use of outdoor air for closed loop inventory control

专利摘要:
systems and methods related to the use of external air for stock control of a closed thermodynamic cycle system or energy storage system, such as a brayton reversible cycle system, are disclosed. one method may involve, in a closed-loop system operating in a power generation mode, circulating a working fluid through a closed-loop fluid path. the fluid path of the closed cycle can include a high pressure leg and a low pressure leg. the method may involve even more in response to a demand for increased energy generation, compression and dehumidification of ambient air. and the method may involve injecting compressed and dehumidified ambient air into the low pressure foot.
公开号:BR112019013446A2
申请号:R112019013446
申请日:2017-12-07
公开日:2019-12-31
发明作者:Larochelle Philippe；Apte Raj
申请人:Malta Inc；
IPC主号:

专利说明:

USE OF EXTERNAL AIR FOR CLOSED CYCLE INVENTORY CONTROL
CROSS REFERENCE FOR RELATED APPLICATION [001] This application claims priority for U.S. Patent Application No. 15 / 394,572, filed December 29, 2016, which is incorporated herein by reference in its entirety.
FUNDAMENTALS [002] In a heat engine or heat pump, a heat exchanger can be used to transfer heat between a thermal storage material and a working fluid for use with turbomachinery. The heat engine can be reversible, for example, it can also be a heat pump, and the working fluid and heat exchanger can be used to transfer heat or cold to a plurality of thermal reserves. Thermal energy within a given system can be stored in various forms and in a variety of containers, including pressure vessels and / or insulated vessels.
SUMMARY [003] A closed thermodynamic cycle system or energy storage system, such as a reversible Brayton cycle system, can include at least one working fluid circulated through a closed cycle fluid path including at least two exchangers of heat, a turbine and a compressor. The closed-loop fluid path can include a high pressure leg and a low pressure leg. At least two temperature reservoirs can each contain a thermal storage medium that can be pumped through heat exchangers.
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2/135 heat, providing and / or extracting thermal energy from the working fluid. A motor / generator can be used to obtain work from the thermal energy in the system, preferably generating electricity from the mechanical energy received from the turbine.
[004] The system may also include a second compressor coupled to the low pressure leg and configured to, on demand, compress ambient air and inject the compressed ambient air into the low pressure leg. Beneficially, the injection of compressed ambient air into the low pressure leg can be used to control the energy of the system.
[005] Examples of methods may include in a closed-loop system operating in a power generation mode, circulating a working fluid through a closed-loop fluid path including, in sequence, a compressor, a heat exchanger of hot side, a turbine and a cold side heat exchanger, wherein the closed loop fluid path comprises a high pressure leg and a low pressure leg; in response to a demand for greater energy generation, to compress and dehumidify ambient air; and inject the compressed and dehumidified ambient air into the low pressure leg.
[006] Examples of methods may include in a closed-loop system in a power generation mode, circulating a working fluid through a closed-loop fluid path including, in sequence, a compressor, a side heat exchanger hot, a turbine and a cold side heat exchanger, the closed-loop fluid path comprises a high-pressure leg and a low-pressure leg, and in which the closed-loop system
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3/135 is configured to thermally contact the working fluid circulating through the cold side heat exchanger with a cold side thermal storage medium (CTS); in response to a demand for reduced power generation, expel working fluid from the closed-loop fluid path through an expansion valve, thereby cooling the expelled working fluid; and thermally contacting the expelled working fluid with a portion of the CTS medium.
[007] Examples of systems may include a first compressor; a hot-side heat exchanger; a turbine; a cold side heat exchanger; a working fluid circulating in a closed cycle fluid path through, in sequence, the first compressor, the hot side heat exchanger, the turbine and the cold side heat exchanger, where the closed cycle fluid path comprises a high pressure leg and a low pressure leg; and a second compressor coupled to the low pressure leg and configured to, on demand, compress ambient air and inject compressed ambient air into the low pressure leg.
[008] Examples of systems may include a first compressor; a hot-side heat exchanger; a turbine; a cold side heat exchanger; a working fluid circulating in a closed cycle fluid path through, in sequence, the first compressor, the hot side heat exchanger, the turbine and the cold side heat exchanger, where the closed cycle fluid path comprises a high pressure leg and a low pressure leg; a cold-side thermal storage medium
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4/135 (CTS), in which the system is configured to thermally contact the working fluid circulating through the cold side heat exchanger with the CTS medium; an expansion valve configured to expel the working fluid from the closed-loop fluid path; and an auxiliary heat exchanger configured to thermally contact the expelled working fluid with at least a portion of the CTS medium.
[009] Example of non-transient computer-readable medium may include instructions stored in it executable by a computing device to make the computing device perform functions, the functions include in a closed loop system operating in a generation mode. circulate a working fluid through a closed-loop fluid path including, in sequence, a compressor, a hot-side heat exchanger, a turbine and a cold-side heat exchanger, where the fluid path closed cycle comprises a high pressure leg and a low pressure leg; in response to a demand for greater energy generation, to compress and dehumidify ambient air; and inject the compressed and dehumidified ambient air into the low pressure leg.
[0010] Example of non-transient computer-readable medium may include instructions stored in it executable by a computing device to make the computing device perform functions, functions include in a closed loop system in a power generation mode , circulate a working fluid through a closed-loop fluid path including, in sequence,
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5/135 a compressor, a hot side heat exchanger, a turbine and a cold side heat exchanger, in which the closed-loop fluid path comprises a high pressure leg and a low pressure leg, and in which the closed cycle system is configured to thermally contact the working fluid circulating through the cold side heat exchanger with a cold side thermal storage medium (CTS); in response to a demand for reduced power generation, expel working fluid from the closed-loop fluid path through an expansion valve, thereby cooling the expelled working fluid; and thermally contacting the expelled working fluid with a portion of the CTS medium.
[0011] Examples of systems may include in a closed cycle system operating in a power generation mode, means for circulating a working fluid through a closed cycle fluid path including, in sequence, a compressor, a heat exchanger hot side heat, a turbine and a cold side heat exchanger, wherein the closed loop fluid path comprises a high pressure leg and a low pressure leg; means in response to a demand for greater energy generation, compressing and dehumidifying ambient air; and means for injecting compressed and dehumidified ambient air into the low pressure leg.
[0012] Examples of systems may include in a closed loop system in a power generation mode, means for circulating a working fluid through a closed loop fluid path including, in sequence, a compressor, a heat exchanger hot side, a
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6/135 turbine and a cold side heat exchanger, in which the closed-loop fluid path comprises a high-pressure leg and a low-pressure leg, and in which the closed-loop system is configured to thermally contact the fluid workflow circulating through the cold-side heat exchanger with a cold-side thermal storage medium (CTS); means for responding to a demand for less energy production, expelling working fluid from the closed-loop fluid path through an expansion valve, thereby cooling the expelled working fluid; and means for thermally contacting the expelled working fluid with a portion of the CTS medium.
BRIEF DESCRIPTION OF THE DRAWINGS [0013] Figure 1 schematically illustrates the operation of a pumped thermal electrical storage system.
[0014] Figure 2 is a schematic flow chart of working fluid and heat storage medium of a thermal system pumped in a load / heat pump mode.
[0015] Figure 3 is a schematic flowchart of working fluid and heat storage medium for a thermal system pumped in a heat engine / discharge mode.
[0016] Figure 4 is a schematic diagram of pressure and temperature of the working fluid as it undergoes the load cycle in Figure 2.
[0017] Figure 5 is a schematic diagram of pressure and temperature of the working fluid as it undergoes the discharge cycle in Figure 3.
[0018] Figure 6 is a schematic perspective view of a closed working fluid system in the thermal system pumped in Figures 2-3.
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7/135 [0019] Figure 7 is a schematic perspective view of the thermal system pumped in Figures 2-3 with hot and cold side storage tanks and a closed cycle working fluid system.
[0020] Figure 8 shows a heat storage load cycle for a molten salt / water system q _c = 0.9 er] t = 0.95. The dashed lines correspond to q _c = qt = 1.
[0021] Figure 9 shows a heat storage discharge (extraction) cycle for the molten salt / water system in Figure 8 with q _c = 0.9 and qt = 0.95. The dashed lines correspond to q _c = qt = 1 · [0022] Figure 10 shows a heat storage cycle in a pumped thermal system with varying compression rates between loading and unloading cycles.
[0023] Figure 11 shows the outward and return efficiency contours for a water / salt system. The symbols © and 0 represent an approximate range of the adiabatic efficiency values of the current turbomachinery. The dashed arrows represent the direction of the efficiency increase.
[0024] Figure 12 shows round-trip efficiency contours for a cooler salt / storage system. The symbols © and 0 represent an approximate range of the adiabatic efficiency values of the current turbomachinery.
[0025] Figure 13 is a schematic flowchart of working fluid and heat storage medium from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a load / heat pump mode.
[0026] Figure 14 is a schematic flow chart of the working fluid and heat storage medium of a system
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8/135 thermal pumped with a gas-gas heat exchanger for the working fluid in a heat engine / discharge mode.
[0027] Figure 15 is a schematic flowchart of working fluid and heat storage medium from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a charge / heat pump mode with rejection of indirect heat to the environment.
[0028] Figure 16 is a schematic flowchart of working fluid and heat storage medium from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a discharge mode / heat engine with rejection of indirect heat to the environment.
[0029] Figure 17 shows a heat storage load cycle for a storage system with a gas-gas heat exchanger, a cold-side storage medium capable of descending to temperatures significantly below room temperature and η ₀ = 0.9 er) t = 0.95.
[0030] Figure 18 shows a heat storage discharge cycle for a storage system with a gas-gas heat exchanger, a cold-side storage medium capable of descending to temperatures significantly below room temperature and η ₀ = 0.9 er) t = 0.95.
[0031] Figure 19 is a schematic flowchart of recharging the hot side in a heat cycle pumped in solar mode with heating of a solar salt only by solar energy.
[0032] Figure 20 is a schematic flowchart of a discharge cycle from a thermal system pumped with heat rejection into the environment.
[0033] Figure 21 is a schematic flowchart of a discharge cycle from a thermal system pumped with rejection
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9/135 heat for an intermediate fluid circulated in a thermal bath at room temperature.
[0034] Figures 22 and 23 are thermal systems pumped with separate compressor / turbine pairs for loading and unloading modes.
[0035] Figures 24 and 25 show pumped thermal systems configured in a combustion heat input generation mode.
[0036] Figure 26 is a schematic flowchart of recharging the hot side in a heat cycle pumped through heating by a combustion heat source or a residual heat source.
[0037] Figure 27 shows an example of a pumped thermal system with pressure regulated energy control.
[0038] Figure 28 shows an example of a pumped thermal system with an encapsulated pressure generator.
[0039] Figure 29 is an example of variable stators in a compressor / turbine pair.
[0040] Figure 30 shows a computer system that is programmed to implement various methods and / or regulate various systems of the present disclosure.
[0041] Figure 31 illustrates an inventory control system, according to an example modality.
[0042] Figure 32 illustrates an inventory control method, according to an example modality.
[0043] Figure 33 illustrates an inventory control method, according to an example modality.
DETAILED DESCRIPTION [0044] Although several embodiments of the invention have been
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10/135 shown and described here, it will be obvious to those skilled in the art that such modalities are provided by way of example only. Numerous variations, changes and substitutions can occur to those skilled in the art without departing from the invention. It is to be understood that various alternatives to the embodiments of the invention described herein can be employed. It should be understood that different aspects of the invention can be appreciated individually, collectively or in combination with each other.
[0045] It should be understood that the terminology used here is used for the purpose of describing specific modalities, and is not intended to limit the scope of the present invention. It should be noted that, as used here, the singular forms of one, one and o include plural references, unless the context clearly dictates otherwise. In addition, unless otherwise indicated, all technical and scientific terms used herein have the same meaning as is normally understood by a person skilled in the art to which this invention belongs.
[0046] Although the preferred embodiments of the present invention are shown and described herein, it will be obvious to those skilled in the art that such modalities are provided by way of example only. Numerous variations, changes and substitutions will now occur to those skilled in the art without departing from the invention. It is to be understood that several alternatives to the embodiments of the invention described herein can be employed in the practice of the invention. It is intended that the following claims define the scope of the invention and that the methods and structures within the scope of these claims and their equivalents are covered
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11/135 hereby.
[0047] The term reversible, as used here, generally refers to a process or operation that can be reversed through infinitesimal changes in some process property or operation without substantial entropy production (for example, energy dissipation). A reversible process can be approximated by a process that is in thermodynamic equilibrium. In some instances, in a reversible process, the direction of the energy flow is reversible. As an alternative, or in addition, the general direction of operation of a reversible process (for example, the direction of fluid flow) can be reversed, such as, for example, from clockwise to counterclockwise, and vice versa.
[0048] The term sequence, as used here, generally refers to elements (for example, unit operations) in order. Such an order can refer to the process order, such as the order in which a fluid flows from an element
to another. In an example, a compressor, unity in storage in heat and turbine in sequence include O compressor a amount of unity in exchange of heat, and The
heat exchange unit upstream of the turbine. In that case, a fluid can flow from the compressor to the heat exchange unit and from the heat exchange unit to the turbine. A fluid that flows through sequential unit operations can flow sequentially through unit operations. A sequence of elements can include one or more intervening elements. For example, a system comprising a compressor, heat storage unit and turbine in sequence may include an auxiliary tank between the compressor and the heat storage unit. A sequence of
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12/135 elements can be cyclical.
I. Overview [0049] An example of a heat engine in which inventory control systems can be implemented is a closed loop system, for example, a closed Brayton cycle system. A Brayton cycle system can use a generator / engine connected to a turbine and a compressor that act on a working fluid circulating in the system. Examples of working fluids include air, argon, carbon dioxide or gas mixtures. A Brayton cycle system can have a hot side and / or a cold side. Each side can include a heat exchanger coupled to one or more cold storage containers and / or one or more hot storage containers. Preferably, the heat exchangers can be arranged as counterflow heat exchangers for greater thermal efficiency. Liquid thermal storage media can be used and can include, for example, liquids that are stable at high temperatures, such as molten nitrate salt or solar salt, or liquids that are stable at low temperatures, such as glycols or alkanes such as hexane. For an example of a molten salt and hexane system, the molten salt on the hot side may include a warm storage at approximately 565 ° C and a cold storage at approximately 2.990 ° C and the cold side hexane may include a warm storage at approximately 35 ° C and cold storage at approximately -60 ° C.
[0050] In a closed cycle system, for example, a closed Brayton cycle system, the working fluid can circulate through a cycle fluid path
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13/135 closed and the closed loop fluid path can include a high pressure leg and a low pressure leg. It may be desirable to vary the mass of fluid (for example, the amount of working fluid) that flows through the closed-loop fluid path. In some embodiments, the variation in the mass flow rate of the working fluid in the closed cycle fluid path can vary the amount of energy generated by the system.
[0051] An example mode of inventory control in a closed cycle system may involve, in response to an increased demand for energy generation, compressing and dehumidifying ambient air and injecting compressed and dehumidified ambient air into the low pressure leg . Beneficially, the injection of compressed and dehumidified ambient air into the low pressure leg can be used to rapidly increase the energy production of the system.
[0052] In some implementations, the system may include a second compressor and a dehumidifier, each coupled to the low pressure leg. The second compressor can, on demand, compress the ambient air and inject the compressed ambient air into the low pressure leg. In addition, the dehumidifier can dehumidify the ambient air prior to injection.
[0053] Another example of an inventory control modality in a closed-loop system may involve extracting the working fluid from the high pressure leg of the closed-loop fluid path, storing the extracted working fluid in a working fluid storage tank, and fluid injection
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14/135 of work extracted from the working fluid storage tank in the low pressure leg simultaneously with the injection of compressed and dehumidified ambient air in the low pressure leg. Beneficially, injecting the working fluid extracted from the working fluid storage tank into the low pressure leg simultaneously with the injection of compressed and dehumidified ambient air into the low pressure leg can quickly increase the mass added to the cycle fluid path closed.
[0054] Another example of an inventory control modality in a closed-loop system may involve, in response to a reduced power generation demand, expelling the working fluid from the closed-loop fluid path through a valve expansion. Beneficially, expelling the working fluid from the closed-loop fluid path can be used to decrease the energy production of the system. In addition, expelling the working fluid from the closed-loop fluid path can cool the expelled working fluid. The cooled fluid can then be thermally contacted to a portion of a cold-side thermal storage medium (CTS), providing a thermodynamic benefit.
II. Illustrative reversible heat engine
A. Pumped thermal systems [0055] The disclosure provides pumped thermal systems capable of storing electrical energy and / or heat and releasing energy (for example, producing electricity) at a later time. The pumped thermal systems of the disclosure can include a heat engine and a heat pump (or cooler). In some cases, the heat engine may be
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15/135 operated in reverse as a heat pump. In some cases, the heat engine can be operated upside down like a refrigerator. Any description of heat pump / heat engine systems or cooler / heat engine systems capable of reversing operation here can also be applied to systems that include heat engine system (s), heat pump system (s) separate and / or reversible heat and / or refrigerator system (s). In addition, since heat pumps and refrigerators share the same operating principles (albeit for different purposes), any description of configurations or operation of heat pumps here can also apply to configurations or operation of refrigerators, and vice versa.
[0056] The systems of the present disclosure can operate as heat engines or heat pumps (or refrigerators). In some situations, the disclosure systems may function alternately as heat engines and heat pumps. In some instances, a system can operate as a heat engine to generate energy and subsequently operate as a heat pump to store energy, or vice versa. Such systems can operate alternately and sequentially as heat engines and as heat pumps. In some cases, such systems operate reversibly or substantially reversibly as heat engines like heat pumps.
[0057] Reference will now be made to the figures, where similar numerals refer to equal parts throughout. It will be appreciated that the Figures and resources therein are not necessarily drawn to scale.
[0058] Figure 1 schematically illustrates the principles
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16/135 of the thermal electrical storage pumped using a heat pump / heat engine electricity storage system. Electricity can be stored in the form of thermal energy from two materials or media at different temperatures (for example, thermal energy tanks comprising heat storage fluids or thermal storage media) using a combined heat pump / heat engine system . In a load mode or heat pump, the system can consume labor to transfer heat from a cold material or medium to a hot material or medium, thereby lowering the temperature (for example, sensitive energy) of the cold material and increasing the temperature ( (ie, sensitive energy) of the hot material. In a discharge or heat engine mode, work can be produced by the system by transferring heat from the hot material to the cold material, thereby lowering the temperature (ie, sensitive energy) of the hot material and increasing the temperature (ie , sensitive energy) of the cold material. The system can be configured to ensure that the work produced by the system at discharge is a favorable fraction of the energy consumed under load. The system can be configured to achieve high round-trip efficiency, defined here as the work produced by the system at discharge divided by the work consumed by the system under load. In addition, the system can be configured to achieve high round-trip efficiency using components at a desired cost (for example, a reasonably low cost). The arrows H and W in Figure 1 represent directions of heat flow and work, respectively.
[0059] Heat engines, heat pumps and coolers
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17/135 of the disclosure may involve a working fluid to and from which heat is transferred during a thermodynamic cycle. The heat engines, heat pumps and coolers of the disclosure can operate in a closed cycle. Closed cycles allow, for example, a wider selection of working fluids, operation at high cold side pressures, operation at lower cold side temperatures, greater efficiency and less risk of damage to the turbine. One or more aspects of the disclosure described in relation to systems with working fluids subjected to closed cycles can also be applied to systems with working fluids subjected to open cycles.
[0060] In one example, heat engines can operate on a Brayton cycle and heat pumps / coolers can operate on a reverse Brayton cycle (also known as a gas cooling cycle). Other examples of thermodynamic cycles that the working fluid can undergo or approximate include the Rankine cycle, the ideal vapor compression refrigeration cycle, the Stirling cycle, the Ericsson cycle or any other cycle advantageously employed in conjunction with exchange of heat with heat storage fluids of the disclosure.
[0061] The working fluid can undergo a thermodynamic cycle operating at one, two or more pressure levels. For example, the working fluid can operate in a closed cycle between a low pressure limit on a cold side of the system and a high pressure limit on a hot side of the system. In some implementations, a low pressure limit of about 10 atmospheres (atm) (1.01325 MPa) or greater can be used. In some cases, the low limit
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18/135 pressure can be at least about 1 atm (0.101325 MPa), at least about 2 atm (0.20265 MPa), at least about 5 atm (0.506625 MPa), at least about 10 atm (1.01325 MPa), at least about 15 atm (1.51988 MPa), at least about 20 atm (2.0265 MPa), at least about 30 atm (3.03975 MPa), at least about 40 atm (4.053 MPa), at least about 60 atm (6.0795 MPa), at least about 80 atm (8.106 MPa), at least about 100 atm (10.1325 MPa), at least about 120 atm (12,159 MPa), at least about 160 atm (16,212 MPa), or at least about 200 atm (20,265 MPa), 500 atm (50,6625 MPa), 1000 atm (101,325 MPa), or more. In some cases, a subatmospheric low pressure limit may be used. For example, the low pressure limit may be less than about 0.1 atm (0.0101325 MPa), less than about 0.2 atm (0.020265 MPa), less than about 0.5 atm (0 , 0506625 MPa) or less than about 1 atm (0.101325 MPa). In some cases, the low pressure limit may be about 1 atmosphere (atm) (0.101325 MPa). In the case of a working fluid operating in an open cycle, the low pressure limit can be about 1 atm (0.101325 MPa) or equal to the ambient pressure.
[0062] In some cases, the low pressure limit value can be selected based on the desired energy output and / or energy input requirements of the thermodynamic cycle. For example, a pumped thermal system with a low pressure limit of about 10 atm (1.01325 MPa) may be able to provide an energy output comparable to an industrial gas turbine with ambient air inlet (1 atm). The low pressure limit value may also be subject to cost / safety trade-offs. In addition, the
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19/135 low pressure limit value can be limited by the high pressure limit value, the hot-side operation intervals and the heat storage medium (eg pressure and temperature ranges over which the storage media heat rates are stable), pressure rates and operating conditions (eg operating limits, optimal operating conditions, pressure drop) achieved by turbomachinery and / or other system components, or any combination thereof. The high pressure limit can be determined according to these system restrictions. In some cases, higher values of the high pressure limit can lead to better heat transfer between the working fluid and the hot-side storage medium.
[0063] Working fluids used in pumped thermal systems may include air, argon, other noble gases, carbon dioxide, hydrogen, oxygen, or any combination thereof, and / or other fluids in a gaseous, liquid, critical, or state supercritical (e.g., supercritical CO2). The working fluid can be a gas or a low-viscosity liquid (for example, viscosity below about 500x10 ⁶ Poise at 1 atm (0.101325 MPa)), satisfying the requirement that the flow be continuous. In some implementations, a gas with a high specific heat rate can be used to achieve greater cycle efficiency than a gas with a low specific heat rate. For example, argon (for example, specific heat ratio of about 1.66) can be used to replace air (for example, specific heat ratio of about 1.4). In some cases, the working fluid can
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20/135 be a mixture of one, two, three or more fluids. In one example, helium (with high thermal conductivity and high specific heat) can be added to the working fluid (eg, argon) to improve heat transfer rates in heat exchangers.
[0064] Here, pumped thermal systems can use heat storage media or materials, such as one or more heat storage fluids. The heat storage means can be gases or liquids of low viscosity, satisfying the requirement that the flow be continuous. Systems can use a first heat storage medium on a hot side of the system (hot side thermal storage medium (HTS) or HTS here) and a second heat storage medium on a cold side of the system (storage medium cold side (CTS) or CTS here). Thermal storage media (for example, low-viscosity liquids) can have high heat capacities per volume unit (for example, heat capacities above 1400 Joule (kilvin Kelvin) ^ -) and high thermal conductivities (for example, thermal conductivity above 0.7 Watt Kelvin) ^x ). In some implementations, several different thermal storage media (also heat storage medium here) or on the hot side, on the cold side or on the hot side and on the cold side can be used.
[0065] The operating temperatures of the hot-side thermal storage medium may be in the liquid range of the hot-side thermal storage medium, and the operating temperatures of the cold side thermal storage medium may be in the liquid range of the thermal medium.
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21/135 thermal storage on the cold side. In some instances, liquids may allow a faster exchange of large amounts of heat for convective counterflow than solids or gases. Thus, in some cases, the liquid HTS and CTS media can be used to advantage. Pumped thermal systems that use thermal storage media here can advantageously provide a safe, non-toxic and geographically independent energy storage alternative (for example, electricity).
[0066] In some implementations, the hot-side thermal storage medium may be a molten salt or a mixture of molten salts. Any salt or salt mixture that is liquid over the operating temperature range of the hot-side thermal storage medium can be employed. Molten salts can provide numerous advantages as a means of storing thermal energy, such as low vapor pressure, lack of toxicity, chemical stability, low chemical reactivity with typical steels (for example, melting point below the creep temperature of steels, low corrosivity, low iron and nickel dissolving capacity) and low cost. In one example, HTS is a mixture of sodium nitrate and potassium nitrate. In some instances, HTS is a eutectic mixture of sodium nitrate and potassium nitrate. In some instances, HTS is a mixture of sodium nitrate and potassium nitrate with a lower melting point than the individual constituents, a higher boiling point than the individual constituents or a combination of these. Other examples include potassium nitrate, calcium nitrate, sodium nitrate, sodium nitrite, lithium nitrate, mineral oil, or any combination
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22/135 of these. Additional examples include any gaseous media (including compressed gases), liquids or solids (for example, powder solids) with adequate thermal storage capacities (for example, high) and / or capable of achieving adequate heat transfer rates (for example , high) with the working fluid. For example, a mixture of 60% sodium nitrate and 40% potassium nitrate (also known as solar salt in some situations) can have a thermal capacity of approximately 1500 Joule (Kelvin mole) ¹ and a thermal conductivity of approximately 0 , 75 Watt (Kelvin meter) ¹ within a temperature range of interest. The hot-side thermal storage medium can be operated over a temperature range that structural steels can handle.
[0067] In some cases, liquid water at temperatures of about 0 ° C to 100 ° C (about 273 K-373 K) and a pressure of about 1 atm (0.101325 MPa) can be used as a medium of cold-side thermal storage. Due to a possible risk of explosion associated with the presence of steam at or near the boiling point of water, the operating temperature can be maintained below 100 ° C or less, maintaining an operating pressure of 1 atm (0.101325 MPa ) (without pressurization). In some cases, the operating temperature range of the cold-side thermal storage medium can be extended (for example, at -30 ° C to 100 ° C at 1 atm (0.101325 MPa)) using a mixture of water and a or more antifreeze compounds (for example, ethylene glycol, propylene glycol or glycerol).
[0068] As described in greater detail elsewhere
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23/135 of this document, the improved storage efficiency can be achieved by increasing the temperature difference at which the system operates, for example, using a cold-side heat storage fluid capable of operating at lower temperatures. In some examples, the cold-side thermal storage medium may comprise hydrocarbons, such as, for example, alkanes (for example, hexane or heptane), alkenes, alkines, aldehydes, ketones, carboxylic acids (for example, HCOOH), ethers , cycloalkanes, aromatic hydrocarbons, alcohols (for example, butanol), other type (s) of hydrocarbon molecules, or any combination thereof. In some cases, the cold-side thermal storage medium may be hexane (for example, n-hexane). Hexane has a wide liquid range and can remain fluid (ie liquid) throughout its liquid range (-94 ° C to 68 ° C in 1 atm (0.101325 MPa)). Low temperature properties of hexanes are aided by their immiscibility with water. Other liquids, such as, for example, ethanol or methanol, may become viscous at the low temperature ends of their liquid ranges due to the pre-crystallization of water absorbed by the air. In some cases, the cold-side thermal storage medium may be heptane (for example, n-heptane). Heptane has a wide liquid range and can remain fluid (ie liquid) throughout its liquid range (-91 ° C to 98 ° C in 1 atm (0.101325 MPa)). The low temperature properties of heptane are aided by its immiscibility with water. At even lower temperatures, other heat storage media can be used, such as, for example,
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24/135 isohexane (2-methylpentane). In some instances, cryogenic liquids with boiling points below -150 ° C (123 K) or about -180 ° C (93.15 K) can be used as a cold-side thermal storage medium (for example, propane, butane, pentane, nitrogen, helium, neon, argon and krypton, air, hydrogen, methane or liquefied natural gas). In some implementations, the choice of the cold-side thermal storage medium may be limited by the choice of the working fluid. For example, when a gaseous working fluid is used, a cold liquid-side thermal storage medium having a liquid temperature range at least partially or substantially above the boiling point of the working fluid may be required.
[0069] In some cases, the operating temperature range of the CTS and / or HTS media can be changed by pressurizing (ie, increasing the pressure) or evacuating (ie, decreasing the pressure) the tanks and thus changing the temperature at which the storage media undergo phase transitions (for example, going from liquid to solid, or from liquid to gas).
[0070] In some cases, the hot and cold side heat storage fluids of the pumped thermal systems are in a liquid state in at least part of the energy storage device's operating temperature range. The hot-side heat storage fluid can be liquid within a certain temperature range. Likewise, the cold-side heat storage fluid can be liquid within a certain temperature range. Fluids from
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25/135 heat storage can be heated, cooled or maintained to reach an adequate operating temperature before, during or after operation.
[0071] Pumped thermal systems of the disclosure can circulate between the loaded and unloaded modes. In some instances, pumped thermal systems can be fully charged, partially charged or partially discharged, or fully discharged. In some cases, the heat storage on the cold side can be loaded (also recharged here) regardless of the heat storage on the hot side. In addition, in some implementations, loading (or part of it) and unloading (or part of it) can occur simultaneously. For example, a first portion of a hot side heat storage can be recharged while a second portion of the hot side heat storage together with a cold side heat storage is being discharged.
[0072] Pumped thermal systems may be able to store energy for a certain period of time. In some cases, a given amount of energy can be stored for at least about 1 second, at least about 30 seconds, at least about 1 minute, for at least
any less about 5 minutes at least about 30 minutes, fur any less fence in 1 hour, fur any less fence in 2 hours, fur any less fence in 3 hours, fur any less fence in 4 hours, fur any less fence in 5 hours, fur any less fence in 6 hours, fur any less fence in 7 hours, fur any less fence in 8 hours, fur any less fence of 9 10 hours hours, at any less about 12 hours fur any less fence of 14 hours , fur any less fence of 16
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26/135 hours, at least about 18 hours, at least about 20 hours, at least about 22 hours, at least about 24 hours (1 day), at least about 2 days, at least about 4 days , at least about 6 days, at least about 8 days, at least about 10 days, 20 days, 30 days, 60 days, 100 days, 1 year or more.
[0073] The pumped thermal systems of the disclosure may be able to store / receive input from, and / or extract / supply output of a substantially large amount of energy and / or power for use with power generation systems (eg systems intermittent power generation such as wind or solar energy), energy distribution systems (eg power grid) and / or other grid-scale loads or uses or independent configurations. During a charging mode of a pumped thermal system, electrical energy received from an external power source (for example, a wind power system, a photovoltaic solar system, an electrical grid, etc.) can be used to operate the thermal system pumped in a heat pump mode (that is, transferring heat from a low temperature reservoir to a high temperature reservoir, thus storing energy). During a pumped thermal system discharge mode, the system can supply electrical energy to an external power system or load (for example, one or more electrical networks connected to one or more loads, a load, such as a factory or a process of energy intensive, etc.) operating in heat engine mode (ie transferring heat from a high temperature reservoir to a low temperature reservoir, thus extracting
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27/135 energy). As described here, during loading and / or unloading, the system can receive or reject thermal energy, including, but not limited to, electromagnetic energy (for example, solar radiation) and thermal energy (for example, sensitive energy from a medium heated by solar radiation, combustion heat, etc.).
[0074] In some implementations, the pumped thermal systems are synchronized to the grid. Synchronization can be achieved by combining the speed and frequency of a system's motors / generators and / or turbomachinery with the frequency of one or more grid networks with which the system exchanges energy. For example, a compressor and a turbine can rotate at a certain fixed speed (for example, 3600 revolutions per minute (rpm)) which is a multiple of the grid frequency (for example, 60 hertz (Hz)). In some cases, this configuration can eliminate the need for additional power electronics. In some implementations, the turbomachinery and / or engines / generators are not synchronized to the grid. In such cases, frequency matching can be performed using energy electronics. In some implementations, the turbomachinery and / or motors / generators are not directly synchronized to the network, but can be combined through the use of gears and / or a mechanical gearbox. As described in greater detail elsewhere, the pumped thermal systems can also be passable (rampable). Such capabilities may allow these grid-scale energy storage systems to operate as peak power plants and / or as load after power plants. In some cases, disclosure systems may be able to operate as
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28/135 base load power plants.
[0075] Pumped thermal systems can have a certain energy capacity. In some cases, the energy capacity during charging may differ from the energy capacity during discharge. For example, each system can have a load and / or discharge capacity of less than 1 megawatt (MW), at least about 1 megawatt, at least about 2 MW, at least about 3 MW, at least about 4 MW, at least about 5 MW, at least about 6 MW, at least about 7 MW, at least about 8 MW, at least about 9 MW, at least about 10 MW, at least 20 MW, at least at least about 30 MW, at least 40 MW, at least about 50 MW, at least about 75 MW, at least about 100 MW, at least about 200 MW, at least about 500 MW, at least 1 gigawatt (GW), at least 2 GW, at least about 5 GW, at least about 10 GW, at least about 20 GW, at least about 30 GW, at least about 40 GW, at least about 50 GW at least about 75 GW, at least about 100 GW, or more.
[0076] Pumped thermal systems can have a certain energy storage capacity. In one example, a pumped thermal system is configured as a 100 MW unit operating for 10 hours. In another example, a pumped thermal system is configured as a 1 GW plant operating for 12 hours. In some cases, the energy storage capacity may be less than 1 megawatt-hour (MWh), at least about 1 megawatt-hour, at least about 10 MWh, at least about 100 MWh, at least 1 gigawatt hour (GWh) at least about 5 GWh, at least about 10 GWh, at least about 20 GWh, at least 50 GWh, at least
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29/135 minus about 100 GWh, at least about 200 GWh, at least about 500 GWh, at least about 700 GWh, at least GWh or more.
[0077] In some cases, a given energy capacity can be obtained with a certain size, configuration and / or operating conditions of the heat motor / heat pump cycle. For example, the size of turbomachinery, ducts, heat exchangers or other components of the system can correspond to a certain energy capacity.
[0078] In some implementations, a given energy storage capacity can be achieved with a certain size and / or number of thermal storage tanks on the hot side and / or thermal storage tanks on the cold side. For example, the heat engine / heat pump cycle can operate at a given energy capacity for a certain period of time defined by the heat storage capacity of the system or plant. The number and / or the heat storage capacity of the hot-side thermal storage tanks may differ from the number and / or the heat storage capacity of the cold-side thermal storage tanks. The number of tanks may depend on the size of the individual tanks. The size of the hot-side storage tanks may differ from the size of the cold-side thermal storage tanks. In some cases, the hot-side thermal storage tanks, the hot-side heat exchanger and the hot-side thermal storage medium can be referred to as a hot-side (thermal) heat storage unit. In some cases, the cold-side thermal storage tanks, the heat exchanger of
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30/135 cold side and the cold side thermal storage medium can be referred to as a cold side (thermal) heat storage unit.
[0079] A pumped thermal storage facility can include any suitable number of hot-side storage tanks, such as at least about 2, at least about 4, at least about 10, at least about 50, at least about 100, at least about 500 about 1,000, at least about 5,000, at least about 10,000, and so on. In some examples, a pumped thermal storage facility includes 2, 3, 4, 5, 6, 7, 8, 9, 10, 15, 20, 30, 40, 50, 60, 70, 80, 90, 100, 200 , 300, 400, 500, 600, 700, 800, 900, 1,000 or more hot side tanks.
[0080] A pumped thermal storage facility may also include any suitable number of cold-side storage tanks, such as at least about 2, at least about 4, at least about 10, at least about 50, at least at least about 100, at least about 500, at least about 1,000, at least about 5,000, at least about 10,000, and so on. In some examples, a pumped thermal storage facility includes 2, 3, 4, 5, 6, 7, 8, 9, 10, 15, 20, 30, 40, 50, 60, 70, 80, 90, 100, 200 , 300, 400, 500, 600, 700, 800, 900, 1,000 or more cold side tanks.
B. Pumped thermal storage cycles [0081] One aspect of the disclosure concerns pumped thermal systems that operate in pumped thermal storage cycles. In some instances, cycles allow electricity to be stored as heat (for example, in
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31/135 form of a temperature differential) and then reconverted to electricity through the use of at least two components of turbomachinery, a compressor and a turbine. The compressor is labor intensive and increases the temperature and pressure of a working fluid (WF). The turbine produces work and reduces the temperature and pressure of the working fluid. In some instances, more than one compressor and more than one turbine are used. In some cases, the system may include at least 1, at least 2, at least 3, at least 4 or at least 5 compressors. In some cases, the system may include at least
any less 1, at least 2, at least 3, at minus 4 or at any less 5 turbines. The compressors can to be willing in series or in parallel. The turbines can to be willing in series or in parallel.
[0082] Figures 2 and 3 are schematic flowcharts of working fluid and heat storage medium of an exemplary pumped thermal system in a charge / heat pump mode and in a discharge / heat motor mode, respectively. The system can be designed to simplify the explanation so that there are no losses (that is, generation of entropy) neither in the turbomachinery or in the heat exchangers. The system may include a working fluid 20 (for example, argon gas) flowing in a closed cycle between a compressor 1, a hot-side heat exchanger 2, a turbine 3 and a cold-side heat exchanger 4. Routes / fluid flow directions for working fluid 20 (for example, a gas), a hot-side thermal storage medium (HTS) 21 (for example, a low-viscosity liquid) and a cold-side thermal storage medium (CTS) 22 (for example, a low
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32/135 viscosity) are indicated by arrows.
[0083] Figures 4 and 5 are schematic diagrams of pressure and temperature of the working fluid 20 as it passes through the load cycles in Figures 2 and 3, respectively, again simplified in the approach of generation without entropy. The normalized pressure is shown on the y axis and the temperature is shown on the x axis. The direction of the processes occurring during the cycles is indicated with arrows, and the individual processes occurring in the compressor 1, the hot side CFX 2, the turbine 3 and the cold side CFX 4 are indicated in the diagram with their respective numerals.
[0084] Heat exchangers 2 and 4 can be configured as counterflow heat exchangers (CFXs), where the working fluid flows in one direction and the substance with which it is exchanging heat is flowing in the opposite direction. In an ideal counterflow heat exchanger with correctly matched flows (ie balanced capacities or capacity flow rates), the temperatures of the working fluid and the thermal storage medium are reversed (ie the counterflow heat exchanger may have unity effectiveness).
[0085] Counterflow heat exchangers 2 and 4 can be designed and / or operated to reduce the generation of entropy in heat exchangers to insignificant levels compared to the generation of entropy associated with other components and / or processes of the system (eg generation of compressor and / or turbine entropy). In some cases, the system can be operated in such a way that the generation of entropy in the system is minimized. For example, the system can be operated in such a way that the generation of entropy associated with
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33/135 heat storage units are minimized. In some cases, a temperature difference between the fluid elements exchanging heat can be controlled during operation, such that the generation of entropy in the hot and cold side heat storage units is minimized. In some cases, the entropy generated in the hot and cold side heat storage units is insignificant when compared to the entropy generated by the compressor, the turbine or both the compressor and the turbine. In some cases, the generation of entropy associated with the heat transfer in heat exchangers 2 and 4 and / or the generation of entropy associated with the operation of the hot-side storage unit, the cold-side storage unit or both storage units hot and cold side can be less than about 50%, less than about 25%, less than about 20%, less than about 15%, less than about 10%, less than about 5%, less about 4%, less than about 3%, less than about 2%, or less than about 1% of the total entropy generated within the system (for example, entropy generated by compressor 1, the heat exchanger on its side 2, the turbine 3, the cold side heat exchanger 4 and / or other components described (for example, a stove). For example, entropy generation can be reduced or minimized if the two heat-exchanging substances do so at a local temperature differential ΔΤ -> 0 (that is, when the temperature difference between any two fluid elements that are in contact near heat exchanger is small). In some examples, the temperature differential ΔΤ between any two elements
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34/135 of fluid that are in close thermal contact can be less than about 300 Kelvin (K) (26.85 ° C), less than about 200 K (-73.15 ° C), less than about 100 K (-
173.15 ° C), less than about 75 K (-198.15 ° C), less than about 50 K (-223.15 ° C), less than about 40 K (-
233.15 ° C), less than about 30 K (-243.15 ° C), less than about 20 K (-253.15 ° C), less than about 10 K (-
263.15 ° C), less than about 5 K (-268.15 ° C), less than about 3 K (-270.15 ° C), less than about 2 K (-271.15 ° C), or less than about 1 K (-272.15 ° C). In another example, the generation of entropy associated with the pressure drop can be reduced or minimized by the appropriate design. In some instances, the heat exchange process can occur at constant or near constant pressure. Alternatively, a negligible pressure drop can be experienced by the working fluid and / or one or more means of thermal storage during passage through a heat exchanger. The pressure drop in the heat exchangers can be controlled (for example, reduced or minimized) through the proper design of the heat exchanger. In some instances, the pressure drop in each heat exchanger may be less than about 20% of the inlet pressure, less than about 10% of the inlet pressure, less than about 5% of the inlet pressure, less than about 3% of the inlet pressure, less than about 2% of the inlet pressure, less than about 1% of the inlet pressure, less than about 0.5% of the inlet pressure, less than about 0, 25% of the inlet pressure or less than about 0.1% of the inlet pressure.
[0086] Upon entering heat exchanger 2, the temperature
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35/135 of the working fluid can either increase (by taking heat from the HTS 21 medium, corresponding to the discharge mode in Figures 3 and 5) or decrease (by giving heat to the HTS 21 medium, corresponding to the loading mode in Figures 2 and 4), depending on the temperature of the HTS medium in the heat exchanger in relation to the temperature of the working fluid. Likewise, when entering the heat exchanger 4, the temperature of the working fluid can either increase (taking heat from the CTS medium 22, corresponding to the charge mode in Figures 2 and 4) or decrease (giving heat to the CTS medium) 22, corresponding to the discharge mode in Figures 3 and 5), depending on the temperature of the CTS medium in the heat exchanger in relation to the temperature of the working fluid.
[0087] As described in more detail with reference to the charging mode in Figures 2 and 4, the process of adding heat to the cold side CFX 4 can occur in a different temperature range than the heat removal process to the side CFX hot 2. Similarly, in the discharge mode in Figures 3 and 5, the heat rejection process on the cold side CFX 4 can occur in a different temperature range than the heat addition process on the hot side CFX 2. At least a portion of the temperature ranges of the hot-side and cold-side heat exchange processes may overlap during loading, during unloading or during loading and unloading.
[0088] As used here, the temperatures To, Ti, To ⁺ and Ti ⁺ are so called because To ⁺ , Ti ⁺ are the temperatures reached with the output of a compressor with a given compression rate r, adiabatic efficiency η ₀ and input temperatures of To, Ti respectively. The examples in the Figures
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2, 3, 4 and 5 can be idealized examples where η ₀ = 1 and where the adiabatic efficiency of the turbine also has the value r | t = 1.
[0089] With reference to the load mode shown in Figures 2 and 4, the working fluid 20 can enter the compressor 1 in position 30 at a pressure P and a temperature T (for example, Τι, P2). As the working fluid passes through the compressor, work Wi is consumed by the compressor to increase the pressure and temperature of the working fluid (for example, for Ti ⁺ , Pi), as indicated by Pf and Tt at position 31. In load mode, the Ti + temperature of the working fluid leaving the compressor and entering the hot side CFX 2 at position 31 is higher than the temperature of the HTS 21 medium entering the hot side CFX 2 at position 32 from a second hot-side thermal storage tank 7 at a To ⁺ temperature (i.e., To ⁺ <Ti ⁺ ). As these two liquids pass in thermal contact with each other in the heat exchanger, the temperature of the working fluid decreases as it moves from position 31, position 34, releasing heat Qi to the medium of HTS, while the temperature the HTS medium in turn increases as it moves from position 32 to position 33, absorbing heat Qi from the working fluid. In one example, the working fluid exits the CFX hot side 2 in position 34 at temperature To ⁺ and the HTS medium exits the CFX hot side 2 in position 33 for a first thermal storage tank 6 side at temperature Ti ⁺ . The heat exchange process can take place at a constant or almost constant pressure, so that the working fluid leaves the hot side CFX 2 in position 34 at a
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37/135 lower temperature, but with the same pressure Pi, as indicated by P and T j, at position 34. Similarly, the temperature of the HTS 21 medium increases in the hot side CFX 2, while its pressure can remain constant or almost constant.
[0090] When exiting the CFX from the hot side 2 in position 34 (for example, in To ⁺ , Pi), the working fluid 20 undergoes expansion in turbine 3 before leaving the turbine in position 35. During expansion, the pressure and the temperature of the working fluid turbine decrease (for example, for To, P2), as indicated by P j, and T j, at position 35. The working magnitude W2 generated by the turbine depends on the enthalpy of the working fluid that enters the turbine and the degree of expansion. In load mode, heat is removed from the working fluid between positions 31 and 34 (on the hot side CFX 2) and the working fluid is expanded back to the pressure at which it initially entered the compressor in position 30 (for example, P2). The compression ratio (for example, P1 / P2) in compressor 1 is equal to the expansion rate in turbine 3, and the enthalpy of the gas entering the turbine is less than the enthalpy of the gas leaving the compressor, work W2 generated by turbine 3 is less than the work Wi consumed by compressor 1 (ie W2 <Wi).
[0091] Because the heat has been removed from the working fluid in the hot side CFX 2, the temperature To at which the working fluid leaves the turbine at position 35 is lower than the temperature Ti at which the working fluid initially entered on the compressor at position 30. To close the cycle (ie, to return the pressure and temperature of the working fluid to its initial values Τι, P2 at position 30),
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38/135 heat Q2 is added to the working fluid from the medium of CTS 22 in the cold side CFX 4 between positions 35 and 30 (i.e., between turbine 3 and compressor 1). In one example, the CTS medium 22 enters the cold side CFX 4 at position 36 from a first cold side thermal storage tank 8 at temperature Ti and exits the cold side CFX 4 at position 37 in a second tank cold-side thermal storage 9 at temperature To, while working fluid 20 enters cold-side CFX 4 at position 35 at temperature To and exits cold-side CFX 4 at position 30 at temperature Ti. Again, the process of heat exchange can take place at a constant or almost constant pressure, so that the working fluid leaves the cold side CFX 2 in position 30 at a higher temperature, but the same pressure P2, as indicated by P and Tΐ in position 30 Similarly, the temperature of the CTS 22 medium decreases in the cold side CFX 2, while its pressure can remain constant or almost constant.
[0092] During charging, heat Q2 is removed from the CTS medium and heat Qi is added to the HTS medium, where Qi> Q2. A net amount of Wi - W2 work is consumed, since the Wi work used by the compressor is greater than the W2 work generated by the turbine. A device that consumes work while moving heat from a cold body or thermal storage medium to a hot body or thermal storage medium is a heat pump; thus, the thermal system pumped in charge mode operates like a heat pump.
[0093] In one example, the discharge mode shown in Figures 3 and 5 may differ from the charge mode shown in
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Figures 2 and 4 on the temperatures of the thermal storage medium being introduced in the heat exchangers. The temperature at which the HTS medium enters the hot-side CFX 2 in position 32 is Ti + instead of To ⁺ , and the temperature of the CTS medium which enters the cold-side CFX 4 in position 36 is To instead of Ti During discharge, the working fluid enters the compressor at position 30 in To and P2, exits the compressor in position 31 at To ⁺ <Ti ⁺ and Pi, absorbs heat from the HTS medium in the hot side CFX 2, enters the turbine 3 in position 34 in Ti + and Pi, leaves the turbine in position 35 in Ti> To and P2 and finally rejects heat to the CTS medium in the cold side CFX 4, returning to its initial state in position 30 in To and P2.
[00 94] The HTS medium at Ti ⁺ temperature can be stored in a first thermal storage tank on the hot side 6, the HTS medium at temperature To ⁺ can be stored in a second thermal storage tank on the hot side 7, the CTS medium at temperature Ti can be stored in a first thermal storage tank on the cold side 8, and the CTS medium at temperature To can be stored in a second thermal storage tank on the cold side 9 during both loading modes. and discharge. In one implementation, the HTS medium inlet temperature at position 32 can be switched between Ti ⁺ and To ⁺ by switching between tanks 6 and 7, respectively. Similarly, the inlet temperature of the CTS medium at position 36 can be switched between Ti and To by switching between tanks 8 and 9, respectively. Switching between tanks can be achieved by including a valve or a valve system (for example, valve systems 12 and
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40/135 in Figure 7) to switch connections between the hot side heat exchanger 2 and the hot side tanks 6 and 7, and / or between the cold side heat exchanger 4 and the cold side tanks 8 and 9 as needed for loading and unloading modes. In some implementations, connections can be connected on the working fluid side, while the connections from storage tanks 6, 7, 8 and 9 to heat exchangers 2 and 4 remain static. In some instances, flow paths and connections to heat exchangers may depend on the design (for example, shell-and-tube) of each heat exchanger. In some implementations, one or more valves can be used to change the direction of the working fluid and the heat storage medium through the counterflow heat exchanger in loading and unloading. Such configurations can be used, for example, due to the high thermal storage capacities of the heat exchanger component, to decrease or eliminate temperature transients, or a combination of these. In some implementations, one or more valves can be used to change the direction of the working fluid only, while the direction of the HTS or CTS can be changed by changing the direction of the pumping, thus maintaining the counterflow configuration. In some implementations, different valve configurations can be used for HTS and CTS. In addition, any combination of valve configurations can be used. For example, the system can be configured to operate using different valve configurations in different situations (for example, depending on the operating conditions of the system).
[0095] In the discharge mode shown in Figures 3 and 5, the
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41/135 working fluid 20 can enter compressor 1 in position at pressure P and temperature T (for example, To, P2) · As the working fluid passes through the compressor, work Wi is consumed by the compressor to increase the pressure and temperature of the working fluid (for example, for To ⁺ , Pi), as indicated by Pt and Tf in position 31. In the discharge mode, the temperature To ⁺ of the working fluid leaving the compressor and enters the hot-side CFX 2 at position 31 is less than the temperature of the HTS 21 medium which enters the hot-side CFX 2 at position 32 of a first hot-side thermal storage tank 6 at a temperature Ti ⁺ (ie is, To ⁺ <Ti ⁺ ). As these two liquids pass in thermal contact with each other in the heat exchanger, the temperature of the working fluid increases as it moves from position 31 to position 34, absorbing heat Qi from the medium of HTS, while the temperature of the medium of HTS, in turn decreases as it moves from position 32 to position 33, releasing heat Qi into the working fluid. In one example, the working fluid exits the CFX hot side 2 at position 34 at temperature Ti ⁺ and the HTS medium exits the CFX hot side 2 at position 33 for the second thermal storage tank 7 at temperature To ⁺ . The heat exchange process can take place at a constant or almost constant pressure, so that the working fluid leaves CFX hot side 2 in position 34 at a higher temperature, but with the same pressure Pi, as indicated by P and Tΐ at position 34. Similarly, the temperature of the HTS 21 medium decreases in the hot-side CFX 2, while its pressure can remain constant or almost constant.
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42/135 [0096] When leaving the hot side CFX 2 in position 34 (for example, in 1i ⁺ , Pi), the working fluid 20 undergoes expansion in turbine 3 before leaving the turbine in position 35. During expansion , the working fluid turbine pressure and temperature decrease (for example, for Τι, P2), as indicated by P j, and T j, at position 35. The working magnitude W2 generated by the turbine depends on the enthalpy of the fluid of work entering the turbine and the degree of expansion. In the discharge mode, heat is added to the working fluid between positions 31 and 34 (on the hot side CFX 2) and the working fluid is expanded back to the pressure at which it initially entered the compressor in position 30 (for example , P2). The compression ratio (for example, P1 / P2) in compressor 1 is equal to the expansion rate in turbine 3 and the enthalpy of the gas entering the turbine is greater than the enthalpy of the gas leaving the compressor, the work W2 generated by turbine 3 is greater than the work Wi consumed by compressor 1 (ie W2> Wi).
[0097] Because heat has been added to the working fluid in the hot-side CFX 2, the temperature Ti at which the working fluid exits the turbine at position 35 is higher than the temperature To where the working fluid initially entered the compressor in position 30. To close the cycle (ie, to return the pressure and temperature of the working fluid to its initial values To, P2 in position 30), heat Q2 is rejected by the working fluid into the CTS medium 22 on the cold side CFX 4 between positions 35 and 30 (that is, between turbine 3 and compressor 1). The CTS medium 22 enters the cold side CFX 4 at position 36 from a second cold side thermal storage tank 9 at
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43/135 temperature To and exits cold side CFX 4 in position 37 to a cold side first storage tank 8 at temperature Ti, while working fluid 20 enters cold side CFX 4 in position 35 to temperature Ti and exits the cold side CFX 4 in position 30 at temperature To. Again, the heat exchange process can take place at a constant or almost constant pressure, so that the working fluid leaves the cold side CFX 2 in position 30 at a higher temperature, but the same pressure P2, as indicated by P and Tj, at position 30. Similarly, the temperature of the CTS 22 medium increases in the cold side CFX 2, while its pressure can remain constant or almost constant.
[0098] During the discharge, heat Q2 is added to the medium of CTS and heat Qi is removed from the medium of HTS, where Qi> Q2 · A net amount of work W2 - Wi is generated, once the work Wi used compressor is less than the W2 work generated by the turbine. A device that generates work while moving heat from a hot body or thermal storage medium to a cold body or thermal storage medium is a heat engine; thus, the thermal system pumped in the discharge mode operates as a heat engine.
[0099] Figure 6 is a simplified schematic perspective view of a closed working fluid system in the thermal system pumped in Figures 2-3. As indicated, working fluid 20 (contained within the pipeline) circulates clockwise between compressor 1, hot-side heat exchanger 2, turbine 3 and cold-side heat exchanger 4. Compressor 1 and the turbine 3 can be grouped on a common mechanical rod 10 such that they rotate
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44/135 together. In some implementations, the compressor and turbine 3 may have separate mechanical rods. A motor / generator 11 (for example, including a synchronous motor - synchronous generator converter on a single common rod) supplies power to and from the turbomachinery. In this example, the compressor, turbine and engine / generator are all located on a common rod. The tubes in positions 32 and 33 transfer hot-side thermal storage fluid to and from the hot-side heat exchanger 2, respectively. The tubes in positions 36 and 37 transfer the cold-side thermal storage fluid to and from the cold-side heat exchanger 4, respectively.
[00100] Although the system of Figure 6 is illustrated as comprising a compressor 1 and turbine 3, the system can include one or more compressors and one or more turbines, which can operate, for example, in a parallel configuration, or alternatively in a series configuration or a combination of parallel and series configurations. In some examples, a system of compressors or turbines can be assembled in such a way that a certain compression ratio is achieved. In some cases, different compression ratios (for example, over loading and unloading) may be used (for example, connecting or disconnecting, in a parallel and / or in series configuration, one or more compressors or turbines from the compressor or turbine system ). In some examples, the working fluid is directed to a plurality of compressors and / or a plurality of turbines. In some instances, the compressor and / or turbine may have temperature-dependent compression ratios. The arrangement and / or operation of the turbomachinery and / or other elements of the
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45/135 system can be adjusted according to temperature dependence (for example, to optimize performance).
[00101] Figure 7 is a simplified schematic perspective view of the thermal system pumped in Figures 2-3 with hot and cold side storage tanks and a closed cycle working fluid system. In this example, the HTS medium is a molten salt and the CTS medium is a low temperature liquid. One, two or more first hot-side tanks 6 (at Ti ⁺ temperature) and one, two or more second hot-side tanks 7 (at To ⁺ temperature), both to maintain the HTS medium, are in fluid communication with one valve 13 configured to transfer HTS medium to and from the hot side heat exchanger 2. One, two or more first cold side tanks 8 (at Ti temperature) and one, two or more second cold side tanks 9 ( at temperature To), both to maintain the CTS medium, are in fluid communication with a valve 12, configured to transfer the CTS medium to and from the cold side heat exchanger 4.
[00102] The thermal energy reservoirs or storage tanks can be thermally insulated tanks that can contain an adequate amount of the relevant thermal storage medium (for example, heat storage fluid). Storage tanks can allow relatively compact storage of large amounts of thermal energy. In one example, hot-side tanks 6 and / or 7 can have a diameter of about 80 meters, while cold-side tanks 8 and / or 9 can have a diameter of about 60 meters. In another example, the size of each (ie, hot side or cold side) thermal storage for
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46/135 a 1 GW plant operating for 12 hours can be about 20 medium-sized oil refinery tanks.
[00103] In some implementations, a third set of tanks containing storage media at intermediate temperatures between the other tanks can be included on the hot side and / or on the cold side. In one example, a third storage or transfer tank (or set of tanks) at an intermediate temperature for the temperatures of a first tank (or set of tanks) and a second tank (or set of tanks) can be provided. A set of valves can be provided to switch the storage medium between the different tanks and heat exchangers. For example, thermal media can be directed to different sets of tanks after the heat exchangers leave, depending on the operating conditions and / or the cycle being used. In some implementations, one or more additional sets of storage tanks at different temperatures can be added on the hot side and / or the cold side.
[00104] Storage tanks (e.g., hot-side tanks comprising the hot-side thermal storage medium and / or cold-side tanks comprising the cold-side thermal storage medium) can operate at ambient pressure. In some implementations, storing thermal energy at ambient pressure can provide safety benefits. Alternatively, storage tanks can operate at high pressures, such as, for example, at a pressure of at least about 2 atm (0.20265 MPa), at least about 5 atm (0.506625 MPa), at least about 10 atm (1.01325 MPa), at least about
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47/135 of 20 atm (2.0265 MPa), or more. Alternatively, storage tanks can operate at reduced pressures, such as, for example, a pressure of at most about 0.9 atm (0.0911925 MPa), at most about 0.7 atm (0.0709275 MPa ), at most about 0.5 atm (0.0506625 MPa), at most about 0.3 atm (0.0303975 MPa), at most about 0.1 atm (0.0101325 MPa), at most about 0.01 atm (0.00101325 MPa), at most about 0.001 atm, (0.000101325 MPa) or less. In some cases (for example, when operating at higher / higher or lower pressures or to avoid contamination of the thermal storage medium), the storage tanks can be sealed from the surrounding atmosphere. Alternatively, in some cases,
storage can no to be sealed. In some implementations , the tanks can include an or more adjustments pressure or systems of relief (per example,
valve for safety or system optimization).
[00105] As used herein, the first hot side tank (s) 6 (at Ti ⁺ temperature) may contain HTS medium at a higher temperature than the second hot side tank (s) 7 (at To ⁺ temperature ⁾ ), and the first cold side tank (s) 8 (at temperature Ti) can contain CTS medium at a higher temperature than the second cold side tank (s) 9 (at temperature To). During loading, the HTS medium in the first hot side (s) tank (s) 6 and / or CTS medium in the second cold side tank (s) 9 can be refilled. During the discharge, half of HTS can be consumed in the first tank (s) on the hot side 6 and / or half of CTS in the second tank (s) on the cold side 9.
[00106] In the previous examples, in both modes of
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48/135 operation, two of the four storage tanks 6, 7, 8 and 9 are feeding the thermal storage medium to heat exchangers 2 and 4 at inlets 32 and 36, respectively, and the other two tanks are receiving medium from thermal storage of heat exchangers 2 and 4 from outlets 33 and 37, respectively. In this configuration, the feed tanks can contain a storage medium at a certain temperature due to previous operating conditions, while the temperatures of the receiving tanks may depend on the current system operation (for example, operating parameters, loads and / or inlet). energy). The temperatures of the receiving tank can be adjusted by the conditions of the Brayton cycle. In some cases, the temperatures in the receiving tank may differ from the desired values due to deviations from predetermined cycle conditions (for example, variation of absolute pressure in response to system demand) and / or due to the generation of entropy within the system. In some cases (for example, due to the generation of entropy), at least one of the four temperatures in the tank may be higher than desired. In some implementations, a radiator can be used to reject or dissipate this residual heat into the environment. In some cases, the heat rejection to the environment can be improved (for example, using evaporative cooling, etc.). The wasted heat generated during the operation of the thermal systems pumped here can also be used for other purposes. For example, residual heat from one part of the system can be used in other parts of the system. In another example, residual heat can be supplied to an external process or system,
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49/135 such as, for example, a manufacturing process that requires low-grade heat, commercial or residential heating, thermal desalination, commercial drying operations, etc.
[00107] Components of thermal systems pumped from the disclosure may exhibit non-ideal performance, leading to losses and / or inefficiencies. The biggest losses in the system can occur due to inefficiencies of the turbomachinery (for example, compressor and turbine) and of the heat exchangers. The losses due to the heat exchangers can be small compared to the losses due to the turbomachinery. In some implementations, losses due to heat exchangers can be reduced to near zero with adequate design and expense. Therefore, in some analytical examples, losses due to heat exchangers and other possible small losses due to pumps, the engine / generator and / or other factors can be overlooked.
[00108] The losses due to turbomachinery can be quantified in terms of adiabatic efficiencies q _c er) t (also known as isentropic efficiencies) for compressors and turbines, respectively. For large turbomachinery, typical values can vary between q _c = 0.85 -0.9 for compressors and r) t = 0.9 - 0.95 for turbines. The actual amount of work produced or consumed by a cycle can then be expressed as APF = VF '= reaS' area (_ (output J 1 _. _R (input, 1 j --— where, in an example, assuming specific heats working fluid constants, ⁼
CpTin (f ~ 1), = ^c p ^T inside (l ~ V> ^_1 ) r where ψ = r Y, r is the compression ratio (that is, the ratio of the highest pressure to the lowest pressure), and γ = c _P / c _v is the specific heat ratio of the working fluid. Due to inefficiencies
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50/135 of the compressor and turbine, more work is needed to achieve a given compression ratio during compaction, and less work is generated during expansion for a given compression ratio. Losses can also be quantified in terms of polytropic or single-stage efficiencies, η _Ο ρ er | tp, for compressors and turbines, respectively. The polytropic efficiencies are related to the adiabatic efficiencies η ₀ er | t by the equations' / ci ^and * [00109] In examples where η _ί: = rjt = 1, pumped thermal cycles of the disclosure can follow identical paths in both load cycles and discharge (for example, as shown in Figures 4 and 5). In the examples where η ₀ <1 and / or r | t <1, the compression in the compressor can lead to a greater temperature increase than in the ideal case for the same compression rate, and the expansion in the turbine can lead to a decrease lower temperature in the ideal case.
[00110] In some implementations, the polytropic efficiency of the compressor can be at least 0.3, at least 0.5, at least 0.6, at least 0.7, at least 0.75, at least 0.8, at least 0.85, at least about 0.9, at least about 0.91, at least about 0.92, at least about 0.93, at least about 0.96, or more. In some implementations, the polytropic efficiency of the η _Ρρ compressor can be at least about 0.3, at least about 0.5, at least about 0.6, at least about 0.7, at least about 0 , 75, at least about 0.8, at least about 0.85, at least 0.9, at least about 0.91, at least about 0.92, at least about 0.93, at least at least about 0.96, at least about 0.97 or more.
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51/135 [00111] Το ⁺ , Τι ⁺ were previously defined as the temperatures reached at the outlet of a compressor with a certain compression rate r, adiabatic efficiency η ₀ and inlet temperatures of To, Ti respectively. In some instances, these four temperatures are related by
7 ^ 4 equation - - - ψ
Τ'ο Λ [00112] Figure 8 shows an exemplary heat storage load cycle for a water (CTS) / molten salt (HTS) system with i) _c = 0.9 and r] _t = 0.95. The dashed lines correspond to η ₀ = ht = 1 and the solid lines show the load cycle with r] _t = 0.95 and η ₀ = 0.9. In this example, the CTS medium on the cold side is water, and the HTS medium on the hot side is molten salt. In some cases, the system may include 4 heat storage tanks. In the load cycle, the working fluid in To and P2 can exchange heat with a CTS medium in the cold side heat exchanger 4, so its temperature can increase for Ti (assuming an insignificant pressure drop, its pressure can remain P2). In compressor 1 with η ₀ = 0.9, the temperature and pressure of the working fluid can increase from Τι, P2 to Ti ⁺ , Pi. The working fluid can then exchange heat with an HTS medium in the hot side heat exchanger 2, such that its temperature can decrease (the constant pressure Pi, assuming the pressure drop is negligible). If the working fluid enters turbine 3 with r] t = 0.95 at temperature To + and expands back to its original pressure P2, its temperature when leaving the turbine may not be To. Instead, the working fluid can enter the turbine at temperature T _o ⁺ and leave the turbine at temperature To and pressure P2. In some examples,
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In temperatures, they are related by the relationship _ ίο some examples, T _o ⁺ is the temperature at which the working fluid enters the entrance of a turbine with adiabatic efficiency and compression rate r to leave at temperature To.
[00113] In some implementations, the temperature T _o ⁺ can be incorporated in load cycles of the disclosure by the first heat exchange of the working fluid with the HTS medium from Ti + to To +, followed by an additional cooling of the Tq fluid to T _o ⁺ , as illustrated by section 38 of the cycle in Figure 8.
[00114] Figure 9 shows an exemplary heat storage discharge (extraction) cycle for the molten water / salt system in Figure 8 with q _c = 0.9 er) t = 0.95. The dashed lines correspond to q _c = r) t = 1 and the solid lines show the load cycle with q _t = 0.95 and q _c = 0.9. In the discharge cycle, the working fluid Ti and P2 can exchange heat with a medium of CTS in the cold side heat exchanger 4, where its temperature can decrease To (assuming that the insignificant pressure drop, the its pressure can remain P2). In compressor 1 with q _c = 0.9, the temperature and pressure of the working fluid can increase from To, P2 to To +, Pi. The working fluid can then exchange heat with an HTS medium in the hot-side heat exchanger 2, such that its temperature can rise (the constant pressure Pi, assuming a negligible pressure drop). The working fluid entering turbine 3 at Tf cannot leave the turbine at temperature Ti as in the load cycle, but can instead leave at temperature T _lf where, in some examples, Tj = T ₁ ⁺ ^ ^_ ' ^7t P. In
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53/135 some examples, T _± is the temperature at which the working fluid leaves the turbine outlet with adiabatic efficiency and compression ratio r after entering the turbine inlet at Ti ⁺ temperature.
[00115] In some implementations, the temperature can be incorporated in the discharge cycles of the disclosure by first cooling the working fluid that leaves the turbine
in T _± for You, how illustrated through the section 39 of cycle on Figure 9, followed by exchange of heat of fluid in job with the medium in CTS of Ti a To.[00116] The cycles loading and discharge can to be closed
by additional heat rejection operations in sections 38 (between To ⁺ and T _o ⁺ ) and 39 (between T and Ti), respectively. In some cases, closing the heat rejection cycles in sections of the cycles where the working fluid can reject heat into the environment at low cost can eliminate the need for additional heat to enter the system. The sections of the cycles where the working fluid can reject heat to room temperature can be limited to sections where the temperature of the working fluid is high enough above room temperature for room cooling to be viable. In some instances, heat can be rejected into the environment in sections 38 and / or 39. For example, heat can be rejected using one or more working fluids to aerate radiators, intermediate water cooling, or various other methods. In some cases, the heat rejected in sections 38 and / or 39 can be used for another useful purpose, such as, for example, cogeneration, thermal desalination and / or other examples described herein.
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54/135 [00117] In some implementations, cycles can be closed by varying the compression rates between the loading and unloading cycles, as shown, for example, in Figure 10. The ability to vary the compression rate on the load and discharge can be implemented, for example, by varying the speed of rotation of the compressor and / or the turbine, by controlling the stator's variable pressure, by diverting a subset of the stages of compression or expansion under load or unloading by using valves, or for using dedicated compressor / turbine pairs for loading and unloading mode. In one example, the compression ratio in the discharge cycle in Figure 9 can be changed in such a way that heat rejection in section 39 is not used, and only heat rejection in section 38 in the load cycle is used. Varying the compression ratio can allow heat (that is, entropy) to be rejected at a lower temperature, thereby increasing the overall round-trip efficiency. In some examples of this configuration, the compression rate τ + t / n * 1 j -ã -i in the load, rc, can be adjusted such that - = W „. ''., And in the discharge, the compression rate ro can be adjusted such that.
~. In some cases, temperatures higher than Ti ⁺ and Ti may be identical in loading and unloading and no removal of heat may be necessary in this portion (also leg here) of the cycle. In such cases, the To ⁺ temperature at the charge (for example, Tq ^ = Toipç ^tp ) and the To ⁺ temperature at the discharge (for example, = Toip _D ^ ^cp ) may be different and the heat may be rejected (also dissipated or discarded) here) for the environment between the To ⁺ ^ and To ⁺ ^ temperatures. In an implementation where only the storage media exchange heat with the environment, a heat rejection device
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55/135 (for example, devices 55 and 56 shown in Figure 16) can be used to lower the CTS temperature from T _o ⁺ ^ to T ^ ^c) between discharge and charge.
[00118] Figure 10 shows an example of a cycle with variable compression rates. The compression ratio can be higher at discharge (when work is produced by the system) than at load (when work is consumed by the system), which can increase the overall efficiency of the system. For example, during a load cycle 80 with T _o , a lower compression ratio of <3 can be used; during a discharge cycle 81 with T ₀ ⁺ ^ ^d a compression ratio> 3 can be used. The higher temperatures reached in the two cycles 80 and 81 can be Ti and Ti ⁺ , and no excess heat can be rejected.
[00119] The compression rate can vary between loading and unloading, in such a way that the heat dissipation into the environment necessary for the closing of the cycle both at loading and at discharge occurs between temperatures Tq ^ (the temperature of the before entering the turbine during the load cycle) and Tq ^ (the temperature of the working fluid when it leaves the compressor at discharge), and not above the temperature Ti (the temperature of the working fluid before entering the compressor under load) and / or leaves the turbine in unloading). In some instances, no heat is rejected at a temperature above the lowest temperature in the HTS medium.
[00120] In the absence of system losses and / or inefficiencies, as, for example, in the case of pumped thermal systems comprising heat pump (s) and heat motor (s) operating at the entropy creation limit
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56/135 zero / isentropic, a certain amount of heat Qh can be transferred using a certain amount of work W in the heat pump (load) mode, and the same Qh can be used in the heating (discharge) mode to produce the same work W, leading to a unit return efficiency (that is, 100%). In the presence of losses and / or inefficiencies of the system, the efficiency of round trip of the pumped thermal systems can be limited by how much the components deviate from the ideal performance.
[00121] The round trip efficiency of a pumped thermal system can be defined as stored η = IW _c ^r _v ^xtra | / | W ^ ^r9a |. In some examples, with an approximation of the ideal heat exchange, the efficiency of the round trip can be derived considering the net output during the discharge cycle, | l4 ^ ^{xf Ni} ' ^GÕ | = '--and the work entry' * ^L. _nr WO. 14 / ^, sctAfo
Required during the load cycle, j ^{= -} using the work and temperature equations given above.
[00122] Round-trip efficiencies can be calculated for different configurations of pumped thermal systems (for example, for different classes of thermal storage media) based on the efficiencies of the turbomachinery components, q _c er) t · [00123] In one example, Figure 11 shows the outward and return efficiency contours for a water / salt system, such as, for example, the water / salt system in Figures 8 and 9 with To = 273 K (0 ° C ), Ti = 373 K (100 ° C) and a compression ratio of r = 5, 65 chosen to achieve compatibility with the salt (s) on the hot side. Examples of round trip efficiency contours in stored η values of 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80% and 90% are shown
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57/135 as a function of the efficiencies of the components η _{0 and} i) t on the x and y axes, respectively. The symbols © and 0 represent the approximate range of the adiabatic efficiency values of the current turbomachinery. The dashed arrows represent the direction of the efficiency increase.
[00124] Figure 12 shows the round-trip efficiency contours for a cooler salt / storage system, such as, for example, a hexane / salt system with a gas-gas heat exchanger in Figures 13, 14, 17 and 18, with To = 194 K (-79 ° C), Ti = 494 K (221 ° C) and a compression ratio of r = 3.28. Examples of round trip efficiency contours in stored η values of 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80% and 90% are shown as a function of the component efficiencies g _{c and} r / t on the x and y axis, respectively. The symbols © and 0 represent the approximate range of the adiabatic efficiency values of the current turbomachinery. As discussed in detail elsewhere, the use of hexane, heptane and / or another CTS medium capable of operating at low temperatures can result in significant improvements in system efficiency.
C. Pumped thermal storage cycles with recovery [00125] Another aspect of the disclosure is directed to pumped thermal systems with recovery. In some situations, the terms regeneration and recovery can be used interchangeably, although they may have different meanings. As used here, the terms recovery and recuperator generally refer to the presence of one or more additional heat exchangers where the working fluid exchanges heat with itself during different cycles of a thermodynamic cycle through continuous heat exchange without
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58/135 intermediate thermal storage. The efficiency of round-trip pumped thermal systems can be substantially improved if the permissible temperature ranges of the storage materials can be extended. In some implementations, this can be done by choosing a material or medium on the cold side that can go below 273 K (0 ° C). For example, a CTS medium (eg, hexane) with a lower temperature limit of about To = 179 K (-94 ° C) can be used in a system with a molten salt HTS medium. However, T _o ⁺ (ie, the lowest working fluid temperature in the hot-side heat exchanger) at some compression rates (for example, modest) may be below the freezing point of the molten salt, making the salt cast feasible as the HTS medium. In some implementations, this can be resolved by including a working fluid in the working fluid heat exchanger (eg gas-gas) (also recoverer here) in the cycle.
[00126] Figure 13 is a schematic flowchart of working fluid and heat storage medium of a thermal system pumped in a load / heat pump mode with a gas-gas heat exchanger 5 for the working fluid. The use of the gas-to-gas heat exchanger may allow the use of a cooler heat storage medium on the cold side of the system. The working fluid can be air. The working fluid can be dry air. The working fluid can be nitrogen. The working fluid can be argon. The working fluid can be a mixture of mainly argon mixed with another gas, such as helium. For example, the working fluid can comprise at least about 50% of
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59/135 argon, at least about 60% argon, at least about 70% argon, at least about 80% argon, at least about 90% argon or about 100% argon, with equilibrium of helium.
[00127] Figure 17 shows a heat storage load cycle for the storage system in Figure 13 with a cold-side storage medium (eg liquid hexane) capable of descending to approximately 179 K (-94 ° C) ) and a molten salt as the hot side storage, and rp = 0.9 and rp = 0.95. The CTS medium can be hexane or heptane and the HTS medium can be molten salt. In some cases, the system may include four heat storage tanks.
[00128] In an implementation, during loading in Figures 13 and 17, the working fluid enters the compressor in Ti and P2, leaves the compressor in Ti ⁺ and Pi, rejects heat Qi in the middle of HTS 21 in the hot side CFX 2, which comes out of the hot side CFX 2 to Ti and Pi, rejects heat Qrecup (also Qregen here, as shown, for example, in the attached drawings) for the cold side (low pressure) working fluid in the heat exchanger or stove 5, leaves stove 5 in To ⁺ and Pi, rejects heat to the environment (or another heat sink) in section 38 (for example, a radiator), enters turbine 3 in Tq and Pi, leaves the turbine at To and P2, absorbs heat Q2 from the medium of CTS 22 in the cold side CFX 4, which leaves the cold side CFX 4 to To ⁺ and P2, absorbs Qrecup heat from the hot side working fluid (high pressure) in the heat exchanger or stove 5 and finally it leaves stove 5 in Ti and P2, returning to its initial state before entering the compressor.
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60/135 [00129] Figure 14 is a schematic flowchart of the working fluid and heat storage medium of the thermal system pumped in Figure 13 in discharge / heat engine mode. Again, the use of the gas-to-gas heat exchanger may allow the use of cooler heat storage fluid (CTS) and / or cooler working fluid on the cold side of the system.
[00130] Figure 18 shows a heat storage discharge cycle for the storage system for the storage system in Figure 14 with a cold side storage medium (eg liquid hexane) capable of descending up to 179 K ( -94 ° C) and a molten salt as the hot side storage, eg _c = 0.9 r / t = 0.95. Again, the CTS medium can be hexane or heptane and the HTS medium can be molten salt, and the system can include 4 heat storage tanks.
[00131] During the discharge in Figures 14 and 18, the working fluid enters the compressor at To and P2, exits the compressor at To + and Pi, absorbs Qrecup heat from the cold (low pressure) working fluid at the heat exchanger or stove 5, leaves stove 5 in Ti and Pi, absorbs heat Qi from the medium of HTS 21 in the hot side CFX 2, leaves the hot side CFX 2 in Ti ⁺ and Pi, enters the turbine 3 in Ti ⁺ and Pi, it leaves the turbine in T _± and P2, rejects heat to the environment (or another heat sink) in section 39 (for example, a radiator), rejects Qrecup heat for the hot working fluid ( high-pressure) in the heat exchanger or stove 5, enters the cold side CFX 4 in To ⁺ and P2, rejects heat Q2 for the CTS medium 22 in the cold side CFX 4, and finally exits the cold side CFX 4 in To and P2,
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61/135 returning to its initial state before entering the compressor.
[00132] In another implementation, shown in Figure 15, the load cycle remains the same as in Figures 13 and 17, except that the working fluid leaves the stove 5 in T _o ⁺ and Pi (instead of in To ⁺ and Pi , as in Figures 13 and 17), enters turbine 3 at To ⁺ and Pi, exits the turbine at To and P2, absorbs heat Q2 from the medium of CTS 22 having a temperature To ⁺ (instead of at To ⁺ as in Figures 13 and 17) on the cold side CFX 4, and exits the cold side CFX 4 in To ⁺ and P2 (instead of in To + and P2 as in Figure 13) before re-entering the stove 5. The heat between the To ⁺ and To ⁺ temperatures are no longer rejected directly from the working fluid into the environment (as in section 38 in Figures 13 and 17).
[00133] During the discharge in Figure 16, the discharge cycle remains the same as in Figures 14 and 8B, except that the temperature of the HTS medium deposited in tank 7 is changed. The working fluid leaves the stove 5 in T) and Pi (instead of Ti and Pi, as in Figures 14 and 8B) and absorbs heat Qi from the HTS 21 medium in the hot side CFX 2. The medium
from HTS leaves of CFX in hot side 2 by having an temperature T (instead in You how in Figures 14 and 18). 0 fluid in job so get out of CFX in hot side 2 in Ti + e P 1, goes into at turbine 3 in Ti + e Pi, and leaves the turbine < sm T and P ₂ before in
re-enter the stove 5. Heat between temperatures T _± and Ti is no longer rejected directly from the working fluid into the environment (as in section 39 in Figures 14 and 18). As in Figure 14, the CTS medium enters tank 8 at temperature Tq ⁺ .
[00134] After the discharge in Figure 16, in preparation for
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62/135 the charge in Figure 15, the heat exchange with the environment can be used to cool the HTS 21 medium from the temperature T _± used in the discharge cycle to the temperature Ti used in the charge cycle. Likewise, heat exchange with the environment can be used to cool the CTS 22 medium from the temperature To ⁺ used in the discharge cycle to the temperature T _o ⁺ used in the charge cycle. Unlike the configuration in Figures 13 and 14, where the working fluid may need to reject a substantial amount of heat (in sections 38 and 39, respectively) at a rapid rate, in this configuration, the hot and cold side storage medium it can be cooled at an arbitrarily slow rate (for example, by radiating away or by other means of releasing heat into the environment).
[00135] As shown in Figure 16, in some implementations, heat can be rejected from the CTS medium into the environment by circulating the CTS medium in tank 8 in a heat rejection device 55 that can absorb heat from of the CTS medium and reject heat into the environment until the CTS medium cools from the To ⁺ temperature to the T _o ⁺ temperature. In some examples, the heat rejection device 55 may be, for example, a radiator, a thermal bath containing a substance such as water or salt water, or a device immersed in a natural body of water such as a lake, river or Ocean. In some instances, the heat rejection device 55 can also be an air cooling device, or a series of tubes that are thermally connected to a solid reservoir (for example, tubes embedded in the ground).
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63/135 [00136] Similarly, in some implementations, heat can be rejected from the HTS medium into the environment by circulating the HTS in tank 7 in a heat rejection device 56 that can absorb heat from the HTS medium and reject heat to the environment until the HTS medium cools from temperature to temperature Ti. In some instances, the heat rejection device 56 may be, for example, a radiator, a thermal bath containing a substance such as water or water saltwater, or a device immersed in a natural body of water such as a lake, river or ocean. In some instances, the heat rejection device 56 may also be an air-cooling device or a series of tubes that are thermally connected to a solid reservoir (for example, tubes embedded in the ground).
[00137] In some implementations, the heat rejection to the environment through the use of the thermal storage medium can be used in conjunction with load cycles and / or discharge of variable compression rate described, for example, in Figure 10. In this system, only the CTS medium can exchange heat with the environment. Such a system can also be implemented with a stove to extend
the breaks in temperature of the means from HTS and CTS us cycles. [00138] On some implementations, three tanks of storage in side cold separated in respective
To, T _o ⁺ , and To ⁺ temperatures can be used (for example, an extra tank can be used in addition to tanks 8 and 9). During the heat exchange in the cold side CFX 4 in the discharge cycle, the heat from the working fluid leaving the stove 5 can be transferred to the CTS medium in the T0 ⁺ tank. The means of
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CTS can be cooled in / by, for example, the heat rejection device 55 before entering the T ₀ ⁺ tank. In some implementations, three hot-side storage tanks separated at respective temperatures Ti, T _lr and Tf can be used (for example, an extra tank can be used in addition to tanks 6 and 7). During the exchange of heat in the hot side 2 CFX discharge cycle, heat from the working fluid exiting the recuperator 5 can be transferred to the middle of the HTS T _x tankers. The HTS medium can be cooled in / by, for example, the heat rejection device 56 before entering the -ι-tank. The rejection of heat to the environment in such a way can present several advantages. In a first example, it can eliminate the need for a potentially expensive working fluid for the ambient heat exchanger that is capable of absorbing heat from the working fluid at a rate proportional to the energy input / output of the system. The HTS and CTS media can instead reject heat for extended periods of time, thereby reducing the cost of cooling infrastructure. In a second example, it can allow the decision on when heat is discarded to the environment to be delayed, so that the exchange of heat to room can be carried out when the temperature (for example, the room temperature) is more favorable.
[00139] In the loading and unloading cycles of Figures 13 and 17 and Figures 14 and 18, respectively, the same compression rates and temperature values are used for both loading and unloading. In this configuration, the round trip efficiency can be about Darmazenado = 74%, as given by To = 194 K (-79 ° C), Ti = 494 K (221 ° C). q _t = 0.95, q _c =
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Ο, 9 and r = 3.3.
[00140] Thus, in some examples involving working fluid for recovery of working fluid, heat rejection on the hot (high pressure) side of the closed load cycle can occur in three operations (heat exchange with the HTS medium, followed by recovery, followed by heat rejection to the environment), and heat rejection on the cold side (low pressure) of the closed discharge cycle can occur in three operations (rejection of heat to the environment, followed by recovery, followed by exchange heat with the CTS medium). As a result of recovery, the higher temperature HTS tank (s) 6 may remain at Ti ⁺ while the lower temperature HTS tank (s) 7 may now be at Ti> To ⁺ temperature , and the temperature CTS tank
lowest 9 can remain in To while the tank (s) Highest temperature CTS 8 can now to be in temperature To ⁺ <Ti. [00141] On some cases, the recovery Can be
implemented using heat exchanger 5 for direct heat transfer between the working fluid on the high pressure side and the working fluid on the low pressure side. In an alternative configuration, an additional pair (or plurality) of heat exchangers together with a heat transfer medium or additional fluid (for example, a thermal heat transfer fluid that is liquid in an appropriate temperature range, such as, for example, Therminol®) can be used to achieve recovery. For example, an additional heat exchanger can be added in series with the cold side heat exchanger and an additional heat exchanger can be added
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66/135 added in series with the hot side heat exchanger. The additional heat transfer medium can circulate between the two additional heat exchangers in a closed loop circuit. In other examples, one or more additional heat exchangers can be placed in other parts of the system to facilitate recovery. In addition, one or more additional heat transfer means or mixtures thereof can be used. The one or more additional heat transfer medium fluids can be in fluid or thermal communication with one or more other components, such as, for example, a cooling tower or a radiator.
[00142] In one example, hexane or heptane can be used as a CTS medium and the nitrate salt can be used as an HTS medium. On the low pressure side of the cycle, the operating temperatures of the pumped thermal storage cycles can be limited by the melting point of hexane (178 K or -95 ° C) in To and the melting point of nitrate (494 K or 221 ° C) in Ti. On the high pressure side of the cycle, operating temperatures can be limited by the boiling point of hexane (341 K or 68 ° C) in To ⁺ and by the decomposition of nitrate (873 K or 600 ° C ) in Ti ⁺ . Under these conditions, the high pressure and low pressure temperature ranges can overlap so that recovery can be implemented. Actual To, Ti, To ⁺ and Ti ⁺ temperatures and pressure rates implemented in hexane / nitrate systems may differ from the above limits.
[00143] In some examples, recovery may allow the compression rate to be reduced. In some cases, reducing the compression ratio can result in reduced compressor and turbine losses. In some cases, the rate
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67/135 of compression can be at least about 1.2, at least about 1.5, at least about 2, at least about 2.5, at least about 3, at least about 3.5 , fur
any less fence in 4, fur any less about 4.5 fur any less fence in 5, fur any less fence of 6, at least fence of 8, fur any less fence in 10, fur any less about 15, fur any less fence in 20, fur any less fence of 30 or more.
[00144] On some cases, To Can be fur any less fence in 30 K . (-243.15 ° C) at least about 50K (-223 , 15th Ç) , fur least about 80 K (-193 , 15 ° C), fur any less fence in 100 K (-173.15 ° C) at least about 120K (-153 , 15th Ç) , fur least about 140 K (-133.15 ° C), fur any less fence in 160 K (-113.15 ° C) at least about 180 K (-93 , 15th Ç) , fur least about 200 K (-73 , 15 ° C), fur any less fence in 220 K (-53.15 ° C) at least about 240 K (-33 , 15th Ç) ,
at least about 260 K (-13.15 ° C), or at least about 280 K (6.85 ° C). In some cases, To ⁺ can be at least about 220 K (-53.15 ° C), at least about 240 K (33.15 ° C), at least about 260 K (-13.15 ° C) ), at least about 280 K (6.85 ° C), at least about 300 K (26.85 ° C), at least 320 K (46.85 ° C), at least 340 K (66.85 ° C), at least 360 K (86.85 ° C), at least about 380 K (106.85 ° C), at least about 400 K (126.85 ° C), or more. In some cases, To and To ⁺ temperatures may be restricted by the ability to reject excess heat into the room at room temperature. In some cases, the To and To ⁺ temperatures may be restricted by the CTS operating temperatures (for example, a phase transition temperature). In some cases, the To and To ⁺ temperatures may be restricted by the compression ratio used.
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Any description of the To and / or To ⁺ temperatures here can be applied to any system or method of disclosure.
[00145] In some cases, Ti can be at least about 350 K (76, 85 ° C), at least about 400 K (126, 85 ° C), at least about 440 K (166.85 ° C ), at least about 480 K (206.85 ° C), at least about 520 K (246.85 ° C), at least about 560 K (286.85 ° C), at least about 600 K (326.85 ° C), at least about 640 K (366.85 ° C), at least about 680 K (406.85 ° C), at least about 720 K (446.85 ° C), at least about 760 K (486.85 ° C), at least about 800 K (526.85 ° C), at least about 840 K (566.85 ° C), at least about 880 K (606 , 85 ° C), at least about 920 K (646, 85 ° C), at least about 960 K (686.85 ° C), at least about 1000 K (726.85 ° C), at least about 1100 K (826.85 ° C), at least about 1200 K, at least about 1300 K, at least about 1400 K (1126.85 ° C), or more. In some cases, Ti ⁺ can be at least about 480 K (206.85 ° C), at least about 520 K (246, 85 ° C), at least about 560 K (286, 85 ° C), at least about 600 K (326.85 ° C), at least about 640 K (366, 85 ° C), at least about 680 K (406, 85 ° C), at least about 720 K (446 , 85 ° C), at least about 760 K (486, 85 ° C), at least about 800 K (526, 85 ° C), at least about 840 K (566,85 ° C), at least about 880 K (606, 85 ° C), at least about 920 K (646, 85 ° C), at least about 960 K (686.85 ° C), at least about 1000 K (726.85 ° C), at least about 1100 K (826.85 ° C), at least about 1200 K (926.85 ° C), at least about 1300 K (1026, 85 ° C), at least about 1400 K (1126, 85 ° C), at least about 1500 K (1226.85 ° C), at least about
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1600 K (1326, 85 ° C), at least about 1700 K (1426, 85 ° C), or more. In some cases, Ti and Ti ⁺ temperatures may be restricted by the HTS operating temperatures. In some cases, Ti and Ti ⁺ temperatures can be restricted by the thermal limits of the metals and materials being used in the system. For example, a conventional solar salt may have a recommended temperature range of approximately 560-840 K (286.85 - 566.85 ° C). Various system improvements, such as, for example, greater round-trip efficiency, greater power and greater storage capacity, can be carried out as available materials, metallurgy and storage materials improve over time and allow different temperature ranges to be achieved. Any description of Ti and / or Ti ⁺ temperatures here can be applied to any system or method of disclosure.
[00146] In some cases, the efficiency of round-trip storage (for example, electricity storage efficiency) with and / or without recovery can be at least about 5%, at least about 10%, at least about 15%, at least about 20%, at least about 25%, at least about 30%, at least about 35%, at least about 40%, at least about 45%, at least about 50%, at least about 55%, at least about 60%, at least about 70%, at least about 75%, at least about 80%, at least about 85%, at least about 90%, or at least about 95%.
[00147] In some implementations, at least part of the heat transfer in the system (for example, heat transfer to and from the working fluid) during a charge and / or discharge cycle includes heat transfer
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70/135 with the environment (for example, heat transfer in sections 38 and 39). The rest of the heat transfer in the system can take place through thermal communication with thermal storage medium (for example, thermal storage medium 21 and 22), through heat transfer in the stove 5 and / or through various transfer processes. heat within the system boundaries (ie, not with the surrounding environment). In some instances, the environment may refer to gaseous or liquid reservoirs around the system (for example, air, water), any system or medium capable of exchanging thermal energy with the system (for example, another cycle or thermodynamic system, systems heating / cooling, etc.), or any combination thereof. In some instances, the heat transferred through thermal communication with the heat storage medium can be at least about 25%, at least about 50%, at least about 60%, at least about 70%, at least about 80%, or at least about 90% of all heat transferred in the system. In some instances, the heat transferred through heat transfer in the stove can be at least about 5%, at least about 10%, at least about 15%, at least about 20%, at least about 25% at least about 50%, or at least about 75% of all heat transferred in the system. In some instances, heat transferred through thermal communication with the heat storage medium and through heat transfer in the stove can be at least about 25%, at least about 50%, at least about 60%, at least about 70%, at least 80%, at least about 90%, or even about 100% of all the heat
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71/135 transferred in the system. In some instances, the heat transferred through heat transfer with the environment may be less than about 5%, less than about 10%, less than about 15%, less than about 20%, less than about 30 %, less than about 40% less than about 50%, less than about 60%, less than about 70%, less than about 80%, less than about 90%, less than about 100% or even at 100% of all heat transferred in the system. In some implementations, the entire heat transfer in the system can be with the thermal storage medium (for example, the CTS and HTS medium), and only the thermal storage medium can conduct the heat transfer with the environment.
[00148] The pumped thermal cycles of the disclosure (for example, the cycles in Figures 13 and 14) can be implemented through various configurations of tubes and valves to transport the working fluid between the turbomachinery and the heat exchangers. In some implementations, a valve system can be used so that the different cycles of the system can be exchanged while maintaining the same or almost the same temperature profile in at least one, through a subset or through all heat exchangers. counterflow in the system. For example, the valve can be configured so that the working fluid can pass through the heat exchangers in opposite flow directions in the loading and unloading and flow directions of the HTS and CTS medium are reversed by reversing the direction of the pumps.
[00149] In some implementations, the system with a stove may have a compression and / or expansion rate
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72/135 different in loading and unloading. This can then involve heat rejection at just one or both heat rejection sites 38 and 39 as shown in Figure 5C along the lines described above.
[00150] Figure 19 is a schematic flowchart of recharging the hot side in a heat cycle pumped in solar mode with heating of a solar salt only by solar energy. The system may include a solar heater to heat the heat storage on the hot side. The HTS medium 21 in the second hot thermal storage tank 7 of a discharge cycle, such as, for example, the HTS medium of the discharge cycle in Figure 14, can be recharged inside the element 17 using the radiation-supplied heating solar. The HTS medium (e.g. molten salt) can be heated by solar heating from temperature Ti in the second hot thermal storage tank 7 to temperature Ti ⁺ in the first hot thermal storage tank 6.
[00151] In some implementations, such as, for example, for the systems in Figures 19 solar heat for heating the HTS medium (for example, from Ti = 493 K (220 ° C) to Ti ⁺ = 873 K (600 ° C)) can be supplied by a solar concentration installation. In some instances, a small-scale concentration facility can be used to provide heat. In some cases, the concentrated solar installation may include one or more components to achieve high efficiency of solar concentration, including, for example, high performance actuators (for example, adaptive fluid actuators made from polymers), multiplication control system , layout of
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73/135 dense heliostat, etc. In some examples, the heat supplied to heat the HTS medium (for example, in element 17) can be a residual heat flow from the solar concentration facility.
[00152] Figure 20 is a schematic flowchart of a pumped thermal system discharge cycle that can be coupled with external heat input (for example, solar, combustion) with rejection of heat to the environment. Such a discharge cycle can be used, for example, in situations where the hot side recharge capacity (for example, using solar heating, residual heat or combustion) is greater than the cold side recharge capacity. Solar heat can be used to load the HTS 21 medium into Ti to Ti ⁺ storage tanks, as described here elsewhere. The discharge cycle can work in a similar way to the discharge cycle in Figure 3, but after leaving the turbine 3, the working fluid 20 can proceed to the cold side CFX 4 heat exchanger 4 where it exchanges heat with a medium intermediate thermal storage (ITS) 61 having a temperature below To at or close to room temperature. The ITS medium 61 enters the cold side CFX 4 from a second intermediate thermal storage tank 59 at temperature To (for example, room temperature) and exits the cold side CFX 4 to a first intermediate thermal storage tank 60 at temperature T _± , while the working fluid 20 enters the cold side CFX 4 at temperature T _± and exits the cold side CFX 4 at temperature To. The working fluid enters the compressor 1 in To and P2, leaves the compressor in To ⁺ and Pi, absorbs heat Qi from the medium of HTS 21 in the hot side CFX 2, leaves the hot side CFX 2
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74/135 in Ti + and Pi, enter turbine 3 in Ti + and Pi, exit the turbine in T _± and P2, Q2 rejects heat Q2 from its medium of ITS 61 in the cold side CFX 4, and exits the CFX of cold side 4 to To and P2, returning to their initial state, before entering the compressor.
[00153] In some implementations, the ITS 61 medium can be a liquid over the entire range from To to T _± . In other implementations, the ITS 61 medium may not be liquid over the entire range from To to T _± , but can be supplied to the counterflow heat exchanger 4 at a higher flow rate in order to achieve a lower temperature increase through of the counterflow heat exchanger (for example, such that the temperature of the ITS medium at the outlet of the counterflow heat exchanger 4 is less than T _± ) while cooling the working fluid from T _± to To. In this case, the temperature of the ITS medium in tank 60 can be less than 77 ° C. The ITS medium in tank 60 can exchange heat with the environment (for example, through a radiator or other implementations described here) to cool it back to the To temperature. In some cases, the ITS medium can then be returned to tank 59. In some cases, the heat deposited in the ITS medium can be used for various useful purposes, such as, for example, residential or commercial heating, thermal desalination or other uses described elsewhere elsewhere.
[00154] Figure 21 is a schematic flowchart of a discharge cycle from a thermal system pumped in solar mode or heated combustion mode with heat rejection to an intermediate fluid circulated in a thermal bath at room temperature. The discharge cycle can work
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75/135 similarly to the discharge cycle in Figure 20, but after leaving the turbine 3, the working fluid 20 can proceed to the cold side CFX 4 where it exchanges heat with a medium or intermediate fluid 62 circulating through a thermal bath 63 at To temperature at or close to room temperature. The medium or intermediate fluid 62 (eg Therminol®, or a heat transfer oil) can be used to exchange heat between the working fluid 20 and a thermal bath 63 in the cold side CFX 4. The use of the intermediate fluid 62 can provide an advantage over contact with a heat sink or inexpensive medium (eg water) directly with the working fluid. For example, the direct contact of this thermal medium with the working fluid in the cold side CFX 4 can cause problems, such as, for example, evaporation or over-pressurization (for example, explosion) of the thermal medium. The intermediate fluid 62 can remain in the liquid phase throughout, at least a portion of, or a significant portion of the operation on the cold side CFX 4. When the intermediate fluid 62 passes through the thermal bath 58, it can be sufficiently cooled to circulate back to the cold side CFX 4 to cool the Para to work fluid. The thermal bath 63 can contain a large amount of cheap heat sink material or medium, such as, for example, water. In some cases, the heat deposited on the heat sink material can be used for various useful purposes, such as, for example, residential or commercial heating, thermal desalination or other uses described here elsewhere. In some cases, the heatsink material can be rebalanced at room temperature (for example,
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76/135 example, through a radiator or other implementations described here).
[00155] In some implementations, the discharge cycles in Figures 20 and / or 21 may include a fireplace, as described in more detail in examples throughout the disclosure. Such systems can be implemented using the temperatures Ti ⁺ , Ti, To ⁺ and To, described in more detail elsewhere.
D. Pumped thermal storage cycles assisted by solar energy with intercooling [00156] In some cases, the pumped thermal system may provide heat sources and / or cold sources for other installations or systems, such as, for example, through colocalization with a liquid gas installation (GTL) or a desalination plant. In one example, GTL installations may make use of one or more cold reservoirs in the system (for example, the CTS medium in tank 9 for use in oxygen separation at the GTL installation) and / or one or more hot reservoirs in the system. system (for example, the HTS medium in tank 6 for use in a Fischer-Tropsch process at the GTL facility). In another example, one or more hot reservoirs or one or more cold reservoirs in the pumped thermal system can be used for operating thermal desalination methods. Other examples of possible uses of heat and cold include co-location or heat exchange with building / area heating / cooling systems.
[00157] Conversely, in some cases, the pumped thermal system may use residual heat sources and / or residual cold sources from other installations or systems, such as, for example, by co-location with a
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77/135 import or export of liquefied natural gas. For example, a residual cold source can be used to cool the cold side thermal storage medium 22. In some implementations, the cold side charge using residual cold can be combined with refilling the hot side thermal storage medium 21 by external heat input (eg solar, combustion, residual heat, etc.). In some cases, the refilled storage medium can then be used in a discharge cycle, such as the discharge cycles in Figures 14 or 16. In some cases, the pumped thermal system can be used as a heat engine with a residual heat source that serves as a hot side heat input and as a residual cold source serving as a cold side heat sink. In another implementation, the hot-side storage medium can be recharged using a modified version of the cycle shown in Figure 15, where the temperature To is above the ambient temperature T _o ⁺ and corresponds to a temperature above the ambient temperature. In some instances, a residual heat source can be used to provide the necessary heat at a temperature of at least To ⁺ to heat the working fluid and / or the CTS medium to To ⁺ . In another implementation, an intermediate fluid (for example,
Therminol ®) that can remain liquid in between at temperatures T _o ⁺ and To Can be used for transfer heat from the source of heat residual to fluid in job.E. Systems thermal pumped with pairs in
dedicated compressor / turbine [00158] In an additional aspect of the disclosure,
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78/135 pumped thermal systems are provided comprising multiple working fluid systems, or working fluid flow paths. In some cases, the components of the thermal system pumped in the loading and unloading modes may be the same. For example, the same compressor / turbine pair can be used for loading and unloading cycles. Alternatively, one or more components of the system may differ between loading and unloading modes. For example, separate compressor / turbine pairs can be used for loading and unloading cycles. In one implementation, the system has a set of heat exchangers, and a common set of HTS and CTS tanks that are loaded or unloaded by two pairs or sets of compressors and turbines. In another implementation, the system has a common set of HTS and CTS tanks, but separate sets of heat exchangers and separate sets of compressors and turbines.
[00159] Pumped thermal systems with recovery, use of external sources of heat, cold and / or residual heat / cold can benefit from having separate compressor / turbine pairs as a result of turbomachinery operation over large and / or different temperature ranges in loading and unloading modes. For example, changes in temperature between loading and unloading cycles can lead to a period of thermal adjustment or other difficulties during the transition between cycles (for example, issues or factors related to metallurgy, thermal expansion, Reynolds number, compression rates dependent on temperature, or rolling friction and / or tip clearance, etc.). In another example, turbomachinery (for
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79/135 example, turbomachinery used in systems with recovery) can operate at a relatively low pressure rate (for example, with relatively few compression steps), but at relatively high temperatures during compression and expansion. Temperature ranges can change (for example, change as in Figures 17 and 18) between loading and unloading modes. In some cases, operation over large temperature ranges during compression and / or expansion can complicate the design of a combined compressor / turbine for both loading and unloading. In addition, recovery, incorporation of residual heat / cold and / or other features of the pumped thermal system can reduce the compressor / turbine compression rate in the load cycle and / or the discharge cycle, thus reducing the cost associated with duplication compressor / turbine assemblies.
[00160] Figures 22 and 23 show thermal systems pumped with separate compressor 1 / turbine 3 pairs for load mode C and discharge mode D. The separate compressor / turbine pairs may or may not be grouped on a common mechanical rod . In this example, the compressor / turbine pairs C and D can have separate rods 10. The rods 10 can rotate at the same speed or different speeds. Separate compressor / turbine pairs or working fluid systems may or may not share heat exchangers (for example, heat exchangers 2 and 4).
[00161] In the example in Figure 22, the system has a common set of HTS 6 and 7 tanks and CTS 8 and 9 tanks. The system has separate pairs of heat exchangers 2
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80/135 and 4 and separate pairs of compressor 1 / turbine 3 for charge mode C and discharge mode D. The HTS and CTS storage medium flow paths for the charge cycle are shown as solid black lines. The flow paths of HTS and CTS storage medium for the discharge cycle are shown as dashed gray lines.
[00162] In the example in Figure 23, the system, shown in a load configuration, has a set of heat exchangers 2 and 4, and a common set of HTS 6 and 7 tanks and CTS 8 and 9 tanks. HTS and CTS tanks can be loaded by a compressor / turbine assembly C, or discharged by a compressor / turbine assembly D, each assembly comprising a compressor 1 and a turbine 3. The system can switch between assemblies C and D using valves 83. In the example in Figure 22, the system, again shown in a load configuration, has a common set of HTS 6 and 7 tanks and CTS 8 and 9 tanks. The HTS and CTS tanks can be loaded by charge set C including a first set of heat exchangers 2 and 4, compressor 1 and turbine 3. The HTS and CTS tanks can be discharged by switching to a separate discharge set C that includes a second set of heat exchangers heat 2 and 4, compressor 1 and turbine 3.
[00163] In one example, if the compressor and turbine loading and unloading assemblies in Figures 22 and 23 are not operated at the same time, the loading and unloading assemblies may share a common set of heat exchangers that are switched between the pairs of turbomachinery using valves 83. In another example, if the sets or pairs of turbomachines for loading and unloading in Figures 22 and 23 are
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81/135 operated at the same time (for example, for one set to charge after intermittent generation and the other to be discharged at the same time after charging), then each set of turbomachinery can have a dedicated set of heat exchangers . In this case, the loading and unloading assemblies may or may not share a set of HTS and CTS tanks.
[00164] In some implementations, separate sets or pairs of compressors / turbines can be advantageously used in pumped thermal systems used with intermittent and / or variable electrical inputs. For example, a first compressor / turbine set can be used in a load cycle that follows wind and / or solar energy (for example, electrical input from wind and / or solar power systems) while a second compressor set / turbine can be used in a discharge cycle that follows a charge (for example, electrical power output to an electrical grid). In this configuration, pumped thermal systems placed between a power generation system and a load can assist in smoothing out variations / fluctuations in the input and / or output power requirements.
F. Hybrid pumped thermal systems [00165] According to another aspect of the disclosure, pumped thermal systems can be augmented by additional energy conversion processes and / or can be used directly as energy conversion systems without energy storage (ie is, like power generation systems). In some instances, pumped thermal systems can be modified to allow generation
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82/135 direct energy using natural gas, diesel fuel, petroleum gas (eg propane / butane), dimethyl ether, fuel oil, wood chips, landfill gas, hexane, hydrocarbons or any other combustible substance (for example , fossil fuel or biomass) to add heat to the working fluid on one hot side of a working fluid cycle and a cold heat sink (eg water) to remove heat from the working fluid on one side of the working cycle working fluid.
[00166] Figures 24 and 25 show pumped thermal systems configured in the generation mode. In some examples, the pumped thermal systems can be modified by adding two additional heat exchangers 40 and 41, four additional valves 19a, 19b, 19c and 19d, a heat sink (for example, a water cooling system; water from a freshwater reservoir like a river, a lake or a reservoir, saltwater from a saltwater reservoir like a sea or an ocean, cooling air using radiators, fans / blowers, convection or an environmental heat sink like soil / earth, cold air etc.) 42, and a heat source (for example, a combustion chamber with a mixture of fuel oxidant) 43. Heat source 43 can exchange heat with a first of the two additional heat exchangers 40, and the heat sink 42 can exchange heat with one second of the two additional heat exchangers 41. The heat source 43 can be used to exchange heat with the working fluid 20.
[00167] The heat source 43 can be a source of combustion heat. In some instances, the heat source of
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83/135 combustion can comprise a combustion chamber for the combustion of a combustible substance (for example, a fossil fuel, a synthetic fuel, solid urban residues (MSW) or biomass). In some cases, the combustion chamber may be separated from the heat exchanger 40. In some cases, the heat exchanger 40 may comprise the combustion chamber. The heat source 43 can be a source of residual heat, such as, for example, heat wasted from an electrical plant, an industrial process (e.g., oven exhaust).
[00168] In some examples, a solar heater, a combustion heat source, a residual heat source, or any combination of these, can be used to heat the hot side heat storage fluid and / or the working fluid . In one example, the working fluid can be heated directly using any of these heat sources. In another example, the hot-side heat storage fluid (or HTS medium) can be heated using any of these heat sources. In another example, the hot-side heat storage fluid (or HTS medium) can be heated in parallel with the working fluid using any of these heat sources.
[00169] The thermal systems pumped in Figures 24 and 25 can be operated as hybrid systems. For example, valves 19a, 19b, 19c and 19d can be used to switch between two modes. When the valves are in the first position, the system can operate as a pumped thermal storage system (for example, closed system in charge / discharge mode). In this configuration, working fluid 20 (for example, argon or air) can exchange heat
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84/135 with an HTS medium (eg molten salt) in the hot side heat exchanger 2 and with a CTS medium (eg hexane) in the cold side heat exchanger 4. When the valves are in a Second, the system can operate as a power generation system (for example, open system in generation mode). In this configuration, heat exchangers 2 and 4 can be bypassed, and working fluid 20 can exchange heat with the combustion chamber 43 in the heat exchanger on the hot side 40 and with the heat sink 42 in the heat exchanger on the side. cold 41. The configuration and / or design of heat transfer processes (eg heat transfer in heat exchangers) described here in relation to pumped thermal systems can also be applied to pumped hybrid thermal systems and vice versa. For example, heat sink 42, heat source 43, heat exchangers 40 and 41 and / or the amount of heat transferred on the cold side and / or the hot side can be configured to decrease or minimize the generation of entropy associated with heat transfer processes and / or maximize system efficiency.
[00170] In some implementations, hybrid systems can operate in storage and generation modes simultaneously. For example, valves 19a, 19b, 19c and 19d can be configured to allow a given division between a working fluid flow rate for heat exchangers 40 and 41 and a working fluid flow rate for heat exchangers. heat 2 and 4. Alternatively, hybrid systems can operate exclusively in storage mode, or exclusively
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85/135 in generation mode (for example, as a peak natural gas plant). In some cases, the division between modes can be selected based on the efficiency of the system, input of available electrical energy (for example, based on availability), desired electrical energy output (for example, based on load demand) etc. For example, thermal efficiency of an ideal system (that is, assuming isentropic compression and expansion processes, ideal heat transfer processes) operating exclusively in the generation mode can be the thermal efficiency of a working fluid subjected to a Brayton cycle ideal. In some instances, thermal efficiencies in hybrid disclosure systems (eg, exclusive and / or split operation) can be at least about 10%, at least 20%, at least about 30%, at least about 40 %, at least about 50%, at least about 60%, or more.
[00171] The heat source 43 can be used to exchange heat with an HTS medium (for example, a molten salt). For example, combustion heat source 43 can be used to heat the HTS 21 medium. In some cases, instead of using combustion heat source 43 to exchange heat in heat exchanger 40 or to exchange heat between gases combustion from the combustion heat source and the working fluid, the combustion heat source 43 can be used to heat the HTS 21 medium between the two HTS tanks 7 and 6.
[00172] Figure 26 is a schematic flowchart of hot side recharge in a heat cycle pumped through heating by the heat source 43 (for example, combustion heat source, residual heat source). In one example,
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86/135 heat source 43 is a residual heat source, such as a residual heat source from a refinery or other processing facility. In one example, the heat source 43 is obtained from the combustion of natural gas to ensure the delivery of electricity even if the pumped thermal system runs out of loaded storage medium. For example, recharging the hot-side storage medium using the heat source 43 can provide an advantage over recharging using electricity or other means (for example, the price of electricity at the moment can be very high). The heat source 43 can be used to heat the HTS 21 medium from the Ti temperature in the tank 7 to the Ti ⁺ temperature in the tank 6. The HTS medium can then be used in the CFX 2 to exchange heat with the cooling fluid. work on a discharge cycle, such as, for example, the discharge cycles in Figures 20 and 21.
[00173] In some examples, such as when the CTS medium is a combustible substance, such as a fossil fuel (eg hexane or heptanes), the burning of the CTS medium stored in CTS tanks (eg tanks 8 and 9) can be used to provide thermal energy to heat the HTS medium as shown, for example, in Figure 26 or for operating the cycles in the configurations shown, for example, in Figures 24 and 25.
[00174] The disclosure systems may be able to operate both in an electricity storage cycle only (comprising heat transfer with an HTS medium and a CTS medium below room temperature) and in an ambient cycle heat engine , where, in a discharge mode, heat is inserted from the HTS medium to the
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87/135 working fluid and discharged to the environment instead of to the CTS medium. This capability can allow the use of heating the HTS with combustible substances (for example, as shown in Figure 26) or the use of solar heating of the HTS (for example, as shown in Figure 19). Heat rejection for room temperature can be implemented using, for example, the discharge cycles in Figures 20 and 21. In some cases, heat can be rejected into the environment with the help of ITS 61 medium or intermediate 62 .
[00175] Aspects of disclosure can be combined synergistically. For example, systems capable of operating in either an electricity storage cycle alone or in an ambient cycle heat engine may comprise a stove. Any description regarding such hybrid systems without a stove can be readily applied to hybrid systems with a stove in at least some configurations. In some cases, hybrid systems can be implemented using, for example, the parallel valve configuration in Figure 24. For example, counterflow heat exchangers 4 in Figures 20 and 21 can be implemented as separate counterflow heat exchangers 67 to exchange heat with the environment, and can be used in combination with cold flow counterflow heat exchangers 4 of the disclosure.
[00176] In some implementations, the systems here can be configured to allow switching between different disclosure cycles using a shared set of valves and tubes. For example, the system can be configured
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88/135 to switch between the electricity-only charge cycle (as shown, for example, in Figure 15), the electricity-only discharge cycle (as shown, for example, in Figure 16), and the heat engine for ambient cycle (as shown in Figure 21).
G. Pumped thermal systems with pressure regulating energy control [00177] In one aspect of the disclosure, the pressure of working fluids in pumped thermal systems can be controlled to achieve energy control. In one example, the energy supplied to a closed system in charge mode and / or the energy extracted from the closed system in discharge and / or generation mode (for example, entry / exit of work using rod 10) is proportional to the rate of mass or molar flow of the circulating working fluid. The mass flow rate is proportional to the density, area and speed of flow. The flow speed can be kept fixed in order to achieve a fixed axis speed (for example, 3600 rpm or 3000 rpm according to the requirements of the 60 and 50 Hz electrical grid, respectively). Thus, as the working fluid pressure changes, the mass flow rate and power can change. In one example, as the mass flow increases in a discharge and / or generation mode, more load must be added to the system to maintain a constant speed of the rotating axis, and vice versa. In another example, if the load is reduced during operation in a discharge and / or generation mode, the reduced load can cause the rod speed to increase, thereby increasing the mass flow rate. For some period of time, before the heat stored in the heat capacity of the heat exchangers themselves is
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89/135 dissipated, this increase in the mass flow rate can lead to an increase in the energy supplied, increasing, in turn, the rod speed. Rod speed and energy can continue to increase uncontrollably, resulting in a leakage from the rotating shaft. In some instances, pressure regulation may allow leakage control and thus stabilization, by adjusting the amount (for example, density) of the circulating working fluid, according to the system requirements. In an example where the rod speed (and turbochargers, such as a turbine, connected to the shaft) starts to escape, a controller can reduce the mass of the circulating working fluid (for example, mass flow rate) to decrease energy supplied, in turn, decreasing the rod speed. Pressure regulation can also allow for an increase in the mass flow rate in response to an increase in load. In each of these cases, the flow rates of the HTS and CTS media through the heat exchangers can be adapted to the heat capacity of the working fluid that passes through the heat exchangers.
[00178] In some examples, the working fluid pressure in the closed system can be varied using an auxiliary working fluid tank in fluid communication with the closed system. In this configuration, the energy input / output can be decreased by transferring the working fluid from the closed loop circuit to the tank, and the energy input / output can be increased by transferring the working fluid from the tank to the circuit. closed-loop. In one example, when the working fluid pressure is decreased, less heat can be transferred between
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90/135 thermal storage tanks on the hot and cold sides of the system, as a result of decreased mass flow rate and less energy can be inserted into / emitted by the system.
[00179] As the working fluid pressure is varied, the compression rates of the components of the turbomachine can remain substantially unchanged. In some cases, one or more operating parameters and / or configuration (eg variable stators, rod speed) of the turbomachine components can be adjusted in response to a change in working fluid pressure (for example, to obtain performance system). Alternatively, one or more pressure rates may change in response to a change in working fluid pressure.
[00180] In some cases, the reduced cost and / or the reduced consumption of parasitic energy can be obtained using the energy control configuration in relation to others
settings (per example, using avalve in strangulation for to control the flow of fluid in job). In some examples, the variation gives pressure in working fluid while maintaining is constant The temperature
and the flow velocity (or almost constant) can lead to the generation of negligible entropy. In some instances, an increase or decrease in system pressure can lead to changes, for example, in the efficiency of turbomachinery.
[00181] Figure 27 shows an example of a pumped thermal system with energy control. The temperature of the working fluid on the hot and cold sides of the system can remain constant or almost constant for a given period of time regardless of the mass flow rate
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91/135 of the working fluid due to the large thermal capacities of heat exchangers 2 and 4 and / or the hot and cold side thermal storage medium in tanks 6, 7, 8 and 9. In some examples, flow rates of the HTS and CTS media through heat exchangers 2 and 4 are varied together with a change in working fluid pressure in order to keep temperatures in heat exchangers and working fluid optimized over longer periods of time long. Thus, pressure can be used to vary the mass flow rate in the system. One or more auxiliary tanks 44 filled with working fluid 20 (for example, air, argon or argon-helium mixture) may be in fluid communication with a hot side (for example, high pressure) of the pumped and / or thermal system a cold side (eg low pressure) of the pumped thermal system. In some examples, the auxiliary tank may be in fluid communication with the working fluid adjacent to a compressor 1 inlet and / or adjacent to a compressor 1 outlet. In some examples, the auxiliary tank may be in fluid communication with the fluid working area adjacent to a turbine inlet 3 and / or adjacent to a turbine 3 outlet. In additional examples, the auxiliary tank may be in fluid communication with the working fluid in one or more location systems (for example, one or more more locations on the high pressure side of the system, on the low pressure side of the system, or any combination of them. For example, the auxiliary tank can be in fluid communication with the working fluid on one high pressure side and one side closed cycle low pressure.In some cases, fluid communication on the high pressure side can be provided after the
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92/135 compressor and before the turbine. In some cases, fluid communication on the low pressure side can be provided after the turbine and before the compressor. In some cases, the auxiliary tank may contain working fluid at a pressure intermediate to the high and low system pressures. The working fluid in the auxiliary tank can be used to increase or decrease the amount of working fluid 20 circulating in the closed cycle of the pumped thermal system. The amount of working fluid circulating in the closed cycle can be decreased by draining the working fluid from the high pressure side of the closed cycle into the tank via a fluid path containing a valve or mass flow controller 46, thus loading the tank 44. The amount of working fluid circulating in the closed cycle can be increased by draining the working fluid from the tank to the low pressure side of the closed loop circuit through a fluid path containing a valve or flow controller. mass 45, thus unloading the tank 44.
[00182] Energy control over longer time scales can be implemented by changing the working fluid pressure and adjusting the flow rates of the hot 21 and cold 22 thermal storage fluids via heat exchangers 2 and 4, respectively.
[00183] In some examples, the flow rates of the thermal storage media 21 and / or 22 can be controlled (for example, by a controller) to maintain given inlet and outlet temperatures of the heat exchanger. In some examples, a first controller (s) may be provided to control the flow rates (for example, mass flow rates) of thermal storage medium,
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93/135 and a second controller can be provided to control the mass flow rate (for example, by controlling mass, mass flow rate, pressure, etc.) of the working fluid.
H. Pumped thermal systems with encapsulated pressure engine / generator [00184] In another aspect of the disclosure, pumped thermal systems with an encapsulated pressure engine / generator are provided. The encapsulated pressure engine / generator can be provided as an alternative to configurations where a rod (also crankshaft) penetrates through a working fluid retaining wall (where it can be exposed to one or more relatively high pressure differentials) to connect to a motor / generator outside the working fluid retaining wall. In some cases, the rod may be exposed to working fluid pressures and temperatures in the low pressure portion of the working fluid cycle, the high pressure portion of the working fluid cycle, or both. In some cases, crankshaft seal (s) capable of containing the pressures to which the crankshaft is exposed within the working fluid containment wall can be difficult to manufacture and / or difficult to maintain. In some cases, a rotating seal between high and low pressure environments can be difficult to achieve. Thus, coupling the compressor and turbine to the engine / generator can be challenging. In some implementations, the engine / generator may therefore be placed entirely within the low pressure portion of the working fluid cycle, such that the outer pressure vessel or working fluid retaining wall may not need to be installed. penetrated.
[00185] Figure 28 shows an example of a system
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94/135 thermal pump pumped with an encapsulated pressure generator 11. The motor / generator is encapsulated inside the pressure vessel or working fluid containment wall (shown as dashed lines) and only electrical feed-through conductors 49 penetrate through the pressure vessel. A thermal insulation wall 48 is added between the motor / generator 11 and the working fluid in the low pressure portion of the cycle. The technical requirements for obtaining an adequate seal through the thermal insulation wall may be less stringent because the pressure is the same on both sides of the thermal insulation wall (for example, both sides of the thermal insulation wall may be located in the cycle pressure). In one example, the low pressure value can be approximately 10 atm (1.01325 MPa). In some cases, the engine / generator can be adapted for operation at high surrounding pressures. An additional thermal insulation wall 50 can be used to create a seal between the outlet of the compressor 1 and the inlet of the turbine 3 at the high pressure portion of the cycle. In some instances, placing the engine / generator on the cold side of the pumped thermal systems can be beneficial for engine / generator operation (for example, cooling a superconducting generator).
I. Pumped thermal systems with variable stator pressure rate control [00186] Another aspect of the disclosure concerns the pressure control in working fluid cycles of pumped thermal systems using variable stators. In some instances, the use of variable stators in turbomachinery components can allow pressure rates in
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95/135 working fluid cycles are varied. The variable compression rate can be performed using mobile stators on the turbomachinery.
[00187] In some cases, the pumped thermal systems (for example, the systems in Figures 17 and 18) can operate at the same compression rate in both the loading and unloading cycles. In this configuration, heat can be rejected (for example, to the environment) in section 38 in the charge cycle and in section 39 in the discharge cycle, where the heat in section 38 can be transferred at a lower temperature than the heat in section 39. In alternative configurations, the compression ratio can be varied by switching between the load cycle and the discharge cycle. In one example, variable stators can be added to the compressor and turbine, thus allowing the compression ratio to be adjusted. The ability to vary the compression ratio between loading and unloading modes can allow heat to be rejected only at the lowest temperature (for example, heat can be rejected in section 38 in the load cycle, but not in section 39 of the discharge cycle). In some instances, a greater portion (or all) of the heat discharged into the environment is transferred at a lower temperature, which can increase the efficiency of the system's round-trip.
[00188] Figure 29 is an example of variable stators in a compressor / turbine pair. The compressor 1 and the turbine 3 can have variable stators, so that the compression rate of each can be adjusted. Such an adjustment can increase the efficiency of the round trip.
[00189] The compressor and / or the turbine may (each) include
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96/135 one or more compression stages. For example, the compressor and / or the turbine may have multiple rows of repeated features distributed along its circumference. Each compression stage can include one or more feature lines. The lines can be arranged in a certain order. In one example, compressor 1 and turbine 3 each comprise a sequence of a plurality of input guide vanes 51, a first plurality of rotors 52, a plurality of stators 53, a second plurality of rotors 52 and a plurality Exit guide vanes. 54. Each plurality of features can be arranged in a line along the circumference of the compressor / turbine. The configuration (for example, direction or angle) of stators 53 can be varied, as shown in Figure 29.
[00190] The compressor / turbine pair can be combined.
In some cases, a compressor outlet pressure may be approximately the same as a turbine inlet pressure, and a compressor inlet pressure may be approximately the same as the turbine outlet pressure; thus, the pressure rate through the turbine can be the same as the pressure rate through the compressor. In some cases, inlet / outlet pressures and / or pressure rates may differ by a certain amount (for example, to account for the pressure drop in the system). The use of variable stators in the compressor and turbine can allow the compressor and turbine to remain compatible as the compression rate is varied. For example, using variable stators, compressor and turbine operation can remain within suitable operating conditions (for example, within a certain interval or at a
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97/135 determined point in their respective operational maps) as the compression rate is varied. Operation within specified intervals or at specified points on the turbomachinery operational maps can allow turbomachinery efficiencies (for example, isentropic efficiencies) and the resulting round-trip storage efficiency to be maintained within a desired range. In some implementations, the use of variable stators can be combined with other methods to vary the compression ratios (for example, variable shaft rotation speed, turbomachine stage deviation, gears, power electronics, etc.)
J. Pumped thermal system units comprising pumped thermal system subunits [00191] Another aspect of the disclosure relates to the control of the charge and discharge rate over the entire range from maximum load / energy input to discharge / output of maximum energy through the construction of pumped thermal system units composed of pumped thermal system subunits. In some instances, pumped thermal systems may have a minimum energy input and / or output (for example, minimum energy input and / or minimum energy) above 0% of the maximum energy input and / or output (for example, input maximum energy output and / or maximum energy output), respectively. In such cases, a single unit alone may be able to move continuously from the minimum energy input to the maximum energy input and from the minimum energy output to the maximum energy output, but it may not be able to pass continuously from the input power. minimum energy to the minimum energy output (or
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98/135 (ie from the minimum energy input to the zero energy input / output and the zero energy input / output to the minimum energy output). An ability to pass continuously from the minimum energy input to the minimum energy output can allow the system to continuously transition from the maximum energy input to the maximum energy output. For example, if both the output power and the input power can be turned off to zero during operation, the system can continuously vary the energy consumed or supplied in an interval from the maximum input (for example, acting as a load on the grid) for maximum output (for example, acting as a generator on the grid). Such functionality can increase (for example, more than double) the continuously passable range of the pumped thermal system. Increasing the continuously passable range of the pumped thermal system can be advantageous, for example, when the continuously passable energy range is used as a metric to determine the value of the grid assets. In addition, such functionality may allow the disclosure systems to follow variable load, variable generation, intermittent generation or any combination thereof.
[00192] In some implementations, pumped thermal system units composed of multiple pumped thermal system subunits can be used. In some cases, each subunit may have a minimum energy input and / or output above 0%. The continuous passage of energy from the maximum energy input to the maximum energy output may include the combination of a certain number of subunits. For example, an adequate number (for example, sufficiently large) of subunits may be necessary
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99/135 for continuous acceleration. In some examples, the number of subunits can be at least about 2, 5, 10, 20, 30, 40, 50, 100, 200, 500, 750, 1000 and the like. In some examples, the number of subunits is 2, 5, 10, 20, 30, 40, 50, 100, 150, 200, 250, 300, 350, 400, 450, 500, 550, 600, 650, 700, 750 , 800, 850, 900, 950, 1000 or more. Each subunit can have a certain energy capacity. For example, each subunit may have an energy capacity that is less than about 0.1%, less than about 0.5%, less than about 1%, less than about 5%, less than about 10 %, less than about 25%, less than about 50%, or less than approximately 90% of the total energy capacity of the compound pumped thermal system. In some cases, different subunits may have different energy capacities. In some examples, a subunit has an energy capacity of about 10 kW, 100 kW, 500 kW, 1 MW, 2 MW, 5 MW, 10 MW, 20 MW, 50 MW, 100 MW or more. The continuous passage of energy from the maximum energy input to the maximum energy output may include controlling the input and / or output of each subunit (for example, power input and / or power output) separately. In some cases, subunits can be operated in opposite directions (for example, one or more subunits can operate in power input mode, while one or more subunits can operate in power output mode). In one example, if each subunit of the pumped thermal system can be continuously passed between a maximum energy input and / or output down to about 50% of the maximum energy input and / or output, respectively, three or more system subunits thermal
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100/135 combined in a composite pumped thermal system unit that can be continuously passed from the maximum energy input to the maximum energy output. In some implementations, the composite pumped thermal system may not have an entirely continuous interval between the maximum input energy and the maximum output energy, but it may have a greater number of operating points in this interval compared to a non-composite system.
K. Energy storage system units comprising energy storage system subunits [00193] Another aspect of the disclosure relates to controlling the charge and discharge rate over a complete range from the maximum charge / energy input to the maximum discharge / energy output by building composite energy storage system units consisting of energy storage system subunits. In some examples, energy storage systems may have a minimum energy input and / or output (for example, minimum energy input and / or minimum energy output) above 0% of the maximum energy input and / or output (for example, maximum energy input and / or maximum energy output), respectively. In such cases, a single unit alone may be able to move continuously from the minimum energy input to the maximum energy input and from the minimum energy output to the maximum energy output, but it may not be able to pass continuously from the input power. minimum energy for the minimum energy output (that is, the minimum energy input for the zero energy input / output and the zero energy input / output for the
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101/135 minimum energy). An ability to move continuously from the minimum power input to the minimum power output can allow the system to move continuously from the maximum power input to the maximum power output. For example, if both the output power and the input power can be completely reset to zero during operation, the system can continuously vary the energy consumed or supplied in an interval from the maximum input (for example, acting as a load in the grid) to the maximum output (for example, acting as a generator in the grid). Such functionality can increase (for example, more than double) the continuously passable interval of the energy storage system. Increasing the continuously passable range of the energy storage system can be advantageous, for example, when the continuously passable range of energy is used as a metric to determine the value of the grid assets. In addition, such functionality may allow the disclosure systems to follow variable load, variable generation, intermittent generation or any combination thereof.
[00194] In some implementations, composite energy storage system units composed of several energy storage system subunits can be used. In some instances, any energy storage system with energy input / output capabilities that can benefit from a composite configuration can be used. In some examples, systems with power input and / or output capabilities that can benefit from a composite configuration may include multiple storage and / or power generation systems, such as
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102/135 natural gas or combined cycle power plants, fuel cell systems, battery systems, compressed air energy storage systems, pumped hydroelectric systems, etc. In some cases, each subunit may have a minimum energy input and / or output above 0%. The continuous passage of energy from the maximum energy input to the maximum energy output may include the combination of a number of subunits. For example, an adequate number (for example, sufficiently large) of subunits may be necessary to achieve continuous acceleration. In some examples, the number of subunits can be at least about 2, 5, 10, 20, 30, 40, 50, 100, 200, 500, 750, 1000 and the like. In some examples, the number of subunits is 2, 5, 10, 20, 30, 40, 50, 100, 150, 200, 250, 300, 350, 400, 450, 500, 550, 600, 650, 700, 750 , 800, 850, 900, 950, 1000 or more. Each subunit can have a certain energy capacity. For example, each subunit may have an energy capacity of less than about 0.1%, less than about 0.5%, less than about 1%, less than about 5%, less than about 10%, less than about 25%, less than about 50%, or less than about 90% of the total energy capacity of the composite energy storage system. In some cases, different subunits may have different energy capacities. In some examples, a subunit has an energy capacity of about 10 kW, 100 kW, 500 kW, 1 MW, 2 MW, 5 MW, 10 MW, 20 MW, 50 MW, 100 MW or more. The continuous passage of energy from the maximum energy input to the maximum energy output may include control of the input and / or output of each subunit (eg
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103/135 example, power input and / or power output) separately. In some cases, subunits can be operated in opposite directions (for example, one or more subunits can operate in power input mode, while one or more subunits can operate in power output mode). In one example, if each subunit of the energy storage system can be continuously passed between a maximum energy input and / or output up to about 50% of the maximum energy input and / or output, respectively, three or more of these energy subunits Energy storage system can be combined into a composite energy storage system unit that can be continuously passed from the maximum energy input to the maximum energy output. In some implementations, the composite energy storage system may not have an entirely continuous interval between the maximum energy input and the maximum energy output, but it may have an increase in the number of operating points in that interval compared to a non-energy system. compound.
L. Control Systems [00195] This disclosure provides computer control systems (or controllers) that are programmed to implement methods of the disclosure. Figure 30 shows a 1901 computer system (or controller) that is programmed or otherwise configured to regulate various process parameters of energy storage and / or recovery systems disclosed herein. Such process parameters can include temperatures, flow rates, pressures and changes in entropy.
[00196] The 1901 computer system includes a drive
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104/135 central processing (CPU, also processor and computer processor here) 1905, which can be a single-core or multiple-core processor, or a plurality of processors for parallel processing. The 1901 computer system also includes memory or 1910 memory location (for example, random access memory, read-only memory, flash memory), 1915 electronic storage unit (for example, hard disk), 1920 communication interface (for example, example, network adapter) for communication with one or more other 1925 systems and peripheral devices, such as cache, other memory, data storage and / or electronic video adapters. Memory 1910, storage unit 1915, interface 1920 and peripheral devices 1925 are in communication with the 1905 CPU through a communication bus (solid lines), such as a motherboard. The 1915 storage unit can be a data storage unit (or data repository) for data storage. The 1901 computer system can be operationally coupled to a 1930 computer network (network) with the aid of the 1920 communication interface. The 1930 network can be the Internet, an internet and / or extranet, or an intranet and / or extranet that is in communication with the Internet. The 1930 network, in some cases, is a telecommunications and / or data network. The 1930 network can include one or more computer servers, which can allow for distributed computing, such as cloud computing. The 1930 network, in some cases with the aid of the 1901 computer system, can implement a peer-to-peer network, which can allow devices coupled to the 1901 computer system to behave like a
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105/135 client or a server.
[00197] The 1901 computer system is coupled with a 1935 energy storage and / or recovery system, which can be as described above or elsewhere in this document. The 1901 computer system can be coupled with various unit operations of the 1935 system, such as flow regulators (for example, valves), temperature sensors, pressure sensors, compressor (s), turbine (s), electric switches and photovoltaic modules. The 1901 system can be directly coupled, or be part of the 1935 system, or be in communication with the 1935 system through the 1930 network.
[00198] The 1905 CPU can execute a sequence of machine-readable instructions, which can be incorporated into a program or software. Instructions can be stored in a memory location, such as 1910 memory. Examples of operations performed by the 1905 CPU may include searching, decoding, executing and writing back.
[00199] With continued reference to Figure 30, the storage unit 1915 can store files, such as controllers, libraries and saved programs. The 1915 storage unit can store user-generated programs and recorded sessions, as well as output (s) associated with the programs. The 1915 storage unit can store user data, for example, user preferences and user programs. The 1901 computer system may in some cases include one or more additional data storage units that are external to the 1901 computer system, as located on a remote server that is communicating with the 1901 computer system via a
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106/135 intranet or the Internet.
[00200] The 1901 computer system can communicate with one or more remote computer systems over the 1930 network. For example, the 1901 computer system can communicate with a user's remote computer system (eg operator). Examples of remote computer systems include personal computers, slate or tablet PCs, phones, smart phones, or personal digital assistants. The user can access the 1901 computer system through the 1930 network.
[00201] The methods described here can be implemented by executable code per machine (for example, computer processor) stored in an electronic storage location of the 1901 computer system, such as, for example, in the 1910 memory or storage unit electronic 1915. Machine-executable or machine-readable code can be provided in the form of software. During use, the code can be executed by the 1905 processor. In some cases, the code can be retrieved from the 1915 storage unit and stored in the 1910 memory for immediate access by the 1905 processor. In some situations, the 1915 electronic storage unit can deleted, and machine executable instructions are stored in 1910 memory.
[00202] The code can be precompiled and configured for use with a machine that has a processor adapted to execute the code, or can be compiled during the execution time. The code can be provided in a programming language that can be selected to allow the code to be executed in a pre-defined manner
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107/135 compiled or as-compiled.
[00203] Aspects of the systems and methods provided here, such as the 1901 computer system, can be incorporated into the programming. Various aspects of technology can be considered as products or articles of manufacture typically in the form of machine executable code (or processor) and / or associated data that are transported or incorporated into a machine-readable type of medium. Machine executable code can be stored on an electronic storage unit, such as memory (for example, read-only memory, random access memory, flash memory) or a hard disk. The Storage medium can include any or all of the tangible memory of computers, processors or the like, or associated modules, such as various semiconductor memories, tape drives, disk drives and the like, which can provide non-transitory storage at any time for storage. software programming. All or part of the software can sometimes be communicated via the Internet or several other telecommunications networks. Such communications, for example, may allow software to be loaded from one computer or processor to another, for example, from a management server or host computer to an application server's computer platform. Thus, another type of medium that may contain the software elements includes optical, electrical and electromagnetic waves, such as those used in physical interfaces between local devices, through terrestrial wired and optical networks and through various aerial links. The physical elements that carry such waves, such as wired or wireless connections,
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108/135 optical connections or similar, can also be considered as means that support the software. As used herein, unless restricted to tangible non-transitory storage media, terms such as a computer or machine-readable medium refer to any medium that participates in providing instructions to a processor for execution.
[00204] Thus, a machine readable medium, such as computer executable code, can take many forms, including, but not limited to, a tangible storage medium, a carrier wave medium or physical transmission medium. Non-volatile storage media include, for example, optical or magnetic disks, such as any of the storage devices on any computer (s) or the like, as can be used to implement the databases, etc. shown in the drawings. Volatile storage media include dynamic memory, like the main memory on such a computer platform. Tangible means of transmission include coaxial cables; copper wire and fiber optics, including the wires that make up a bus within a computer system. The carrier wave transmission means can take the form of electrical or electromagnetic signals, or acoustic or light waves, such as those generated during radio frequency (RF) and infrared (IR) data communications. Common forms of computer-readable medium include, for example: a floppy disk, a floppy disk, hard disk, magnetic tape, any other magnetic medium, a CD-ROM, DVD or DVD-ROM, any other optical medium, paper tape punched cards, any other physical storage medium with hole patterns, a
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RAM, a ROM, a PROM and EPROM, a FLASH-EPROM, any other chip or memory cartridge, a carrier wave carrying data or instructions, cables or links carrying such a carrier wave, or any other medium from which a computer can read programming code and / or data. Many of these forms of computer-readable media can be involved in transporting one or more sequences of one or more instructions to a processor for execution.
III. Illustrative inventory control systems [00205] Figure 31 illustrates an example of a closed loop system, for example, a closed Brayton system, and includes a working fluid that flows through at least one compressor 101, a heat exchanger hot-side 102, a turbine 103 and a cold-side heat exchanger 104. A storage medium can flow between a cold-side storage container (CSC) 106 and a hot-side storage container (HSC) 107 through the hot-side heat exchanger 102. Another thermal storage medium can flow between at least CSC 108 and HSC 109 through cold-side heat exchanger 104. The fluid paths are as shown in Figure 31 and the flow direction of a fluid in a given fluid path is indicated by one or more arrows. Each of the fluids, components and / or fluid paths identified above can be the same or similar to the closed cycle described above (for example, Brayton cycle), as working fluid 20, compressor 1, hot-side heat exchanger 2 , turbine 3, cold side heat exchanger 4, medium of HTS 21, tank of HTS 7, tank of HTS 6, medium of
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CTS 22, CTS 8 tank and CTS 9 tank. Figure 31 is only illustrative and other fluids, components and / or fluid paths may be present. Some components, such as a heat exchanger or hot or cold side tanks, can be replaced with other components that have a similar thermal purpose.
[00206] In particular, Figure 31 illustrates an inventory control system 100 implemented in a Brayton cycle heat engine. System 100 may include several pumps (for example, variable speed pumps) configured to pump fluid to, through, or from
components of system. For purposes of illustration, the pumps are not shown in Figure 31. [00207] 0 engine heat can be reversible (this is, operate as a bomb of heat) and you can take the form of
other heat engines and / or reversible heat engines described here and may include additional components in addition to those shown in the illustration, including a stove. The heat engine may include a generator / engine 111 that can generate electricity and distribute some or all of the generated electricity to a grid system, including a local, municipal, regional or national grid. When the heat engine is in power generation mode (i.e., discharge mode), generator / engine 111 can also practically be referred to only as a generator, since it can function primarily or entirely as a device for generating electricity. Generator / engine 111, as illustrated, can include an alternator, a high speed alternator and / or power electronics (e.g., power frequency conversion electronics) to manage,
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111/135 convert and / or modify electrical phase, voltage, current and frequency of energy generated and / or distributed. The generator / engine 111 can be mechanically coupled to compressor 101 and turbine 103. Compressor 101 and turbine 103 can be coupled to generator / engine 111 via one or more rods 110. Alternatively, compressor 101 and turbine 103 they can be coupled to the generator / engine 111 through one or more gearboxes and / or rods.
[00208] The heat engine may include a hot-side heat exchanger 102 coupled downstream of the compressor 101 and upstream of the turbine 103. Furthermore, the heat engine may include a cold-side heat exchanger 104 coupled upstream compressor 101 and downstream of turbine 103. In the heat engine, a working fluid can circulate through a closed-loop fluid path that includes, in sequence, compressor 101, hot-side heat exchanger 102, a turbine 103 and cold-side heat exchanger 104. In some embodiments, closed-loop fluid path may include a stove. The closed-loop fluid path can include a high-pressure leg 201 and a low-pressure leg 202. The high-pressure leg 201 can include all or a portion of the closed-loop fluid path downstream of compressor 101 and upstream of the turbine 103. The low pressure leg 202 may include all or part of the closed-loop fluid path upstream of the compressor 101 and downstream from the turbine 103. The pressure of the working fluid in the high pressure leg 201 may be greater than the working fluid pressure in the low pressure leg 202. Non-limiting examples of working fluids include air, argon, carbon dioxide
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112/135 or gas mixtures.
[00209] Within the hot-side heat exchanger 102, the working fluid circulating through the closed-loop fluid path can thermally contact a hot-side thermal storage medium (HTS). Preferably, the HTS medium can be a molten salt. The hot-side heat exchanger 102 can be a counterflow heat exchanger. An HSC 107 can be coupled to the hot side heat exchanger 102. In addition, a CSC 10 6 can be coupled to the hot side heat exchanger 102. When the heat engine operates in power generation mode, a pump connected between the hot-side heat exchanger 102 and HSC 107 can pump the HTS medium from the HSC 107, through the hot-side heat exchanger 102 and to the CSC 106. Alternatively, when the heat engine operates as a pump heat in an energy storage mode (ie charge mode), the pump can be connected between the hot-side heat exchanger 102 and the CSC 106, and can pump the HTS medium from the CSC 106, via hot-side heat exchanger 102, and for HSC 107. Also, as used here, hot storage and cold storage are used to reflect relative temperatures between storage containers that can share a common thermal storage medium and do not refer to you need to places inside a hot or cold side of a heat engine or heat pump.
[00210] Inside the cold side heat exchanger 104, the working fluid circulating through the closed cycle fluid path can come into thermal contact with a cold side thermal storage (CTS), which can be
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113/135 different from the HTS medium. Preferably, the CTS medium can be an alkane, such as hexane. The cold-side heat exchanger 104 can be a counterflow heat exchanger. A CSC 108 can be coupled to the cold side heat exchanger 104. In addition, an HSC 109 can be coupled to the cold side heat exchanger 108. When the heat engine operates in power generation mode, a pump is started between the cold side heat exchanger 104 and the CSC 108 can pump the CTS medium from the CSC 108, through the cold side heat exchanger 104, and to the HSC 109. Alternatively, when the heat engine operates as a heat pump in energy storage mode, a pump can be connected between the cold side heat exchanger 104 and the HSC 109, and can pump the CTS medium from the HSC 109, through the heat exchanger 104 and for CSC 108.
[00211] The heat engine can include a second compressor 120 and a dehumidifier 121. The second compressor 120 can be attached to the low pressure leg 202 and dehumidifier 121 can be attached to the low pressure leg 202. As shown, the dehumidifier 121 is located downstream of the second compressor 120 and upstream of the low pressure leg 202. However, in other examples, dehumidifier 121 may be located upstream of the second compressor 120. Valves 122 and 123 may be located between the second compressor 120 and the low pressure leg 202. In addition, valves 122 and 123 can be located between dehumidifier 121 and the low pressure leg 202.
[00212] The second compressor 120 can be configured
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114/135 to, on demand, compress ambient air and inject compressed ambient air into the low pressure leg 202. In addition, dehumidifier 121 can be configured to dehumidify ambient air.
[00213] As shown, the second compressor 120 is configured to, on demand, inject compressed ambient air into the low pressure leg 202 downstream of the cold side heat exchanger 104 and upstream from the compressor 101. However, in other examples, the second compressor 120 can be configured, on demand, to inject compressed ambient air into other locations of the low pressure leg 202, including, without limitation, upstream of the cold side heat exchanger 104 and downstream of the turbine 103 .
[00214] Furthermore, as shown, the second compressor 120 supplies compressed ambient air to dehumidifier 121 for dehumidification. Thus, in the illustrated example, the ambient air is dehumidified after the ambient air is compressed. However, in other examples, dehumidifier 121 can supply dehumidified ambient air to the second compressor
120 for compression. For example, when the dehumidifier
121 is located upstream of the second compressor 120, the dehumidifier 121 can supply dehumidified ambient air to the second compressor 120 for compression. Thus, in some instances, the ambient air can be dehumidified before the ambient air is compressed.
[00215] Inside dehumidifier 121, the ambient air can thermally contact a portion of the CTS medium. For example, a pump can be located between dehumidifier 121 and CSC 108 and can pump the portion of
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115/135 CTS medium from CSC 108, through dehumidifier 121, and to HSC 109 or elsewhere, including back to CSC 108. Upon thermal contact with ambient air with a portion of the CTS medium, the water can condense out of the ambient air. Condensing the water out of the ambient air before injecting the ambient air into the low pressure leg 202 can reduce corrosion of one or more components in the closed cycle fluid path and / or prevent a change in thermal capacity and / or expansion of the working fluid.
[00216] Alternatively, the heat engine can include an intermediate CTS storage container (ISC) 124 and a pump can be located between dehumidifier 121 and CSC 108 and can pump the CTS medium portion from CSC 108, through the dehumidifier, and to ISC 124 (as shown by the dashed fluid flow path). ISC 124 can store the CTS medium at a temperature between the temperature of the CTS medium stored in the HSC 109 and the temperature of the CTS medium stored in the CSC 108. For example, the ISC 124 can store the CTS medium at a temperature which is (i) lower than the temperature of the CTS medium stored in the HSC 109 and (ii) higher than the temperature of the CTS medium stored in the CSC 108.
[00217] In some implementations, ambient air can be filtered before being injected into the low pressure leg 202. For example, dehumidifier 121 may include a filter element (not shown) that is configured to filter out impurities from ambient air . In another example, the filter element can be a separate component upstream of the low pressure leg 202. The separate filter element can be upstream of the second compressor
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120 or downstream of the second compressor 120. In addition, the separate filter element can be upstream of dehumidifier 121 or downstream of dehumidifier 121.
[00218] 0 heat engine can include one tank in storage in fluid job 130. 0 tank in storage in working fluid 130 can to be a tank
pressure. The working fluid storage tank 130 can be coupled to the high pressure leg 201 and the low pressure leg 202. The valve 132 can be located between the high pressure leg 201 and the working fluid storage tank 130. In addition in addition, valves 133 and 123 can be located between the low pressure leg 201 and the working fluid storage tank 130. As illustrated, the working fluid tank 130 shares a common fluid path and valves 123 and 133 with the path of injected ambient air; however, the working fluid tank may have a connection point and valve system separate from the injected ambient air path.
[00219] Each of the valves 122, 123, 132 and 133 can be any suitable valve capable of allowing and blocking the flow of working fluid and / or ambient air, including a gate valve, globe valve, plug valve, ball valve, butterfly valve, check valve, pinch valve and diaphragm valve. In some embodiments, valves 122, 123, 132 and 133 can each be the same type of valve. However, in other embodiments, at least two of the valves 122, 123, 132 and 133 can be different types of valves.
[00220] The heat engine may also include an expansion valve 140 and may also include a heat exchanger
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Auxiliary heat exchanger 141. The auxiliary heat exchanger 141 may be a counterflow heat exchanger. Expansion valve 140 may be downstream of cold-side heat exchanger 104 and upstream of compressor 101. Expansion valve 140 may be located elsewhere in the closed-loop fluid path, including upstream of the heat exchanger cold side 104 and downstream of turbine 103. Expansion valve 140 can be configured to expel working fluid from the closed cycle fluid path. Auxiliary heat exchanger 141 may be downstream of expansion valve 140.
[00221] Within the auxiliary heat exchanger 141, the working fluid flowing through the expansion valve 140 can thermally contact a portion of the CTS medium. For example, a pump can be located between auxiliary heat exchanger 141 and HSC 10 9 and can pump a portion of the CTS medium from HSC 10 9, through auxiliary heat exchanger 141, and back to HSC 109 As other examples, working fluid flowing through expansion valve 140 can thermally contact the CTS medium from CSC 108 or ISC 124 (not shown). In addition or alternatively, the working fluid flowing through the auxiliary heat exchanger 141 can be released (e.g., vented) into the atmosphere.
[00222] The sensors can be located in several places along the heat engine or external to the heat engine. The sensors can be configured to determine and / or report one or more operating conditions inside or outside the system. In the examples of modalities illustrated in Figure 31, the pressure sensors can be located in
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118/135 various entries and freckles for components within the system. For example, the pressure sensor 154 can determine and report the working fluid pressure in the high pressure leg 201, the pressure sensor 155 can determine and report the working fluid pressure in the low pressure leg 202 and the pressure sensor pressure 156 can determine and report working fluid pressure in working fluid storage tank 130. In addition, in the example modalities illustrated in Figure 31, temperature sensors can be located at various inlets and outlets for components within the system . For example, temperature sensor 157 can determine and report the temperature of the compressed ambient air, temperature sensor 158 can determine and report the temperature of the CTS medium downstream of dehumidifier 121 and temperature sensor 159 can determine and report the working fluid temperature downstream of expansion valve 140. As illustrative examples, operating conditions may include sensor readings (for example, working pressure on high pressure leg 201) and / or a combination of sensor readings, and / or a derived value based on sensor readings (for example, difference between the working fluid pressure in the high pressure leg 201 and the working fluid pressure in the low pressure leg 202). In practical application, the illustrated sensors can reflect multiple sensors in a fluid path (for example, pressure sensor 154 can be two or more sensors in the high pressure leg 201).
[00223] Alternatively or additionally, other types of sensors that determine and / or report one or more conditions
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119/135 operating systems can be located throughout the illustrated system. The sensor 150 can connect to the generator / engine ill and to several discrete components included in it, such as alternators and / or power electronics. The sensor 150 can also connect to an electrical power connection between the generator / engine ill and the electrical grid to which the generator / engine 111 is supplying electrical power. The sensor 150 can determine and report current, voltage, phase, frequency and / or the amount of electrical energy generated and / or distributed by the generator / motor 111 and / or its associated discrete components. Sensor 151 can determine and report the phase of the network and sensors 150 and 151 can together or in combination determine and report a phase difference between the generated electrical energy and the grid. Sensor 152a can determine and report the turbine torque, turbine RPM, generator torque and / or generator RPM. If rod 110 is a common rod and not a split rod between turbine 103 and compressor 101, then sensor 152a can also determine and report the compressor torque and / or the compressor RPM. Alternatively, sensor 152b can determine and report the compressor torque and / or the compressor RPM.
[00224] Each of the valves 122, 123, 132, 133 and 140 can be connected to one or more control devices. For example, valves 122, 123, 132, 133 and 140 can be connected to control device 162. In some implementations, control device 162 can be connected wirelessly to valves 122, 123, 132, 133 and 140 Control device 162 can be configured to operate valves 122 and 123 to control the flow of compressed ambient air to low pressure leg 202.
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Thus, control device 162 may be able to operate valves 122 and 123 to (i) allow the flow of compressed ambient air to the low pressure leg 202 and (ii) block the flow of compressed ambient air to the pressure leg. low pressure 202. Similarly, control device 162 may be able to operate valves 133 and 123 to (i) allow the flow of working fluid from working fluid storage tank 130 to the lower leg pressure 202 and (ii) block the flow of working fluid from the working fluid storage tank 130 and low pressure leg 202. In addition, control device 162 may be able to operate expansion valve 140 to expel working fluid from the closed cycle fluid path. Although the heat engine is described as including control device 162, in other examples, a heat engine can include multiple control devices with independent or coordinated control over valves 122, 123, 132, 133 and 140.
[00225] Control device 162 may be in communication with controller 164. Controller 164 may be able to direct control device 162 to operate, as non-limiting examples, (i) valves 122 and 123 to change a quantity flow rate of compressed ambient air, (ii) valves 133 and 123 for changing a quantity of working fluid flow and (iii) expansion valve 140 for expelling working fluid from the closed-cycle fluid path. For example, controller 164 may be able to issue an instruction to control device 162 to open or close valves 122 and 123 for a specified amount (for example,
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121/135 open, partially open, closed, partially closed). Controller 164 can be any practical form known in the art, including those commonly used in industrial control systems, such as PLC controllers. In addition, controller 164 may be in communication with second compressor 120. Although the heat engine is described as including controller 164, in other examples, a heat engine may include multiple controllers with independent or coordinated control over valves 122, 123, 132, 133 and 140.
[00226] Controller 164 can also be in communication with one or more of the sensors. For clarity of illustration, the connections are not shown in Figure 31 between controller 164 and each of the illustrated sensors with which controller 164 may be in communication, but it should be understood that controller 164 may be able to receive sensor data from a relevant sensor. Controller 164 can communicate with and receive data from the sensors in any practical manner, including wired electrical data communication, wireless data communication, optical transmission and / or intermediate sources, or through other ways known in the art.
[00227] Controller 164 may be able to compare calculated data or reported data from one or more sensors with reported data from one or more other sensors, historical sensor data, internal settings or other comparators. For example, controller 164 can compare reported data from at least two of sensors 150, 151, 152a, 152b, 154, 155, 156, 157, 158 and 159. Additionally, controller 164 can determine a phase difference between
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122/135 generated electrical energy and grid energy for comparing reported data from sensors 150 and 151.
[00228] In some implementations, a heat engine may also include one or more reciprocating heat exchangers (or stoves) that can transfer heat between the working fluid at various stages within the closed cycle flow path. Preferably, the recuperative heat exchanger is a counterflow heat exchanger. In one example, the recuperative heat exchanger thermally contacts the working fluid downstream of the compressor and upstream of the hot side heat exchanger with the working fluid downstream of the turbine and upstream of the cold side heat exchanger, in preferably counterflow.
[00229] In a heat engine that includes a recuperative heat exchanger, the working fluid can circulate through a closed loop circuit that includes, in sequence, the compressor, the recuperative heat exchanger, the side heat exchanger hot, the turbine, the recuperative heat exchanger again (in thermal counterflow contact with the previous flow), the cold side heat exchanger, and back to the compressor. There may be no reciprocating heat exchangers in a heat engine, or there may be more than one recuperative heat exchanger in a heat engine and one or more reciprocating heat exchangers may be located in alternate locations than the location within the scheme. circulation described above.
A. Example of injection of ambient air into the closed-loop fluid path [00230] Using the illustration in Figure 31, a working fluid can be circulated through the fluid path
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123/135 closed cycle which includes, in sequence, compressor 101, hot side heat exchanger 102, turbine 103 and cold side heat exchanger 104. The cycle fluid path includes the high pressure leg 201 and the low pressure leg 202. In some instances, the working fluid may be air.
[00231] In an example of a modality, the inventory control in system 100 may involve, in response to an increased demand for energy generation, compressing and dehumidifying the ambient air; and injecting the compressed and dehumidified ambient air into the low pressure leg 202.
[00232] The demand for increased power generation can be received or determined by one or more components of the system 100. As an example, the demand for increased power generation can be received by controller 164. Controller 164 can receive demand for increased energy generation from, for example, the grid system. As another example, the demand for increased power generation can be determined by controller 164. Controller 164 can determine the demand for increased power generation based on any of the operating conditions described above, including turbine torque, turbine RPM, generator torque and generator RPM; and current, voltage, phase, frequency and / or amount of electrical energy generated and / or distributed by the generator and / or its discrete components. In addition, the demand for increased power generation can occur when any of the operating conditions described above reaches a threshold demand value.
[00233] In addition, in some implementations, in response to the demand for increased energy generation, the
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124/135 controller 164 can instruct the second compressor 120 to compress ambient air and inject the compressed ambient air into the low pressure leg 202. The second compressor 120 can compress the ambient air, such that the ambient air pressure is equal to or greater than the working fluid pressure in the low pressure leg 202. In addition, in response to the demand for increased power generation, controller 164 can instruct control device 162 to open valves 122 and 123 to allow ambient air to flow compressed for low pressure leg 202.
[00234] In addition, in response to the demand for greater energy generation, dehumidifier 121 can dehumidify ambient air. Dehumidifier 121 can dehumidify ambient air by making thermal contact with ambient air with a portion of the CTS medium and condensing water out of ambient air. Other dehumidification methods are also considered, including, without limitation, non-CTS coolers, external coolers and absorption / desiccants.
[00235] In another example embodiment, the inventory control in system 100 may involve the extraction of working fluid from the high pressure leg 201 of the closed cycle fluid path; storing the extracted working fluid in the working fluid storage tank 130; and injecting the working fluid extracted from the working fluid storage tank 130 into the low pressure leg 202 simultaneously with the injection of compressed and dehumidified ambient air into the low pressure leg 202.
[00236] In one embodiment, the working fluid can be extracted from the closed cycle fluid path by opening the
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125/135 hot-side valve 132, such that the working fluid pressure in the high pressure leg 201 decreases and the working fluid pressure in the tank 130 increases. When the hot side valve 132 is open, the cold side valve 133 can be closed.
[00237] The hot side valve 132 can be opened by the control device 162. For example, controller 164 can instruct the control device 162 to open the hot side valve 132 when the working fluid pressure in the high leg pressure 201 or the low pressure leg 202 reaches a threshold pressure value. In addition, controller 164 can determine an operating condition of system 100 and the threshold pressure value can be set based on the determined operating condition. The threshold pressure value can be set based on any of the operating conditions described above. As another example, controller 164 can instruct control device 162 to open hot-side valve 132 in response to a demand for reduced power generation. (Example demands for reduced power generation are described below in Section III.B).
[00238] In addition, the hot-side valve 132 can be closed by the control device 162. For example, controller 164 can instruct the control device 162 to close the hot-side valve 132 when the working fluid pressure in the storage tank 130 reaches a threshold pressure value. The threshold pressure value can be defined, for example, as an equilibrium pressure between the working fluid pressure in the high pressure leg 201 and the working fluid pressure in the tank
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126/135 working fluid storage 130 or as a pressure less or greater than an equilibrium pressure between the working fluid pressure in the high pressure leg 201 and the working fluid pressure in the fluid storage tank work 130. In addition, controller 164 can determine an operating condition of system 100 and the threshold pressure value can be set based on the determined operating condition. The threshold pressure value can be set based on any of the operating conditions described above. In some embodiments, the threshold pressure value related to the opening of the hot side valve 132 may differ from the threshold pressure value related to the closing of the hot side valve 132. In addition, the working fluid storage tank 130 can store the extracted working fluid when the hot-side valve 132 and the cold-side valve 133 are each closed.
[00239] In another embodiment, the extracted working fluid can be injected from the working fluid storage tank 130 into the low pressure leg 202 simultaneously with the injection of compressed and dehumidified ambient air into the low pressure leg 202 by opening the cold side valve 133. When cold side valve 133 is open, hot side valve 132 can be closed. In addition, when the cold side valve 133 is opened, valve 123 can be opened. The cold side valve 133 can be opened by the control device 162. For example, controller 164 can instruct the control device 162 to open the cold side valve 133 in response to the demand for increased power generation. Alternatively, the fluid
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127/135 extracted work can be injected from the working fluid storage tank 130 into the low pressure leg 202 before or after the compressed and dehumidified ambient air is injected into the low pressure leg 202.
B. Example of expelling working fluid from the closed cycle fluid path [00240] In a closed cycle system, it may be desirable to remove an amount of working fluid from the closed cycle fluid path to reduce the system power. For example, it may be desirable to remove an amount of working fluid from the closed loop fluid path that was previously added to the closed loop fluid path. In some embodiments, removing the working fluid from the closed-loop fluid path can decrease the mass flow rate in the closed-loop fluid path and thus decrease the amount of electricity generated by the system.
[00241] Using the illustration in Figure 31, a working fluid can be circulated through the closed-loop fluid path that includes, in sequence, the compressor 101, the hot-side heat exchanger 102, the turbine 103 and the exchanger cold-side heat exchanger 104. The fluid path
cycle includes high leg pressure 201 and the leg in low pressure 202. One recovered r too can be included gone in the system.[00242] In a modality exemplary, O control in
inventory in system 100 may involve, in response to a reduced power generation demand, expelling working fluid from the closed-loop fluid path through expansion valve 140, thereby cooling
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128/135 the expelled working fluid; and thermally contacting the expelled working fluid with a portion of the CTS medium.
[00243] The demand for reduced power generation can be received or determined by one or more components of the system 100. As an example, the demand for reduced power generation can be received by controller 164. Controller 164 can receive demand for reduced energy generation from, for example, the grid system. As another example, demand for reduced power generation can be determined by controller 164. Controller 164 can determine demand for reduced power generation based on any of the operating conditions described above, including turbine torque, turbine RPM, generator torque and generator RPM; and current, voltage, phase, frequency and / or amount of electrical energy generated and / or distributed by the generator and / or its discrete components. In addition, the demand for reduced power generation can occur when any of the operating conditions described above reaches a threshold demand value. In some modalities, the threshold demand value related to an increased power generation demand may differ from the threshold demand value related to a reduced power generation demand.
[00244] In addition, in some implementations, in response to the demand for reduced power generation, controller 164 may instruct control device 162 to operate expansion valve 140 to expel working fluid from the flow fluid path. closed cycle. The working fluid can be expelled from the low pressure leg 202. In operation, the expansion valve 140 can
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129/135 expand the working fluid flowing from the low pressure leg 202 through valve 140 to atmospheric pressure. In addition, the expansion valve 140 can cool the working fluid flowing from the low pressure leg 202 through the expansion valve 140.
[00245] The auxiliary heat exchanger 141 can contact the working fluid with a portion of the CTS medium. As mentioned, the CTS medium portion can be pumped from HSC 10 9 or CSC 108 through auxiliary heat exchanger 141.
C. Quiescent Mode [00246] Brayton cycle systems can operate in charge or discharge modes, where the discharge mode is generally consistent with converting stored thermal energy into a substantial amount of electrical energy for distribution to a grid or another significant user of power and charge mode is generally consistent with storing substantial amounts of thermal energy in the system for later use. However, the Brayton cycle system can also operate in quiescent mode, where the system is neither producing a substantial amount of electrical energy nor storing substantial amounts of thermal energy.
[00247] Pumps and / or turbomachines not operating in a quiescent mode will cause the temperature profile in a Brayton cycle heat exchanger to be significantly different from the desired temperature profile when the heat exchanger is operating in loading or unloading. This difference can lead to long acceleration times for a Brayton cycle system
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130/135 go online and start supplying or accepting energy. It can also lead to additional thermal stresses as the temperature changes. Beneficially, the inventory control described here can be implemented to operate the compressor and the turbine at a very low speed to leak heat into or out of the heat exchangers to maintain a desired temperature profile in the heat exchangers that allows a quick transition to optimized operation in loading or unloading modes. For example, a power system can be operated in a quiescent mode such that the cycle is operated at a level sufficient to circulate working and / or thermal fluids, but is effectively generating zero or negligible liquid electrical energy. In the quiescent mode, the inventory control described here can be implemented to maintain a desired mass flow rate in the closed loop fluid path such that when the system transitions to, for example, discharge mode, the heat exchangers are already close to operating temperatures. In this way, the transition from quiescent to discharge modes can take very little, for example, less than 15 seconds.
IV. Illustrative Methods [00248] Figure 32 is a flow chart illustrating a 3200 method of inventory control, according to an example modality. Illustrative methods, such as the 3200 method, can be performed in whole or in part by a component or components of a closed loop system, such as the 100 system.
[00249] As shown by block 3202, method 3200 may involve a closed loop system operating in a
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131/135 power generation, circulate a working fluid through a closed-loop fluid path including, in sequence, a compressor, a hot-side heat exchanger, a turbine, and a cold-side heat exchanger, wherein the closed loop fluid path comprises a high pressure leg and a low pressure leg. In some embodiments, the closed loop system may include a closed Brayton loop system. In addition, in some embodiments, the working fluid may be air.
[00250] As shown by block 3204, the 3200 method can involve, in response to an increased demand for energy generation, compress and dehumidify the ambient air. In some modalities, the demand for increased energy generation can be received or determined. The demand for increased power generation can be determined based on any of the operating conditions described above. In addition, in some modalities, the demand for increased power generation may occur when any of the operating conditions described above reaches a threshold demand value.
[00251] In some embodiments, the closed-loop system can be configured to thermally contact the working fluid circulating through the cold side heat exchanger with a CTS medium and dehumidifying the ambient air may involve the transfer of at least a portion from the CTS medium to a dehumidifier and thermally contact the ambient air with the CTS medium inside the dehumidifier and condense the water out of the ambient air. In addition, in some embodiments, dehumidification of ambient air can occur prior to compression of ambient air. Furthermore, in
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132/135 some modalities, dehumidification of ambient air can occur after compression of ambient air.
[00252] As shown by block 3206, method 3200 may involve the injection of compressed and dehumidified ambient air in the low pressure leg.
[00253] In some embodiments, the 3200 method may also involve the extraction of the working fluid from the high pressure leg of the closed cycle fluid path; storing the extracted working fluid in a working fluid storage tank; inject the working fluid extracted from the working fluid storage tank into the low pressure leg simultaneously with the injection of compressed and dehumidified ambient air into the low pressure leg.
[00254] In addition, in some modalities, the 3200 method may involve, even after thermal contact of the ambient air with the CTS medium in the dehumidifier and the condensation of water out of the ambient air, transferring at least a portion of the CTS medium from the dehumidifier for an intermediate CTS storage tank.
[00255] Figure 33 is a flow chart illustrating a 3300 method of inventory control, according to an example modality. Illustrative methods, such as the 3300 method, can be performed in whole or in part by a component or components of a closed loop system, such as system 100.
[00256] As shown by block 3302, method 3300 may involve, in a closed loop system in a power generation mode, circulating a working fluid through a closed loop fluid path including, in sequence,
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133/135 a compressor, a hot side heat exchanger, a turbine and a cold side heat exchanger, in which the closed-loop fluid path comprises a high pressure leg and a low pressure leg, and in which the closed loop system is configured to thermally contact the working fluid circulating through the cold side heat exchanger medium with a cold side thermal storage (CTS). In some embodiments, the closed loop system may include a closed Brayton loop system. In addition, in some embodiments, the working fluid may be air.
[00257] As shown by block 3304, the 3300 method may involve, in response to a demand for reduced energy generation, expelling working fluid from the closed cycle fluid path through an expansion valve, thereby cooling the flow fluid. expelled work. In some modalities, the demand for reduced energy generation can be received or determined. The demand for reduced power generation can be determined based on any of the operating conditions described above. In addition, in some modalities, the demand for reduced power generation may occur when any of the operating conditions described above reaches a threshold demand value. In addition, in some embodiments, the working fluid can be expelled from the low pressure leg.
[00258] As shown by block 3306, method 3300 may involve the thermal contact of the expelled working fluid with a CTS medium port. In some embodiments, the expelled working fluid can be thermally contacted with a portion of the CTS medium in a heat exchanger
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Auxiliary 134/135.
V. Illustrative non-transient computer-readable medium [00259] Some or all of the functions described above and illustrated in Figures 32 and 33 can be performed by a computing device in response to the execution of instructions stored in a non-transient computer-readable medium. The non-transitory computer readable medium can be, for example, a random access memory (RAM), a read-only memory (ROM), a flash memory, a cache memory, one or more magnetically encoded disks, one or more disks optically encrypted, or any other form of non-transitory data storage. The non-transitory computer-readable medium can also be distributed among several data storage elements, which can be located remotely from each other. The computing device that executes the stored instructions can be the 1901 computer system, as described and illustrated in Figure 30.
[00260] The non-transient computer-readable medium can store instructions executable by a processor (for example, CPU 1905) to perform various functions. Functions can include in a closed-loop system operating in a power generation mode, circulating a working fluid through a closed-loop fluid path including, in sequence, a compressor, a hot-side heat exchanger, a turbine and a cold side heat exchanger, wherein the closed loop fluid path comprises a high pressure leg and a low pressure leg; in response to a demand for greater generation of
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135/135 energy, compress and dehumidify the ambient air; and inject the compressed and dehumidified ambient air into the low pressure leg.
[00261] In addition, the functions may include in a closed-loop system in a power generation mode, circulating a working fluid through a closed-loop circuit including, in sequence, a compressor, a side heat exchanger hot, a turbine and a cold-side heat exchanger, where the closed-loop fluid path comprises a high-pressure leg and a low-pressure leg, and where the closed-loop system is configured to thermally contact the fluid workflow circulating through the cold-side heat exchanger with a cold-side thermal storage medium (CTS); in response to a demand for reduced power generation, expel working fluid from the closed-loop fluid path through an expansion valve, thereby cooling the expelled working fluid; and thermally contacting the expelled working fluid with a portion of the CTS medium.
SAW. Conclusion [00262] Although several aspects and modalities have been disclosed here, other aspects and modalities will be evident to those skilled in the art. The various aspects and modalities disclosed herein are for illustrative purposes and are not intended to be limiting, the true scope and spirit being indicated by the following claims.

权利要求:
Claims (21)
[1]
1. Method characterized by the fact that it comprises:
in a closed loop system operating in a power generation mode, circulate a working fluid through a closed loop fluid path including, in sequence, a compressor, a hot-side heat exchanger, a turbine and an exchanger cold-side heat, where the closed-loop fluid path comprises a high pressure leg and a low pressure leg;
in response to an increased demand for energy generation, to compress and dehumidify ambient air; and inject compressed and dehumidified ambient air into the low pressure leg.
[2]
2. Method according to claim 1, characterized by the fact that the closed cycle system comprises a closed Brayton cycle system.
[3]
3. Method, according to claim 1, characterized by the fact that it also comprises:
extracting working fluid from the high pressure leg of the closed-loop fluid path;
storing the extracted working fluid in a working fluid storage tank; and injecting the working fluid extracted from the working fluid storage tank into the low pressure leg simultaneously with injecting the compressed and dehumidified ambient air into the low pressure leg.
[4]
4. Method according to claim 1, characterized by the fact that the closed loop system is configured to thermally contact the working fluid circulating through a cold side heat exchanger with a
Petition 870190100337, of 10/07/2019, p. 8/13
2/5 cold-side thermal storage (CTS), in which dehumidification of ambient air comprises:
transferring at least a portion of the CTS medium to a dehumidifier; and thermally contacting the ambient air with the CTS medium inside the dehumidifier and condensing water out of the ambient air.
[5]
5. Method according to claim 4, characterized by the fact that dehumidification of ambient air occurs before compressing ambient air.
[6]
6. Method according to claim 4, characterized by the fact that dehumidification of ambient air occurs after compressing ambient air.
[7]
7. Method, according to claim 4, characterized by the fact that it also comprises:
after thermally contacting the ambient air with the CTS medium inside the dehumidifier and condensing water out of the ambient air, transfer at least a portion of the CTS medium from the dehumidifier to the intermediate CTS storage tank.
[8]
8. Method according to claim 1, characterized by the fact that the working fluid is air.
[9]
9. Method characterized by the fact that it comprises:
in a closed-loop system in a power generation mode, circulate a working fluid through a closed-loop fluid path including, in sequence, a compressor, a hot-side heat exchanger, a turbine and a heat exchanger. cold-side heat, where the closed-loop fluid path comprises a high pressure leg and a low pressure leg, and the system
Petition 870190100337, of 10/07/2019, p. 9/13
3/5 closed cycle is configured to thermally contact the working fluid circulating through the cold side heat exchanger with a cold side thermal storage medium (CTS);
in response to a demand for reduced power generation, expel working fluid from the closed-loop fluid path through an expansion valve, thereby cooling the expelled working fluid; and thermally contacting the expelled working fluid with a portion of the CTS medium.
[10]
Method according to claim 9, characterized in that the expelled working fluid is thermally contacted with a portion of the CTS medium in an auxiliary heat exchanger.
[11]
11. Method according to claim 9, characterized by the fact that working fluid is expelled from the low pressure leg.
[12]
12. Method according to claim 9, characterized by the fact that the working fluid is air.
[13]
13. System characterized by the fact that it comprises:
a first compressor;
a hot-side heat exchanger;
a turbine;
a cold side heat exchanger;
a working fluid circulating in a closed cycle fluid path through, in sequence, the first compressor, the hot side heat exchanger, the turbine and the cold side heat exchanger, in which the closed cycle fluid path comprises a high pressure leg and a low pressure leg; and
Petition 870190100337, of 10/07/2019, p. 10/13
4/5 a second compressor coupled to the low pressure leg and configured to, on demand, compress ambient air and inject compressed ambient air into the low pressure leg.
[14]
14. System, according to claim 13, characterized by the fact that it also comprises:
a cold-side thermal storage medium (CTS), in which the system is configured to thermally contact the working fluid circulating through the cold-side heat exchanger with the CTS medium;
a CTS storage tank configured to store the CTS medium; and a dehumidifier configured to thermally contact the ambient air with a portion of the CTS medium and condense the water out of the ambient air.
[15]
15. System according to claim 13, characterized by the fact that the dehumidifier supplies dehumidified ambient air to the second compressor for compression.
[16]
16. System, according to claim 13, characterized by the fact that the second compressor supplies compressed ambient air to the dehumidifier for dehumidification.
[17]
17. System according to claim 13, characterized by the fact that it also comprises an intermediate CTS storage tank configured to receive CTS medium from the dehumidifier.
[18]
18. System according to claim 13, characterized by the fact that it also comprises a working fluid storage tank containing
Petition 870190100337, of 10/07/2019, p. 11/13
5/5 working at a pressure greater than a working fluid pressure in the low pressure leg, where the system is configured to, on demand, inject working fluid from the working fluid storage tank into the leg of low pressure simultaneously with the compressed ambient air.
[19]
19. System according to claim 13, characterized by the fact that the working fluid is air.
[20]
20. System characterized by the fact that it comprises: a first compressor;
a hot-side heat exchanger;
a turbine;
a cold side heat exchanger;
a working fluid circulating in a closed cycle fluid path through, in sequence, the first compressor, the hot side heat exchanger, the turbine and the cold side heat exchanger, in which the closed cycle fluid path comprises a high pressure leg and a low pressure leg;
a cold-side thermal storage medium (CTS), in which the system is configured to thermally contact the working fluid circulating through the cold-side heat exchanger with the CTS medium;
the expansion valve configured to expel working fluid from the closed-loop fluid path; and the auxiliary heat exchanger configured to thermally contact the expelled working fluid with at least a portion of the CTS medium.
[21]
21. System according to claim 20, characterized by the fact that the working fluid is air.

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CA3087032A1|2018-07-05|

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AU2017387788A1|2019-07-18|

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CN110366632A|2019-10-22|

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AU2020267295A1|2020-12-10|

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AU2017387788B2|2020-08-13|

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法律状态:
2021-10-13| B350| Update of information on the portal [chapter 15.35 patent gazette]|

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2021-12-07| B06W| Patent application suspended after preliminary examination (for patents with searches from other patent authorities) [chapter 6.23 patent gazette]|

优先权:

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申请号 | 申请日 | 专利标题

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US15/394,572|US10221775B2|2016-12-29|2016-12-29|Use of external air for closed cycle inventory control|

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PCT/US2017/065201|WO2018125535A1|2016-12-29|2017-12-07|Use of external air for closed cycle inventory control|

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