Devices and methods for energy generation and storage

Abstract

A device (1) for storing energy includes: a housing (5) for storing a working fluid in a gaseous phase and in pressure equilibrium with the atmosphere, which is not atmospheric air; and a container (9) for storing the working fluid in a liquid or supercritical phase at a temperature close to a critical temperature, wherein the critical temperature is close to ambient temperature. The device (1) is configured to perform a closed-loop thermodynamic conversion (CTT) between the housing (5) and the container (9), first in a charge configuration in one direction and then in a discharge configuration in the opposite direction; wherein the device (1) stores heat and pressure in the charge configuration and generates energy in the discharge configuration. The device (1) is also configured to define a closed loop and is optionally configured to perform a closed-loop thermodynamic cycle (TC) in the closed loop using at least a portion of the working fluid while the device (1) is in either the charge or discharge configuration.

Description

Technical Field

[0001] The object of this invention is an apparatus and method for generating and storing energy.

[0002] More precisely, the object of the present invention is a system capable of absorbing / using energy, retaining stored energy over time, converting stored energy into mechanical energy for actuating one or more slave motors, and / or converting stored energy into electrical energy and reintroducing said electrical energy into the power grid when needed, and generating electrical energy from external energy sources (e.g., recovered heat / WHR, solar energy, hydrogen (H2), biomass, waste, fossil fuels).

[0003] More specifically, the present invention relates to a system for generating electrical energy from various sources and storing such electrical energy in the form of potential energy (pressure) and thermal / thermodynamic energy through actuation via thermodynamic cycles and / or cyclic thermodynamic conversions.

[0004] This invention relates to the field of medium to large-scale systems for generating and storing energy from various sources for both terrestrial and marine applications. These systems typically have power ranging from hundreds of kW to tens of MW (e.g., 20 MW to 25 MW), but can also be hundreds of MW, and storage capacities ranging from hundreds of kWh to hundreds of MWh and even several GWh.

[0005] The present invention also relates to the field of small-scale systems for generating and storing energy from various sources for domestic and commercial applications, both on land and at sea, typically having power ranging from several kW to hundreds of kW and storage capacity ranging from several kWh to hundreds of kWh.

[0006] definition

[0007] The following definitions will be referenced in this specification and the appended claims.

[0008] • Thermodynamic cycle (TC): Thermodynamic transformation from point X to point Y, where X and Y coincide; Unlike the CTT (cyclic thermodynamic transformation) mentioned below, TC does not accumulate mass within the cycle (which is significant for energy purposes), while CTT typically operates between two working fluid reservoirs, namely an initial working fluid reservoir and a final working fluid reservoir.

[0009] • Cyclic thermodynamic transition (CTT): Thermodynamic transitions from point X to point Y and from point Y to point X do not necessarily pass through the same intermediate point;

[0010] • Closed-loop TC and / or CTT: No mass exchange with the atmosphere (significant for energy purposes);

[0011] • Open TC and / or CTT: Mass exchange with the atmosphere (significant for energy purposes). Background Technology

[0012] Recently, energy storage systems have become increasingly important due to the growing popularity of systems that produce energy from renewable energy sources, particularly wind and solar power—systems characterized by variable and unpredictable production.

[0013] Along with the above needs, there is also a growing need for systems that generate and recover energy from unconventional and non-programmable sources, such as thermodynamic solar energy, without “energy storage”.

[0014] Publication WO / 2020 / 039416 under the same applicant describes an energy storage device and method. The device includes: a housing for storing a working fluid that is non-atmospheric air in a gaseous phase and in pressure equilibrium with the atmosphere; and a container for storing such a working fluid in a liquid or supercritical phase at a temperature close to a critical temperature, wherein the critical temperature is close to ambient temperature. The device is configured to perform a closed-loop thermodynamic conversion between the housing and the container, first in a filling configuration in one direction and then in a discharging configuration in the opposite direction. In the filling configuration, the device stores heat and pressure, and in the discharging configuration, the device generates energy. Summary of the Invention

[0015] The applicant has observed that the method and apparatus described in WO / 2020 / 039416 can be further improved, and in particular, the flexibility of the method and apparatus can be further improved.

[0016] The applicant has also observed that the method can be improved to achieve integration and configuration of systems for generating mechanical / electrical energy from non-programmable sources and from other sources.

[0017] The applicant feels a particular need to manufacture systems for generating mechanical / electrical energy that can regulate the absorption and generation of energy, especially electrical energy exchanged with the grid in a disproportionate manner to the energy input, thereby obtaining a prime mover (or conversely, a heat pump) capable of delivering power disproportionate to or better proportional to the energy input but shifting over time.

[0018] In this context, the applicant has set forth the purpose of conceiving and implementing devices and methods for energy generation and storage, which allow for: temporarily releasing mechanical / electrical output from energy input and / or regulating grid frequency (both ultra-fast and primary regulation); performing rapid ramp operation, balancing operation, etc.

[0019] The applicant has discovered that the above and other objectives can be achieved by an energy storage system that operates by combining a cyclic thermodynamic transformation (CTT) of the working fluid as described in WO / 2020 / 039416 with a closed thermodynamic cycle (TC) of at least a portion of the same working fluid.

[0020] The CTT (Chemical Energy Storage) system operates first in one direction and then in the opposite direction between two independent containers storing the working fluid. One state of the working fluid (at a lower temperature) is at atmospheric pressure, but the working fluid is not composed of atmospheric air but of another gas in pressure equilibrium with the atmosphere. The system is further characterized in that it stores energy, thereby transforming the working fluid from an initial gaseous / vapor state to a final liquid or supercritical state at temperatures close to the critical temperature (e.g., less than 1.2 times, preferably between 0.5 and 1.2 times, in Kelvin). It is also characterized in that the critical temperature is preferably not far from the ambient temperature, preferably close to the ambient temperature (preferably between 0°C and 200°C, more preferably between 0°C and 100°C).

[0021] A closed thermodynamic cycle (TC) can be subcritical, supercritical, or transcritical, and is actuated by the same machines used in a cell-to-cell (CTT) energy storage system, which operate as a prime mover (or as a heat pump). Overall, the system is thus hybrid and functions both as a battery (CTT) and as a prime mover / heat pump (TC).

[0022] The working fluid is preferably carbon dioxide (CO2), but to improve system performance, and also depending on the specific environmental conditions under which the system operates, a mixture of CO2 and other substances can be used to correct the fluid's critical temperature T. C Other fluids, such as SF6 and N2O, can be used either always in their pure form or mixed with other substances. In the proposed system, there is a reservoir for heat recovered from the compressor's delivery. Both the high-pressure and low-pressure vessels operate at constant pressure, or, in any case, at pressures regulated within certain well-defined ranges, when the system may operate under subcritical and supercritical conditions using different regulation strategies.

[0023] In particular, the above and other objectives are achieved substantially by devices and methods for energy generation and storage of the type claimed in the appended claims and / or described in the following aspects.

[0024] In its independent aspect, the present invention relates to an energy generation and storage device.

[0025] Preferably, the device includes: a working fluid, which is not atmospheric air; a housing configured to store the working fluid in a gaseous phase and in pressure equilibrium with the atmosphere; and a container configured to store the working fluid in a liquid or supercritical phase at a temperature close to a critical temperature.

[0026] Preferably, the critical temperature is close to the ambient temperature, and more preferably between 0°C and 100°C.

[0027] Preferably, the device is configured to perform a closed-loop thermodynamic conversion (CTT) between the shell and the container, first in a filling configuration in one direction and then in a discharging configuration in the opposite direction; wherein the device stores heat and pressure in the filling configuration and generates energy in the discharging configuration.

[0028] Preferably, the device is further configured to define / define a closed loop and to perform a closed thermodynamic cycle (TC) in the closed loop using a portion of the working fluid.

[0029] Preferably, the device is further configured to perform a closed thermodynamic cycle (TC) while the device is in a charging configuration or a discharging configuration.

[0030] In a separate aspect, the present invention relates to a method for energy generation and storage.

[0031] Alternatively, such a method may be performed using a device according to the foregoing aspects and / or according to at least one of the following aspects.

[0032] Preferably, the method includes performing a closed-loop thermodynamic conversion (CTT) between a shell and a container, first in a filling configuration / phase in one direction and then in a discharging configuration / phase in the opposite direction, wherein the shell is used to store a working fluid in the gaseous phase and in pressure equilibrium with the atmosphere (non-atmospheric air), and the container is used to store the working fluid in the liquid or supercritical phase at a temperature close to its critical temperature. The method accumulates heat and pressure during the filling phase and generates energy during the discharging phase.

[0033] Preferably, the critical temperature is close to the ambient temperature, and more preferably between 0°C and 100°C.

[0034] Preferably, the method includes: performing a closed thermodynamic cycle (TC) using at least a portion of the working fluid.

[0035] Preferably, the closed thermodynamic cycle (TC) is the Brayden cycle.

[0036] Preferably, the closed thermodynamic cycle (TC) is activated simultaneously with the charging phase or the discharging phase.

[0037] In one respect, the closed thermodynamic cycle (TC) operates without accumulation and release, that is, under high and low pressures, the net flow of working fluid from the reservoir (container and shell) and toward the reservoir is negligible or zero.

[0038] In one respect, a closed thermodynamic cycle (TC) is a closed thermodynamic cycle of a prime mover that generates electrical and / or mechanical energy, optionally without accumulating or discharging additional energy.

[0039] In different respects, a closed thermodynamic cycle (TC) is a closed thermodynamic cycle of a heat pump that generates and releases heat, optionally without accumulating or discharging additional energy.

[0040] The applicant has confirmed that the device and method according to the invention allow for the achievement of a pre-set target.

[0041] In particular, the applicant has demonstrated that the present invention allows for the management of absorbed, stored, returned, and generated energy in a flexible and efficient manner.

[0042] For example, this invention allows for the adjustment of the power grid frequency; and the execution of operations such as rapid ramp, rapid standby unit or rapid control standby, primary standby, and balancing.

[0043] For example, assuming a certain amount of working fluid accumulates in container 9, and assuming an additional thermal energy of 20 MW (given by another heat exchanger receiving heat from the additional heat source) and a closed thermodynamic cycle (TC) with 25% efficiency, the net electrical energy of the cycle is equal to 5 MWe (the result of a 13 MWe turbine and an 8 MWe compressor, minus the 8 MWe produced by the compressor from the 13 MWe produced by the turbine). If necessary, compressor 3 can be shut down or, in any case, placed in a minimum absorption state, and thus a rapid standby unit of 13 MW can be provided by utilizing the working fluid stored in container 9.

[0044] The applicant further confirms that the invention allows for the safe and low-environmental-impact operation of energy storage in locations without specific geographical features, similarly suitable for marine / offshore applications. The applicant also confirms that the invention allows for achieving high RTE (Resource-to-Energy).

[0045] The following are various aspects of the invention.

[0046] In one respect, the working fluid has a critical temperature ranging from 0°C to 200°C.

[0047] In one respect, the working fluid has a temperature of 0.5 kg / m³ at 25°C. 3Up to 10kg / m 3 The density between.

[0048] In one respect, the working fluid is selected from the group consisting of CO2, SF6, and N2O.

[0049] In one aspect, the device includes a compressor and a motor that are mechanically connected to each other.

[0050] In one aspect, the device includes a turbine and a generator and / or a slave motor (different from a generator) mechanically connected to each other.

[0051] In one respect, the motor and generator are a single motor-generator.

[0052] In one aspect, a friction-type connection device placed between the motor generator and the turbine, and between the motor generator and the compressor, is configured to connect the turbine and / or compressor to the motor generator or disconnect the turbine and / or compressor from the motor generator according to a command.

[0053] In one aspect, the device includes the housing, which is externally exposed to the atmosphere and internally defines a volume configured to contain a working fluid at atmospheric or near-atmospheric pressure, wherein the volume is selectively in fluid communication with either the inlet of a compressor or the outlet of a turbine.

[0054] In one respect, the primary heat exchanger is selectively fluidly connected to either the compressor outlet or the turbine inlet.

[0055] In one aspect, the device includes the container, which is in fluid communication with a primary heat exchanger to collect working fluid.

[0056] In one aspect, the secondary heat exchanger operates operatively between the primary heat exchanger and the container or operatively within the container.

[0057] In one aspect, an additional heat exchanger is operatively placed between the casing and the compressor and / or between the casing and the turbine.

[0058] In one respect, another heat exchanger is operatively positioned between the turbine and the primary heat exchanger.

[0059] In one respect, another heat exchanger is operatively associated with an additional heat source.

[0060] In one respect, if the closed thermodynamic cycle (TC) is the closed thermodynamic cycle of the prime mover, then an additional heat source provides heat to the working fluid through another heat exchanger.

[0061] In one respect, another heat exchanger is operatively associated with the heat user.

[0062] In one respect, if the closed thermodynamic cycle (TC) is the closed thermodynamic cycle of the heat pump, then another heat exchanger connected to the working fluid transfers heat to the heat user.

[0063] In one respect, the device is configured to operate in either a filling or venting configuration.

[0064] In one respect, the device is configured to define a closed loop and perform a closed thermodynamic cycle (TC).

[0065] In one aspect, in the charging configuration, the housing is in fluid communication with the compressor inlet, and the primary heat exchanger is in fluid communication with the compressor outlet.

[0066] In one aspect, in the charging configuration, the turbine is either stationary or active in order to perform a closed thermodynamic cycle (TC).

[0067] In one respect, in the charging configuration, the turbine passes through with minimal fluid.

[0068] In one aspect, in the filling configuration, the motor operates and drives the compressor to compress the working fluid from the housing.

[0069] In one aspect, in the charge configuration, the primary heat exchanger functions as a cooler to remove heat from the compressed working fluid, thereby cooling the compressed working fluid and storing thermal energy.

[0070] In one aspect, in the charge configuration, the secondary heat exchanger functions as a cooler to remove more heat from the compressed working fluid and store more thermal energy.

[0071] In one aspect, in a filling configuration, the container receives and stores compressed and cooled working fluid, wherein the working fluid stored in the container has a temperature close to its critical temperature.

[0072] In one aspect, in the exhaust configuration, the casing is in fluid communication with the turbine outlet, and the primary heat exchanger is in fluid communication with the turbine inlet.

[0073] In one aspect, in the emission configuration, the compressor is either stationary or active in order to perform a closed thermodynamic cycle (TC).

[0074] In one aspect, in the emission configuration, the compressor is rotating (connected to the motor / generator), but in the fluid recirculation configuration, it reabsorbs minimal energy.

[0075] In one respect, all rotating machines (turbines, compressors, motors, generators, motor generators) are rotating in the emission configuration and / or charge configuration and / or during the execution of a closed thermodynamic cycle (TC).

[0076] In one respect, rotating machines are synchronized with the power grid.

[0077] The applicant has demonstrated that setting the machine (one or more turbines and / or one or more compressors) to rotate independently of the closed thermodynamic cycle (TC) allows for a very rapid transition from the charging phase to the discharging phase in even less than one second, and that the fact that the machine is connected to the grid allows for the provision of grid inertia, thereby enabling the sale of ultra-fast regulation services.

[0078] In one aspect, in the exhaust configuration, the secondary heat exchanger functions as a heater to release heat to the working fluid from the container.

[0079] In one aspect, in the exhaust configuration, the primary heat exchanger functions as a heater to release more heat to the working fluid and heat it.

[0080] In one aspect, in the emission configuration, the turbine rotates through a heated working fluid and drives a generator and / or a slave motor to generate energy.

[0081] In one aspect, in the exhaust configuration, the working fluid returns to the housing at atmospheric pressure or essentially atmospheric pressure.

[0082] In one respect, a closed loop includes or passes through: a compressor, another heat exchanger, a turbine, and an additional heat exchanger.

[0083] In one aspect, in the closed loop, the compressor outlet is in fluid communication with another heat exchanger, the turbine outlet is in fluid connection with the compressor inlet, and the additional heat exchanger is operatively positioned between the turbine outlet and the compressor inlet.

[0084] In one aspect, the charging phase includes: compressing the working fluid from the housing in a compressor to absorb energy, the housing being in external contact with the atmosphere and internally defining a volume configured to contain the working fluid at atmospheric or near-atmospheric pressure.

[0085] In one aspect, the charging phase includes: introducing the compressed working fluid through a primary heat exchanger and a secondary heat exchanger arranged in series to bring the temperature of the working fluid close to its critical temperature; wherein the primary heat exchanger functions as a cooler to remove heat from the compressed working fluid, cool the compressed working fluid, and store thermal energy, and wherein the secondary heat exchanger functions as a cooler to remove more heat from the compressed working fluid and store more thermal energy.

[0086] In one aspect, the filling stage includes: storing the working fluid to be cooled in the container; wherein a secondary heat exchanger and a primary heat exchanger perform a supercritical conversion of the working fluid, such that the working fluid accumulates in the container in a supercritical phase, or wherein a secondary heat exchanger and a primary heat exchanger perform a subcritical conversion of the working fluid, such that the working fluid accumulates in the container in a liquid phase.

[0087] In one respect, the temperature of the working fluid stored in the container is between 0°C and 100°C.

[0088] In one respect, the pressure of the working fluid stored in the container is between 10 bar and 150 bar.

[0089] In one aspect, the discharge stage includes: passing the working fluid from the container through a secondary heat exchanger and a primary heat exchanger; wherein the secondary heat exchanger functions as a heater to release heat to the working fluid from the container, and wherein the primary heat exchanger functions as a heater to release more heat to the working fluid and to heat the working fluid.

[0090] In one aspect, the emission stage includes: passing a heated working fluid through a turbine, wherein the turbine rotates through the heated working fluid and drives a generator and / or a slave motor to generate energy, wherein the working fluid expands and cools within the turbine.

[0091] In one aspect, the emission phase includes reintroducing the working fluid from the turbine into the casing at atmospheric or near-atmospheric pressure.

[0092] In one aspect, a closed thermodynamic cycle (TC) includes compressing at least a portion of the working fluid in a compressor.

[0093] In one aspect, a closed thermodynamic cycle (TC) includes passing at least a portion of the working fluid through another heat exchanger operatively associated with an additional heat source, and further heating the at least a portion of the working fluid.

[0094] In one aspect, a closed thermodynamic cycle (TC) includes: expanding at least a portion of the heated working fluid via a turbine, wherein the turbine rotates through the heated working fluid and drives a generator and / or a slave motor to generate energy, wherein the working fluid expands and cools within the turbine.

[0095] In one aspect, a closed thermodynamic cycle (TC) includes: cooling at least a portion of the working fluid in an additional heat exchanger, and reintroducing at least a portion of the working fluid into the compressor.

[0096] In one aspect, a portion of the working fluid operating according to a closed thermodynamic cycle (TC) includes between 0% and 100% of the working fluid.

[0097] In one aspect, a portion of the working fluid operating according to a closed thermodynamic cycle (TC) is comprised of the working fluid between 20% and 30%.

[0098] In one aspect, the remaining portion of the working fluid that accumulates in the container or housing includes between 100% and 0% of the working fluid.

[0099] In one aspect, the remaining portion of the working fluid that accumulates in the container or housing comprises between 80% and 70% of the working fluid.

[0100] In one aspect, a first bypass catheter is provided.

[0101] In one aspect, the first bypass conduit includes a corresponding first valve.

[0102] In one aspect, the first bypass duct is configured to connect the compressor outlet to another heat exchanger and bypass the first heat exchanger and the container.

[0103] In one aspect, a second bypass catheter is provided.

[0104] In one aspect, the second bypass conduit includes a corresponding second valve.

[0105] In one aspect, the second bypass duct is configured to connect the turbine outlet to the compressor inlet and bypass the housing.

[0106] In one aspect, a delivery pipe extending from the shell to the container and a return pipe extending from the container to the shell are provided.

[0107] In one aspect, the first bypass conduit connects the delivery pipe and the return pipe near the first heat exchanger.

[0108] In one aspect, the second bypass conduit connects the delivery tube to the return tube near the housing.

[0109] In one respect, the first and second valves can be throttled to regulate the flow rate of the working fluid in a closed thermodynamic cycle (TC).

[0110] In one respect, the primary heat exchanger is a thermal storage device (thermal energy storage device - TES) or is operatively associated with a thermal storage device (thermal energy storage device - TES).

[0111] In one aspect, the delivery pipe includes a first section extending between the housing and the compressor inlet.

[0112] In one aspect, the delivery pipe includes a second section extending between the compressor outlet and the primary heat exchanger.

[0113] In one aspect, the delivery pipe includes a third section extending between the primary heat exchanger and the secondary heat exchanger.

[0114] In one aspect, the return pipe includes a first section extending between the secondary heat exchanger and the primary heat exchanger.

[0115] In one aspect, the return pipe includes a second section extending between the primary heat exchanger and the turbine inlet.

[0116] In one aspect, the return pipe includes a third section extending between the turbine outlet and the casing.

[0117] In one aspect, the second section of the delivery pipe and the second section of the return pipe are connected to each other and to a single pipe located on one side of the primary exchanger.

[0118] The third section of the delivery pipe and the first section of the return pipe are connected to each other and to a single pipe on one side of the primary exchanger.

[0119] In one aspect, the single or multiple tubes pass through a primary heat exchanger, performing a delivery function when the equipment is in a charging configuration / phase, and a return function when the equipment is in a discharging configuration / phase.

[0120] In one aspect, at least one valve is operatively located on a first section of the delivery pipe and / or a third section of the return pipe to alternately arrange the housing in fluid communication with the compressor or the turbine with the housing.

[0121] In one aspect, at least one valve is operatively located on a second or third section of the delivery pipe and / or a second or first section of the return pipe, to alternatively arrange the compressor in fluid communication with the primary heat exchanger and container or the primary heat exchanger and container with the turbine.

[0122] In one aspect, an additional heat exchanger is operatively connected to the first section of the delivery pipe and / or the third section of the return pipe.

[0123] In one aspect, another heat exchanger is operatively connected to the second section of the return pipe.

[0124] In one respect, the closed thermodynamic cycle (TC) is restorative.

[0125] In one respect, the regenerator operates operatively between the primary heat exchanger and another heat exchanger, and between the turbine outlet and an additional heat exchanger.

[0126] In one respect, the regenerator is operatively connected to the second and third sections of the return pipe.

[0127] In one respect, additional heat sources are: solar energy (e.g., solar fields) and / or waste heat recovered from industry (waste heat recovery) and / or waste heat (GT) from gas turbines and / or heat from fuel boilers.

[0128] In one respect, the additional heat source is the top thermodynamic cycle. In other words, the closed thermodynamic cycle (TC) is the bottom thermodynamic cycle of the combined system / cycle (top + bottom).

[0129] In one respect, the turbine is multi-stage and inter-stage heated.

[0130] In one respect, the expansion is achieved through intermediate heating.

[0131] In one aspect, another heat exchanger is fluidly connected to at least one stage of the turbine to provide intermediate heating for the turbine.

[0132] In one aspect, the intermediate heat loop connects the turbine to another heat exchanger.

[0133] In one respect, another heat exchanger provides intermediate heating for the turbine.

[0134] In one respect, intermediate heating is performed with approximately half the expansion.

[0135] In one respect, the compressor is multi-stage and intercooled.

[0136] In one aspect, multiple intermediate coolings are configured to be performed during the charging phase and / or in a closed thermodynamic cycle (TC).

[0137] In one respect, the primary heat exchanger is a heat regenerator having a fixed or movable bed, or includes a heat regenerator having a fixed or movable bed.

[0138] In one respect, the shell is deformable.

[0139] In one respect, the housing has the structure of a gas meter.

[0140] In one respect, the shell is a pressure balloon.

[0141] In one aspect, the housing is made of a flexible material, preferably plastic, such as polyester fabric coated with PVC.

[0142] In one respect, the compression of the working fluid in the compressor is intercooled.

[0143] In one respect, the container is spherical or nearly spherical.

[0144] In one respect, the container is cylindrical or basically cylindrical.

[0145] In one respect, the outer wall of the container is made of metal.

[0146] In one respect, the temperature of the working fluid stored in the container is between 0°C and 100°C.

[0147] In one aspect, the pressure of the working fluid stored in the container is between 10 bar and 150 bar, preferably between 10 bar and 150 bar, preferably between 50 bar and 100 bar, and preferably between 60 bar and 85 bar.

[0148] In one respect, the ratio between the density of the working fluid when contained in the container and the density of the same working fluid when contained in the shell is between 200 and 500.

[0149] In one aspect, the secondary heat exchanger and the primary heat exchanger are configured for operating a supercritical conversion of the working fluid, such that the working fluid accumulates in the container in a supercritical phase.

[0150] In one aspect, heat is removed from the working fluid in the primary exchanger until the working fluid reaches a temperature above the critical temperature in the TS diagram and above the Andrews curve.

[0151] In one aspect, heat is removed from the working fluid in a secondary heat exchanger, allowing the working fluid to enter the supercritical phase and causing the working fluid to follow the right-hand portion of the Andrews curve.

[0152] In one aspect, the secondary heat exchanger and the primary heat exchanger are configured for operating a subcritical conversion of the working fluid, such that the working fluid accumulates in the container in a liquid phase.

[0153] In one aspect, heat is removed from the working fluid in the primary exchanger until the working fluid reaches a temperature below the critical temperature in the TS diagram and is located at a point on the left side of the Andrews curve.

[0154] In one aspect, a method is provided to remove heat from the working fluid in a secondary heat exchanger by causing the working fluid to traverse the saturated vapor zone until it reaches the liquid phase.

[0155] In one respect, the closed thermodynamic cycle (TC) has a higher pressure, wherein the higher pressure is lower than the maximum pressure of the cycle thermodynamic conversion (CTT) in the charge configuration / stage.

[0156] In one respect, the closed thermodynamic cycle (TC) has a lower pressure, wherein the lower pressure is higher than the minimum pressure of the cycle thermodynamic conversion (CTT) in the emission configuration / stage.

[0157] In one respect, the lower pressure of a closed thermodynamic cycle (TC) is higher than atmospheric pressure.

[0158] In other words, a closed thermodynamic cycle (TC) has two pressures, one higher and one lower, which can be the same as the pressures at the beginning and end of the cycle thermodynamic conversion (CTT), or they can be different from the pressures at the beginning and end of the cycle thermodynamic conversion (CTT).

[0159] In one aspect, an additional primary heat exchanger is provided between the primary heat exchanger and the secondary heat exchanger.

[0160] In one aspect, an additional compressor is provided between the primary heat exchanger and the secondary heat exchanger.

[0161] In one aspect, an additional turbine is provided between the primary heat exchanger and the secondary heat exchanger.

[0162] In one aspect, during the charging configuration / stage, the primary heat exchanger is in fluid communication with the inlet of the additional compressor, while the outlet of the additional compressor is in fluid communication with the additional primary heat exchanger.

[0163] In one aspect, in the emission configuration / stage, the additional primary heat exchanger is in fluid communication with the inlet of the additional turbine, while the outlet of the additional turbine is in fluid communication with the primary heat exchanger.

[0164] In one aspect, during the filling configuration / stage, the working fluid is compressed in a compressor and an additional compressor.

[0165] In one aspect, in the emission configuration / stage, the working fluid is expanded in the turbine and the additional turbine.

[0166] In one aspect, during the charging configuration / stage, a compressed working fluid is introduced via a primary heat exchanger, an additional primary heat exchanger, and a secondary heat exchanger.

[0167] In one aspect, in the emission configuration / stage, working fluid from the vessel is introduced via a secondary heat exchanger, an additional primary heat exchanger, and a primary heat exchanger.

[0168] In one respect, a closed loop includes or passes through: a compressor, another heat exchanger, a turbine, and an additional heat exchanger.

[0169] In one respect, the additional compressor and additional turbine are not part of a closed loop and / or closed thermodynamic cycle (TC).

[0170] In one aspect, a system was set up to increase the pressure in the discharge configuration / stage via a pump.

[0171] In one respect, the pump operates operatively on the return pipe and is configured to increase the pressure in the discharge configuration / stage.

[0172] In one aspect, the pump is located downstream of the vessel, optionally between the secondary heat exchanger and the primary heat exchanger.

[0173] Other features and advantages will become clearer through a detailed description of preferred, but not exclusive, embodiments of the apparatus and method for energy generation and storage according to the invention. Attached Figure Description

[0174] Such a description will be illustrated below with reference to the accompanying drawings, which are provided as non-limiting examples only, in which:

[0175] ■ Figure 1 An embodiment of the energy generation and storage device in an operational configuration according to the present invention is schematically illustrated;

[0176] ■ Figure 2 It is about Figure 1 The TS diagram of the operation configuration;

[0177] ■ Figure 3 The diagram illustrates the different operating configurations. Figure 1 The equipment;

[0178] ■ Figure 4 It is about Figure 3 The TS diagram of the operation configuration;

[0179] ■ Figure 5 The illustration shows a variation of an embodiment of the energy storage device according to the present invention;

[0180] ■ Figure 6 , Figure 8 and Figure 10 The illustrations show different implementation variations of the device in corresponding operating configurations;

[0181] ■ Figure 7 , Figure 9 and Figure 11 It is about Figure 6 , Figure 7 and Figure 8 The TS diagram of the operation configuration;

[0182] ■ Figure 12 The illustration shows another embodiment variation of the energy storage device according to the present invention;

[0183] ■ Figure 13 Another TS diagram related to the present invention is illustrated;

[0184] ■ Figure 14 The illustration shows another embodiment variation of the energy storage device according to the present invention;

[0185] ■ Figure 15 The diagram shows Figure 3 Equipment variants;

[0186] ■ Figure 16 It is about Figure 15 The TS diagram of the operation configuration. Detailed Implementation

[0187] Referring to the accompanying drawings, reference numeral 1 generally indicates an energy generation and storage device according to the present invention.

[0188] For example, device 1 operates using a working fluid that is different from atmospheric air.

[0189] For example, device 1 operates using a working fluid selected from the group consisting of: carbon dioxide (CO2), sulfur hexafluoride (SF6), and nitrous oxide (N2O). In the following description, the working fluid used in conjunction with the described device 1 is carbon dioxide (CO2).

[0190] Device 1 is configured to perform a closed-loop thermodynamic conversion (CTT) first in a charge configuration / stage in one direction and then in a discharge configuration / stage in the opposite direction, wherein in the charge configuration device 1 stores heat and pressure and in the discharge configuration device generates electrical and / or mechanical energy.

[0191] The device 1 is also configured to define / define a closed loop and to perform a closed thermodynamic cycle (TC) in the closed loop using at least a portion of the same working fluid while the device 1 is also in a charging configuration or a discharging configuration.

[0192] Reference Figure 1 The device 1 includes a turbine 2 and a compressor 3. The compressor 3 is schematically illustrated as comprising three stages. The compressor 3 is connected to a motor 4a. The turbine 2 is mechanically connected to a generator 4b and to a driven motor 300, which... Figure 1 The turbine 2 is schematically represented and is different from the generator. The turbine 2 is mechanically connected to the generator 4b and the driven motor 300 by means of a transmission device, such as a friction-type connection device, which allows the turbine 2 to be connected and disconnected from the generator 4 and / or the driven motor according to commands.

[0193] Device 1 includes a housing 5, which is preferably defined by a pressure balloon made of a flexible material, such as PVC-coated polyester fabric. The pressure balloon is disposed on the surface and is in contact with atmospheric air externally. The pressure balloon defines within itself a volume configured to contain a working fluid at atmospheric pressure or near-atmospheric pressure, i.e., pressure balanced with the atmosphere. Housing 5 may also be made into a gas meter or any other storage system for gases at low or zero overpressure.

[0194] A first section 6a of a delivery pipe extends between the housing 5 and the inlet 3a of the compressor 3. A third section 6b of a return pipe extends between the housing 5 and the outlet 2b of the turbine 2, thereby establishing fluid communication between the internal volume of the housing 5 and the compressor 3 and the turbine 2. Valves or valve systems are operatively located on such sections 6a and 6b to alternately establish fluid communication between the housing 5 and the inlet 3a of the compressor 3 or between the outlet 2b of the turbine 2 and the housing 5.

[0195] The device 1 includes a primary heat exchanger 7, which can be selectively arranged in fluid communication with either the outlet 3b of the compressor 3 or the inlet 2a of the turbine 2.

[0196] For this purpose, a second section 8a of a delivery pipe extends between the outlet 3b of the compressor 3 and the primary heat exchanger 7. A second section 8b of a return pipe extends between the primary heat exchanger 7 and the inlet 2a of the turbine 2. Valves or valve systems are operatively located on sections 8a and 8b to alternately arrange the primary heat exchanger 7 in fluid communication with the inlet 2a of the turbine 2 or with the outlet 3b of the compressor 3 and the primary heat exchanger 7.

[0197] The container 9 is in fluid communication with the primary heat exchanger 7, and the container 9 is configured to accumulate the working fluid in the liquid or supercritical phase. The container 9 is preferably made of metal and has an outer wall with a cylindrical or spherical shape.

[0198] The secondary heat exchanger 10 operates operatively between or within the primary heat exchanger 7 and the container 9, and the secondary heat exchanger 10 is configured to operate on the stored working fluid or to operate within the container 9 during the filling phase.

[0199] according to Figure 1 As shown in the embodiment, the secondary heat exchanger 10 is integrated into the container 9 in the following sense: the secondary heat exchanger 10 has its heat exchange portion 11, which is housed within the container 9 and configured to be impacted by the working fluid contained in the container 9.

[0200] A third section 12a of a delivery pipe and a first section 12b of a return pipe extend between the primary heat exchanger 7 and the container 9 to arrange the primary heat exchanger 7 in fluid communication with the container 9 and the secondary heat exchanger 10.

[0201] Valves or valve systems are operatively located on sections 12a and 12b to alternately arrange the compressor 3 in fluid communication with the primary heat exchanger 7 and the container 9, or to arrange the primary heat exchanger 7 and the container 9 in fluid communication with the turbine 2.

[0202] The device 1 also includes an additional heat exchanger 13 and another heat exchanger 220, the additional heat exchanger 13 being operatively positioned between the turbine 2 and the casing 5, and the other heat exchanger 220 receiving heat from an additional heat source 230. The other heat exchanger 220 is located on a second section 8b of the delivery pipe between the inlet 2a of the turbine 2 and the primary heat exchanger 7. As a non-limiting example, the additional heat source 230 may be solar energy (e.g., a solar field), industrially recovered waste heat (waste heat recovery), gas turbine waste heat, etc.

[0203] The delivery pipe of device 1 includes corresponding first section 6a, second section 8a, and third section 12a. Therefore, the return pipe includes corresponding first section 12b, second section 8b, and third section 6b.

[0204] The first bypass conduit 310 is configured to connect the outlet of the compressor 3 to another heat exchanger 220 and bypass the first heat exchanger 7 and the container 9. The first bypass conduit 310 connects the second section 8a of the delivery pipe to the second section 8b of the return pipe and is provided with a corresponding first valve 311.

[0205] The second bypass conduit 320 is configured to connect the outlet 2b of the turbine 2 to the inlet 3a of the compressor 3, and bypasses the housing 5. The second bypass conduit 320 connects the first section 6a of the delivery pipe to the third section 6b of the return pipe, and is provided with a corresponding second valve 321.

[0206] The first bypass conduit 310 and the second bypass conduit 320 can define a closed loop including the compressor 3, the turbine 2, the additional heat exchanger 13 and another heat exchanger 220.

[0207] Device 1 also includes a control unit (not shown) that is operatively connected to various components of device 1 itself and is configured / programmed to manage the operation of the various components of device 1.

[0208] Equipment 1 is configured to operate in either a charging configuration or a discharging configuration, i.e., to perform a method that includes an energy charging phase and an energy discharging and generation phase.

[0209] Device 1 is also configured to perform a closed thermodynamic cycle (TC) in a closed loop, such as the Brayden cycle.

[0210] Figure 1 The configuration shown in the diagram is the charging configuration / stage that occurs simultaneously with the closed thermodynamic cycle (TC).

[0211] Device 1 from the first state ( Figure 2 Starting from point A in the TS diagram, in the first state, the working fluid (CO2) in gaseous form is entirely contained in the housing 5 at atmospheric pressure or near-atmospheric pressure and at a temperature substantially equal to ambient temperature. The housing 5 is arranged to communicate with the inlet 3a of the compressor 3 via a valve system. Furthermore, the primary heat exchanger 7 is arranged to be in fluid communication with the outlet 3b of the compressor 3 via the valve system. The motor 4 drives the compressor 3 to compress the working fluid from the housing 5. The working fluid is compressed and heated in the compressor 3 by intercooling (from...) Figure 2 (TS diagram A to B).

[0212] By controlling the valve, a portion of the working fluid (e.g., 70%) is directed toward the primary heat exchanger 7, while another portion (e.g., 30%) flows through the first bypass conduit 310 and toward another heat exchanger 220.

[0213] The primary heat exchanger 7 functions as a cooler to remove heat from the compressed working fluid, thereby cooling the compressed working fluid. Figure 2 Point C in the TS diagram stores the heat energy removed from the working fluid. At point C, the working fluid is found to be at a temperature below the critical temperature of the fluid, and in the case of slight superheat, it is located to the right of the Andrews curve or slightly outside the curve. The compression described above can be adiabatic, intercooled, or isothermal.

[0214] In a variant of the implementation not illustrated in detail, heat is removed from the working fluid in the primary exchanger 7 until the working fluid reaches a temperature above the critical temperature on the TS curve and above the Andrews curve.

[0215] The working fluid enters container 9, where the secondary heat exchanger 10, which functions as a cooler in this configuration, removes more heat from the working fluid and stores more thermal energy. The working fluid traverses the saturated vapor zone until it reaches the liquid phase (…). Figure 2 The working fluid is stored up to point D in the TS diagram. Therefore, container 9 stores the working fluid in a liquid phase at a temperature below the critical temperature Tc of the working fluid. In this second state, for example, the working fluid (CO2, Tc = 31°C) in liquid form at 20°C is entirely contained in container 9. Therefore, the secondary heat exchanger 10 and the primary heat exchanger 9 are configured to operate the subcritical transition of the working fluid, such that the working fluid accumulates in the liquid phase in container 9.

[0216] In a variant of the implementation not illustrated in detail, heat is removed from the working fluid in the secondary heat exchanger 10, thereby causing the working fluid to enter the supercritical phase and to follow the right-hand portion of the Andrews curve.

[0217] A portion (30%) of the working fluid, operating according to a closed thermodynamic cycle (TC), is heated in another heat exchanger 220 (until...). Figure 2 The fluid flows from point E on the TS diagram and then into turbine 2, where it expands and cools (until...) Figure 2 Point F of the TS diagram). Turbine 2 converts the energy of the working fluid into electrical energy via generator 4b and / or converts it into mechanical energy in the actuator 300. Then, this portion of the working fluid is cooled in an additional heat exchanger 13 (and carried back). Figure 2 Point A of the TS diagram crosses the second bypass duct 320 and is reintroduced into the compressor 3 to restart the closed thermodynamic cycle (TC).

[0218] exist Figure 1 and Figure 3 In the embodiment shown, the additional heat exchanger 13 is mounted on the third section 6b of the return pipe and then operates in a closed thermodynamic cycle (TC), but the additional heat exchanger 13 does not operate on the working fluid stored in the charging configuration / stage.

[0219] When the charging phase has ended and 70% of the working fluid has accumulated in container 9, the closed thermodynamic cycle (TC) with the remaining 30% of the working fluid can still continue due to the heat supplied to the additional heat source 230.

[0220] Figure 3 The configuration shown is the emission configuration / stage that is simultaneous with the closed thermodynamic cycle (TC).

[0221] Device 1 from the second state ( Figure 4 The TS diagram begins at point G. The casing 5 is positioned to communicate with the outlet 2b of the turbine 2 via a valve system. Furthermore, the primary heat exchanger 7 is positioned to be in fluid communication with the inlet 2a of the turbine 2 via the valve system.

[0222] The secondary heat exchanger 10 operates as a heater and transfers a portion of the heat previously stored in the charging configuration to the working fluid in vessel 9. The working fluid traverses the saturated steam zone until it reaches the steam phase ( Figure 4 Point H in the TS diagram). The working fluid crosses the primary heat exchanger 7, which now functions as a heater and transfers additional heat previously stored in the charging configuration to the working fluid, thus heating the working fluid. Figure 4 Point I in the TS diagram.

[0223] The working fluid then crosses another heat exchanger 220 (which receives heat from an additional heat source 230) and is further heated (until...). Figure 4 Point L in the TS diagram.

[0224] The heated working fluid enters turbine 2, where it expands and cools. Figure 4 The point M in the TS diagram is used to determine the rotation of turbine 2. Generator 4b and driven motor 300 connected to turbine 2 rotate turbine 2 by the expansion of working fluid. The expansion of working fluid in turbine can be adiabatic, interheated, or isothermal.

[0225] The working fluid exiting turbine 2 is cooled in an additional heat exchanger 13. Figure 4 (Point N in the TS diagram). The additional heat exchanger 13 (located on the third section 6b of the return pipe) operates in a closed thermodynamic cycle (TC) and also operates on the working fluid discharged in the discharge configuration / stage. In another embodiment variant not shown in detail, the additional heat exchanger 13 may be located on the first section 6a of the delivery pipe or on both the first section 6a of the delivery pipe and / or the third section 6b of the return pipe.

[0226] At this point, by controlling the valve, a portion of the working fluid (e.g., 70%) is directed toward housing 5 and returns to housing 5 at atmospheric or near-atmospheric pressure. Another portion (e.g., 30%) flows through the second bypass conduit 320 and is sent back to compressor 2, and then through the first bypass conduit 310 to re-execute the closed thermodynamic cycle (TC).

[0227] When the discharge phase ends and 70% of the working fluid has accumulated in the casing 5, the closed thermodynamic cycle (TC) with the remaining 30% of the working fluid can still continue due to the heat supplied to the additional heat source 230.

[0228] For example, the working fluid (CO2) stored in container 9 has a temperature of 24°C and a pressure of 65 bar. The density of CO2 at 25°C and atmospheric pressure is approximately 1.8 kg / m³. 3 The density of CO2 in container 9 is approximately 730 kg / m³. 3 Therefore, the ratio between the density of the working fluid contained in container 9 under the above-mentioned conditions and the density of the same working fluid contained in shell 5 under atmospheric conditions is approximately 400. In this regard, it can be observed that if atmospheric air stored in container 9 at 65 bar and 24°C is used instead of CO2, its density will be only 78 kg / m³. 3 Furthermore, the theoretically required volume for container 9 would be more than ten times that of container 9.

[0229] The primary heat exchanger 7 can be a heat regenerator with a fixed bed, comprising, for example, a thermomass element made of metal balls. In the charging configuration / stage, the thermomass element is impacted by a hot and compressed working fluid, which transfers heat to the metal balls, accumulating thermal energy. In the discharging configuration / stage, the thermomass element is impacted by a cold working fluid, which absorbs heat from the metal balls and is heated. In a variant not shown, the heat regenerator can also be of the type with a movable bed. Thus, the primary heat exchanger 7 is a thermal energy storage device (thermal energy storage TES). Instead of a heat regenerator with a fixed bed, other types of heat regenerators can exist, such as those described in publication WO / 2020 / 039416 under the same applicant's name.

[0230] In addition, different types of secondary heat exchangers 10 are described, for example, in the published document WO / 2020 / 039416 under the same applicant's name.

[0231] Figure 5 The illustration shows a variation of device 1. Here, one can see... Figure 1The common main components are turbine 2, compressor 3, motor 4a, generator 4b, driven motor 300, housing 5, primary heat exchanger 7 (heat storage TES), container 9, secondary heat exchanger 10, another heat exchanger 220, and additional heat exchanger 13.

[0232] In this variant, the secondary heat exchanger 10 is positioned between the primary heat exchanger 7 and the container 9, meaning the secondary heat exchanger 10 is not integrated into the container 9. The secondary heat exchanger 10 is aligned in a straight line with the third section 12a of the delivery pipe and the first section 12b of the return pipe.

[0233] Figure 5 The secondary heat exchanger 10 shown includes a secondary loop 20 through which a secondary fluid, such as water, flows. The secondary loop 20 has a heat exchange section 11 that is impacted by and configured to exchange heat with the working fluid, which flows through a third section 12a of the delivery pipe and a first section 12b of the return pipe.

[0234] The secondary loop 20 includes a secondary storage chamber 200 for storing hot secondary fluid after heat removal from the working fluid during the charging configuration / phase of the apparatus / method, and for storing cold secondary fluid after heat transfer to the working fluid during the discharging configuration / phase of the apparatus / method. The secondary storage chamber 200 is also connected to a radiator 23 equipped with one or more fans 24, which is positioned on the recirculation pipe and cools the secondary fluid, for example, at night and heats it during the day. The secondary storage chamber 200 is also connected via a corresponding loop 210 to an additional heat exchanger 13 and an intercooler 322 connected to the compressor 3.

[0235] The device 1 also includes a regenerator 400, which operates operatively between the primary heat exchanger 7 and another heat exchanger 220, and between the outlet of the turbine 2 and an additional heat exchanger 13. Thus, the regenerator 400 is operatively connected to the second section 8b and the third section 6b of the return tube and allows actuation of a restorative closed thermodynamic cycle (TC).

[0236] Figures 6 to 11 Other variations of the apparatus 1 and method according to the present invention are illustrated. Figures 1 to 4Unlike the previous device 1 and method, this variant of device 1 allows the actuation of a closed thermodynamic cycle (TC) using lower and higher pressures, respectively, different from the maximum and minimum pressures of the cycle thermodynamic conversion (CTT) in the charge and discharge configurations / stages. Specifically, the higher pressure is lower than the maximum pressure of the cycle thermodynamic conversion (CTT) in the charge configuration / stage. The lower pressure is higher than the minimum pressure of the cycle thermodynamic conversion (CTT) in the discharge configuration / stage, preferably higher than atmospheric pressure.

[0237] For this purpose, device 1 includes an additional compressor 3', an additional turbine 2', and an additional primary heat exchanger 7'. Furthermore, motor 4a and generator 4b are defined by a single motor-generator 4, which is connected to compressor 3, the additional compressor 3', turbine 2, and the additional turbine 2' via corresponding transmissions. For example, friction-type connection devices are placed between motor-generator 4 and turbine 2 and the additional turbine 2', and between motor-generator 4 and compressor 3 and the additional compressor 3', and are configured to connect or disconnect such rotating machinery from motor-generator 4 according to command.

[0238] An additional primary heat exchanger 7' is located between the primary heat exchanger 7 and the secondary heat exchanger 10, or in other words, operates on the third section 12a of the delivery pipe and the first section 12b of the return pipe. Furthermore, the additional primary heat exchanger 7' may be a thermal energy storage device (TES).

[0239] An additional compressor 3' is located between the primary heat exchanger 7 and the secondary heat exchanger 10, that is, the additional compressor 3' operates on the third section 12a of the delivery pipe and the first section 12b of the return pipe. The primary heat exchanger 7 is in fluid communication with the inlet 3'a of the additional compressor 3', while the outlet 3'b of the additional compressor 3' is in fluid communication with the additional primary heat exchanger 7'.

[0240] The additional turbine 2' is located between the primary heat exchanger 7 and the secondary heat exchanger 10, that is, the additional primary heat exchanger 7' is in fluid communication with the inlet 2'a of the additional turbine 2', and the outlet 2'b of the additional turbine 2' is in fluid communication with the primary heat exchanger 7.

[0241] In this embodiment, only one or more pipes 500 pass through the primary heat exchanger 7. One or more pipes perform a conveying function when the device 1 is in the charging configuration / stage and a return function when the device 1 is in the discharging configuration / stage. The second section 8a of the conveying pipe and the second section 8b of the return pipe are connected to each other and to a single pipe 500 located on one side of the primary heat exchanger 7. The third section 12a of the conveying pipe and the first section 12b of the return pipe are connected to each other and to a single pipe 500 located on the other side of the primary heat exchanger 7. Furthermore, the first section 6a of the conveying pipe and the third section 6b of the return pipe are connected in a single pipe 600 connected to the housing 5.

[0242] An additional heat exchanger 13' is located on the single pipe 600. The closed loop is defined by a first section 6a of the delivery pipe, a second section 8a of the delivery pipe, a second section 8b of the return pipe, and a third section 6b of the return pipe. The closed loop includes or passes through: the compressor 3, another heat exchanger 220, the turbine 2, and the additional heat exchanger 13.

[0243] In the charging configuration / stage, the working fluid in both compressor 3 and auxiliary compressor 3' is compressed, and the compressed working fluid is introduced through primary heat exchanger 7, auxiliary primary heat exchanger 7', and secondary heat exchanger 10. Figure 8 and Figure 9 ).

[0244] In the discharge configuration / stage, the working fluid is arranged to expand in turbine 2 and additional turbine 2', and the working fluid from the container is introduced through secondary heat exchanger 10, additional primary heat exchanger 7', and primary heat exchanger 7. Figure 10 and Figure 11 ).

[0245] Therefore, the additional compressor 3' and the additional turbine 2' are not part of a closed loop and / or a closed thermodynamic cycle (TC). Figure 6 and Figure 7 ).

[0246] Figure 12 The diagram illustrates the relationship with Figure 5 Another variant similar to the one described above, but with... Figures 6 to 11 Similar to other equipment, this configuration allows for the actuation of a closed thermodynamic cycle (TC) at lower and higher pressures, respectively, different from the maximum and minimum pressures of the Cyclic Thermodynamic Transformation (CTT) in the charge configuration / stage and the discharge configuration / stage. Figure 13 The diagram below illustrates the TS diagram related to this transformation. Figure 5Unlike other components, the auxiliary turbine 2' is mounted on the first section 12b of the return pipe, and the auxiliary compressor 3' is mounted on the third section 12a of the delivery pipe. An additional primary heat exchanger 7' operates on both the first section 12b of the return pipe and the third section 12a of the delivery pipe.

[0247] Figure 14 Another variation is illustrated, in which the closed thermodynamic cycle (TC) is the closed thermodynamic cycle of the heat pump. The compressor 3 is not intercooled, while the turbine 2 is multi-stage and has multiple intermediate heaters (reheaters). The generated heat is released to the user through an additional heat exchanger 220.

[0248] Figure 15 The diagram shows Figure 3 The equipment is a variant in the emission configuration / stage that is simultaneous with the closed thermodynamic cycle (TC).

[0249] Regarding references Figure 3 Described, Figure 15 The equipment also includes a pump 25, which is arranged on the first section 12b of the return pipe, i.e., between the secondary heat exchanger 10 and the primary heat exchanger 7. The function of pump 25 is to increase the pressure in the discharge configuration / stage (from G to G', e.g., by drawing liquid working fluid from container 9 and delivering the liquid working fluid at higher pressures, even supercritical pressures) Figure 16 (as shown in the diagram) to achieve a larger expansion gradient. In this way, the specific work of the cycle is increased, and this allows for a reduction in the size of the storage container given the same storage energy.

[0250] Figure 16 The device also illustrates the above-mentioned intermediate heating circuit 26 (e.g. Figure 15 (As shown) Intermediate heating operates between stages of turbine 2. Intermediate heating circuit 26 connects turbine 2 to another heat exchanger 220. In this embodiment, in the discharge configuration / stage, the working fluid in turbine 2 under expansion (in...) Figure 16 From L' to L", and then from L'" to M') is heated by an additional heat source 230 (in Figure 16 The expansion is from L” to L'” to about half. Intermediate heating (reheating) to about half the expansion is used to increase the specific work within the cycle. This also allows for a reduction in the size of the storage container for the same stored energy.

[0251] As can be observed in this embodiment, the fluid portion operating in the closed thermodynamic cycle (TC) also follows the IHG path of the TS diagram in the discharge configuration / stage (e.g. Figure 16 (as shown in the image).

[0252] In other variations not shown in the figure, device 1 may alternatively include pump 25 or intermediate heating circuit 26.

[0253] Component list

[0254] 1. Energy storage equipment

[0255] 2 turbines

[0256] 2' Additional turbine

[0257] 2a Turbine inlet

[0258] 2b Turbine outlet

[0259] 3. Compressor

[0260] 3' Additional compressor

[0261] 3a Compressor inlet

[0262] 3b Compressor outlet

[0263] 4-motor generator

[0264] 4A motor

[0265] 4b Generator

[0266] 5. Housing

[0267] 6a First section of conveying pipe

[0268] 6b Return pipe, third section

[0269] 7. Primary heat exchanger

[0270] 7' Additional primary heat exchanger

[0271] 8a Second section of delivery pipe

[0272] 8b Return pipe, second section

[0273] 9 containers

[0274] 10 secondary heat exchangers

[0275] 11. Heat exchange section of the secondary heat exchanger

[0276] 12a Third Section Conveying Pipe

[0277] 12b First Section Return Pipe

[0278] 13 Additional heat exchangers

[0279] 13' Additional auxiliary heat exchanger

[0280] 20 secondary circuits

[0281] 23 Radiator

[0282] 24 fans

[0283] 25 pumps

[0284] 26 Intermediate heating circuit

[0285] 200 secondary storage rooms

[0286] 210 Additional heat exchanger loop

[0287] 220 Another heat exchanger

[0288] 230 Additional heat source

[0289] 300 From Motivation

[0290] 310 First bypass catheter

[0291] 311 First Valve

[0292] 320 Second bypass catheter

[0293] 321 Second Valve

[0294] 322 Intercooler

[0295] 400 Regenerator

[0296] 500 single tubes

[0297] 600 single pipes

Claims

1. An energy generation and storage device, the device comprising: Working fluid, which is not atmospheric air; The housing (5) is configured to store the working fluid in the gas phase and in pressure equilibrium with the atmosphere; Container (9), the container (9) is configured to store the working fluid in a liquid or supercritical phase at a temperature close to a critical temperature, wherein the critical temperature is between 0°C and 200°C; A compressor (3) and a motor, wherein the compressor (3) and the motor are mechanically connected to each other; A turbine (2) and a generator (4b) and / or a driven motor (300) are mechanically connected to each other; wherein the housing (5) is in external contact with the atmosphere and defines a volume portion inside the housing (5) configured to accommodate the working fluid at atmospheric pressure, wherein the volume portion is selectively in fluid communication with the inlet (3a) of the compressor (3) or with the outlet (2b) of the turbine (2); A primary heat exchanger (7) is selectively in fluid communication with either the outlet (3b) of the compressor (3) or the inlet (2a) of the turbine (2); wherein the container (9) is in fluid communication with the primary heat exchanger (7) to collect the working fluid. Secondary heat exchanger (10), which operates operatively between or within the primary heat exchanger (7) and the container (9); An additional heat exchanger (13) is operatively positioned between the housing (5) and the compressor (3) and / or between the housing (5) and the turbine (2); Another heat exchanger (220) is operatively positioned between the turbine (2) and the primary heat exchanger (7); The device is configured to perform a closed-loop thermodynamic conversion (CTT) between the housing (5) and the container (9) first in a filling configuration in one direction and then in a discharging configuration in the opposite direction; wherein the device stores heat and pressure in the filling configuration and generates energy in the discharging configuration. In the filling configuration, the housing (5) is in fluid communication with the inlet (3a) of the compressor (3), and the primary heat exchanger (7) is in fluid communication with the outlet (3b) of the compressor (3). The turbine (2) is stationary, the motor (4a) operates and drives the compressor (3) to compress the working fluid from the housing (5), the primary heat exchanger (7) functions as a cooler to remove heat from the compressed working fluid, cool the compressed working fluid, and store thermal energy, the secondary heat exchanger (10) functions as a cooler to remove more heat from the compressed working fluid and store more thermal energy, and the container (9) receives and stores the compressed and cooled working fluid, wherein the working fluid stored in the container (9) has a temperature close to the critical temperature of the working fluid itself. In the emission configuration, the housing (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 compressor (3) is stationary. The secondary heat exchanger (10) functions as a heater to release heat to the working fluid from the container (9). The primary heat exchanger (7) functions as a heater to release more heat to the working fluid and heat the working fluid. The turbine (2) rotates through the heated working fluid and drives the generator (4b) and / or the driven motor (300) to generate energy. The working fluid returns to atmospheric pressure in the housing (5). The device is further configured to define a closed loop and to perform a closed thermodynamic cycle (TC) in the closed loop using at least a portion of the working fluid. In the closed loop, the outlet (3b) of the compressor (3) is in fluid communication with the other heat exchanger (220), the outlet (2b) of the turbine (2) is in fluid communication with the inlet (3a) of the compressor (3), and the additional heat exchanger (13) is operatively positioned between the outlet (2b) of the turbine (2) and the inlet (3a) of the compressor (3). The device includes: A first bypass conduit (310) including a corresponding first valve (311), wherein the first bypass conduit (310) is configured to connect the outlet (3b) of the compressor (3) to the other heat exchanger (220) and is configured to bypass the primary heat exchanger (7) and the container (9); A second bypass duct (320) including a corresponding second valve (321) is configured to connect the outlet (2b) of the turbine (2) to the inlet (3a) of the compressor (3) and is configured to bypass the housing (5).

2. The device according to claim 1, wherein, The working fluid has the following chemical-physical properties: a critical temperature between 0°C and 100°C, and a flow rate of 0.5 kg / m³ at 25°C. 3 With 10kg / m 3 The density between.

3. The device according to claim 1 or 2, wherein, The shell (5) is a pressure balloon.

4. The device according to claim 1, wherein, The first valve (311) and the second valve (321) can be throttled to regulate the flow rate of the working fluid in the closed thermodynamic cycle (TC).

5. The device according to claim 1, comprising a regenerator (400) operatively operating between the primary heat exchanger (7) and the other heat exchanger (220) and between the outlet (2b) of the turbine (2) and the additional heat exchanger (13).

6. The device according to claim 1, wherein, The compressor (3) is multi-stage and intercooled.

7. The device according to claim 1, wherein, The other heat exchanger (220) is fluidly connected to at least one stage of the turbine (2) to provide intermediate heating for the turbine (2).

8. The device according to claim 1, wherein, A pump (25) is located between the secondary heat exchanger (10) and the primary heat exchanger (7) and is configured to increase the pressure in the discharge configuration.

9. The device according to claim 1, comprising a delivery pipe and a return pipe, the delivery pipe extending from the housing (5) to the container (9), and the return pipe extending from the container (9) to the housing (5), wherein, The first bypass conduit (310) connects the delivery pipe and the return pipe near the primary heat exchanger (7), and the second bypass conduit (320) connects the delivery pipe and the return pipe near the housing (5).

10. A method for energy generation and storage, wherein, The method is implemented using the device according to claim 1, wherein the method includes: The closed-loop thermodynamic conversion (CTT) is performed between the shell (5) and the container (9) first in one direction during the filling phase and then in the opposite direction during the discharge phase. The shell (5) stores the working fluid in the gas phase and in pressure equilibrium with the atmosphere, and the container (9) stores the working fluid in the liquid or supercritical phase at a temperature close to the critical temperature, wherein the critical temperature is between 0°C and 200°C. The method accumulates heat and pressure during the filling phase and generates energy during the discharge phase. The closed-loop thermodynamic cycle is performed simultaneously with the charging phase or the discharging phase using at least a portion of the working fluid.

11. The method according to claim 10, wherein, The filling phase includes: - The working fluid from the housing (5) is compressed in the compressor (3) to absorb energy, the housing (5) being in contact with the atmosphere on the outside and defining a volume portion inside the housing that is configured to accommodate the working fluid at atmospheric pressure; - The compressed working fluid is introduced through the primary heat exchanger (7) and the secondary heat exchanger (10) arranged in series to bring the temperature of the working fluid close to its own critical temperature; wherein the primary heat exchanger (7) functions as a cooler to remove heat from the compressed working fluid, cool the compressed working fluid and store thermal energy, wherein the secondary heat exchanger (10) functions as a cooler to remove more heat from the compressed working fluid and store more thermal energy; - The working fluid to be cooled is collected in the container (9); wherein the secondary heat exchanger (10) and the primary heat exchanger (7) perform a supercritical conversion of the working fluid, such that the working fluid is collected in the container (9) in a supercritical phase, or wherein the secondary heat exchanger (10) and the primary heat exchanger (7) perform a subcritical conversion of the working fluid, such that the working fluid is collected in the container (9) in a liquid phase; wherein the temperature of the working fluid collected in the container (9) is between 0°C and 100°C, and wherein the pressure of the working fluid collected in the container (9) is between 10 bar and 150 bar.

12. The method according to claim 11, wherein, The emission stages include: - The working fluid from the container (9) is passed through the secondary heat exchanger (10) and the primary heat exchanger (7); wherein the secondary heat exchanger (10) functions as a heater to transfer heat to the working fluid from the container (9), and wherein the primary heat exchanger (7) functions as a heater to transfer more heat to the working fluid and heat the working fluid. - The heated working fluid is passed through the turbine (2), wherein the turbine (2) is rotated by the heated working fluid and drives the generator (4a) and / or the slave motor (300) to generate energy, wherein the working fluid expands and cools in the turbine (2); - The working fluid from the turbine (2) is reintroduced into the housing (5) at atmospheric pressure.

13. The method according to claim 11, wherein, The closed thermodynamic cycle (TC) includes: - Compress at least a portion of the working fluid into the compressor (3); - Pass at least a portion of the working fluid through the other heat exchanger (220) operatively associated with the additional heat source (230); - The turbine (2) expands at least a portion of the heated working fluid, wherein the turbine (2) rotates by the heated working fluid and drives the generator (4b) and / or the slave motor (300) to generate energy, wherein the working fluid expands and cools in the turbine (2); - The at least portion of the working fluid is cooled in the additional heat exchanger (13) and the at least portion of the working fluid is reintroduced into the compressor (3).

14. The method according to claim 11, wherein, The compression of the working fluid in the compressor is intercooled; wherein the closed thermodynamic cycle (TC) is restorative.

15. The method according to claim 10, wherein, The closed thermodynamic cycle (TC) has a higher pressure and a lower pressure; wherein the higher pressure is equal to or lower than the maximum pressure of the cycle thermodynamic conversion (CTT) in the charge configuration / stage; wherein the lower pressure is equal to or higher than the minimum pressure of the cycle thermodynamic conversion (CTT) in the discharge configuration / stage.

16. The method of claim 10, wherein, The portion of the working fluid that operates according to the closed thermodynamic cycle (TC) is between 0% and 50% of the working fluid; wherein the remaining portion of the working fluid that accumulates in the container (9) or the shell (5) is between 100% and 50% of the working fluid.

17. The method according to claim 10, wherein, The working fluid is selected from the group consisting of CO2, SF6, and N2O.

18. The method according to claim 12, wherein, The expansion of the working fluid in the turbine (2) is intermediately heated.

19. The method of claim 12, comprising: The pressure of the discharge stage is increased by a pump (25) placed between the secondary heat exchanger (10) and the primary heat exchanger (7).

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