excess heat storage on cold side of thermal motor

专利摘要:
the extra heat in a closed cycle power generation system, such as a reversible closed brayton cycle system, can be dissipated between discharge and charge cycles. an extra cooling heat exchanger can be added to the discharge cycle and discarded between a cold side heat exchanger and a compressor inlet. additionally or alternatively, a cold thermal storage medium that passes through the heat exchanger on the cold side may be allowed to heat up to a higher temperature during the discharge cycle than is required at the entrance to the charge cycle and the additional heat dissipated then to the atmosphere.
公开号:BR112019013376A2
申请号:R112019013376
申请日:2017-11-30
公开日:2019-12-17
发明作者:Larochelle Philippe；Apte Raj
申请人:Malta Inc；
IPC主号:

专利说明:

LOWER TEMPERATURE RESERVOIR
1/113
EXCESSIVE HEAT STORAGE IN COLD ENGINE SIDE
THERMAL
CROSS REFERENCE TO RELATED ORDER [0001] This order claims priority for the Order
in Patent U.S. No. 15 / 392,657, deposited on 2 8 of December in 2016, the what is incorporated here how reference in your totality • BACKGROUND [0002] On a thermal engine or heat pump heat one exchanger
Heat transfer can be used to transfer heat between a thermal storage material and a working fluid for use with turbomachinery. The thermal motor can be reversible, for example, it can also be a heat pump, and the working fluid and heat exchanger can be used for the transfer of heat or cold to a plurality of thermal stores. The thermal energy in a given system can be stored in several ways and in a variety of containers, including pressure vessels and / or insulated vessels.
SUMMARY [0003] A closed cycle system, such as a Brayton cycle system, can include at least one working fluid circulated through a closed cycle fluid path including at least two heat exchangers, a turbine and a compressor . In some systems, one or more reciprocating heat exchangers may also be included. At least two temperature reservoirs can hold thermal fluids that can be pumped through heat exchangers, providing and / or extracting thermal energy from the working fluid. A motor / generator can be
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2/113 used to obtain work from thermal energy in the system, preferably by generating electricity from the mechanical energy received from the turbine.
[0004] In some cases, inefficiencies in the system can be such that excess heat must be removed from the system to close the thermodynamic cycle. Excess heat in a discharge cycle can be stored on the cold side of the thermal engine, prior to removal.
[0005] Example systems include: a compressor; a stove; a hot-side heat exchanger; a turbine; a cold side heat exchanger; a cooling heat exchanger; and a working fluid circulating in a closed cycle path through, in sequence, the compressor, the stove, the hot side heat exchanger, the turbine, the stove, the cooling heat exchanger and the heat exchanger of cold side, where the cooling heat exchanger is configured to remove heat from the working fluid.
[0006] Other example systems may include: a compressor; a stove; a hot-side heat exchanger; a turbine; a cold side heat exchanger; a working fluid circulating in a closed cycle path through, in sequence, the compressor, the stove, the heat exchanger on the hot side, the turbine, the stove and the heat exchanger on the cold side; a cold-side thermal storage medium (CTS); a first CTS tank; an intermediate CTS tank; a CTS heat exchanger, wherein the CTS heat exchanger is configured to remove heat from the CTS medium; a second CTS tank; a first flow path configured to flow the CTS medium to
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3/113 from the first CTS tank, through the cold side heat exchanger and to the intermediate CTS tank; and a second flow path configured to flow the CTS medium from the intermediate CTS tank, through the CTS heat exchanger and to the second CTS tank.
[0007] Example methods may include in a closed-loop system operating in a power generation mode, the circulation of a working fluid through a closed-loop flow path including, in sequence, a compressor, a stove , a hot side heat exchanger, a turbine, the stove and a cold side heat exchanger; the flow of a cold-side thermal storage medium (CTS) at a first variable flow from the first CTS tank, through the cold-side heat exchanger and in thermal contact with the working fluid, and to a Intermediate CTS; and the flow of the CTS medium from the intermediate CTS tank, through a CTS heat exchanger and to a second CTS tank, in which the CTS heat exchanger is configured to remove heat from the CTS medium.
BRIEF DESCRIPTION OF THE DRAWINGS [0008] Figure 1 schematically illustrates an operation of a pumped thermoelectric storage system.
[0009] Figure 2 is a schematic flow chart of working fluid and heat storage medium for a thermal system pumped in a load / pump mode.
[0010] Figure 3 is a schematic flowchart of working fluid and heat storage medium for a thermal system pumped in a thermal engine / discharge mode.
[0011] Figure 4 is a schematic diagram of pressure and
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4/113 working fluid temperature as it passes through the load cycle in figure 2.
[0012] Figure 5 is a schematic diagram of pressure and temperature of the working fluid as it passes through the discharge cycle in figure 3.
[0013] Figure 6 is a schematic perspective view of a closed working fluid system in the thermal system pumped in figures 2 to 3.
[0014] Figure 7 is a schematic perspective view of the thermal system pumped in figures 2 to 3 with hot and cold side storage tanks and a closed cycle working fluid system.
[0015] Figure 8 shows a heat storage load cycle for a molten water / salt system with r / c = 0.9 and pt = 0.95. The dashed lines correspond to p _c = pt = 1.
[0016] Figure 9 shows a discharge (extraction) cycle for the molten water / salt system of figure 8 with p _c = 0.9 and pt = 0.95. The dashed lines correspond to p _c = pt = 1.
[0017] Figure 10 shows a heat storage cycle in a pumped thermal system with varying compression ratios between loading and unloading cycles.
[0018] Figure 11 shows roundtrip efficiency contours for a water / salt system. The symbols © and 0 represent an approximate range of adiabatic efficiency values of large turbomachines present.
[0019] Figure 12 shows roundtrip efficiency contours for a cooler water / salt system. The symbols © and 0 represent an approximate range of adiabatic efficiency values of large turbomachines present.
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5/113 [0020] Figure 13 is a schematic flow chart of working fluid and heat storage media from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a thermal pump / load mode. .
[0021] Figure 14 is a schematic flowchart of working fluid and heat storage media from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a thermal engine / discharge mode.
[0022] Figure 15 is a schematic flowchart of working fluid and heat storage media from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a charge / heat pump with rejection mode indirect heat to the environment.
[0023] Figure 16 is a schematic flowchart of working fluid and heat storage media from a thermal system pumped with a gas-gas heat exchanger to the working fluid in a discharge mode / thermal engine with rejection of indirect heat to the environment.
[0024] 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 rjc = 0.9 and qt = 0.95.
[0025] 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 rjc = 0.9 and qt = 0.95.
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6/113 [0026] 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 solely by solar power.
[0027] Figure 20 is a schematic flowchart of a thermal system discharge cycle pumped with heat rejection into the environment.
[0028] Figure 21 is a schematic flowchart of a discharge cycle of a thermal system pumped with heat rejection to an intermediate fluid circulated in a thermal bath at room temperature.
[0029] Figures 22 and 23 are thermal systems pumped with separate compressor / turbine pairs for loading and unloading modes.
[0030] Figures 24 and 25 are pumped thermal systems configured in a combustion heat input generation mode.
[0031] 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 loss heat source.
[0032] Figure 27 shows an example of a pumped thermal system with a pressure regulated power control.
[0033] Figure 28 shows an example of a thermal system pumped with an encapsulated pressure generator.
[0034] Figure 29 is an example of variable stators in a compressor / turbine pair.
[0035] Figure 30 shows a computer system that is programmed to implement various methods and / or regulate
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7/113 various systems of the present exhibition.
[0036] Figure 31 illustrates a thermodynamic graph of pressure and temperature for a content for a load cycle, according to an example modality.
[0037] Figure 32 illustrates a thermodynamic graph of pressure and temperature for a content for a discharge cycle, according to an example modality.
[0038] Figure 33 illustrates a Brayton system in a discharge mode with cold side heat storage, according to an example modality.
[0039] Figure 34 illustrates a Brayton system in a discharge mode with cold side heat storage, according to an example modality.
[0040] Figure 35 illustrates a method for storing and dissipating heat from a cold side heat storage, according to an example modality.
DETAILED DESCRIPTION [0041] Although various modalities of the invention have been shown and described here, it will be obvious to those skilled in the art that these modalities are provided by way of example only. Numerous variations, changes and substitutions can occur for those skilled in the art, without deviating 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.
[0042] It should be understood that the terminology used here is used for the purpose of describing specific modalities,
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8/113 and is not intended to limit the scope of the present invention. It should be noted that, as used here, the singular forms one, one and (a) include plural references, unless the context clearly dictates otherwise. In addition, unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by someone of ordinary skill in the art to which this invention pertains.
[0043] Although preferable embodiments of the present invention are shown and described here, it will be obvious to those skilled in the art that these modalities are provided by way of example only. Numerous variations, changes and substitutions will now occur to those skilled in the art, without deviating from the invention. It is to be understood that various 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 methods and structures within the scope of these claims and their equivalents are covered in this way.
[0044] The term reversible, as used here, generally refers to a process or operation that can be reversed through infinitesimal changes in some property of the process or operation, without producing substantial entropy (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 energy flow is reversible. As an alternative or additionally, the general direction of operation of a reversible process (eg
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9/113 example, the direction of fluid flow) can be reversed, such as, for example, from clockwise to counterclockwise, and vice versa.
[0045] The term sequence, as used here, generally refers to elements (for example, unit operations) in order. This order can refer to a process order, such as, for example, the order in which a fluid flows from one element to another. In one example, a compressor, a heat storage unit and a turbine in sequence include the compressor upstream of the heat exchange unit, and the heat exchange unit upstream of the turbine. In such a case, a fluid can flow from the compressor to the heat exchange unit and from the heat exchange unit to the turbine. A fluid flowing through unit operations in sequence can flow through unit operations sequentially. A sequence of elements can include one or more intervening elements. For example, a system comprising a compressor, a heat storage unit and a sequential turbine can include an auxiliary tank between the compressor and the heat storage unit. A sequence of elements can be cyclical.
I. Overview [0046] A closed cycle system, such as a closed Brayton cycle system, can use a generator / motor connected to a turbine and a compressor, which act on a working fluid circulating in the system. Examples of working fluids include air, argon, carbon dioxide or gas mixtures. A closed-loop system can have a hot side and / or a cold side. Each side can include a
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10/113 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 countercurrent heat exchangers for higher thermal efficiency. A thermal liquid storage medium may be used and may 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 molten salt and hexane system, the molten salt on the hot side can include a hot storage at approximately 565 ° C and a cold storage at approximately 290 ° C, and the cold side hexane can include a hot storage at approximately 35 ° C and cold storage at approximately -60 ° C.
[0047] If polytropic turbomachinery efficiencies are less than 100% in a Brayton cycle power generation system, excess heat may need to be dissipated between the discharge and charge cycles. In one embodiment, an extra cooling heat exchanger can be added to the discharge cycle and arranged between the cold side heat exchanger and the turbine outlet. In the cooling heat exchanger, the working fluid can exchange heat with another fluid, such as water or Therminol® to take the excess heat away. In another embodiment, instead of having another heat exchanger in the working fluid path, a cold thermal storage medium (CTS) through the cold side heat exchanger can be allowed to warm up to a
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11/113 higher temperature during the discharge cycle than is required at the entrance to the charge cycle. This warmer CTS medium can then be stored in an intermediate tank. The hotter CTS medium can then be passed through an intermediate cooling mechanism and returned to a final CTS tank, ready to be used in the charge cycle. This modality has an advantage over the previous modality in that (i) it eliminates the need for an additional working fluid cooling heat exchanger and a different heat exchange fluid, and (ii) it decouples the power of instant cooling of the immediate heat dissipation needs in the discharge cycle. Specifically, the heat of loss is being stored in the CTS medium, so the system in general can use a lesser amount of cooling power than required in the previous modality by dissipating the same number of Joules, but for a longer amount of time . In additional embodiments, the working fluid temperature in the cold-side heat exchanger may be above the boiling temperature of the CTS medium at ambient pressure. In one embodiment, the flow of CTS medium through the cold-side heat exchanger can be increased, so that the same amount of cooling is performed, but the CTS medium is not allowed to reach its boiling point. In another embodiment, the CTS medium can be allowed to evaporate, taking advantage of its latent heat of vaporization and then recondensed in a subsequent infrastructure.
II. Illustrative Reversible Thermal Engine
Pumped thermal systems
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12/113 [0048] The exhibition provides pumped thermal systems capable of storing electrical energy and / or heat, and releasing energy (for example, producing electricity) at a later time. The thermal systems pumped from the exhibition can include a thermal motor and a heat pump (or a refrigerator). In some cases, the thermal engine can be operated in reverse as a refrigerator. Any description of heat pump / thermal engine systems or cooler / thermal engine systems capable of reversing operation here can also be applied to systems comprising separate systems and / or a combination of separate and reversible operable thermal engine systems, heat pump and / or cooler systems. Also, as 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 be applied to configurations or the operation of refrigerators and vice versa.
[0049] The systems in this exhibition can operate as thermal engines or heat pumps (or refrigerators). In some situations, the exhibition systems may alternatively operate as thermal motors and heat pumps. In some instances, a system can operate as a thermal engine to generate power, and subsequently operate as a heat pump to store energy, or vice versa. These systems can operate, alternatively and sequentially, as thermal motors as heat pumps. In some cases, these systems operate in a reversible or substantially reversible manner as thermal engines as heat pumps.
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13/113 [0050] A reference will now be made to the figures, in which equal numbers refer to equal parts throughout them. It will be appreciated that the figures and resources there are not necessarily drawn to scale.
[0051] Figure 1 schematically illustrates operating principles of pumped thermoelectric storage using a heat pump / thermal motor 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) by using a combined heat pump / thermal engine system . In a loading or heat pump mode, labor can be consumed by the system for traditionally and 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 (that is, the sensitive energy) of the hot material. In a thermal engine or unloading mode, work can be produced by the system by transferring heat from the hot material to the cold material, thereby lowering the temperature (ie, the sensitive energy) of the hot material and increasing the temperature (ie that is, the sensitive energy) of the cold material. The system can be configured to ensure that the work produced by the system at the discharge is a favorable fraction of the energy consumed at the load. The system can be configured to obtain a roundtrip efficiency, defined here as the work produced by the system in the discharge divided by the work consumed by the
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14/113 system under load. Furthermore, the system can be configured to obtain high roundtrip efficiency using components of a desired cost (for example, acceptably low). The arrows H and W in figure 1 represent directions of heat flow and work, respectively.
[0052] Thermal motors, heat pumps and refrigerators in the exhibition can involve a working fluid to and from which heat is transferred while going through a thermodynamic cycle. The thermal motors, heat pumps and refrigerators of the exhibition can operate in a closed cycle. Closed cycles allow, for example, a wider selection of working fluids, operation at high cold side pressures, lower transaction at cold side, improved efficiency and reduced risk of damage to the turbine. One or more aspects of the exposure described in relation to systems having working fluids going through closed cycles can also be applied to systems having working fluids going through open cycles.
[0053] In one example, thermal 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 through which the working fluid can pass or approach include the Rankine cycle, the ideal vapor-compression refrigeration cycle, the Stirling cycle, the Ericsson cycle or any other cycle advantageously employed in accordance with a heat exchange with exposure heat storage fluids.
[0054] The working fluid can go through a cycle
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15/113 thermodynamic 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 around 10 atmospheres (atm) (1.01325 MPa) or greater can be used. In some cases, the low pressure limit may be at least around 1 atm (0.1013 MPa), at least around 2 atm (0.2027 MPa), at least around 5 atm (0, 5066 MPa), at least around 10 atm (1.01325 MPa), at least around 15 atm (1.5199 MPa), at least around 20 atm (2.0265 MPa), at least around 30 atm (3.0397 MPa), at least around 40 atm (4.053 MPa), at least around 60 atm (6.095 MPa), at least around 80 atm (8.106 MPa), at least around 100 atm (10.1325 MPa), at least around 120 atm (12.159 MPa), at least around 160 atm (16.212 MPa), or at least around 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 around 0.1 atm (0.01013 MPa), less than around 0.2 atm (0.02023 MPa), less than around 0.5 atm (0.05066 MPa), or less than around 1 atm (0.1013 MPa). In some cases, the low pressure limit can be around 1 atm (0.1013 MPa). In the case of a
operating work in a cycle open, the limit in pressure low may be in around 1 atm (0.1013 MPa) or equal to ambient pressure.[0055] In some cases, the limit value in pressure
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Low 16/113 can be selected based on desired power output and / or power input requirements of the thermodynamic cycle. For example, a pumped thermal system with a low pressure limit of around 10 atm (1.01325 MPa) may be able to provide a power output comparable with an industrial gas turbine with ambient air intake (1 atm ( 0.1013 MPa)). The low pressure limit value may also be subject to cost / security compromises. In addition, the value of the low pressure limit can be limited by the value of the high pressure limit, the operating ranges of the hot and cold side storage media (for example, pressure and temperature ranges by which the storage media are stable), pressure ratios and operating conditions (for example, operating limits, optimal operating conditions, pressure loss) obtainable 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 an improved heat transfer between the working fluid and the hot-side storage medium.
[0056] The 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 supercritical state ( for example, supercritical CO2). The working fluid can be a gas or a low video liquid (for example, a viscosity below 500x10 ⁶ Poise at 1 atm (0.1013 MPa)) satisfying the
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17/113 requirement that the flow be continuous. In some implementations, a gas with a high specific heat ratio can be used to achieve a higher cycle efficiency than a gas with a low specific heat ratio. For example, argon (for example, with a specific heat ratio of around 1.66) can be used to replace air (for example, a specific heat ratio of around 1.4). In some cases, the working fluid may be a mixture of one, two, three or more fluids. In one example, helium (having a high thermal conductivity and high specific heat) can be added to the working fluid (eg, argon) to improve heat transfer rates in heat exchangers.
[0057] The thermal systems pumped here 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 (thermal side storage medium (HTS) or HTS here) and a second heat device medium on a cold side of the system (storage medium cold side (CTS) or CTS here). The thermal storage medium (for example, low viscosity liquids) can have high thermal capacities per unit volume (for example, thermal capacities above about 1400 Joules (kilvin Kelvin) ^x ) and high thermal conductivities (for example, conductivities over 0.7 Watt (Kelvin meter) ^x ). In some implementations, several means of
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18/113 thermal storage (for example, heat storage media here) on the hot side, the cold side, or both the hot side and the cold side can be used.
[0058] The operating temperatures of the hot side thermal storage medium can be in the liquid range of the hot side thermal storage medium, and the operating temperatures of the cold side thermal storage medium can be in the liquid range of the hot side. cold-side thermal storage medium. In some instances, liquids may allow a faster exchange of large amounts of heat for a convective countercurrent than solids or gases. Thus, in some cases, the liquid HTS and CTS media can be used to advantage. Thermal systems pumped using thermal storage media here can advantageously provide a safe, non-toxic and geographically independent energy storage alternative (eg electricity).
[0059] 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 within 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 dissolution capacity of iron and nickel), and low cost. In one example, HTS is a
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19/113 mixture of sodium nitrate and potassium nitrate. In some instances, HTS is a eutectic mixture of sodium nitrate and potassium nitrate. In some examples, HTS is a mixture of sodium nitrate and potassium nitrate, with a melting point decreased in relation to the individual constituents, an increased boiling point in relation to the individual constituents, or a combination thereof. Other examples include potassium nitrate, calcium nitrate, sodium nitrate, sodium nitride, lithium nitrate, mineral oil, or any combination thereof. Other examples include any gaseous media (including compressed gases), liquids or solids (for example, powdered solids) having adequate thermal storage capacities (for example, high) and / or capable of obtaining adequate heat transfer rates (for example , high) with the working fluid. For example, a mixture of 60% sodium nitride and 40% potassium nitrate (also referred to as solar salt in some situations) may have a thermal capacity of approximately 1500 Joules (Kelvin mole) ¹ and a thermal conductivity of approximately 0 , 75 Watts (Kelvin meter) ¹ in a temperature range of interest. The hot-side thermal storage medium can be operated in a temperature range that structural steels can handle.
[0060] In some cases, liquid water at a temperature of around 0 ° C to 100 ° C (around 273 K to 373 K) and a pressure of around 1 atm (0.1013 MPa) can be used as the cold-side thermal storage medium. Due to a possible explosion risk associated with the presence of steam at or near the boiling point of water, the
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20/113 operation can be kept below around 100 ° C or less, while maintaining an operating pressure of 1 atm (0.1013 MPa) (ie, no pressurization). In some cases, the temperature operating range of the cold-side thermal storage medium can be extended (for example, from -30 ° C to 100 ° C to 1 atm (0.1013 MPa)) by using a mixture of water and one or more antifreeze compounds (for example, ethylene glycol, propylene glycol, or glycerol).
[0061] As described in greater detail elsewhere here, an improved storage efficiency can be achieved by increasing the temperature difference in which the system operates, for example, by using a cold-side heat storage fluid capable of operate at lower temperatures. In some examples, cold-side thermal storage media 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). A hexane has a wide liquid range and can remain fluid (that is, dripping) over its entire liquid range (-94 ° C to 68 ° C at 1 atm (0.1013 MPa)). The low temperature properties of hexane are aided by its immiscibility with water. Other liquids, such as, for example, ethanol or methanol, can become viscous at the temperature extremes
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21/113 drops in their liquid ranges, due to a pre-crystallization of water absorbed from the air. In some cases, the cold-side thermal storage medium may be heptane (for example, n-heptane). Heptane has a wide range of liquid and can remain fluid (i.e., dripping) over its entire liquid range (-91 ° C to 98 ° C at 1 atm (0.1013 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, isohexane (2-methylpentane). In other examples, cryogenic liquids having boiling points below around 150 ° C (123 K) or around -180 ° C (93.15 K) can be used as cold storage media (for example , propane, butane, pentane, nitrogen, helium, neon, argon and krypton, air, hydrogen, methane or liquefied natural gas). In some implementations, a choice of cold-side thermal storage media may be limited by the choice of working fluid. For example, when a gaseous working fluid is used, a liquid cold-side thermal storage medium may have a liquid temperature range at least partially or substantially above the boiling point of the working fluid may be required.
[0062] In some cases, the operating temperature range of CTS and / or HTS media can be changed by pressurizing (ie, increasing the pressure) or evacuating (for example, decreasing the pressure) of the tanks and thus changing the temperature at which the storage media undergo phase transitions (for example, going from liquid
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22/113 for solid or liquid for gas).
[0063] In some cases, the hot-side and cold-side heat storage fluids of the pumped thermal systems are in a liquid state for at least a portion of the operating temperature range of the energy storage device. The hot-side heat storage fluid can be liquid within a given temperature range. Heat storage fluids can be heated, cooled or maintained to obtain an appropriate operating temperature before, during or after an operation.
[0064] The thermal systems pumped from the exhibition can have cycles between charged and discharged modes. In some instances, pumped thermal systems can be fully charged, partially charged or partially discharged, or fully charged. In some cases, a cold side heat storage can be loaded (also recharged here) regardless of a hot side heat storage. Also, in some implementations, a loading (or some portion of it) and a downloading (or some portion 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 in conjunction with a cold side heat storage is being discharged.
[0065] Pumped thermal systems may be able to store energy for a given amount of time. In some cases, a given amount of energy can be stored for at least about 1 second, at least
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23/113 about 30 seconds, at least about 1 minute, at least about 5 minutes, at least about 30 minutes, at least about 1 hour, at least about 2 hours, at least at least around 3 hours, at least around 4 hours, at least around 5 hours, at least around 6 hours, at least around 7 hours, at least around 8 hours, at least in around 9 hours, at least around 10 hours, at least around 12 hours at least around 14 hours, at least around 16 hours, at least around 18 hours, at least around 20 hours, at least around 22 hours, at least around 24 hours (1 day), at least around 2 days, at least around 4 days, at least around 6 days, at least around 8 days, at least around 10 days, 20 days, 30 days, 60 days, 100 days, 1 year or more.
[0066] The thermal systems pumped from the exhibition may be able to store / receive an input from and / or extract / provide an output to / from a substantially large amount of energy and / or power for use with power generation systems (eg example, intermittent power generation systems, such as wind power or solar power), power distribution systems (eg power grid), and / or other loads or uses in grid-scale or independent scenarios. During a charging mode of a pumped thermal system, the electrical power received from an external power source (for example, a wind power system, a solar photovoltaic power system, an electrical network, etc.) can be used to operate the pumped thermal system in a mode
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24/113 heat pump (ie 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 power 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 intense power, etc.) by operating in a thermal engine mode (ie, transferring heat from a high temperature reservoir to a low temperature reservoir, thus extracting energy). As described elsewhere here, during a load and / or discharge, the system can receive or reject thermal power, including, but not limited to, electromagnetic power (eg, solar radiation) and thermal power (eg, sensitive energy from a medium heated by solar radiation, combustion heat, etc.).
[0067] In some implementations, the pumped thermal systems are synchronized with the network. A synchronization can be achieved by combining the speed and frequency of motors / generators and / or turbomachines of a system with frequency of one or more interconnected networks with which the system exchanges power. For example, a compressor and a turbine can run at a given fixed speed (for example, 3600 revolutions per minute (rpm)) which is a multiple of a mains frequency (for example, 60 Hertz (Hz)). In some cases, a configuration like this can eliminate the need for additional power electronics. In some implementations, turbomachinery and / or engines / generators are not synchronized with the network. In such cases, a combination
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25/113 frequency can be performed through the use of power electronics. In some implementations, turbomachinery and / or motors / generators are not directly synchronized with the network, but can be combined through the use of gears and / or a mechanical transmission box. As described in more detail elsewhere here, pumped thermal systems can also be pliable. These capabilities may allow these grid-scale energy storage systems to operate as peak power plants and / or as power plants following a load. In some cases, the exhibition systems may be able to operate as base load power plants.
[0068] Pumped thermal systems can have a given power capacity. In some cases, a power capacity during a charge may differ from a power capacity during a discharge. For example, each system may have a load and / or discharge power capacity of less than around 1 megawatt (MW), at least around
of 1 megawatt, fur any less in lathe in 2 MW, fur any less in lathe in 3 MW, fur any less in lathe in 4 MW, fur any less in lathe in 5 MW, fur any less in lathe in 6 MW, fur any less in lathe in 7 MW, fur any less in lathe in 8 MW, fur any less in lathe in 9 MW, fur any less in lathe in 10 MW, fur any less in lathe in 20 MW, fur any less in lathe in 30 MW, fur any less in lathe in 40 MW, fur any less in lathe in 50 MW, fur any less in lathe in 75 MW, fur any less in lathe in 100 MW, fur any less in
around 200 MW, at least around 500 MW, at least around 1 gigawatt (GW), at least around 2 GW, at least around 5 GW, at least around 10 GW,
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11/26
fur any less in lathe in 20 GW, at any less in lathe in 30 GW fur any less in lathe in 40 GW, at any less in lathe in 50 GW fur any less in lathe in 75 GW, at any less in lathe in 100 GW
or more.
[0069] Pumped thermal systems can have a given 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 around 1 megawatt hour, at least around 10 MWh, at least around 100 MWh, at least around 1 gigawatt hour (GWh), at least around 5 GWh, at least around 10 GWh, at least around 20 GWh, around 50 GWh, at least around 100 GWh, at least around 200 GWh, at least around 500 GWh, at least around 700 GWh, at least around 1000 GWh, or more.
[0070] In some cases, a given power capacity can be obtained with a given size, configuration and / or operating conditions of the thermal motor / heat pump cycle. For example, the size of turbomachinery, ducts, heat exchangers or other system components can correspond to a given power capacity.
[0071] In some implementations, a given energy storage capacity can be obtained with a given size and / or a number of thermal storage tanks on the hot side and / or thermal storage tanks on the cold side. For example, the thermal motor / heat pump cycle can operate at a given power capacity for a given
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27/113 amount of time regulated by the capacity of the system or plant's heat device. 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 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 may be referred to as a hot-side (thermal) heat storage unit. In some cases, the cold side thermal storage tanks, the cold side heat exchanger and the cold side thermal storage medium can be referred to as a cold side (thermal) storage unit.
[0072] A pumped thermal storage facility can include any suitable number of hot-side storage tanks, such as at least around 2, at least around 4, at least around 10, at least around 50, at least around 100, at least around 500, at least around 1,000, at least around 5,000, at least around 10,000, and the like. 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.
[0073] A pumped thermal storage facility
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11/28 can also include any number of cold-side storage tanks, such as at least around 2, at least around 4, at least around 10, at least around 50, at least around from 100, at least around 500, at least around 1,000, at least around 5,000, at least around 10,000, and the like. 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.
Pumped thermal storage cycles [0074] One aspect of the exhibition refers to pumped thermal systems operating in pumped thermal storage cycles. In some instances, cycles allow electricity to be stored as heat (for example, in the form of a temperature differential) and then converted back into electricity using at least two types of turbomachinery, a compressor and a turbine . The compressor consumes work and raises the temperature and pressure of a working fluid (WF). The turbine produces work and decreases 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 1, at least 2, at least 3, at least 4 or at least 5 turbines. The compressors can be arranged in series or in parallel. The turbines can be arranged in series or in parallel.
[0075] Figures 2 and 3 are schematic flowcharts of
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29/113 working fluid and heat storage means of an example pumped thermal system in a load / heat pump mode and in a discharge / thermal engine mode, respectively. The system can be designed for simplicity of explanation so that there are no losses (ie, entropy generation) in turbomachinery or heat exchangers. The system can 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. The paths flow rate / 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 thermal storage medium for cold side (CTS) 22 (for example, a low viscosity liquid) are indicated by arrows.
[007 6] 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, once again simplified with the approach of no generation of entropy. A normalized pressure is shown on the y axes and the temperature is shown on the x axes. The direction of processes occurring during the cycles is indicated with arrows, and the individual processes occurring in compressor 1, hot side CFX 2, turbine 3 and cold side CFX 4 are indicated in the diagram with their respective numbers.
[0077] Heat exchangers 2 and 4 can be configured as countercurrent heat exchangers (CFXs), in which the working fluid flows in one direction and the substance with which it is exchanging heat is flowing in the
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11/303 opposite direction. In an ideal countercurrent heat exchanger with correctly matched flows (that is, balanced capacities or capacity flows), the temperatures of the working fluid and thermal storage medium reverse (that is, the countercurrent heat exchanger can have a unit effectiveness).
[0078] Countercurrent heat exchangers 2 and 4 can be designed and / or operated to reduce the generation of entropy in the heat exchangers to negligible levels, compared to an entropy generation associated with other system components and / or processes (eg, compressor and / or turbine entropy generation). In some cases, the system can be operated so that the generation of entropy in the system is minimized. For example, the system can be operated so that the generation of entropy associated with heat storage units is minimized. In some cases, a temperature difference between heat exchanging fluid elements can be controlled during an operation, so that the generation of entropy in 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 negligible when compared to the entropy generated by the compressor, the turbine or both the compressor and the turbine. In some cases, an entropy generation associated with heat transfer in heat exchangers 2 and 4 and / or entropy generation associated with an operation of the hot side storage unit, the cold side storage unit or both hot and cold side storage can be less than around 50%, less than around
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25%, smaller of what in lathe in 20%, smaller of what in lathe in 15%, smaller of what in lathe in 10%, smaller of what in lathe in 5%, smaller of what in lathe in 4%, smaller of what in lathe in
3%, less than around 2%, or less than around 1% of the total entropy generated in the system (for example, the entropy generated by compressor 1, by the hot-side heat exchanger 2, by turbine 3 , by the cold side heat exchanger 4 and / or by other components described here, such as, for example, a stove). For example, an entropy generation can be reduced or minimized if two substances exchanging heat do so at a local temperature differential ΔΤ -> 0 (that is, when the temperature difference between any two fluid elements that are in close thermal contact) in the heat exchanger is small). In some examples, the temperature differential ΔΤ between any two fluid elements that are in close thermal contact may be less than around 300 Kelvin (K), less than around 200 K, less than around 100 K, less than around 75 K, less
of what in lathe in 50 K, smaller than in around 40 K, smaller of what in lathe in 30 K, smaller than in around 20 K, smaller of what in lathe in 10 K, smaller than around 5 K, smaller of what in become > of 3 K, smaller than around in 2 K, or
less than around 1 K. In another example, a generation of entropy associated with a pressure loss can be reduced or minimized by an appropriate design. In some instances, the heat exchange process can occur at a constant or near constant pressure. Alternatively, a negligible pressure loss can be experienced by the working fluid and / or another storage medium
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32/113 thermal during a passage through a heat exchanger. A pressure loss in heat exchangers can be controlled (for example, reduced or minimized) through an appropriate heat exchanger design. In some instances, the pressure loss through each heat exchanger may be less than around 20% inlet pressure, less than around 10% inlet pressure, less than around 5% inlet pressure, less than around 3% inlet pressure, less than around 2% inlet pressure, less than around 1% inlet pressure, less than around 0.5% inlet pressure, less than around 0.25% inlet pressure, or less than around 0.1% inlet pressure.
[0079] Upon entering the hot side heat exchanger 2, the temperature of the working fluid may increase (taking heat from the HTS 21 medium, corresponding to the discharge mode in figures 3 and 5) or decrease (providing heat to the HTS 21, corresponding to the charging 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. Similarly, when entering the cold side heat exchanger 4, the temperature of the working fluid may increase (taking heat from the CTS 22 medium, corresponding to the charge mode in figures 2 and 4) or decrease (providing heat to the medium of CTS 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.
[0080] As described in greater detail with reference to the charging mode in figures 2 and 4, the process of
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33/113 addition of heat to the cold side CFX 4 can occur over a different range of temperatures compared to the heat removal process in the hot side CFX 2. Similarly, in the discharge mode in figures 3 and 5, the The heat rejection process on the cold side CFX 4 can occur over a different temperature range compared to the heat addition process on the hot side CFX 2. At least a portion of the temperature ranges of the side heat exchanger processes hot and cold side can overlap during loading, during unloading or during both loading and unloading.
[0081] As used here, the temperatures To, Ti, To ⁺ and Ti ⁺ are called so because To ⁺ , Ti ⁺ are the temperatures obtained at the outlet of a compressor with a given compression rate r, an adiabatic efficiency p _c and input temperatures of To, Ti, respectively. The examples in figures 2, 3, 4 and 5 can be idealized examples where 7] _c = 1 and where the adiabatic efficiency of turbine 7] _t also has a value of = 1.
[0082] With reference to the load mode shown in figures 2 and 4, the working fluid 20 can enter the compressor 1 in a position 30 at a pressure P and a temperature T (for example, in Τι, P2). As the working fluid passes through the compressor, work Wi is consumed by the compressor to increase the working fluid pressure and temperature (for example, for Ti ⁺ , Pi), as indicated by Pf and Tf in position 31. In load mode, the Ti ⁺ temperature of the working fluid exiting the compressor and entering the hot side CFX 2 in position 31 is higher than the temperature of the HTS 21 medium entering the hot side CFX 2 in position 32 a from a second
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34/113 hot-side thermal storage tank 7 at a temperature of To ⁺ (ie, To ⁺ <Ti ⁺ ). As these two fluids pass in thermal contact with each other in the heat exchanger, the temperature of the working fluid decreases as it moves from position 31 to position 34, giving off heat Qi to the HTS medium, while the temperature of the medium HTS 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 exits the hot side CFX 2 in position 34 at a lower temperature, but at the same pressure Pi, as indicated by P and T j. in 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.
[0083] When exiting the CFX from the hot side 2 in position 34 (for example, in To ⁺ , Pi), the working fluid 20 undergoes an expansion in the turbine 3, before leaving the turbine in position 35. During the expansion, the pressure and temperature of the working fluid decrease (for example, for To, P2), as indicated by P j. and T j. in position 35. The working magnitude W2 generated by the turbine depends on the enthalpy of the working fluid entering 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
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35/113 work is expanded back to the pressure at which it initially entered the compressor at position 30 (eg, P2) · The compression ratio (eg, P1 / P2) in compressor 1 being equal to the expansion ratio in turbine 3, and the enthalpy of gas entering the turbine being less than the enthalpy of gas leaving the compressor, the work W2 generated by turbine 3 is less than the work Wi consumed by compressor 1 (i.e., W2 <Wi).
[0084] Due to the heat that was taken from the working fluid in the hot side CFX 2, the temperature To at which the working fluid exits the turbine at position 35 is lower than the temperature Ti at which the working fluid initially entered the compressor at position 30. To close the cycle (that is, to return the pressure and temperature of the working fluid to its initial values Τι, P2 at position 30), heat Q2 is added to the working fluid in the middle of CTS 22 on the cold side CFX 4 between positions 35 and 30 (that is, 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 to a second tank of cold storage thermal 9 at temperature To, while working fluid 20 enters the signal to select column at position 35 at temperature To and exits CFX of cold side 4 at position 30 at temperature Ti. Again, the process of heat exchange can take place at constant or almost constant pressure, so that the working fluid leaves the hot side CFX 2 in position 30 at a higher temperature, but at the same pressure P2, as indicated by P and T | in position 30.
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36/113 similarly, the temperature of the CTS 22 medium decreases in the cold side CFX 2, while its pressure can remain constant or almost constant.
[0085] 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.
[0086] In one example, the discharge mode shown in figures 3 and 5 may differ from the charge mode shown in figures 2 and 4 in the temperatures of the thermal storage media being introduced into the heat exchangers. The temperature at which the HTS medium enters the hot side CFX 2 at position 32 is Ti ⁺ , instead of To ⁺ , and the temperature of the CTS medium entering the cold side heat exchanger 4 at position 36 is To, instead of Ti. During a discharge, the working fluid enters the compressor in position 30 to To and P2, leaves the compressor in position 31 to To ⁺ <Ti ⁺ and Pi, absorbs heat from the HTS medium in the CFX of hot side 2, enters turbine 3 at position 34 at Ti ⁺ and Pi, exits the turbine at position 35 at 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 to To and P2.
[0087] HTS medium at Ti ⁺ temperature can be stored in the first thermal storage tank on the hot side
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37/113
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 medium of CTS at temperature To can be stored in a second thermal storage tank on the cold side 9 during both loading and unloading modes. 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 13 in figure 7) for switching connections between the hot-side heat exchanger 2 and the hot side 6 and 7, and / or between the cold side heat exchanger 4 and cold side tanks 8 and 9, as needed for loading and unloading modes. In some implementations, connections can be switched on the working fluid side, instead, while storage tank connections 6,
7, 8 and 9 for heat exchangers 2 and 4 to remain static. In some instances, flow paths and connections for heat exchangers may depend on the design (for example, hull and tube) of each heat exchanger. In some implementations, one or more valves can be used to switch the direction of the working fluid and the heat storage medium through the countercurrent heat exchanger for loading and unloading. These settings
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38/113 can be used, for example, due to the high thermal storage capacities of the heat exchanger component, for decreasing or eliminating temperature transients or a combination thereof. 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 pumping direction, thereby maintaining the countercurrent configuration. In some implementations, different valve configurations can be used for HTS and CTS. In addition, any combination of the valve configurations here 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).
[0088] In the discharge mode shown in figures 3 and 5, working fluid 20 can enter compressor 1 in position 30 at pressure P and temperature T (for example, To, P2) · Depending on the working fluid passes through the compressor, the 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 Tt in position 31. In the discharge mode, the To ⁺ temperature of the working fluid exiting the compressor and entering the hot side CFX 2 at position 31 is lower than the temperature of the HTS 21 medium entering the hot side CFX 2 at position 32 from a first tank thermal storage side 6 at Ti ⁺ temperature (ie, To ⁺ <Ti ⁺ ). As these two fluids pass in thermal contact with each other in the heat exchanger, the working fluid temperature increases
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39/113 as it moves from position 31 to position 34, absorbing heat Qi from the HTS medium, while the temperature of the HTS medium, in turn, decreases, as it moves from position 32 to position 33 , giving off Qi heat to 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 exits the hot side CFX 2 in position 34 at a higher temperature, but at the same pressure Pi, as indicated by P and T | in 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.
[0089] When exiting the CFX from the hot side 2 in position 34 (for example, Ti ⁺ , Pi), the working fluid 20 undergoes an expansion in turbine 3, before leaving the turbine in position
35. During expansion, the working fluid pressure and temperature decrease (for example, for paraι, P2), as indicated by P j. and T j. in position 35. The working magnitude W2 generated by the turbine depends on the enthalpy of the working fluid 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 at position 30 (eg P2) · The compression ratio (eg, P1 / P2) mp compressor 1 being equal to the expansion ratio in turbine 3
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40/113 and the enthalpy of gas entering the turbine being higher than the enthalpy of gas leaving the compressor, the work W2 generated by turbine 3 is greater than the work Wi consumed by compressor 1 (ie W2> Wi) .
[0090] Due to the heat that was added to the working fluid in the hot-side heat exchanger 2, the temperature Ti at which the working fluid exits the turbine at position 35 is higher than the temperature To at which the working fluid work initially entered the compressor at position 30. To close the cycle (ie, to return the pressure and temperature of the working fluid to its initial values To, P2 at position 30), heat Q2 is rejected by the working fluid to the CTS medium 22 in the cold side CFX 4 between positions 35 and 30 (i.e., 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 temperature To and exits the cold-side CFX 4 at position 37 to a first thermal storage tank of cold side 8 at Ti temperature, while the working fluid 20 enters the cold side heat exchanger 4 at position 35 at Ti temperature and exits the CFX cold side heat exchanger 4 at 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 hot side CFX 2 in position 30 at a higher temperature, but at the same pressure P2, as indicated by P and Tj, in position 30. Similarly, the temperature of the CTS 22 medium rises in the hot-side heat exchanger 2, while its pressure can remain constant or almost constant.
[0091] During discharge, heat Q2 is added to the
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41/113 CTS medium and heat Qi is removed from the HTS medium, where Qi> Q2 · A net amount of work W2 - Wi is generated, since the work Wi used by the compressor is less than the work W2 generated by the turbine. A device that generates work while moving heat from a hot thermal storage medium or body to a cold thermal storage medium or body is a thermal engine; thus, the thermal system pumped in the discharge mode operates like a thermal engine.
[0092] Figure 6 is a simplified schematic perspective view of a closed working fluid system in the thermal system pumped in Figures 2 to 3. As indicated, working fluid 20 (contained within a pipe) circulates clockwise between compressor 1, hot side heat exchanger 2, turbine 3 and cold side heat exchanger 4. Compressor 1 and turbine 3 can be joined on a common mechanical axis 10, so that they can rotate together. In some implementations, compressor 1 and turbine 3 may have separate mechanical shafts. A motor / generator 11 (for example, including a synchronous motor converter - synchronous generator on a single common axis) provides power to and from turbomachinery. In this example, the compressor, turbine and engine / generator are all located on a common axis. The tubes in positions 32 and 33 transfer thermal storage fluid from the hot side to and from the heat exchanger 2, respectively. The tubes in positions 36 and 37 transfer cold-side thermal storage fluid to and from the cold-side heat exchanger 4, respectively.
[0093] Although system 6 in figure 6 is illustrated
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42/113 comprising a compressor 1 and a 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 or in a configuration a configuration in parallel and or in a combination of configurations in parallel and in series. In some examples, a system of compressors or turbines can be assembled, so that a given compression ratio is obtained. In some cases, different compression ratios (for example, loading and unloading) may be used (for example, by connection or disconnection, in a parallel and / or series configuration, of 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 the turbine may have temperature-dependent compression ratios. An arrangement and / or operation of the turbomachinery and / or other elements of the system can be adjusted according to the temperature dependence (for example, to optimize performance).
[0094] Figure 7 is a simplified schematic perspective view of the thermal system pumped in Figures 2 and 3 with storage tanks on the hot and cold sides 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 communication
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43/113 fluid with a valve 13 configured for transferring the HTS medium to and from the hot-side heat exchanger 2. One or more first cold-side tanks 8 (at Ti temperature) and one or more seconds cold side tanks 9 (at temperature To), both to maintain the CTS medium, are in fluid communication with a valve 12 configured for the transfer of CTS medium to and from the cold side heat exchanger 4.
[0095] Thermal energy reservoirs or storage tanks can be thermally insulated tanks that can maintain an adequate amount of the relevant thermal storage medium (for example, a heat storage fluid). Storage tanks can allow relatively compact storage of large amounts of thermal energy. In one example, hot-side tanks 6 or 7 can have a diameter of around 80 meters, while cold-side tanks 8 and 9 can have a diameter of around 60 meters. In another example, the size of each thermal storage (ie, hot or cold side) for a 1 GW plant operating for 12 hours can be around 20 medium-sized oil refinery tanks.
[0096] 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 with the temperatures of a first tank (or set of tanks) and a second tank (or set of tanks) can be
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44/113 provided. A set of valves can be provided for switching the storage media between the different tanks and heat exchangers. For example, thermal media can be directed to different sets of tanks after leaving the heat exchangers, depending on operating conditions and / or 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.
[0097] Storage tanks (e.g., hot-side tanks comprising a hot-side thermal storage medium and / or cold-side tanks comprising a 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 around 2 atm (0.2027 MPa), at least around 5 atm (0.5066 MPa), at least around 10 atm (1.01325 MPa), at least around 20 atm (2.0265 MPa), or more. Alternatively, storage tanks can operate at reduced pressures, such as, for example, a pressure of at most around 0.9 atm (91.19 kPa), at most around 0.7 atm (70, 93 kPa), at most around 0.5 atm (50.66 kPa), at most around 0.3 atm (30.40 kPa), at most around 0.1 atm (10.13 kPa ), at most around 0.01 atm (1.013 kPa), at most around 0.001 atm (0.101 kPa), or less. In some cases (for example, when operating at higher / higher or lower pressures or to avoid contamination of the media
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45/113 thermal storage), storage tanks can be sealed in relation to the surrounding atmosphere. Alternatively, in some cases, storage tanks may not be sealed. In some implementations, tanks may include one or more pressure relief or regulation systems (for example, a valve for safety or system organization).
[0098] As used here, the first hot-side thermal storage tank (s) 6 (at Ti ⁺ temperature) may contain the HTS medium at a higher temperature than (s) second hot-side tank (s) 7 (at To ⁺ temperature), and the first cold-side tank (s) 8 (at Ti temperature) may contain medium of CTS 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 tank (s) 6 and / or the CTS medium in the second side tank (s) cold (lower temperature) 9 can be replenished. During discharge, the HTS medium in the first hot side tank (s) (highest temperature) 6 and / or the CTS medium in the second side tank (s) cold (lower temperature) 9 can be consumed.
[0099] In the preceding examples, in any mode of operation, two of the four storage tanks 6, 7, 8 and 9 are supplying thermal storage medium for heat exchangers 2 and 4 at inlets 32 and 36, respectively, and two other tanks are receiving thermal storage medium from heat exchangers 2 and 4 from outlets 33 and 37, respectively. In this configuration, the feed tanks can contain
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46/113 a storage medium at a given temperature, due to previous operating conditions, while receiving tank temperatures may depend on the current system operation (for example, operating parameters, loads and and / or power input). Receiving tank temperatures can be regulated by Brayton cycle conditions. In some cases, the receiving tank temperatures may deviate from the desired values due to deviations from predetermined cycle conditions (for example, an absolute pressure variation in response to a system demand) and / or due to an entropy generation in the system. In some cases (for example, due to the generation of entropy), at least one of the four tank temperatures may be higher than desired. In some implementations, a radiator can be used to discard or dissipate the heat loss to the environment. In some cases, a rejection of heat to the environment can be improved (for example, using evaporative cooling, etc.). The heat loss generated during an operation of the thermal system pumped here can also be used for other purposes. For example, a heat loss from one part of the system can be used elsewhere in the system. In another example, the heat loss can be provided for an external process or system, such as, for example, a manufacturing process requiring low grade heat, commercial or residential heating, thermal desalination, commercial drying operations, etc.
[0100] The components of thermal systems pumped from the exhibition may exhibit non-ideal performance, leading to losses and / or inefficiencies. The largest losses in the system can
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47/113 occur due to inefficiencies of turbomachinery (eg compressor and turbine) and heat exchangers. Losses due to heat exchangers can be small compared to losses due to turbomachinery. In some implementations, losses due to heat exchangers can be reduced to almost zero with adequate design and cost. Therefore, in some analytical examples, losses due to heat exchangers and other possible small losses due to pumps, the motor / generator and other factors can be neglected.
[0101] Losses due to turbomachinery can be quantified in terms of adiabatic efficiencies r] _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 àw = w ^ in which, in an example assuming specific heats (teíjfirrita) constant in the working fluid, - 1), f ^: ' ^em C ^ue ψ = r, r is the compression ratio (that is, a ratio of the highest pressure to the lowest pressure), and γ = cp / cv is the ratio of specific heats of the working fluid. Due to compressor and turbine inefficiencies, more work is required to obtain a given compression ratio during compression, and less work is generated during an expansion for a given compression ratio. Losses can also be quantified in terms of polytropic or single-stage efficiencies, q _C per] tp, for compressors and turbines, respectively. Polytropic efficiencies are related to adiabatic efficiencies q _c er] t by
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48/113 • η ₌ ~ ¹ 1 - Φ ^{> Í ÍJ} equations f / r ^and £ =>
[0102] In examples where q _c = jt = 1, the thermal cycles pumped from the exposure can follow identical paths in both the loading and unloading cycles (for example, as shown in figures 4 and 5). In examples where rjc <1 and / or r] t <1, a compression in the compressor can lead to a higher temperature increase than in the ideal case for the same compression ratio, and an expansion in the turbine can lead to a decrease lower temperature than in the ideal case.
[0103] In some implementations, the polytropic efficiency of the q _cp compressor can be at least around 0.3, at least around 0.5, at least around 0.6, at least around 0 , 7, at least around 0.75,
fur any less in lathe in 0.8, fur any less in lathe in 0.85, fur any less in lathe in 0, 9, fur any less in lathe in 0.91, fur any less in lathe in 0.92, fur any less in lathe in 0.93, fur any less around in 0, 96, or more In some
implementations, the polytropic efficiency of the compressor
can be at less in around 0.3 at least around in 0, 5, at least t 3m around 0.6 , fur any less in lathe in 0, 7, at least in lathe in 0.75, fur any less in lathe in 0, 8, at least in lathe in 0.85, fur any less in lathe in 0, 9, at least in lathe in 0.91, fur any less in lathe in 0, 92, at least in lathe in 0.93, fur any less in lathe in 0, 96, at least in lathe in 0.97 or more
[0104] To ⁺ , Ti ⁺ were previously defined as the temperatures obtained at the outlet of a compressor, with a given compression ratio r, an adiabatic efficiency q _c and inlet temperatures of To, Ti, resistance. In some instances, these four temperatures are related to the
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49/113. T _& ⁺ equation -— =
Tj [0105] A ₌
Figure 8 shows an example heat storage load cycle for a water (CTS) / molten salt (HTS) system with r / _c = 0.9 and r] t = 0.95. The dashed lines correspond to ar / c = pt = 1 and the continuous lines show the load cycle with r / t = 0.95 and r / c = 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 to To and P2 can exchange heat with a medium of CTS in the cold side heat exchanger 4, whereby its temperature can increase for Ti (assuming a negligible pressure loss, its pressure can remain
P2) · In compressor 1 with η _α = 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, so that its temperature can decrease (at a constant pressure Pi, assuming a negligible pressure loss). If the working fluid enters turbine 3 at r / t = 0.95 at temperature To ⁺ and expands back to its original pressure P2, its temperature when exiting the turbine may not be To. Instead, the working fluid can enter the turbine at a temperature To ⁺ and leave the turbine at temperature To and pressure P2. In some examples, the temperatures are related by the relation is the temperature at which the working fluid enters through the entrance of a turbine with an adiabatic efficiency 7] _t and a compression ratio r in order to leave at temperature To.
[010 6] In some implementations, the temperature T _o ⁺ can some examples, T _o ⁺
In
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50/113 be incorporated into exposure load cycles by the first heat exchange of the working fluid with the HTS medium from to T _o ⁺ , followed by additional cooling of the working fluid from To ⁺ to To ⁺ , as illustrated by the section 38 of the circle in figure 8.
[0107] Figure 9 shows an example heat storage discharge (extraction) cycle for the molten water / salt system in figure 8 with r / _c = 0.9 and r / t = 0.95. The dashed lines correspond to air / c = = 1 and the continuous lines show the load cycle with pt = 0.95 and r / c = 0.9. In the discharge cycle, the working fluid in Ti and P2 can exchange heat with a medium of CTS in the cold side heat exchanger 4, whereby its temperature can decrease to To (assuming a negligible pressure loss, its pressure can remain P2). In compressor 1 with η _α = 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, so that its temperature can rise (at a constant pressure Pi, assuming a negligible pressure loss). A working fluid entering turbine 3 à may not leave the turbine at temperature Ti as in the charge cycle, but, instead, it can leave at a temperature T _lr where, in some examples, T =. In some examples, T is the temperature at which the working fluid exits through a turbine outlet with adiabatic efficiency 7] _t and the compression ratio r after entering the turbine inlet at temperature Tf.
[0108] In some implementations, the temperature Tj can be incorporated in the exposure discharge cycles by
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51/113 first cooling of the working fluid leaving the turbine at T _± to Ti, as illustrated by section 39 of the cycle in figure 9, followed by the heat exchange of the working fluid with the CTS medium from Ti to To.
[0109] The loading and unloading cycles can be closed by additional heat rejection operations in sections 38 (between T _o ⁺ and T _o ⁺ ) and 39 (between T and Ti), respectively. In some cases, closing the cycles through heat rejection 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 input into the system. The sections of the cycles where the working fluid can reject heat into the environment can be limited to sections where the temperature of the working fluid is high enough above the ambient temperature for room cooling to be practicable. In some examples, heat can be rejected into the environment in sections 38 and / or 39. In some examples, heat can be rejected using one or more working fluids for air radiators, intermediate water cooling or several others methods. In some cases, the heat rejected in sections 38 and / or 39 can be used for another special purpose, such as, for example, cogeneration, thermal desalination and / or other examples described here.
[0110] In some implementations, cycles can be closed by varying the compression ratios between the loading and unloading cycles, as shown, for example, in figure 10. The ability to vary the loading and unloading compression ratio can be implemented, for example, by varying the speed of rotation of the compressor and / or the
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52/113 turbine, by a variable stator pressure control, by the deviation of a subset of the stages of compression or expansion in loading or unloading by the use of valves, or by the use of 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, so that a heat rejection in section 39 is not used, and only a heat rejection in section 38 in the load cycle is used. A variation in the compression ratio can allow heat (i.e., entropy) to be rejected at a lower temperature, thereby increasing overall round-trip efficiency. In some examples of this configuration, the compression ratio at load, rc, can be adjusted so that ii ⁺ __ i - -, and at discharge, the compression ratio ro can
Tf __ j '/ fp be set so that ~. In some cases,
Higher temperatures and Ti can be identical in loading and unloading and no heat removal may be necessary in this portion (also leg here) of the cycle. In such cases, the charged To ⁺ temperature (for example, Tq ^ = Toipç ^tp ) and the charged To ⁺ temperature (for example, To ⁺ ^ = T _o ipJ ^ηερ ) can be dissimilar and heat can be rejected (also dissipated) or abandoned here) to the environment between temperatures and. In an implementation where only the storage media exchange heat with the environment, a heat rejection device (for example, devices 55 and 56 shown in figure 16) can be used to decrease the CTS temperature from Tq ^ to Tq ^ between discharge and loading.
[0111] Figure 10 shows an example of a cycle with variable compression ratios. The compression ratio
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53/113 can be higher in discharge (when a job is produced by the system) than in load (when job is consumed by the system), which can increase the overall roundtrip efficiency of the system. For example, during a load cycle 80 with T ₀ ⁺ ^ ^c a lower compression ratio of <3 can be used; during a discharge cycle 81 with T _o ⁺ ^, a compression ratio of> 3 can be used. The higher temperatures reached in both cycles 80 and 81 can be T e, and no excess heat can be rejected.
[0112] The compression ratio can be varied between loading and unloading, so that the heat dissipation into the environment required to close the load and unload cycle between temperatures T _o (the temperature of the working fluid before it enters in the turbine during the load cycle) and Tq ^ (the temperature of the working fluid as it exits the compressor under discharge) and not above the temperature Ti (the temperature of the working fluid before it enters the compressor under load and / or out of the turbine at discharge). In some instances, no heat is rejected at a temperature
above the lowest medium temperature inin HTS. [0113] In the absence in losses system and / or inefficiencies, such as, per example, at the systems case
pumped thermals comprising heat pump (s) and thermal motor (s), operating at the entropy / isentropic creation limit, a given amount of heat Qh can be transferred using a given amount of IV in work in heat pump mode heat (charge), and the same Qh can be used in a thermal engine (discharge) mode to produce the same IV, leading to unitary roundtrip efficiency
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54/113 (i.e., 100%). In the presence of system losses and / or inefficiencies, the roundtrip efficiencies of the pumped thermal systems can be limited by how far the components deviate from optimal performance.
[0114] The roundtrip efficiency of a pumped thermal system can be defined as η _α Γτηαζβηααο = » ^{tra, cío} | / IWc ^c v ^arga l. In some examples, with an ideal heat exchange approach, the roundtrip efficiency can be derived by considering the net working output during the cycle of iM / esrífHKfc 1 __ ™, Siriite unload, PAt { ^{- {} ít ^v * ideal ^- , and the work entry 'ÍS' entíwtfc [Uf | - '' VíísttJ __ Μ7 liquid output during the charge cyclej ^ w I ^- '/ f ^ ídeaí using the equations for work and temperature given above.
[0115] Roundtrip efficiencies can be calculated for different configurations of pumped thermal systems (for example, for different classes of thermal storage media) based on turbomachine component efficiencies, r / _{c and} r / t.
[0116] In an example, figure 11 shows roundtrip 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 obtain compatibility with the salt (s) on the hot side. The example roundtrip efficiency outlines at r / _stored values of 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80% and 90% are shown as a function of component efficiencies rjc and x and y axes, respectively. The symbols © and 0 represent the approximate range of present values of adiabatic efficiency of large turbomachinery. The dashed arrows represent the direction of increased efficiency.
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55/113 [0117] Figure 12 shows roundtrip efficiency outlines 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. The example roundtrip efficiency outlines at stored n values of 10%, 20%, 30%, 40%, 50%, 60%, 70%, 80% and 90% are shown as a function of q component efficiencies _{c and} r / t on the x and y axes, respectively. The © and 0 symbols represent the approximate range of adiabatic efficiency values of large turbomachinery present. As discussed in detail elsewhere here, using hexane, heptane and / or another CTS medium capable of low temperature operation can result in significant improvements in system efficiency.
Pumped thermal recovery cycles with recovery [0118] Another aspect of the exposure is addressed 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, in which the working fluid exchanges heat with itself during different segments of a thermodynamic cycle through a continuous heat exchange without a intermediate thermal storage. The roundtrip efficiency of pumped thermal systems can be substantially improved, if the permissible temperature ranges of the storage materials
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56/113 can be extended. In some implementations, this can be accomplished 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 low temperature limit of approximately To = 179 K (94 ° C) can be used in a system with a molten salt HTS medium. However, T _o ⁺ (ie, the lowest temperature of the working fluid in the hot-side heat exchanger) in some compression ratios (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 a working fluid heat exchanger (for example, gas-gas) (also recoverer here) in the cycle.
[0119] Figure 13 is a schematic flowchart of working fluid and heat storage media from 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-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 argon. The working fluid can be a mixture of primarily argon mixed with another gas, such as helium. For example, the working fluid can comprise at least around 50% argon, at least around 60% argon, at least around 70% argon, at least around 80% argon, at least around 90% argon, or around 100% argon, with a helium balance.
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57/113 [0120] 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 dropping to approximately 179 K (- 94 ° C) and a molten salt as the hot side storage, ep _c = 0.9 and pt = 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.
[0121] In one implementation, during a load in figures 13 and 17, the working fluid enters the compressor at Ti and 2, leaves the compressor at Ti ⁺ and Pi, rejects heat Qi to the medium of HTS 21 in the CFX of hot side 2, leaving the hot side 2 CFX to Ti and Pi, rejects heat Qrecup (also Qregen in which, as shown, for example, in the associated drawings) for the cold side (low pressure) working fluid in the heat exchanger heat or stove 5, leaves stove 5 to To ⁺ and Pi, rejects heat to the environment (or another heat sink) in section 38 (for example, a radiator), enters turbine 3 to T _o ⁺ and Pi, leaves turbine to To and P2, absorbs heat Q2 from the medium of CTS 22 in the cold side CFX 4, leaving 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 leaves stove 5 Ti and P2, returning to its initial state before entering the compressor.
[0122] Figure 14 is a schematic flowchart of working fluid and heat storage media for the thermal system pumped in figure 13 in a thermal engine / discharge mode. Again, the use of the gas-gas heat exchanger
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58/113 may allow the use of the cooler heat storage fluid (CTS) and / or a cooler working fluid on the cold side of the system.
[0123] 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 dropping to 179 K ( -94 ° C) and a molten salt as the hot side storage, eq _c = 0.9 r / t = 0.95. Again, the CTS medium can be hexane or heptane and the HTS medium can be a molten salt, and the system can include 4 heat storage tanks.
[0124] During a 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 side (low pressure) working fluid at heat exchanger or stove 5, leaves stove 5 to Ti and Pi, absorbs heat Qi from the medium of HTS 21 in the hot side CFX 2, leaving the hot side CFX 2 to Ti ⁺ and Pi, enters the turbine 3 to Ti ⁺ and Pi, leaves the turbine at 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 side working fluid ( heat exchanger or stove 5, enters the cold side CFX 4 to To ⁺ and P2, rejects heat Q2 to the CTS 22 medium in the cold side CFX 4, and finally exits the cold side CFX 4 to To and P2, returning to their initial state before entering the compressor.
[0125] In another implementation, shown in figure 15, the load cycle remains the same as in figures 13 and 17, except for the fact that the working fluid leaves the
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59/113 stove 5 to T _o ⁺ and Pi (instead of To ⁺ and Pi as in figures 13 and 17), turbine 3 enters To ⁺ and Pi, leaves the turbine to To e 2, absorbs heat Q2 from the middle of CTS 22 having a temperature To ⁺ (instead of To ⁺ as in figures 13 and 17) in cold side CFX 4, and out of cold side CFX 4 to To ⁺ and P2 (instead of a To ⁺ and P2 as in figure 13) before re-entering the stove 5. The heat between the temperatures To ⁺ and Tq is no longer discharged from the working fluid into the environment directly (as in section 38 in figures 13 and 17 ).
[0126] During a discharge in figure 16, the discharge cycle remains the same as in figures 14 and 8B, except that the temperature of the HTS medium being deposited in tank 7 is changed. The working fluid leaves the stove 5 at T _± e 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 HTS medium exits the CFX on the hot side 2 having a temperature (instead of Ti as in figures 14 and 18). The working fluid then leaves the CFX on the hot side 2 at Ti ⁺ and Pi, enters turbine 3 at Ti ⁺ and Pi, and leaves the turbine at T _± and P2 before re-entering the stove 5. Heat between temperatures and 7 ^ is no longer discarded from the working fluid to the environment directly (as in section 39 in figures 14 and 18). as in figure 14, the CTS medium enters tank 8 at temperature To ⁺ .
[0127] After the discharge in figure 16, in preparation for the charge in figure 15, a heat exchange with the environment can be used to cool the HTS 21 medium from the temperature used in the discharge cycle to the temperature Ti used in the load cycle. Similarly, an exchange of
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60/113 heat 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 side and side storage media cold can be cooled at an arbitrarily slow rate (for example, by radiation or by another means of shedding heat into the environment).
[0128] 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 the medium CTS and reject heat into the environment until the CTS medium cools from temperature T _o ⁺ to temperature Tf. In some instances, 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, a 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).
[0129] Similarly, in some implementations, heat can be rejected from the HTS medium to the environment by circulating the HTS in tank 7 in a heat rejection device 56 that can absorb heat from the
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61/113 HTS medium and reject heat into the environment until the HTS medium cools from temperature T _± to temperature Ti. In some examples, the heat rejection device 5 6 can 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 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).
[0130] In some implementations, rejecting heat to the environment through the use of thermal storage media can be used in conjunction with the loading and / or unloading cycles of variable compression ratio 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 temperature ranges of the HTS and CTS media in the cycles.
[0131] In some implementations, three separate cold-side storage tanks at respective temperatures T _o , Tf and Tf can be used (for example, an extra tank can be used in addition to tanks 8 and 9). During a heat exchange on the cold side CFX 4 in the discharge cycle, heat from the working fluid exiting the stove 5 can be transferred to the CTS medium in the tank at Tf. The CTS medium can be cooled in / by, for example, the heat rejection device 55 before entering the tank at Tf. In some implementations, three separate hot-side storage tanks at respective temperatures T _lr T _r e
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62/113
Tf can be used (for example, an extra tank can be used in addition to tanks 6 and 7). During a heat exchange on the hot side CFX 2 in the discharge cycle, heat from the working fluid exiting the stove 5 can be transferred to the HTS medium in the 7 tank. The HTS medium can be cooled in / by, for example, the heat rejection device 56 before entering the tank at 7 °. Heat rejection to the environment in this way can have 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 power input / output of the system. The HTS and CTS media can reject heat, instead, for extended periods of time, thereby reducing the cost of the cooling infrastructure. In a second example, it can allow the decision with respect to when the heat is rejected to the environment to be delayed, so that a heat exchange with the environment can be carried out when a temperature (for example, the room temperature) is more favorable .
[0132] In the loading and unloading cycles of figures 13 and 17, and figures 14 and 18, respectively, the same compression ratios and the same temperature values are used for loading and unloading. In this configuration, the roundtrip efficiency can be around η stored - 7 4% _r as given by To = 194 K (-79 ° C), Ti = 494 K (221 ° C). r] t = 0.95, r / c = 0.9 and r = 3.3.
[0133] Thus, in some examples involving a working fluid for recovery of working fluid, a rejection
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63/113 heat on the hot side (high pressure side) of the closed charge cycle can occur in three operations (heat exchange with the HTS medium, followed by recovery, followed by rejection of heat to the environment), and rejection Heat on the cold side (low pressure side) of the closed discharge cycle can occur in three operations (rejection of heat to the environment, followed by recovery, followed by heat exchange 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 lowest temperature CTS tank (s) 9 can remain at To the highest temperature CTS tank (s) 8 can now (m) be at temperature To ⁺ <Ti.
[0134] In some cases, a recovery can be implemented using heat exchanger 5 for a 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 a plurality) of heat exchangers together with an additional heat transfer medium or fluid (for example, a dedicated thermal heat transfer fluid that is liquid in an appropriate temperature range , such as, for example, Therminol®) can be used for recovery. For example, an additional heat exchanger can be added in series to the cold side heat exchanger, and an additional heat exchanger can be added in series to the hot side heat exchanger. The additional heat transfer medium can circulate between the two additional heat exchangers in a closed loop. In others
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64/113 examples, one or more additional heat exchangers can be placed elsewhere in the system to facilitate recovery. In addition, one or more additional heat transfer media or mixtures may be used. One or more fluids from additional heat transfer media may be in fluid or thermal communication with one or more other components, such as, for example, a cooling tower or a radiator.
[0135] In one example, hexane or heptane can be used as the CTS medium, and 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) to To and the melting point of nitrate (494 K or 221 ° C) to 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) to To ⁺ and by the decomposition of nitrate (873 K or 600 ° C ) to Ti ⁺ . Under these conditions, the high pressure and low pressure temperature ranges can overlap, so that a recovery can be implemented. Actual To, Ti, To ⁺ and Ti ⁺ temperatures and pressure ratios implemented in hexane / nitrate systems may differ from the above limits.
[0136] In some instances, a recovery may allow the compression ratio to be reduced. In some cases, a reduction in the compression ratio can result in reduced compressor and turbine losses. In some cases, the compression ratio can be at least around 1.2, at least around 1.5, at least around 2, at least around 2.5, at least around 3, at least in
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65/113 around 3.5, at least around 4, at least around 4.5, at least around 5, at least around 6, at least around 8, at least around from 10, at least around 15, at least around 20, at least around 30, or more.
[0137] In some cases, T _o can be at least around 30 K, at least around 50 K, at least around
80 K, fur any less in lathe in 100 K, at any less in lathe in 120 K, fur any less in lathe in 140 K, at any less in lathe in 160 K, fur any less in lathe in 180 K, at any less in lathe in 200 K, fur any less in lathe in 220 K, at any less in lathe in 240 K, fur any less in lathe in 260 K, or at least around
280 K. In some cases, Tf may be at least around
in 220 K, fur any less in lathe in 240 K, at any less in lathe in 260 K, fur any less in lathe in 280 K, at any less in lathe in 300 K, fur any less in lathe in 320 K, at any less in lathe in 340 K, fur any less in lathe in 360 K, at any less in lathe in 380 K, fur any less in lathe in 400 K, or more. In . some
In such cases, temperatures T _o and Tf can be restricted by the ability to reject excess heat into the environment at room temperature. In some cases, T _or eTf temperatures may be restricted by CTS operating temperatures (for example, a phase transition temperature). In some cases, temperatures T _Q and Tf may be restricted by the compression ratio being used. Any description of temperatures T _o and / or Tf here can apply to any system or method of exposure.
[0138] In some cases, Τ _χ can be at least around 350 K, at least around 400 K, at least around 440 K, at least around 480 K, at least around
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in 520 K, fur any less in lathe in 560 K, fur any less in lathe in 600 K, fur any less in lathe in 640 K, fur any less in lathe in 680 K, fur any less in lathe in 720 K, fur any less in lathe in 760 K, fur any less in lathe in 800 K, fur any less in lathe in 840 K, fur any less in lathe in 880 K, fur any less in lathe in 920 K, fur any less in lathe in 960 K, fur any less in lathe in 1000 K, fur any less in lathe in 1100 K, fur any less in lathe
1200 K, at least around 1300 K, at least around 1400 K, or more. In some cases, Tf may be
fur any less in lathe in 480 K, at any less in lathe in 520 K, fur any less in lathe in 560 K, at any less in lathe in 600 K, fur any less in lathe in 640 K, at any less in lathe in 680 K, fur any less in lathe in 720K at least around in 760
K, fur any less in lathe in 800 K, at any less in lathe in 840 K, fur any less in lathe in 880 K, at any less in lathe in 920 K, fur any less in lathe in 960 K, at any less in lathe in 1000
K, at least around 1100 K, at least around 1200 K, at least around 1300 K, at least around 1400 K, at least around 1500 K, at least around 1600 K, at least around 1700 K, or more. In some cases, the T _± and Tf temperatures may be restricted by the HTS operating temperatures. In some cases, temperatures T _± and Tf may be restricted by the thermal limits of the metals and materials being used in the system. For example, a conventional solar salt can have a recommended temperature range of approximately 560 to 840 K. Various system improvements, such as, for example, increased roundtrip efficiency, increased power and increased storage capacity, can be performed according to available materials , metallurgy and materials
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67/113 storage improves over time and allows different temperature ranges to be obtained. Any description of temperatures T and / or Tf here can apply to any system or method of exposure.
[0139] In some cases, roundtrip efficiency η stored (eg electricity storage efficiency) with and / or without recovery can be at least around 5%, at least around 10%, at least in around 15%, at least around 20%, at least around 25%, at least around 30%, at least around 35%, at least around 40%, at least around 45%, at least around 50%, at least around 55%, at least around 60%, at least around 65%, at least around 70%, at least around 75% , at least around 80%, at least around 85%, at least around 90%, or at least around 95%.
[0140] In some implementations, at least a portion of the heat transfer in the system (for example, a heat transfer to and from the working fluid) during a charge and / or discharge cycle includes a heat transfer with the environment (for example, a transfer in sections 38 and 39). The rest of the traditionally and heat in the system can occur through thermal communication with the thermal storage media (for example, the thermal storage media 21 and 22), through a heat transfer in the stove 5 and / or through several heat transfer processes at the boundaries of the system (ie, not with the surrounding environment) In some instances, the environment may refer to gas or liquid reservoirs surrounding the system
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68/113 (for example, air, water), any system or medium capable of exchanging thermal energy with the system (for example, another thermodynamic cycle or system, heating / cooling systems, etc.), or any combination thereof . In some instances, heat transferred through thermal communication with the heat storage media can be at least around 25%, at least around 50%, at least around 60%, at least around 70%, at least around 80%, or at least about 90% of all heat transferred in the system. In some instances, heat transferred through heat transfer in the stove can be at least around 5%, at least around 10%, at least around 15%, at least around 20%, at least less than 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 media and through heat transfer in the stove can be at least around 25%, at least around 50%, at least around 60%, at least around 70%, at least around 80%, at least in
lathe in 90% , or same in in lathe in 100% at all < □ heat transferred in the system. In some examples, one heat transferred through in transfer in heat with the environment can to be in any less of what in lathe in 5%, any less of what in lathe in 10% , any less of what in lathe in 15%, any less of what in lathe in 20% , any less of what in lathe in 30%, any less of what in lathe in 40% , any less of what in lathe in 50%, any less of what in lathe in 60% , any less of what in lathe in 70%, any less of what in lathe in 80% , any less of what in lathe in 90%, any less of what in
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69/113 around 100%, or even 100% of all the heat transferred in the system. In some implementations, all heat transfer in the system can be with thermal storage media (for example, CTS and HTS media), and only thermal storage media can conduct heat transfer with the environment.
[0141] The thermal cycles pumped from the exhibition (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 different cycles of the system can be interchanged, while maintaining the same or nearly the same temperature profile, through at least one, through a subset or through of all countercurrent heat exchangers in the system. For example, valves can be configured so that the working fluid can pass through the heat exchangers in opposite directions of flow under load and discharge and flow directions of the HTS and CTS media are reversed by reversing the direction of the pumps.
[0142] In some implementations, the system with a stove may have a different compression and / or expansion ratio in loading and unloading. This can then involve heat rejection at only one or both heat rejection locations 38 and 39, as shown in figure 5C along the lines described above.
[0143] Figure 19 is a schematic flow chart of a hot side recharge in a pumped heat cycle.
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70/113 in solar mode with heating of a solar salt only by solar power. The system may comprise a solar heater for heating the hot side heat storage. The HTS medium 21 in the second hot-side thermal storage tank 7 of a discharge cycle, such as, for example, the HTS medium of the discharge cycle in figure 14, can be refilled with the element 17 using a heating provided by solar radiation. The HTS medium (e.g., a molten salt) can be heated from the temperature Ti in the second hot-side thermal storage tank 7 to the Ti ⁺ temperature in the first hot-side thermal storage tank 6.
[0144] In some implementations, such as, for example, for the systems in figures 19, a solar heat for heating the HTS medium (for example, from Ti = 493 K (220 ° C) to Ti ⁺ = 873 K ( 600 ° C)) can be provided by a solar concentration facility. In some instances, a small scale concentration facility can be used for the provision of heat. In some cases, the solar concentration installation may include one or more components to achieve high solar concentration efficiency, including, for example, high performance actuators (for example, adaptive fluid actuators made from polymers), multiplexing control, dense heliostat layout, etc. In some instances, the heat provided for heating the HTS medium (for example, in element 17) may be a loss heat stream from the solar concentration facility.
[0145] Figure 20 is a schematic flowchart of a pumped thermal system discharge cycle that can be
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71/113 coupled with an external heat input (eg solar, combustion) with heat rejection to the environment. Such a discharge cycle can be used, for example, in situations where the capacity for recharging on the hot side (for example, using solar heating, heat loss or combustion) is greater than the capacity for recharging on the side cold. A solar heat can be used to load the HTS 21 medium into the T to Tf hot-side storage tanks, as described elsewhere here. The discharge cycle can operate similarly 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, the heat exchanger 4, in which it exchanges heat with an intermediate thermal storage medium (ITS) 61 that has a lower temperature To at or near room temperature. ITS medium 61 enters the cold side CFX 4 from a second intermediate thermal attribute tank 59 at temperature To (for example, at room temperature), and exits the cold side CFX 4 to a first thermal storage tank intermediate 60 at temperature T _± , while working fluid 20 enters the cold side CFX 4 at temperature T _x and exits the cold side CFX 4 at temperature To. The working fluid enters compressor 1 to To and P2, leaves compressor to To ⁺ and Pi, absorbs heat Qi from the medium of HTS 21 in the hot side CFX 2, leaves the heat exchanger 2 to Tf and Pi, enters turbine 3 at Tf and Pi, exits the turbine at T _± and P2, rejects heat Q2 from the medium of ITS 61 in the cold side CFX 4, and leaves the cold side CFX 4 at To and P2, returning to its initial state before entering the compressor.
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72/113 [0146] In some implementations, the ITS 61 medium can be liquid over the entire range from T _o to T _x . In other implementations, the ITS 61 medium may not be a liquid over the entire range from T _o to T _lr but can be provided for the heat exchanger in countercurrent at a higher flow, in order to obtain a higher temperature rise. low through the countercurrent heat exchanger (for example, so that the temperature of the ITS medium at the outlet of the countercurrent heat exchanger 4 is lower than Tj) while the 7 to T working fluid is still cooled _o . In this case, the temperature of the ITS medium in tank 60 may be less than 7 °. The ITS medium in tank 60 can exchange heat with the environment (for example, through a radiator or other implementations described here), in order to cool back to temperature T _o . In some cases, the ITS medium can then be returned to tank 59. In some cases, the heat can be deposited in the ITS medium can be used for various useful purposes, such as, for example, residential or commercial heating, thermal desalination or other used described elsewhere here.
[0147] Figure 21 is a schematic flowchart of a thermal system discharge cycle pumped in solar mode or combustion-heated mode with heat rejection to an intermediate fluid circulated in a thermal bath at room temperature. The discharge cycle can operate similarly to the discharge cycle in figure 20, but after leaving 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 temperature To at or close to temperature
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73/113 environment. The intermediate medium or medium 62 (for example, Therminol®, or a heat transfer oil) can be used for the exchange of heat between the working fluid 20 and a thermal bath 63 in the cold side CFX 4. The use of intermediate fluid 62 can provide an advantage by contacting a heatsink or inexpensive thermal medium (e.g., water) directly with the working fluid. For example, a direct contact of a thermal medium like this with the working fluid in the cold side CFX 4 can cause problems, such as, for example, evaporation or overpressurization (for example, explosion) of the thermal medium. The intermediate fluid 62 can remain in liquid phase for the entire operation, for at least a portion of it or for a significant portion of the operation on the cold side CFX 4. As the intermediate fluid 62 passes through the thermal bath 58, it can be sufficiently cooled to circulate back to the cold side CFX 4 for cooling the working fluid from to T _o . The thermal bath 63 can contain a large amount of inexpensive material or heat dissipating medium, such as, for example, water. In some cases, the heat deposited on the heat dissipating material can be used for several useful purposes, such as, for example, residential or commercial heating, thermal desalination or other used described elsewhere here. In some cases, the heat dissipating material can be rebalanced with room temperature (for example, through a radiator or other implementations described here).
[0148] In some implementations, the discharge cycles in figures 20 and / or 21 may include a stove, as
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74/113 described in greater detail in the examples throughout the exhibition. These systems can be implemented using the Ti ⁺ , Ti, To ⁺ and To temperatures described in more detail elsewhere here.
Solar assisted pumped thermal storage cycles with intercooling [0149] 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 a colocalization with a liquid gas installation (GTL) or a desalination plant. In one example, GTL facilities 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 facility) 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 and cooling systems.
[0150] Conversely, in some cases, the pumped thermal system may make use of sources of heat loss and / or sources of loss cold from other installations or systems, such as, for example, through colocalization with a terminal for import or export of liquefied natural gas. For example, a source of loss cold can be used to cool thermal storage media
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75/113 cold side 22. In some implementations, a cold side recharge using loss cold can be combined with a recharge of the hot side thermal storage media 21 by an external heat input (for example, solar, combustion, loss heat, etc.). In some cases, the recharged storage media can then be used in a discharge cycle, such as, for example, the discharge cycles in figures 14 or 16. In some cases, the pumped thermal system can be used as a thermal motor with a loss heat source serving as the hot side heat input and a loss heat source serving as the cold side heat sink. In another implementation, the hot-side storage media can be refilled using a modified version of the cycle shown in figure 15, where the temperature T _o is almost room temperature and T _o ⁺ corresponds to a temperature above the temperature environment. In some instances, a loss heat source can be used to provide the necessary heat at a temperature of at least To ⁺ for heating the working fluid and / or the CTS to Tf medium. In another implementation, an intermediate fluid (eg Therminol®) that can remain liquid between temperatures Tf and TQ can be used to transfer the heat from the source of heat loss to the working fluid.
Thermal systems pumped with dedicated pairs of
[0151] In an additional aspect of the exhibition, pumped thermal systems comprising multiple working fluid systems or working fluid flow paths are provided. In some cases, the components of
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76/113 thermal system pumped in the loading and unloading modes can be the same. For example, the same compressor / turbine pair can be used for loading and unloading cycles. Alternatively, one or more system components 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.
[0152] Thermal systems pumped with recovery, use of external sources of heat, cold and / or heat / cold loss can benefit from having separate compressor / turbine pairs as a result of turbomachinery operation over large temperature ranges and / or different 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 a transition between cycles (for example, issues or factors related to metallurgy, thermal expansion, Reynolds number, temperature-dependent compression, tip clearance and / or bearing friction, etc.). In another example, turbomachinery (for example, turbomachinery used in systems with recovery) can operate at a relatively low pressure ratio (for example, with relatively little compression stages), but at a relatively large temperature in
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77/113 compression and expansion. The temperature ranges can vary (for example, switch 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 loading and unloading. Furthermore, a recovery, incorporation of loss heat / cold and / or other pumped thermal system resources can reduce the compression ratio of the compressor / turbine in the load cycle and / or in the discharge cycle, thereby reducing the cost associated with duplicating compressor / turbine assemblies.
[0153] Figures 22 and 23 show thermal systems pumped with separate pairs of compressor 1 / turbine 3 for a loading mode C and a discharge mode D. The separate pairs of compressor / turbine may or may not be connected on a mechanical axis. common. In this example, the compressor / turbine pairs C and D can have separate axes 10. The axes 10 can rotate at the same speed or at different speeds. Separate compressor / turbine pairs or working fluid systems may or may not share their heat exchangers (for example, heat exchangers 2 and 4).
[0154] 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 and 4 and separate pairs of compressor 1 / turbine 3 for load mode C and discharge mode D. The flow paths of HTS and CTS storage media for the load cycle are shown as continuous black lines. The
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78/113 HTS and CTS storage medium flow paths for the discharge cycle are shown as dashed gray lines.
[0155] 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 tanks for HTS 6 and 7 and tanks for CTS 8 and 9. The HTS and CTS tanks can be loaded by a compressor / turbine set C, or discharged by a compressor / turbine set D, each set comprising a compressor 1 and a turbine 3. The system can switch between sets C and D using the 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 the load set C which includes a first set of heat exchangers 2 and 4, the compressor 1 and the turbine 3. The HTS and CTS tanks can be discharged by switching to a separate discharge set C which includes a second set of heat exchangers 2 and 4, compressor 1 and turbine 3.
[0156] 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 pairs of turbomachinery using valves 83. In another example, if the loading or unloading turbomachinery assemblies or parts in figures 22 and 23 are operated at the same time (for example, in order for a set to load, followed by to an intermittent generation, and the other set to discharge at the same
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79/113 time, following a load), then each set of turbomachinery can have a dedicated set of heat exchangers. In this case, the loading and unloading sets may or may not share a set of HTS and CTS banks.
[0157] In some implementations, separate compressor / turbine sets or pairs can be used advantageously 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 power (for example, an electrical power input from wind and / or solar power systems), while a second compressor / turbine assembly can be used in a discharge cycle that follows a charge (for example, electrical power drawn into a power grid). In this configuration, pumped thermal systems positioned between a power generation system and a load can help to attenuate variations / fluctuations in input and / or output power requirements.
Hybrid pumped thermal systems [0158] According to another aspect of the exhibition, pumped thermal systems can be augmented by additional energy conversion processes and / or used directly as energy conversion systems without energy storage (ie as power generation systems). In some instances, the thermal systems pumped here can be modified to allow direct power generation using natural gas, diesel fuel, petroleum gas (eg propane / butane), dimethyl ether, fuel oil, chips
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80/113 of wood, landfill gas, hexane, hydrocarbons or any other combustible substance (for example, fossil fuel or biomass) for adding heat to the working fluid on a hot side of a working fluid cycle, and a wire side heat sink (eg water) for removing heat from the working fluid on a cold side of the working fluid cycle.
[0159] Figures 24 and 25 show pumped thermal systems configured in a generation mode. In some examples, the thermal systems pumped here can be modified by adding 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, such as a river, a lake or a reservoir; saltwater from a saltwater reservoir, such as from the sea or ocean; an air cooling using radiators, fans / blowers, convection; or a heatsink of environmental heat, such as ground / soil, cold air, etc.) 42, and a heat source (for example, a combustion chamber with a mixture of fuel and oxidizer) 43. The heat source 43 can exchange heat with a first exchanger of the two additional heat exchangers 40, and the heat sink 42 can exchange heat with a exchanger set of the two additional heat exchangers 41. The heat source 43 can be used to exchange heat with the working fluid 20.
[0160] The heat source 43 can be a source of combustion heat. In some instances, the combustion heat source may comprise a combustion chamber for combustion of a combustible substance (for example, a
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81/113 fossil fuel, synthetic fuel, municipal solid waste (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 heat loss, such as, for example, heat loss from a power plant, an industrial process (e.g., oven exhaust).
[0161] In some examples, a solar heater, a combustion heat source, a loss heat source, or any combination thereof can be used for heating the hot-side heat storage fluid and / or the heating fluid job. 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.
[0162] 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 for switching between two modes. When the valves are in the first position, the system can operate as a pumped thermal storage system (for example, a closed system in charge / discharge mode). In this configuration, the working fluid 20 (for example, argon or air) can exchange heat with an HTS medium (for example, a molten salt)
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82/113 on the hot side heat exchanger 2 and with a CTS medium (eg hexane) on the cold side heat exchanger 4. When the valves are in a second position, the system can operate as a generation system (for example, an open system in generation mode). In this configuration, heat exchangers 2 and 4 can be bypassed and the working fluid 20 can exchange heat with the combustion chamber 43 in the hot side heat exchanger 40 and with the heat sink 42 in the cold side heat exchanger. 41. Any description of the configuration and / or design of heat transfer processes (for example, heat transfer in heat exchangers) described here in relation to pumped thermal systems can also be applied to hybrid pumped thermal systems, and vice versa. For example, the heat sink 42, the heat source 43, the 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 heat. entropy associated with heat transfer processes and / or to maximize system efficiency.
[0163] 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 flow of working fluid for heat exchangers 40 and 41 and a flow of working fluid for heat exchangers 2 and 4. Alternatively, hybrid systems can operate exclusively in storage mode, or exclusively in generation mode (for example, as a peak natural gas plant). In some
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83/113 cases, the division between modes can be selected based on a system efficiency, available electrical power input (for example, based on availability), desired electrical power output (for example, based on load demand ), etc. For example, the thermal efficiency of an ideal system (that is, assuming isentropic expansion compression processes, ideal heat transfer processes) operating exclusively in generation mode can be the thermal efficiency of a working fluid going through a Brayton cycle ideal. In some cases, thermal efficiencies in hybrid exposure systems (for example, operation in exclusive and / or split mode) can be at least around 10%, at least around 20%, at least around 30 %, at least around 40%, at least around 50%, at least around 60%, or more.
[0164] Heat source 43 can be used to exchange heat with an HTS medium (for example, a molten salt). For example, the combustion heat source 43 can be used for heating the HTS 21 medium. In some cases, instead of using the combustion heat source 43 for heat exchange in the heat exchanger 40 or for exchange of heat directly between combustible gases of the combustion heat source and the working fluid, the combustion heat source 43 can be used for heating the HTS 21 medium between the two tanks of HTS 7 and 6.
[0165] Figure 26 is a schematic flowchart of hot side recharging in a heat system pumped through heating by heat source 43 (for example, a combustion heat source, a loss heat source). In one example, heat source 43 is a heat source
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84/113 waste heat, such as a source of waste heat from a refinery or other processing plant. In one example, the heat source 43 is obtained from the combustion of natural gas, in order to guarantee the sending of electricity even if the pumped thermal system runs out of charged storage media. For example, recharging the hot-side storage media using the heat source 43 can provide an advantage over recharging using electricity or other media (for example, the hourly electricity price may be too 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 for heat exchange with the working fluid in a discharge cycle, such as, for example, the discharge cycles in figures 20 and 21.
[0166] In some examples, such as, for example, when the CTS medium is a combustible substance, such as a fossil fuel (for example, hexane or heptanes), the burning of the CTS medium stored in the CTS tanks (for example, tanks 8 and 9) can be used for the provision of thermal energy for heating 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 .
[0167] The exhibition systems may be able to operate in an electricity-only storage cycle (comprising a heat transfer with an HTS medium and a CTS medium below room temperature) and in a thermal engine cycle for the environment , in which, in a
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85/113 discharge, heat is introduced from the HTS medium into the working fluid and discarded into the environment, rather than into 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). A heat rejection to the environment 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 the ITS 61 medium or the intermediate fluid 62.
[0168] Aspects of exposure can be combined synergistically. For example, systems capable of operating on an electricity-only storage cycle and an ambient thermal engine cycle may comprise a stove. Any description regarding these hybrid systems without a stove can be readily applied to systems hybridized with a stove in at least some configurations. In some cases, hybrid systems can be implemented using, for example, the parallel configuration, with valve in the figure in figure 24. For example, the countercurrent heat exchangers 4 in figures 20 and 21 can be implemented as heat exchangers. separate countercurrent heat 67 for heat exchange with the environment, and can be used in combination with countercurrent heat exchangers on the cold side 4 of the display.
[0169] In some implementations, the systems here can be configured to allow switching between different exposure cycles using a shared set of valves and tubes. For example, the system can be
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86/113 configured to switch between the electricity-only charge cycle (buffer as shown, for example, in figure 15), the electricity-only discharge cycle (as shown, for example, in figure 16), and the thermal engine cycle for environment (as shown in figure 21).
Pumped thermal systems with pressure regulating power control [0170] In one aspect of the exposure, the pressure of working fluids in pumped thermal systems can be controlled to achieve power control. In one example, the power provided for a closed system in charge mode and / or the power extracted from the closed system in a discharge and / or generation mode (for example, a work input / output using the axis 10) is proportional to the molar or mass value of the circulating working fluid. The mass flow is proportional to the peripheral portions, the area and the flow speed. The flow speed can be kept fixed in order to obtain a fixed axis speed (for example, 3,600 rpm or 3000 rpm, according to the 60 and 50 Hz power grid requirements, respectively). Thus, as the working fluid detector pressure changes, mass flow 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 axis of rotation 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 shaft speed to increase, thereby increasing the mass flow. For some period of time, before the heat stored in the
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87/113 thermal capacity of the heat exchangers itself to be dissipated, this increased mass flow can lead to an increase in the power sent, in turn increasing the speed of the shaft. Axis speed and power can continue to increase without control, resulting in uncontrolled rotary axis. In some examples, a pressure regulation can allow a control and, thus, a stabilization of the uncontrolled through an adjustment of the quantity (for example, density) of working fluid circulating according to the requirements of the system. In an example where an axle speed (and of a turbocharger, such as a turbine, affixed to the axle) starts to run out of control, a controller can reduce the mass of circulating working fluid (for example, the mass flow), in order to increase the power sent, in turn decreasing the speed of the axis. A pressure regulation can also allow for an increase in mass flow 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 combined with the heat capacity of the working fluid passing through the heat exchangers.
[0171] In some examples, the working fluid pressure in the closed system can be varied by using an auxiliary working fluid tank in fluid communication with the closed system. In this configuration, the power input / output can be decreased by transferring the working fluid from the closed loop loop to the tank, a power input / output can be increased by transferring the working fluid from the tank to the loop. closed cycle. In one example, when
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88/113 the working fluid pressure is decreased, less heat can be transferred between the thermal storage tanks on the hot and cold sides of the system as a result of the decreased mass flow and less power can be introduced into / extracted by the system.
[0172] As the working fluid pressure is varied, the compression ratios of turbomachine components can remain substantially unmodified. In some cases, one or more operating parameters and / or a configuration (for example, variable stators, axis speed) of turbomachinery components can be adjusted in response to a change in working fluid pressure (for example, to achieve a desired system performance). Alternatively, one or more pressure ratios may change in response to a change in working fluid pressure.
[0173] In some cases, a reduced cost and / or reduced parasitic energy consumption can be obtained using the power control setting in relation to other settings (for example, using a throttle valve to control the working fluid flow). In some instances, a variation in working fluid pressure while maintaining a constant (or almost constant) temperature and flow rate can lead to negligible entropy generation. In some instances, an increase or decrease in system pressure can lead to changes, for example, in turbomachinery efficiencies.
[0174] Figure 27 shows an example of a pumped thermal system with power control. The temperature of the
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89/113 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 a mass flow of working fluid due to the large heat capacities of heat exchangers 2 and 4 e / or the hot and cold side thermal storage media in tanks 6, 7, 8 and 9. In some instances, the flow rates of the HTS and CTS media through heat exchangers 2 and 4 are varied in line with a pressure change of the working fluid in order to maintain the temperatures in the heat exchangers and a working fluid in order to maintain the temperatures in the heat exchangers and in the working fluid optimized for longer periods of time. Thus, a pressure can be used to vary the mass flow in the system. One or more auxiliary tanks 44 filled with working fluid 20 (for example, air, argon or a mixture of argon and helium) may be in fluid communication with a hot side (for example, at high pressure) of the pumped thermal system and / or a cold side (for example, 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 working fluid 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 system locations (for example , one or more locations on the high pressure side of the system, on the low pressure side of the system, or
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90/113 any combination thereof). For example, the auxiliary tank can be fluid communication with the working fluid on a high pressure side and a low pressure side of the closed cycle. In some cases, fluid communication on the high pressure side can be provided after the 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 an intermediate pressure at 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 loop loop can be decreased by bleeding the working fluid from the high pressure side of the closed loop loop into the tank via a fluid path containing a valve or flow controller in mass 46, thereby loading tank 44. The amount of working fluid circulating in the closed loop loop can be increased by bleeding the working fluid from the tank to the low pressure side of the closed loop loop via a fluid path containing a valve or a controller and mass flow 45, thereby discharging the tank 44.
[0175] A power control over longer time intervals can be implemented by changing the working fluid pressure and adjusting the flow rates of the heat storage fluids on the hot side 21 and the cold side 22 through heat exchangers 2 and 4, respectively.
[0176] In some examples, flow rates from the media
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91/113 thermal storage 21 and / or 22 can be controlled (for example, by a controller) to maintain given heat exchanger inlet and outlet temperatures. In some instances, a first controller (s) may be provided for flow control (eg, mass flow) of thermal storage media, and a second controller may be provided for control of flow mass flow (for example, by mass control, mass flow, pressure, etc.) of the working fluid.
Pumped thermal systems with closed pressure generator / generator [0177] In another aspect of the exhibition, pumped thermal systems with closed pressure generator / generator are provided. The closed pressure generator / motor can be provided as an alternative for configurations where an axle (also a crankshaft here) penetrates through a working fluid retaining wall (where it can be exposed to one or more differentials of relatively high pressure), in order to connect to a motor / generator outside the
job. In some cases, the axis can to be exposed to pressures and temperatures of fluid in job at portion in pressure low cycle in fluid in job, at portion in pressure high cycle in fluid in job or both. In some cases, the seal (s) tree of cranks able in retain
the pressures to which the crankshaft is exposed to the interior of the working fluid retaining wall may be difficult to manufacture and / or difficult to maintain. In some cases, a rotary seal between high and low pressure environments can be difficult to obtain. Thus, a coupling
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92/113 from the compressor and turbine to the engine / generator can be challenging. In some implementations, therefore, the engine / generator can be placed entirely in the low pressure portion of the working fluid cycle, so that the outer pressure vessel or the working fluid retaining wall may not need to be penetrated.
[0178] Figure 28 shows an example of a thermal system pumped with a closed pressure generator 11. The motor / generator is closed in the pressure vessel or in the working fluid containment wall (shown as broken lines) and electrical cables feed-only 49 penetrate through the pressure vessel. A thermal insulation wall 48 is added to the motor / generator 11 and the working fluid in the low pressure portion of the cycle. The technical requirements for obtaining a suitable seal through the thermal insulation wall may be less restricted due to the pressure being the same on both sides of the thermal insulation wall (for example, both sides of the thermal insulation wall may be located in the low pressure portion of the cycle). In one example, the low pressure value can be around 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 intake of the turbine 3 in 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 to the operation of the engine / generator (for example, cooling a superconducting generator).
Pumped thermal systems with
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93/113 variable stator pressure
[017 9] One aspect additional gives exposure if refers to Control of pressure in cycles in fluid from work of thermal systems pumped by use of stators variables.
In some instances, the use of variable stators in turbomachine components can allow pressure ratios in working fluid cycles to be varied. The variable compression ratio can be achieved by having mobile stators in the turbomachinery.
[0180] In some cases, pumped thermal systems (for example, the systems in figures 17 and 18) can operate at the same compression ratio in both 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 when switching between the load cycle and the discharge cycle. In one example, different stators can be added to the compressor and the turbine, thus allowing the compression ratio to be regulated. The ability to vary the compression ratio between loading and unloading modes can allow heat to be rejected at the lowest temperature only (for example, heat can be rejected in section 38 in the load cycle, but not in section 39 in the cycle discharge). In some instances, a larger portion (or all) of the heat discharged into the environment is transferred at a lower temperature, which can increase the system's round-trip efficiency.
[0181] Figure 29 is an example of variable stators
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94/113 in a compressor / turbine pair. The compressor and turbine 3 can both have variable stators, so that the compression ratio for each can be regulated. This fine adjustment can increase roundtrip efficiency.
[0182] The compressor and / or the turbine may include (each) one or more stages of compression. For example, the compressor and / or the turbine may have multiple rows of repeated features distributed along its circumference. Each compression stage can comprise one or more rows of resources. The rows can be arranged in a given order. In one example, compressor 1 and turbine 3 each comprise a sequence of a plurality of inlet guide vanes 51, a first plurality of rotors 52, a plurality of stators 53, a second plurality of rotors 52 and a plurality of outlet guide vanes 54. Each of the plurality of features can be arranged in a row 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.
[0183] The compressor / turbine pair can be combined. In some cases, a compressor outlet pressure can be almost the same as a turbine inlet pressure, and a compressor inlet pressure can be almost the same as the turbine outlet pressure; thus, the pressure ratio through the turbine can be the same as the pressure ratio through the compressor. In some cases, inlet / outlet pressures and / or pressure ratios may differ by a given amount (for example, to account for pressure loss in the system). The use of variable stators
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95/113 on the compressor and the turbine can allow the compressor and the turbine to remain combined, as the compression ratio is varied. For example, using variable stators, a compressor and turbine operation can remain with adequate operating conditions (for example, in a given range or at a given point in their respective operation maps), depending on the compression ratio is varied. An operation in given ranges or at given points on turbomachinery operation maps can allow turbomachinery efficiencies (eg isentropic efficiencies) and the resulting roundtrip storage efficiency to be maintained within a desired range. In some implementations, the use of variable stators can be combined with other methods for varying the compression ratios (for example, variable axis rotation speed, deviation of turbomachine stages, gears, power electronics, etc.).
Pumped thermal system units comprising pumped thermal system subunits [0184] An additional aspect of the exposure relates to a control of loading and unloading rate over a full load input / maximum power range for unloading output / maximum power for the construction of composite pumped thermal system units comprised of pumped thermal system subunits. In some instances, pumped thermal systems may have a minimum power input and / or output (for example, a minimum power input and / or a minimum power output) above 0% of a power input and / or output maximum (for example, a maximum power input
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96/113 and / or a maximum power output), respectively. In such cases, a single unit by itself may be able to ramp continuously from the minimum power input to the maximum power input and from the minimum power output to the maximum power output, but it may not be able to continuously ramp from the input minimum power output for minimum power output (ie minimum power input for zero power input / output, and zero power input / output for minimum power output). An ability to continuously ram from the minimum power input to the minimum power output can allow the system to continuously ram from the maximum power input to the maximum power output. For example, if both the output power and the input power can be deactivated all the way to zero during an operation, the system may be able to continuously vary the power consumed or supplied across a range of the maximum input (for example, acting as a load on the grid) to the maximum output (for example, acting as a generator on the grid). This functionality can increase (for example, more than double) the continuously branchable range of the pumped thermal system. An increase in the continuously branchable range of the pumped thermal system can be advantageous, for example, when a continuously branchable power range is used as a measure for determining the value of network assets. Furthermore, this functionality can allow the exhibition systems to follow a variable load, a variable generation, an intermittent generation or any combination of them.
[0185] In some implementations, composite pumped thermal system units comprise multiple
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97/113 pumped thermal system subunits can be used. In some cases, each subunit may have a minimum power input and / or output above 0%. The continuous rampage of the power from the maximum power input to the maximum power output may include the combination of a given number of subunits. For example, an adequate number (for example, sufficiently large) of subunits may be necessary to obtain a continuous ramp. In some examples, the number of subunits can be at least around 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 each power capacity. For example, each subunit may have a power capacity that is less than around 0.1%, less than around 0.5%, less than around 1%, less than around 5%, less than around 10%, less than around 25%, less than around 50%, or less than about 90% of the total power capacity of the composite pumped thermal system. In some cases, different subunits may have different power capacities. In some examples, a subunit has a power capacity of around 10 kW, 100 kW, 500 kW, 1 MW, 2 MW, 5 MW, 10 MW, 20 MW, 50 MW, 100 MW, or more. The continuous rampage of the power from the maximum power input to the maximum power output can include the control of input and / or power output of each subunit (for example, one or more subunits can operate in a power input mode, while one or more subunits
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98/113 can operate in power output mode). In one example, if each pumped thermal system subunit can be ramped continuously between a maximum power input and / or output down to around 50% of the maximum power input and / or output, respectively, three or more of these pumped thermal system subunits may be combined into a composite pumped thermal system unit that can be continuously ramped from maximum input power to maximum output power. In some implementations, the composite pumped thermal system may not have a fully continuous range between the maximum input power and the maximum output power, but it may have an increased number of operating points in this range, compared to a non-composite system.
Energy storage system units comprising energy storage system subunits [0186] An additional aspect of the exposure relates to a control of loading and unloading rate over a full load input / maximum power range for unloading output / maximum power by building composite energy storage system units comprised of energy storage system subunits. In some instances, energy storage systems may have a minimum power input and / or output (for example, a minimum power input and / or a minimum power output) above 0% of the input and / or output of maximum power (for example, a maximum power input and / or maximum power output), respectively. In such cases, a single unit by itself may be able to
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99/113 continuously ramping from the minimum power input to the maximum power input and from the minimum power output to the maximum power output, but you may not be able to continuously ram from the minimum power input to the maximum power output minimum power (that is, from the minimum power input to zero power input / output, and from a zero power input / output to the minimum power output). An ability to continuously ram from the minimum power input to the minimum power output can allow the system to continuously ram from the maximum power input to the maximum power output. For example, if both the output power and the input power can be deactivated all the way to zero during an operation, they may be able to continuously vary the power consumed or supplied across a range from the maximum input (for example , acting as a load on the grid) to the maximum output (for example, acting as a generator on the grid). This functionality can increase (for example, more than double) the continuously branchable strip of the energy storage system. An increase in the continuously branchable range of the energy storage system can be advantageous, for example, when a continuously branchable power range is used as a measure for determining the value of network assets. Furthermore, this functionality can allow the exhibition systems to follow a variable load, a variable generation, an intermittent generation or any combination of them.
[0187] In some implementations, composite energy storage system units comprised of multiple energy storage system subunits
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100/113 can be used. In some examples, any energy storage system having power input / output characteristics that can benefit from a composite configuration can be used. In some examples, systems having power input and / or power output characteristics that can benefit from a composite configuration may include various storage and / or power generation systems, such as, for example, power plants. natural or combined cycle gas, fuel cell systems, battery systems, compressed air storage systems, pumped hydroelectric systems, etc. In some cases, each subunit may have a minimum power input and / or output above 0%. The continuous rampage of the power from the maximum power input to the maximum power output may include the combination of a given number of subunits. For example, an adequate number (for example, sufficiently large) of subunits may be necessary to obtain a continuous ramp. In some examples, the number of subunits can be at least around 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 may have an given capacity of power. Per example, each subunit may have an
power capacity that is less than around 0.1%,
smaller of what in lathe in 0.5% , smaller than around in 1% smaller of what in lathe in 5%, smaller of what in lathe in 10% smaller of what in lathe in 25%, smaller of what in lathe in 50%
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101/113 or less than around 90% of the total power capacity of the composite energy storage system. In some cases, different subunits may have different power capacities. In some examples, a subunit has a power capacity of around 10 kW, 100 kW, 500 kW, 1 MW, 2 MW, 5 MW, 10 MW, 20 MW, 50 MW, 100 MW, or more. The continuous rampage of the power from the maximum power input to the maximum power output can include controlling the input and / or power output of each subunit (eg power input and / or power output) separately. In some cases, the subunits can be operated in opposite directions (for example, one or more subunits can operate in a power input mode, while one or more subunits can operate in a power output mode). In one example, if each energy storage system subunit can be continuously ramped between a maximum power input and / or output down to around 50% of the maximum power input and / or output, respectively, three or more these energy storage system subunits may be combined into a composite energy storage system unit that can be continuously ramped from maximum input power to maximum output power. In some implementations, the composite energy storage system may not have a fully continuous range between the maximum input power and the maximum output power, but it may have an increased number of operating points in this range, compared to a non-powered system. composite '.
Control system
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102/113 [0188] The present exhibition provides computer control systems (or controllers) that are programmed to implement the methods of the exhibition. Figure 30 shows a 1901 control system (or controller) that is programmed or otherwise configured to regulate various process parameters of storage and / or energy recovery systems exposed here. These process parameters can include temperatures, flows, pressures and changes in entropy.
[0189] The 1901 computer system includes a central processing unit (CPU, also processor and computer program here) 1905, which can be a single-core or multi-core processor, or a plurality of processors for processing in parallel. The 1901 computer system also includes a memory or 1910 memory location (for example, a random access memory, a read-only memory, a flash memory), a 1915 electronic storage unit (for example, a hard disk), a 1920 communication interface (for example, a network adapter) for communication with one or more other systems, and 1925 peripheral devices, such as cache, other memory, data storage and / or electronic display adapters. The memory 1910, the storage unit 1915, the interface 1920 and peripheral devices 1925 are in communication with the 1905 CPU through a communication bus (continuous lines), such as a motherboard. The 1915 storage unit can be a data storage unit (or a data repository) for data storage. The 1901 computer system can
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103/113 be operatively coupled to a computer network (network)
1930 with the aid of the 1920 communication interface.
1930 may it will be Internet, an internet and / or extranet, or an intranet and / or extranet what it is in communication with The Internet. The 1930 network in some cases it's a network in
telecommunication and / or data. 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 client or a server.
[0190] The 1901 computer system is coupled with a 1935 energy storage and / or recovery system, which can be as described above or elsewhere here. The 1901 computer system can be coupled with various unit operations of the 1935 system, such as flow regulators (eg valves), temperature sensors, pressure sensors, compressor (s), turbine (s), electric switches and photovoltaic modules. The 1901 system can be directly coupled to or be part of the 1935 system, or be in communication with the 1935 system through the 1930 network.
[0191] The 1905 CPU can execute a sequence of instructions that can be read on a machine, which can be implemented in 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 initial writing.
[0192] With continued reference to figure 30, the unit
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104/113 storage 1915 can store files such as drivers, 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, such as located on a remote server that is communicating with the 1901 computer system via an intranet or from Internet.
[0193] 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 (for example, an operator ). Examples of remote computer systems include trainsets, slate or tablet PCs, phones, smartphones, or personal digital assistants. The user can access the 1901 computer system through the 1930 network.
[0194] The methods as described here can be implemented using machine executable code (for example, a computer processor) stored in an electronic storage location on the 1901 computer system, such as, for example, in 1910 memory or on the 1915 electronic storage unit. Code that is executable on a machine or that can be read on a machine can be provided in the form of software. During use, the code can be executed by the 1905 processor. In some cases,
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105/113 the code can be retrieved from the 1915 storage unit and stored in the 1910 memory for ready access by the 1905 processor. In some situations, the 1915 electronic storage unit can be deleted, and machine executable instructions are stored in the memory 1910.
[0195] The code can be precompiled and configured for use with a machine having a processor adapted to execute the code, or it can be compiled during the run time. The code can be supplied in a programming language that can be selected to allow the code to be executed in a pre-compiled form or as compiled.
[0196] Aspects of the systems and methods provided here, such as the 1901 computer system, can be realized in programming. Various aspects of technology can be thought of as products or articles of manufacture typically in the form of code executable on a machine (or processor) and / or associated data that is ported or realized in a type of medium that can be read on a machine. Machine executable code can be stored in an electronic storage unit, such as a memory (for example, a read-only memory, a random access memory, a flash memory) or a hard disk. Storage type media can include any or all of the computers' tangible memory, processors or similar or associated modules, such as various semiconductor memories, tape drives, disk drives and the like, which can provide a non-transitory storage in
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106/113 any time for software programming. All portions of the software can sometimes be communicated via the Internet or several other telecommunication 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 media that can carry the software elements includes optical, electrical and electromagnetic waves, such as used through physical interfaces between local devices, through wired and optical landline networks and through various air links. The physical elements that can carry these waves, such as wired or wireless links, optical links or the like, can also be considered as media carrying the software. As used here, unless restricted to non-transitory tangible storage media, terms such as medium that can be read on a computer or machine refer to any medium that participates in providing instructions for a processor to run.
[0197] Thus, a medium that can be read on a machine, such as executable code on a computer, can take many forms, including, but not limited to, a tangible storage medium, a carrier wave or a physical transmission medium. Non-volatile storage media include, for example, optical or magnetic disks, such as any storage devices on any computers or the like, as can be used for implementing databases, etc., shown in

权利要求:
Claims (5)
[1]
1. System, characterized by the fact of understanding:
a compressor;
a stove;
a hot-side heat exchanger;
a turbine;
a cold side heat exchanger;
a cooling heat exchanger; and a working fluid circulating in a closed cycle path through, in sequence, the compressor, the stove, the hot side heat exchanger, the turbine, the stove, the cooling heat exchanger and the heat exchanger of cold side, where the cooling heat exchanger is configured to remove heat from the working fluid.
[2]
2. System, according to claim 1, characterized by the fact that it still comprises:
a first cold-side thermal storage tank (CTS);
a second CTS tank; and a CTS medium flowing from the first CTS tank, through the cold side heat exchanger and to the second CTS tank.
3. System, in a deal with The claim 2 characterized by fact of the means of CTS be hexane. 4. System, in a deal with The claim 2
characterized by the fact that it still understands:
a first hot-side thermal storage tank (HTS);
a second tank of HTS; and
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2/5 an HTS medium flowing from the first HTS tank, through the hot side heat exchanger and to the second HTS tank.
5. System according to claim 4, characterized in that the HTS medium is molten salt.
6. System according to claim 1, characterized by the fact that the cooling heat exchanger is a radiator, in which the working fluid circulating through the cooling heat exchanger expels heat into the air.
7. System according to claim 1, characterized by the fact that the cooling heat exchanger circulates a thermal fluid in thermal contact with a heat sink.
8. System according to claim 7, characterized by the fact that the heat sink is a cooling tower.
9. System, characterized by the fact of understanding:
a compressor;
a stove;
a hot-side heat exchanger;
a turbine;
a cold side heat exchanger;
a working fluid circulating in a closed cycle path through, in sequence, the compressor, the stove, the hot side heat exchanger, the turbine, the stove, and the cold side heat exchanger;
the cold-side thermal storage medium (CTS);
a first CTS tank;
an intermediate CTS tank;
Petition 870190095539, of 9/24/2019, p. 8/13
[3]
3/5 a CTS heat exchanger, in which the CTS heat exchanger is configured to remove heat from the CTS medium;
a second CTS tank;
a first flow path configured to flow CTS medium from the first CTS tank, through the cold side heat exchanger and to the intermediate CTS tank; and a second flow path configured to flow CTS medium from the intermediate CTS tank, through the
heat exchanger10. System, of CTSin is forwake up the second CTS tank. with The claim 9 characterized by fact of the means of CTS be hexane. 11. System, in wake up with The claim 9
characterized by the fact that it still understands:
a first hot-side thermal storage tank (HTS);
a second tank of HTS; and an HTS medium flowing from the first HTS tank, through the hot side heat exchanger and to the second HTS tank.
12. System, according with the claim 11, characterized by fact that exchanger CTS heat to be a cooling tower. 13. System, according with the claim 11,
characterized by the fact that the CTS heat exchanger is a radiator, in which the CTS medium flowing through the CTS heat exchanger expels heat into the air.
14. System, according to claim 11, characterized by the fact that it also comprises a third flow path configured to flow the CTS medium to
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[4]
4/5 from the second CTS tank to the first flow path and inject CTS medium from the second CTS tank to the first flow path.
15. System according to claim 14, characterized in that the third flow path intercepts the first flow path at an intermediate location for the first flow path entering the cold side heat exchanger and for the first flow path. flow out of the heat exchanger.
16. Method, characterized by the fact of understanding:
in a closed-loop system operating in a power generation mode, the circulation of a working fluid through a closed-loop fluid path, including, in sequence, a compressor, a stove, a hot-side heat exchanger , a turbine, the stove and a cold side heat exchanger;
the flow of a hot-side thermal storage medium (CTS) at a first variable flow from a first CTS tank, through the cold-side heat exchanger and in thermal contact with the working fluid, and to a tank intermediate CTS; and the flow of the CTS medium from the intermediate CTS tank, through a CTS heat exchanger and to a second CTS tank, in which the CTS heat exchanger is configured to remove heat from the CTS medium.
17. Method according to claim 16, characterized in that the closed loop system is a closed Brayton cycle system.
18. Method, according to claim 16, characterized by the fact that it still comprises varying the
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[5]
5/5 first variable flow based on a CTS medium temperature.
19. Method, according to claim 18, characterized by the fact that it still comprises the flow of the CTS medium in a second variable flow from the second tank to the cold side heat exchanger.
20. Method, according to claim 19, characterized by the fact that it still comprises the variation of the second variable flow based on a temperature of the CTS medium.

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CA3087030C|2021-06-15|

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WO2018125510A3|2018-08-02|

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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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2022-01-25| 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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US15/392,657|US10233787B2|2016-12-28|2016-12-28|Storage of excess heat in cold side of heat engine|

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PCT/US2017/064074|WO2018125510A2|2016-12-28|2017-11-30|Storage of excess heat in cold side of heat engine|

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