprises:

compressing the working fluid, coming from said casing externally in contact with the atmosphère and delimitîng inside a volume configured to contain said working fluid at atmospheric pressure or substantially atmospheric, absorbing energy;

injecting the compressed working fluid through a primary heat exchanger (or even a plurality of primary heat exchangers eventually operating with different fluids on their secondary side) and a secondary heat exchanger placed in sériés to bring a température of the working fluid near its own criticai température; wherein the primary heat exchanger works as a cooler to

-920837 remove heat from the compressée! working fluid, cool it and store thermal energy, wherein the secondary heat exchanger works as a cooler to remove further heat from the compressed working fluid and store further thermal energy;

accumulating the cooled working fluid in said tank; wherein the secondary heat exchanger and the primary heat exchanger operate a super-critical transformation of the working fluid so that said working fluid îs accumulated in the super-critical phase in the tank or wherein the secondary heat exchanger and the primary heat exchanger operate a sub-critical transformation of the working fluid so that said working fluid is accumulated in the liquid phase in the tank (preferably also with the aim of regulating the pressure to a reiatively minimum/low value).

The phase of discharge and power génération comprises:

passing the working fluid, coming from the tank, through the secondary heat exchanger and the primary heat exchanger; wherein the secondary heat exchanger works as a heater to transfer heat to the working fluid coming from the tank (preferably also with the aim of regulating the pressure to a reiatively high/maximum value), wherein the primary heat exchanger works as a heater to release additional heat to the working fluid and heat it up;

passing the heated working fluid through a turbine, wherein the turbine is rotated by the heated working fluid and drives a generator generating energy, wherein the working fluid expands and cools in the turbine;

re-injecting the working fluid from the turbine into the casing at atmospheric or substantially atmospheric pressure.

The applicant has verified that the process and the apparatus according to the invention allow to achieve the set objectives.

In particular, the applicant has verified that the invention allows the storage of energy in places without particular geo-morphological characteristics, even for marine/off-shore applications, in a safe manner and with a low environmental impact.

The applicant has also verified that the manufacture and subséquent maintenance of an apparatus according to the invention are reiatively inexpensive.

The applicant has also verified that the invention enables high RTE to be achieved.

The applicant has also verified that the invention allows to operate an energy storage with the possibility to regulate the pressure in the storage tanks, thus allowing a better -1020837 operabilîty of the System, a greater efficiency of both the turbomachinery and the System in terms of RTE.

Aspects ofthe invention are listed below.

In one aspect, the primary heat exchanger is, or is operatively coupied to, a thermal storage (Thermal Energy Storage - TES).

In one aspect, first pipelines develop between the casing and the compressor inlet and between the casing and the turbine outlet to connect the fluid casing with the compressor and turbine.

In one aspect, at least one valve is operationally placed on said first pipelines to connect the fluid alternately with the compressor casing or the turbine with the casing.

In one respect, second pipelines develop between the turbine inlet and the primary heat exchanger and between the compressor outlet and the primary heat exchanger to put in fluid communication said primary heat exchanger with said compressor and turbine.

In one aspect, at least one valve is operationally placed on said second pipelines to put in fluid communication the compressor with the primary heat exchanger or the primary heat exchanger with the turbine.

In one aspect, third pipelines develop between the primary heat exchanger and the secondary heat exchanger to put in fluid communication said primary heat exchanger with said secondary heat exchanger.

In one aspect, an additional heat exchanger is operationally placed between the casing and the compressor and between the casing and the turbine to pre-heat the working fluid before compression in the compressor, in the charge configuration, or to cool the working fluid coming from the turbine, in the discharge configuration.

In one aspect, the additional heat exchanger is operationally associated with the first pipelines.

In one aspect, the additional heat exchanger comprises an additional thermal energy storage device.

In one aspect, in the charge configuration, the additional heat exchanger works as a heater to pre-heat working fluid.

In one aspect, in the discharge configuration, the additional heat exchanger works as a cooler to cool the working fluid and store additional thermal energy that is used in the charge configuration to pre-heat said working fluid.

In one aspect, a cooler is placed on a branch of the first pipelines connected to the outlet of the turbine.

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In one aspect, a further heat exchanger operatively associated with an additional heat source is operatively interposed between the turbine and the primary heat exchanger and is configured to further heat the working fluid in the discharge phase before entering the turbine.

In one aspect, in the discharge configuration, the additional heat source provides additional heat to the working fluid.

In one aspect, in the discharge phase and génération of energy, between the primary heat exchanger and the turbine, it is envisaged to further heat the working fluid via an additional heat source.

In one aspect, the additional heat source is: a solar source (e.g. solar field) and/or industrial waste heat recovery (Waste Heat Recovery) and/or exhaust heat from gas turbines (GT).

In one aspect, a température at which the working fluid is brought in the discharge phase and just before entering the turbine, via the additional heat source and the further heat exchanger, is greater than a température of the working fluid at the end of compression during the charge phase.

In one aspect, the température at which the working fluid is brought via the additional heat source and the additional heat exchanger îs greater of about 100°C, but also 200°C or 300°C or 400°C compared to the température of the working fluid at the end of compression.

The Applicant has verified that the further heating of the working fluid by the additional heat source allows to considerably increase the Round Trip Efficiency (RTE).

In one aspect, the casing is déformable.

In one aspect, the casing has the structure of a gasometer.

In one aspect, the casing is a pressure-balloon.

In one aspect, the casing is made of flexible material, preferably plastic, e.g. PVC coated polyester fabric.

In one aspect, the motor and generator are distinct éléments, wherein the motor is preferably permanently connected to the compressor and the generator is preferably permanently connected to the turbine.

In one aspect, the motor and the generator are defined by a single motor-generator.

In one aspect, the plant comprises connection devices, preferably of the clutch type, between the motor-generator and the compressor and also between the motor

-1220837 generator and the turbine to connect mechanically and alternateiy the motor-generator to the compressor or ta the turbine.

In one aspect, the motor-generator, the compressor and the turbine are arranged on a same axis.

In one aspect, the compression of the working fluid in the compressor is adiabatic, intercooled or isothermal.

In one aspect, the working fluid expansion in the turbine is adiabatic, inter-heated or isothermal.

In one aspect, an auxiliary thermal storage (Thermal Energy Storage TES) is connected to the compressor and to the turbine.

In one aspect, the auxiliary thermal accumulator is configured to realize, in the compressor and during the charge phase, an inter-cooled compression, with one or more inter-coolings.

In one aspect, the auxiliary thermal accumulator is configured to perform, in the turbine and during the discharge phase, an inter-heated expansion, with one or more interheatings.

In one aspect, it is envisaged to perform a plurality of inter-coolings in the charge phase and to perform a smaller number of inter-heatings than the number of inter-coolings using heat (accumulated in the auxiliary thermal accumulator) of only part of the intercoolings.

In one aspect, it is envisaged to perform a plurality of inter-coolings in the charge phase and to perform a single inter-heating in the discharge phase by using heat (accumulated in the auxiliary thermal accumulator) of the last inter-cooling only.

The Applicant has verified that the combination of the further heating of the working fluid by the additional heat source together with the inter-coolings and the above mentioned inter-heatings allows to increase the Round Trip Efficiency (RTE) up to values greater than 100%.

In one aspect, the primary heat exchanger is or comprises a fixed or movîng bed heat regenerator

In one aspect, the fixed or movîng bed heat regenerator comprises at least one thermal mass lapped by the working fluid.

In one aspect, the fixed or movîng bed heat regenerator comprises at least one thermal mass not lapped by the working fluid, but separated from it by a wall, typically made of

-1320837 métal, which is capable of containing the pressure, and therefore the mass is at atmospheric pressure.

In one aspect, the thermal mass comprises incohérent material, optionally gravel or métal or ceramic balls.

In one aspect, the thermal mass comprises cohérent material, optionally cernent or ceramic or métal.

In one aspect, the primary heat exchanger comprises a primary circuit crossed by a primary fluid or several primary circuits crossed by several primary fluids, optionally water, oil or salts.

In one aspect, the primary circuit comprises a heat exchange portion configured to exchange heat with the working fluid.

In one aspect, the primary circuit comprises at least one primary storage chamber, preferably two storage chambers, for said primary fluid.

In one aspect, the primary circuit comprises a hot primary storage chamber, for the hot primary fluid accumulated after removing heat from the working fluid in the charge configuration/phase of the apparatus/process, and a cold primary storage chamber, for the cold primary fluid accumulated after transferring heat to the working fluid in the discharge configuration/phase of the apparatus/process.

In one aspect, the primary circuit comprises a fixed bed heat regenerator, preferably operating at atmospheric pressure, which is lapped by the primary fluid.

In one aspect, the secondary heat exchanger comprises a secondary circuit crossed by a secondary fluid, optionally air or water.

In one aspect, the secondary circuit comprises a heat exchange portion configured to be lapped by the working fluid.

In one respect, the secondary circuit comprises at least one secondary storage chamber for this secondary fluid.

In one aspect, the secondary circuit comprises a hot secondary storage chamber, for the hot secondary fluid accumulated after removing heat from the working fluid in the charge configuration/phase of the apparatus/process, and a cold secondary storage chamber, for the cold secondary fluid accumulated after releasing heat to the working fluid in the discharge configuration/phase of the apparatus/process.

In one aspect, the secondary heat exchanger is located between the primary heat exchanger and said tank.

In one aspect, the secondary heat exchanger is integrated into the tank.

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In one aspect, the secondary heat exchanger is equipped with Systems for regulating the flow rate and/or température of secondary fluid, typically water or air, capable of regulating the pressure in the storage tanks within certain limits, when the System operates in sub-critical conditions.

Température control can be carried out by adding heat from the atmosphère or removing heat to the atmosphère, also taking advantage of the normal fluctuations in ambient température of air and water at different times of the day.

In one aspect, the secondary heat exchanger is placed in a basin full of water, consisting of one chamber or two chambers. In said secondary heat exchanger the working fluid is condensed during charge phase and evaporated in discharge phase by circulating water, preferably through immersion pumps. The two chambers of said basin may be covered or uncovered and in communication or not with the environment so that the chamber from which the water is circulated for the condensation in charge phase is always cooled by the surrounding environment, while that from which the water is circulated for évaporation in discharge phase is always heated by the surrounding environment and possibly kept warm by covering.

In one aspect, the above can be further supported by spécial exchange Systems that absorb heat or release heat, in a convective and radiant way with the environment, all for improving the RTE of the System. This way a pressure adjustment when the System is operating under sub-critical conditions is performed.

In one aspect, the heat exchange portion of the secondary heat exchanger is housed inside the tank.

In one aspect, the secondary circuit is configured to remove heat from the working fluid, in the charge configuration, or to transfer heat to the working fluid, in the discharge configuration, at a température beiow 100°C, optionally between 0°C and 50°C, optionally at a température close to the ambient température.

In one aspect, in the charge configuration/phase, since the secondary heat exchanger works in conditions close to ambient température, due to the fact that the fluid has a critical température close to ambient température, it is possible that the phase of heat removal through the secondary heat exchanger is assisted by a phase of direct or indirect exchange with the atmosphère.

In one aspect, in the discharge configuration/phase, since the secondary heat exchanger works in conditions close to ambient température, due to the fact that the fluid has a critical température close to ambient température, it is possible that the -1520837 phase of heat supply through the secondary heat exchanger is assisted by a phase of direct or indirect exchange with the atmosphère.

In one aspect, the tank is spherical or substantially sphericaL

In one aspect, the tank is cylindricaï or substantially cylindrical.

In one aspect, an outer wall of the tank is made of métal.

In one aspect, a température of the working fluid accumulated in the tank is between 0°C and 100°C.

In one aspect, a pressure the working fluid accumulated in the tank is between 10 bar and 150 bar, preferably between 10 bar and 150 bar, preferably between 50 and 100 bar, preferably between 65 and 85 bar.

In one aspect, a ratio between a density of the working fluid when contained in the tank and a density of the working fluid when contained in the casing is between 200 and 500. In one aspect, the secondary heat exchanger and the primary heat exchanger are configured to operate a super-critical transformation of the working fluid so that said working fluid is accumulated in the tank in super-critical phase.

In one aspect, it is provided for removing heat from the working fluid in the primary heat exchanger until it is brought, in a T-S diagram, to a température above the critical température and above the Andrews bell.

In one aspect, it is provided for removing heat from the working fluid in the secondary heat exchanger by bringing it into the super-critical phase and making it follow the right portion of the Andrews bell.

In one aspect, the tank comprises a séparation membrane configured to internally separate the tank into a first chamber with variable volume for the working fluid in supercritical phase and a second chamber with variable volume in fluid communication with a compensation circuit containing a non-compressible fluid, optionally water.

In one aspect, the compensation circuit is configured to maintain a substantially constant pressure in the super-critical working fluid contained in the first variable volume chamber of the tank, or at least to maintain the working fluid pressure always above a certain minimum value.

In one aspect, the compensation circuit comprises an auxiliary tank for the noncompressible fluid, optionally at atmospheric pressure, in fluid communication with the second variable volume chamber.

In one aspect, the compensation circuit comprises an auxiliary turbine connected to an auxiliary generator and configured to be rotated by the incompressible fluid coming from

-1620837 the second variable volume chamber in the charge confjguration/phase of the apparatus/process.

In one aspect, the expansion energy ofthe liquid (typically water) of the compensation circuit in charge phase is between 1/100 and 7/100 of the charging energy of the storage System through the compressor.

In one aspect, the compensation circuit comprises a pump connected to an auxiliary motor and configured to pump the non-compressible fluid from the auxiliary tank into the second variable-volume chamber in the discharge confîguratîon/phase of the apparatus/process.

In one aspect, the pumping energy of the liquid (typically water) of the compensation circuit in discharge phase is between 1/100 and 7/100 of the discharge energy of the storage System through the turbine.

In one aspect, the secondary heat exchanger and the primary heat exchanger are configured to perform a sub-critical transformation of the working fluid so that the working fluid is accumulated in the tank in liquid phase.

In one aspect, it is provided for removing heat from the working fluid in the primary heat exchanger until it is brought to a température below the critical température in a T-S diagram and to a point on the left portion of the Andrews bell.

In one aspect, it is provided for removing heat from the working fluid in the secondary heat exchanger by passing it through the saturated vapor zone until it reaches the liquid phase.

Further features and advantages will appear in greater detail in the detailed description of preferred, but not exclusive, embodiments of a plant and process for energy storage according to the présent invention.

Description of drawinqs

This description will be set out below with reference to the attached drawings, which are provided for indicative and non-limiting purposes, in which:

figure 1 schematically shows an embodiment of an energy storage plant according to the présent invention;

figure 2 shows a variant of the plant of figure 1 ;

figure 3 is a T-S diagram showing a process according to the présent invention implemented in the plants of figure 1 or 2;

-1720837 figure 4 shows a further embodiment of an energy storage plant according to the présent invention;

* figure 5 shows a variant of the plant of figure 4;

figure 6 is a T-S diagram showing a process according to the présent invention implemented in the plants of figure 4 or 5;

• figure 7 is a T-Q diagram showing a part of the process according to the présent invention implemented in the plants of figure 4 or 5;

figures 8, 9 and 10 show respective variants of a portion of the plant of figure 2;

figures 11 and 12 show respective variants of a different portion of the plants in figures 1,2, 4 and 5;

figure 13 shows a further embodiment of an energy storage plant according to the présent invention.

Detailed description

With reference to the attached figures, with the reference number 1, a plant for the storage of energy (energy storage) according to the présent invention has been indicated overall.

The plant 1, for example, opérâtes with a working fluid other than atmospheric air.

For example, plant 1 opérâtes with a working fluid chosen from the group including: carbon dioxide CO₂, sulphur hexafluoride SF₆, nitrous oxide N₂O. In the following description, the working fluid used in combination with described plant 1 is carbon dioxide CO₂.

Plant 1 is configured to perform a closed cyclic thermodynamic transformation (TTC), first in one direction into a charge configuration/phase and then in the opposite direction into a discharge configuration/phase, in which plant 1 stores heat and pressure in the charge configuration and generates electrical energy in the discharge configuration.

With reference to figure 1, plant 1 comprises a turbine 2 and a compressor 3 mechanically connected to a shaft of a single motor-generator 4. The motor-generator 4, the compressor 3 and the turbine 2 are arranged on a same axis. A shaft of the turbine 2 is coupled to one end of the shaft of the motor-generator 4 by means of connection devices, e.g. of the clutch type, which make it possible to connect and disconnect, on command, the turbine 2 to and from the motor-generator 4. Similarly, a shaft of the compressor 3 is coupled to an opposite end of the shaft of the motorgenerator 4 by means of connection devices, e.g. of the clutch type, which allow the

-1820837 compresser 3 to be connected to and disconnected, on command, from the motorgenerator 4. In other embodiments not shown here, the motor is firmly connected to the compressor 3 and the generator is firmly connected to the turbine 2. In such a case, the motor is permanently connected to compressor 3 and the generator is permanently connected to turbine 2.

Plant 1 comprises a casîng 5 preferably defined by a pressure-balloon made of flexible material, e.g. PVC coated polyester fabric. The pressure-balloon is placed on the earth’s surface and is externally in contact with atmospheric air. The pressure-balloon delimits inside a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric pressure, i.e. in equilibrium of pressure with the atmosphère. The casing 5 may also be designed as a gasometer or any other gas storage System with low or no overpressure.

First pipelines 6 develop between the casing 5 and an inlet 3a of the compressor 3 and between the casing 5 and an outlet 2b of the turbine 2 to connect the internai volume of the casing 5 with said compressor 3 and turbine 2. A valve or a valve System, not illustrated, may be operationally placed on the first pipelines 6 to put in fluid communication alternately the casing 5 with the inlet 3a of the compressor 3 or the outlet 2b of the turbine 2 with the casing 5.

The plant 1 comprises a primary heat exchanger 7 which can be selectively put in fluid communication with an outlet 3b of compressor 3 or with an inlet 2a of turbine 2. For this purpose, second pipelines 8 develop between the inlet 2a of the turbine 2 and primary heat exchanger 7 and between the outlet 3b of the compressor 3 and the primary heat exchanger 7. A valve, or a valve System, not illustrated, is operationally located on the second pipelines 8 to connect the primary heat exchanger 7 with the inlet 2a of turbine 2 or the outlet 3b of compressor 3 with the primary heat exchanger 7. In a preferred embodîment, there is only one valve or valve System located on the second pipelines 8.

A tank 9 is in fluid communication with the primary heat exchanger 7 and is configured to store the working fluid in liquid or supercritical phase.

The tank 9 is preferably made of métal with a spherical outer wall.

A secondary heat exchanger 10 is operationally active between the primary heat exchanger 7 and the tank 9, or in said tank 9, and is configured to operate on the working fluid accumulated or in accumulation phase in the tank 9. According to what is shown in the embodîment of figure 1, the secondary heat exchanger 10 is integrated in

-1920837 tank 9 in the sense that it has its own heat exchange portion 11 housed inside the tank 9 and configured to be touched by the working fluid contained in said tank 9. Third pipes 12 develop between the primary heat exchanger 7 and the tank 9 to put in fluid communication said primary heat exchanger 7 with said tank 9 and with said secondary heat exchanger10.

In the schematic représentation of figure 1, the plant 1 may also comprise an additional heat exchanger 13 operationally placed between the casing 5 and the compresser 2 and between the casing 5 and the turbine 2 and possibly a cooler 13a positioned on a branch of the first pipelines 6 connected to the outlet 2b of turbine 2.

The plant 1 also comprises a control unit, not shown, operationally connected to the different éléments of the same plant 1 and configured/programmed to manage its operation.

The plant 1 is configured to operate in a charge configuration or in a discharge configuration or to perform a process comprising a phase of energy charge and a phase of discharge and energy génération.

In the charge configuration, the plant 1 starts from a first State in which the working fluid (CO₂) in gaseous form is ali contained in the casing 5 at atmospheric pressure or substantially atmospheric pressure and at a température substantially equal to the ambient température (point A of the T-S diagram in figure 3). Casing 5, through the valve System, is connected to the inlet 3a of the compresser 3 while communication with the outlet 2b of the turbine 2 is blocked. In addition, by means of the valve system, the primary heat exchanger 7 is in fluid communication with the outlet 3b of the compressor 3 and communication with the inlet 2a of the turbine 2 is blocked. The motor-generator 4 is coupled to the compressor 3 only and is decoupled from the turbine 2 (which is at rest) and works as motor to drive the compressor 3 such as to compress the working fluid coming from the casing 5.

Before entering the compressor 3, the working fluid passes through the additional heat exchanger 13 which acts as a heater to pre-heat the working fluid (point B of the T-S diagram in figure 3). The working fluid is then compressed in the compressor 3 and heats up (point C of the T-S diagram in figure 3). The working fluid then flows through the primary heat exchanger 7 which works as a cooler to remove heat from the compressed working fluid, cool it (point D of the T-S diagram in Figure 3) and store the thermal energy removed from the working fluid. At point D the working fluid is at a température lower than the critical température of the working fluid and at a point on the

-2020837 left side of the Andrews bell or slightly outside the bell in conditions of slight overheating. This compression may be adiabatic, inter-cooled or isothermal.

The working fluîd enfers the tank 9 where the secondary heat exchanger 10, which in this configuration works as a cooler, removes further heat from the working fluid and accumulâtes further thermal energy. The working fluid passes through the saturated vapor zone until it reaches the liquid phase (point E of the T-S diagram in Figure 3). The tank 9 therefore accumulâtes the working fluid in the liquid phase at a température lower than its own critical température Te. In this second state, the working fluid (CO₂, Te = 31 °C) in liquid form, for example at 20°C, is ail contained in the tank 9. The secondary heat exchanger 10 and the primary heat exchanger 9 are therefore configured to perform a sub-critical transformation of the working fiuid so that the working fluid is accumulated in the tank 9 in liquid phase.

In the discharge configuration, the plant 1 starts from the second state (point F of the TS diagram in figure 3). The casing 5, through the valve System, is put in communication with the outlet 2b of turbine 2 while communication with the inlet 3a of the compressor 3 is blocked. In addition, by means of the valve System, the primary heat exchanger 7 is in fluid communication with the inlet 2a of the turbine 2 and the communication with the outlet 3b of the compressor 3 is blocked. The motor-generator 4 is coupled to turbine 2 only and is decoupled from compressor 3 (which is at rest) and works as a generator driven in rotation by the turbine 2 driven by the expanding working fluid.

The secondary heat exchanger 10 works as a heater and transfers some of the heat previously accumulated in the charge configuration to the working fluid in the tank 9. The working fluid passes through the saturated steam zone until it reaches the steam phase (point G of the T-S diagram in Figure 3). The working fluid passes through the primary heat exchanger 7 which now works as a heater and releases additional heat, previously accumulated in the charge configuration, to the working fluid and heats it (point H of the T-S diagram in figure 3).

The heated working fluid enters the turbine 2, expands and cools (point I of the T-S diagram in figure 3) and causes the rotation of the turbine 2. The turbine 2, rotated by the heated working fluid, drives the motor-generator 4, which works as a generator and generates electrical energy. The working fluid expansion in the turbine may be adiabatic, inter-heated or isothermal.

The working fluid coming from turbine 2 is cooled in the additional heat exchanger 13 (point J of diagram T-S in figure 3) and returns into the casing 5 at atmospheric or

-2120837 substantially atmospheric pressure. The additional heat exchanger 13 in this phase stores additional thermal energy in a respective additional thermal energy storage device, which will be used in the next charge phase to pre-heat the working fluid.

In the transformation illustrated in figure 3, the secondary circuit 20 is configured to remove heat from the working fluid, in the charge configuration, or to transfer heat to the working fluid, in the discharge configuration, at a température close to the ambient température, for example, of about 20°C.

Both in the charge and in the discharge configuration/phase, since the secondary heat exchanger 10 opérâtes in conditions close to the ambient température, due to the fact that the fluid has a critical température close to the ambient température, it is possible that the heat removal phase and/or the heat supply phase by the secondary heat exchanger is/are assisted by a phase of direct or indirect exchange with the atmosphère.

For example, a working fluid température (CO₂) accumulated in the tank 9 is 24°C and a working fluid pressure accumulated in the tank 9 is 65 bar. The density of CO₂ at 25°C and atmospheric pressure is about 1.8 kg/m³. The density of CO2 in the tank 9 is about 730 kg/m³. The ratio between the density of the working fluid when contained in the tank 9 under the indicated conditions and the density of the same working fluid when contained in the casing 5 under atmospheric conditions is therefore about 400. It should be noted in this regard that if instead of CO2 the atmospheric air stored at 65 bar and 24°C in the tank 9 were used, its density would be only 78 kg/m³ and the volume of the tank 9 theoretically required would be about ten times greater.

For example, for a plant 1 according to the invention able to store 100MWh of energy, the volume of the pressure-balloon is about 400000 m³ while the volume of the tank is about 1000 m³.

The variant of figure 2 shows a type of primary heat exchanger 7, i.e. a fixed bed heat regenerator comprising a thermal mass 14 consisting, for example, of métal balls. In the charge configuration/phase, the thermal mass 14 is lapped by the hot, compressed working fluid, which transfers heat to the métal balls that store thermal energy. In the discharge configuration/phase, the thermal mass 14 is lapped by the cold working fluid, which absorbs heat from the métal balls and heats up. In a variant not shown, the heat regenerator may also be of the moving bed type. The primary heat exchanger 7 is therefore a thermal storage (Thermal Energy Storage TES).

-2220837

Instead of the fixed bed heat regenerator shown in figure 2, other types of heat regenerator may be used.

For example, a possible primary heat exchanger 7 is shown in figure 11. As shown in Figure 11, the primary heat exchanger 7 comprises a primary circuit 15 crossed by a primary fluid, such as water, oil or salts. The primary circuit 15 comprises a heat exchange portion 16 configured to exchange heat with the working fluid. For example, in the schematic embodiment illustrated above, a section of the second 8 pipelines through which the working fluid fiows passes through the heat exchange section 16, so that the primary fluid touches said section. The primary circuit 15 comprises a hot primary storage chamber 17, for the hot primary fluid accumulated after removing heat from the working fluid in the charge configuration/phase of the apparatus/process, and a cold primary storage chamber 18, for the cold primary fluid accumulated after transferring heat to the working fluid in the discharge configuration/phase of the apparatus/process. The heat exchange portion 16 is placed between the hot primary storage chamber 17 and the primary cold storage chamber 18. In the charge configuration/phase of the apparatus/process, the primary fluid flows from the cold primary storage chamber 18 to the hot primary storage chamber 17, removing heat from the working fluid. In the discharge configuration/phase of the apparatus/process, the primary fluid flows from the hot primary storage chamber 17 to the cold primary storage chamber 18 releasing heat from the working fluid.

A different possible primary heat exchanger 7 is shown in figure 12. According to what is illustrated in figure 12, the primary circuit 15 of the primary heat exchanger 7 comprises a heat exchange portion 16 defined by a section of primary circuit 15 that is lapped by the working fluid that passes through the second pipelines 8. The primary circuit 15 also comprises a fixed bed heat regenerator 19, preferably operating at atmospheric pressure and preferably similar to that described above, which is lapped by the primary fluid.

The variant of figure 2 is not equipped with the additional heat exchanger 13 so that the corresponding T-S diagram, not illustrated, does not show, with respect to the diagram of figure 3, points B and J.

The variant in Figure 2 also has a spécial structure of the secondary heat exchanger 10. The secondary heat exchanger 10 shown includes a secondary circuit 20 crossed by a secondary fluid, such as air or water. The secondary circuit 20, in addition to the heat exchange portion 11 housed inside the tank 9, comprises a secondary hot storage

-2320837 chamber 21, for the secondary hot fluid accumulated after removing heat from the working fluid in the charge configuration/phase of the apparatus/process, and a secondary coid storage chamber 22, for the secondary cold fluid accumulated after releasing heat to the working fluid in the discharge configuration/phase of the apparatus/process. The above mentioned chambers 21, 22 are also connected to each other, in addition to the above mentioned heat exchange portion 11, through a radiator 23 equipped with fans 24 and with recirculation ducts that cools the secondary fluid during the night and heats it during the day.

Figures 8, 9 and 10 show other variants of the secondary heat exchanger 10 associated with tank 9.

In Figure 8, the secondary circuit 20, in addition to the heat exchange portion 11, is equipped with an additional heat exchange portion 25 through which it exchanges heat with e.g. air or sea water.

In Figure 9, the secondary circuit 20 is equipped with a secondary tank 26 with water/ice or another two-phase System operationally connected to an auxiliary chiller 27.

In Figure 10, the secondary circuit 20 is located in a basin full of water consisting of severai chambers 28a, 28b, 28c. The embodiment illustrated in figure 10 shows a chamber 28a for hot water storage, a chamber 28b for cold water storage and a chamber 28c in fluid communication with the others and housing part of the secondary circuit 20. The secondary fluid in the secondary circuit 20 is cooled or heated by the water in the basin. The working fluid is condensed in the charge phase and evaporated in the discharge phase by the suitably circulated water, preferably through immersion pumps and through the secondary fluid. The chambers 28 of said basin can be covered or uncovered and in communication or not with the environment so that the chamber from which the water is circulated for condensation during charging is always cooled by the surrounding environment, by appropriate panels 29, while the one from which the water is circulated for évaporation during discharging is always heated by the surrounding environment and possibly kept warm by a cover. The above can be further supported by spécial exchange Systems that absorb heat or release heat, both through convection and radiation, with the environment, ail in order to improve the RTE of the System.

The embodiments of figures 4 and 5 differ structurally from what has already been described because the secondary heat exchanger 10 is placed between the primary heat exchanger 7 and the tank 9, Le. it is not integrated in the tank 9. The secondary -2420837 heat exchanger 10 is in line on the third pipelines 12. Figure 4 schematically illustrâtes a generic secondary heat exchanger 10. Figure 5 shows a schematic design example of the secondary heat exchanger 10.

The secondary heat exchanger 10 shown in figure 5 comprises a secondary circuit 20 crossed by a secondary fluid, e.g. water. The secondary circuit 20 has a heat exchange portion 11 that is lapped by the working fluid that passes through the third pipelines 12 and is confîgured to exchange heat with the working fluid.

The secondary circuit 20 of figure 5 comprises a secondary hot storage chamber 21, for the secondary hot fluid accumulated after removing heat from the working fluid in the charge configuration/phase of the apparatus/process, and a secondary cold storage chamber 22, for the secondary cold fluid accumulated after releasing heat to the working fluid in the discharge configuration/phase of the apparatus/process.

The heat exchange portion 11 is located between the secondary hot storage chamber 21 and the secondary cold storage chamber 22. In the charge configuration/ phase of the apparatus/process, the secondary fluid flows from the secondary cold storage chamber 22 to the secondary hot storage chamber 21, removing heat from the working fluid. In the discharge configuration/phase of the apparatus/process, the secondary fluid flows from the secondary hot storage chamber 21 to the secondary cold storage chamber 21, releasing heat from the working fluid. The secondary circuit 20 also comprises one or more intermediate secondary storage chambers 30 to adjust/vary the flow rate of the secondary fluid in the heat exchange portion 11 and the température variation of the working fluid exchanging heat with this secondary fluid. Figure 5 shows two intermediate secondary storage chambers 30.

The embodiments of Figures 4 and 5 differ structurally from what has already been described also because the tank 9 comprises a séparation membrane 31 confîgured to internally separate the tank 9 in a first chamber with variable volume 32 for the working fluid in super-critical phase and in a second chamber with variable volume 33 in fluid communication with a compensation circuit 34 containing water. The compensation circuit 34 is confîgured to maintain a substantîally constant pressure in the super-critical working fluid coming from the secondary heat exchanger 20 and contained in the first variable volume chamber 32 of the tank 9.

The compensation circuit 34 comprises an auxîliary tank 35 for water at atmospheric pressure, which is in fluid communication, through appropriate pipelines, with a lower portion of the tank 9 and with the second variable volume chamber 33. An auxîliary

-2520837 turbine 36 has an iniet in communication with the second variable volume chamber 33 and an outlet connected to the auxiliary tank 35. The auxiliary turbine 36 is connected to an auxiliary generator 37 and is configured to be rotated by the water coming from the second variable volume chamber 33 in the charge configuration/phase of the apparatus/process. A pump 38 has an inlet in communication with the auxiliary tank 35 and an outlet connected to the second variable volume chamber 33. The pump 38 is connected to an auxiliary motor 39 and is configured to pump water from the auxiliary tank 35 into the second variable volume chamber 33 in the discharge configuration/phase of the apparatus/process.

Figure 6 shows the T-S dîagram for the embodiments of Figures 4 and 5.

Figure 7 shows the T-Q diagram relating to a part of the thermodynamic transformation carried out by the embodiment of Figure 5.

The secondary heat exchanger 10 and the primary heat exchanger 7 of the embodiments of Figures 4 and 5 are configured to operate a super-critical transformation of the working fluid so that said working fluid is accumulated in the tank in super-critical phase. In fact, unlike what is shown in Figure 3, the primary heat exchanger 7 removes heat from the working fluid up to bring it (point D of figure 6) to a température higher than the critical température and above the Andrews belk Subsequently, the secondary heat exchanger 10 brings the working fluid into supercritical phase (point E) making it follow the right side of Andrews' bell. Figure 7 shows the température decrease from point D to point E ofthe working fluid during the charge phase and the corresponding température increase ofthe secondary working fluid ofthe secondary heat exchanger 10 of Figure 5 (points U, V, W, Z). The same Figure 7 also illustrâtes the température increase from point F to point G of the working fluid during the discharge phase and the corresponding température decrease of the secondary working fluid ofthe secondary heat exchanger 10 of Figure 5 (points Z, W, V, U).

For instance, a working fluid température (CO2) accumulated in super-critical phase in the tank 9 is 25°C and a working fluid pressure accumulated in super-critical phase in the tank 9 is 100 bar. The density of CO2 at 25°C and atmospheric pressure is about 1.8 kg/m³. The density of CO₂ in the tank 9 is about 815 kg/m³. The ratio between the density ofthe working fluid when contained in the tank 9 under the indicated conditions and the density of the same working fluid when contained in the casing 5 under atmospheric conditions is therefore about 450.

-2620837

It should be noted that the structure of the secondary heat exchanger of Figure 10 may also be adopted in the embodiment of Figures 4 and 5,

In addition, the secondary heat exchanger may be equipped with flow rate and/or température control Systems for secondary fluid, typically water or air, capable of regulating the pressure in the storage tanks within certain limits, when the System opérâtes in sub-critical conditions. Température control may, for example, be carried out by adding heat from the atmosphère or removing heat to atmosphère, also taking advantage of the normal fluctuations in the ambient température of air and water at different times of the day.

In the illustrated embodiments using CO₂ as the working fluid, a CO₂ déhydration System, a de-humidifier, for example with zeolites, is also preferably présent to avoid potential formation of carbonic acid in the circuit.

Figure 13 shows a further variant of plant 1. It shows the main éléments common to Figure 1, i.e. the turbine 2, the compresser 3, the motor generator 4, the casing 5, the primary heat exchanger 7 (TES thermal storage), the tank 9 and the secondary heat exchanger 10. Plant 1 shown here also comprises the additional heat exchanger 13. As in the embodiment shown in Figure 4, the secondary heat exchanger 10 is iocated between the primary heat exchanger 7 and the tank 9, i.e. it is not integrated in tank 9. Similar to the plant shown in Figure 2, the secondary heat exchanger 10 comprises a secondary circuit 20 crossed by a secondary fluid, e.g. water. The secondary circuit 20, in addition to the heat exchange portion 11 comprises a secondary storage chamber 200, for the secondary hot fluid accumulated after removing heat from the working fluid in the charge configuration/phase of the apparatus/process and for the secondary cold fluid accumulated after releasing heat to the working fluid in the discharge configuration/phase of the apparatus/process. The above mentioned secondary storage chamber 200 is also combined with a radiator 23 equipped with one or more fans 24 placed on a recirculation duct which, for example, cools the secondary fluid during the night and heats it during the day. The above-mentioned secondary storage chamber 200 is also connected to the additional heat exchanger 13 via a corresponding circuit 210.

In this embodiment, plant 1 also comprises at least one additional heat exchanger 220 which receives heat from an additional heat source 230. The additional heat exchanger 220 is Iocated on the second pipeline 8, between the inlet 2a of turbine 2 and the primary heat exchanger 7. The additional heat source 230 is, for example but not

-27 20837 exclusively, a solar source (e.g. solar field), residual heat deriving from industrial recovery (Waste Heat Recovery), exhaust heat from gas turbines, etc.. The additional heat source 230 provides additional heat during the discharge phase. The température at which the working fluid is brought during the discharge phase and just before it enters turbine 2, via the additional heat source 230 and the additional heat exchanger 220, is higher than the température of the working fluid that is obtained at the end of the compression during the charge phase. For example, the température at which the working fluid is brought by the additional heat source 230 and the additional heat exchanger 220 is about 100°C but also 200°C or 300°C or 400°C higher than the température of the working fluid at the end of compression.

Plant 1 is also equipped with an auxiliary thermal storage 240 (Thermal Energy Storage TES) connected, through appropriate circuits, to the compressor 2 and the turbine 2 in order to achieve, in the compressor 3 (during the charge phase), an inter-cooled compression (with one or more inter-coolings) and to achieve, in the turbine 2 (during the discharge phase), an inter-heated expansion (with one or more inter-heatings). The heat accumulated in the auxiliary heat accumulator 240 during the inter-cooled compression is used in whole or in part to achieve the inter-heated expansion.

In an embodiment of the process performed with the plant of figure 13, it is provided not to carry out inter-coolings in the charge phase and not to carry out inter-heatings in the discharge phase and to provide additional heat in the discharge phase through the additional heat source 230 and the additional heat exchanger 220.

In variants of the process performed with the plant of figure 13, it is provided to make one or more inter-coolings in the charge phase and an equal number of inter-heatings in the discharge phase, in addition to providing additional heat in the discharge phase through the additional heat source 230 and the additional heat exchanger 220.

In a further embodiment of the process performed with the plant of figure 13, it is provided to carry out a number of inter-coolings in the charge phase and to carry out a single inter-cooling in the discharge phase using the heat (accumulated in the auxiliary thermal accumulator 240) only of the last inter-cooling, in addition to heat with the additional heat through the additional heat source 230 and the additional heat exchanger 220, The heat stored in the auxiliary heat storage 240 and coming from the remaining intercoolings can be used for other purposes, e.g. for co-generation, The invention is not limited to the embodiment/s illustrated in the drawings. Accordingly it should be understood that where features mentioned in the appended daims are

-2820837 followed by reference signs, such signs are included solely for the purpose of enhancing the intelligibility ofthe daims and are in no way limiting on the scope ofthe daims.

List of éléments energy storage plant turbine

2a turbine inlet

2b turbine outlet compressor

3a compressor inlet

3b compressor outlet motor-generator casing first pipelines primary heat exchanger second pipelines tank secondary heat exchanger heat exchange portion of secondary heat exchanger third pipelines additional heat exchanger

13a cooler thermal mass primary circuit heat exchange portion of the primary circuit primary hot storage chamber primary cold storage chamber fixed bed heat regenerator secondary circuit secondary hot storage chamber secondary cold storage chamber radiator fans

-2920837 intermediate secondary storage chambers séparation membrane first variable volume chamber second variable volume chamber compensation circuit auxiliary tank auxiliary turbine auxiliary generator pump auxiliary motor secondary storage chamber additional heat exchanger circuit additional heat exchanger additional heat source auxiliary thermal storage

Claims (15)

1. Energy storage plant, comprising:

a casing (5) storing a working fluid other than atmospheric air, in a gaseous phase and in equilibrium of pressure with the atmosphère, wherein said casing (5) is a pressureballoon or has the structure of a gasometer;

a tank (9) storing said working fluid in liquid or supercritical phase with a température close to the critical température; wherein said critical température is close to the ambient température;

wherein the plant is configured to perform a closed cyclic thermodynamic transformation (TTC), first in one direction in a charge configuration and then in an opposite direction in a discharge configuration, between said casing (5) and said tank (9); wherein in the charge configuration the plant stores heat and pressure and in the discharge configuration generates energy.

2. Plant according to claim 1, wherein the working fluid has the following chemicalphysical properties: critical température between O’C and 200°C, density at 25°C between 0.5 kg/m³ and 10 kg/m³; and/or is chosen in the group including: CO₂, SF₆, N₂O.

3. Plant according to claim 1 or 2, comprising:

a compressor (3) and a motor mechanically connected to each other;

a turbine (2) and a generator mechanically connected to each other;

said casing (5) extemally in contact with the atmosphère and delimiting inside a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric pressure, wherein said volume is selectively in fluid communication with an inlet (3a) of the compressor (3) or with an outlet (2b) of the turbine (2);

a primary heat exchanger (7) selectively in fluid communication with an outlet (3b) of the compressor (3) or with an inlet (2a) of the turbine (2);

said tank (9) in fluid communication with the primary heat exchanger (7) to accumulate the working fluid;

a secondary heat exchanger (10) operationally active between the primary heat exchanger (7) and the tank (9) or in said tank (9);

said plant being configured to operate in the charge configuration or in the discharge configuration;

-3120837 wherein, in the charge configuration, the casing (5) is in fluid communication with the inlet (3a) of the compresser (3) and the primary heat exchanger (7) is in fluid communication with the outlet (3b) of the compresser (3), the turbine (2) is at rest, the motor is operating and drives the compresser (3) to compress the working fluid coming from the casing (5), the primary heat exchanger (7) works as a cooler to remove heat from the compressed working fluid, cool it and store thermal energy, the secondary heat exchanger (10) works as a cooler to remove additional heat from the compressed working fluid and store additional thermal energy, the tank (9) receives and stores the compressed and cooled working fluid, wherein the working fluid stored in the tank (9) has a température close to its own critical température;

wherein, in the discharge configuration, the casing (5) is in fluid communication with the outlet (2b) of the turbine (2) and the primary heat exchanger (7) is in fluid communication with the inlet (2a) of the turbine (2), the compresser (3) is at rest, the secondary heat exchanger (10) works as a heater to release heat to the working fluid coming from the tank (9), the primary heat exchanger (7) works as a heater to release further heat to the working fluid and heat it, the turbine (2) is rotated by the heated working fluid and drives the generator generating energy, the working fluid returns in the casing (5) to atmospheric or substantially atmospheric pressure.

4. Plant according to claim 3, comprising an additional heat exchanger (13) operationally placed between the casing (5) and the compresser (3) and between the casing (5) and the turbine (2) to pre-heat the working fluid before compression in the compresser (3), in the storage configuration, or to cool the working fluid from the turbine (2), in the discharge configuration.

5. Plant according to one of the above daims 3 or 4, wherein the motor and the generator are separate éléments; or wherein the motor and the generator are defined by a single motor-generator (4) and the plant comprises connection devices between said motor-generator (4) and the compresser (3) and the turbine (2) to connect mechanically and alternately the motor-generator (4) to the compresser (3) or to the turbine (2).

6. Plant according to one of the above daims 3, 4 or 5, wherein the secondary heat exchanger (10) and the primary heat exchanger (7) are configured to operate a supercritical transformation of the working fluid so that said working fluid is accumulated in the tank (9) in super-critical phase.

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7. Plant according to the previous daim, wherein the tank (9) comprises a separating membrane (31) configured to internally separate the tank (9) into a first chamber with variable volume (32) for the working fluid in super-crîtical phase and into a second chamber with variable volume (33) in fluid communication with a compensation 5 circuit (34) containing a non-compressible fluid.

8. Plant according to one of the above daims from 3 to 5, wherein the secondary heat exchanger (10) and the primary heat exchanger (7) are configured to operate a sub-critical transformation of the working fluid so that the working fluid is accumulated in the tank (9) in liquid phase.

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9. Plant according to one of the above daims 3 to 8, wherein the primary heat exchanger (7) is a fixed or moving bed heat regenerator or comprises a water, oil or sait primary circuit (15) with at least one primary storage chamber (17, 18).

10. Plant according to one of the above daims from 3 to 9, wherein the secondary heat exchanger (10) comprises a secondary air or water circuit (20) with at least one 15 secondary storage chamber (21, 22) and is configured to remove heat from the working fluid, in the charge configuration, or to transfer heat to the working fluid, in the discharge configuration, at a température below 100°C.

11. Process for energy storage, comprising:

carrying out a closed thermodynamic cyclic transformation (TTC), first in one direction in 20 a charge configuration/phase and then in an opposite direction in a discharge configuration/phase, between a casing (5) for the storage of a working fluid different from atmospheric air, in a gaseous phase and in pressure equilibrium with the atmosphère, and a tank (9) for the storage of said working fluid in a liquid or supercritica! phase with a température dose to the critical température; wherein said 25 critical température is close to the ambient température; wherein, in the charge phase, the process accumulâtes heat and pressure and, in the discharge phase, generates energy.

12. Process according to daim 11, wherein the charge phase comprises:

compressing said working fluid, coming from said casing (5) externally in 30 contact with the atmosphère and delimiting inside a volume configured to contain the working fluid at atmospheric pressure or substantially atmospheric, absorbing energy;

injecting the compressed working fluid through a primary heat exchanger (7) and a secondary heat exchanger (10) placed in sériés to bring a température

-33 20837 of the working fluid close to its own critical température; wherein the primary heat exchanger (7) works as a coder to remove heat from the compressed working fluid, cool it and store thermal energy, wherein the secondary heat exchanger (10) works as a coder to remove further heat from the compressed working fluid and store further thermal energy;

accumulating the cooled working fluid in said tank (9); wherein the secondary heat exchanger (10) and the primary heat exchanger (7) carry out a supercritical transformation of the working fluid so that said working fluid is accumulated in the tank (9) in super-critical phase or wherein the secondary heat exchanger (10) and the primary heat exchanger (7) carry out a subcritical transformation of the working fluid so that said working fluid is accumulated in the tank (9) in liquid phase; wherein a température of the working fluid accumulated in the tank (9) is between 0 °C and 100 °C and wherein a pressure of the working fluid accumulated in the tank (9) is between 10 bar and 150 bar.

13. Process according to claim 11 or 12, wherein said working fluid has the following physical-chemical properties: critical température between 0 °C and 200 °C, density at 25 °C between 0,5 kg/m³ and 10 kg/m³; and/or it is chosen in the group including: CO₂, SF_6i n₂o.

14. Process according to claim 12 or 13, wherein the phase of discharge and génération of energy comprises:

passing the working fluid from the tank (9) through the secondary heat exchanger (10) and the primary heat exchanger (7); wherein the secondary heat exchanger (10) works as a heater to transfer heat to the working fluid coming from the tank (9), wherein the primary heat exchanger (7) works as a heater to transfer further heat to the working fluid and heat it;

passing the heated working fluid through a turbine (2), wherein the turbine (2) is rotated by the heated working fluid and drives the generator generating energy, wherein the working fluid expands and cools down in the turbine (2); re-injecting the working fluid coming from the turbine (2) into the casing (5) at atmospheric or substantially atmospheric pressure.

15. Process according to claim 14, wherein in the discharge phase and energy génération, between the primary heat exchanger (7) and the turbine (2), it is provided to further heat the working fluid through an additional heat source (230).