WO2010085574A1 - Stockage d'énergie thermique pour applications en surchauffe - Google Patents

Stockage d'énergie thermique pour applications en surchauffe Download PDF

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Publication number
WO2010085574A1
WO2010085574A1 PCT/US2010/021675 US2010021675W WO2010085574A1 WO 2010085574 A1 WO2010085574 A1 WO 2010085574A1 US 2010021675 W US2010021675 W US 2010021675W WO 2010085574 A1 WO2010085574 A1 WO 2010085574A1
Authority
WO
WIPO (PCT)
Prior art keywords
thermal energy
energy storage
conduit
storage medium
thermal
Prior art date
Application number
PCT/US2010/021675
Other languages
English (en)
Inventor
David R. Mills
Weili Cheng
Original Assignee
Ausra, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ausra, Inc. filed Critical Ausra, Inc.
Publication of WO2010085574A1 publication Critical patent/WO2010085574A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/028—Steam generation using heat accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F28D2020/0047—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material using molten salts or liquid metals
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • Thermal energy storage systems may, in various circumstances, be incorporated in thermal power plants and process or industrial steam systems, including those that employ nuclear reactors, package boilers and solar energy collector systems.
  • the thermal energy storage systems may be required as buffers against transient demands that exceed the steady state output capacities of plants, against temporary reduction in input heat or, alternatively, to provide long term thermal energy storage when heat generating capabilities cannot, for various reasons, be synchronized with load demands.
  • One or the other or all of these requirements may exist in relation to thermal power plants and in process or industrial steam systems, including those incorporating solar energy collector systems for use in generating thermal energy.
  • Solar energy collector systems may comprise, for example, parabolic trough systems, central receiver with 2-axis heliostat systems, or Linear Fresnel Collector (LFR) systems.
  • LFR systems employ a field of reflectors and elevated receivers that are illuminated by reflected radiation for energy exchange with fluid that is carried through the receivers.
  • An LFR system is typically employed in the heating of a working fluid for delivery to an electrical generating plant, either for admission directly to a turbine or for heat exchange with fluid that is expanded through the turbine. Heated working fluid may also be used in process or industrial steam systems.
  • Solar energy collector systems function only when adequate incident solar radiation is present and, in order to prolong the duty cycle of solar-based power generation, to help to accommodate transient reductions of solar radiation, or to provide a buffer against transient loads, thermal energy produced in excess of demand during periods of high-level solar radiation and/or low power consumption may be stored.
  • Thermal energy stored in the thermal energy storage system may be extracted by heating a working fluid, which may be delivered to an electrical generating plant, either for admission directly to a turbine or for heat exchange with a fluid that is expanded through the turbine. Steam turbines utilizing superheated steam are more efficient than those using saturated steam. Thus, thermal energy storage systems which can store thermal energy and can generate superheated steam upon discharging are desired. Additionally, thermal energy stored in the thermal energy storage system may be extracted for use in process or industrial steam systems. Superheated steam may additionally be desired for use in these applications.
  • the invention provides thermal energy storage systems and methods for using the thermal energy storage systems to store thermal energy, wherein the source of the thermal energy is superheated steam.
  • the thermal energy may be extracted from the thermal energy storage system as superheated steam at a later time point during discharge of the system.
  • the thermal energy storage systems of the invention are comprised of one or more conduits arranged to carry a working fluid (e.g. water/steam) disposed within, and in thermal contact with, a thermal energy storage medium.
  • the thermal energy storage system is charged by flowing superheated steam into the conduit(s), whereby heat is transferred from the steam to the medium for storage.
  • the thermal energy storage system may be discharged at a later time point by flowing water into the conduit(s), whereby heat is transferred from the medium to the water, thereby producing superheated steam.
  • superheated steam may be extracted from the thermal energy storage system upon discharge.
  • the zones shown in Figure IA shift to the right (see Figure IB), or, within the context of the thermal energy storage system, the zones shift within the medium longitudinally along the length of the conduit towards the system exit.
  • the system may or may not have a preheat zone. While not necessary to the operation of the system, it is preferred in some embodiments that sufficient heat from the working fluid be transferred to the thermal energy storage medium such that little or no steam exits the system, in order to avoid waste of thermal energy.
  • the temperature gradient created within the thermal energy storage medium along the length of the conduit is maintained by limiting thermal conductivity within the thermal energy storage medium in the longitudinal direction along the length of the conduit.
  • the thermal storage medium may in some variations be homogeneous in composition and/or structure along the length of the conduit, and in other variations, the composition and/or structure of the storage medium may vary along the length of the conduit. In some variations, the volume and/or mass of the storage medium that is in thermal contact with the conduit may vary along the length of the conduit.
  • a storage medium may be selected to have an intermediate thermal conductivity, high enough so that sufficient heat can be transferred to the medium within a desired storage time period without requiring excessive conduit lengths, but not so high that substantially thermal equilibration along the length of the conduit occurs within the storage period.
  • limited thermal conductivity may be achieved by the particular materials used for the thermal energy storage medium and/or by physical barriers within the medium. Creation and maintenance of the temperature gradient may result in more efficient and effective utilization of stored heat, may increase efficient heat transfer into and out of the thermal energy storage medium, may increase the maximum temperature of the heated working fluid upon system discharge, and may increase the length of time in which superheated steam may be extracted from the thermal energy storage system.
  • a thermal energy storage medium which has very high or infinite thermal conductivity within the medium longitudinally along the length of the conduit would quickly reach temperature equilibrium as heat is transferred from the medium into the working fluid during discharge, and the medium would not support two or more discernable temperature zones (e.g. superheat, latent heat, and preheat zones), but would have essentially a single temperature zone.
  • the temperature of the working fluid exiting the system upon system discharge is limited by the temperature of the medium.
  • the temperature of the medium decreases upon thermal heat extraction, the temperature of the working fluid exiting the system will decrease accordingly.
  • superheated steam may be initially extracted from such a system, if the temperature of substantially the entire volume of the medium is initially heated to a superheat temperature, once sufficient heat is transferred out of the medium, the medium temperature would reach that of the latent heat zone. Once the medium is at the latent heat zone temperature, no additional superheated steam may be extracted from the thermal energy storage system, and saturated steam is produced. As more thermal energy is transferred into the working fluid, the medium temperature eventually reaches the preheat zone, and heated water is produced. Such a medium limits the ultimate temperature of the steam and the amount of superheated steam which may be extracted from the thermal energy storage system, and additionally, if there is no practical use for the lower energy working fluid (i.e. saturated steam and heated water), wastes a large portion of the thermal energy stored within the medium.
  • saturated steam and heated water wastes a large portion of the thermal energy stored within the medium.
  • the temperature gradient within the medium is maintained longitudinally along the length of the conduit, such that a superheat zone is maintained within the system for a much longer period of time, and superheated steam may be extracted over a much longer period of time.
  • a thermal energy storage system comprising: (a) a conduit arranged to carry a working fluid; and (b) a thermal energy storage medium; wherein the conduit is disposed within and in thermal contact with the thermal energy storage medium; wherein during charging or discharging of the thermal energy storage system with thermal energy, a temperature gradient is created in the thermal energy storage medium longitudinally along the length of the conduit.
  • the temperature gradient may shift along the length of the conduit as the system continues to charge and/or discharge.
  • the thermal energy storage system may generate superheated working fluid (e.g. superheated steam) upon discharge of the system.
  • the thermal energy storage medium has a substantially homogeneous composition and/or structure along the length of the conduit.
  • the thermal energy storage medium composition and/or structure varies (e.g. in two or more discernible regions) along the length of the conduit.
  • the physical distribution of a thermal energy storage medium varies along the length of the conduit, e.g. so that a volume or mass of the medium in contact with the conduit at one end of the system is less than a volume or mass of the medium in contact with the conduit at an opposing end of the system.
  • the thermal energy storage medium is not pumped or otherwise moved under an external force.
  • the thermal energy storage medium comprises a highly viscous liquid or slurry, where convective heat exchange is low due to the high viscosity, and where conductive heat exchange is also low as compared to a metal such as iron or steel.
  • one or more regions of the thermal energy storage medium are physically separated from each other, for example by a thermally insulating material having a thermal conductivity much less than adjacent material.
  • the conduit may be linear and/or follow a serpentine or coiled (e.g. helical) or other non-linear path within the thermal energy storage medium.
  • a conduit may be substantially in one plane (e.g. linear, serpentine), or may be three- dimensional (e.g. coiled). In some embodiments, the conduit is linear.
  • the conduit is serpentine. In some embodiments, the conduit is coiled. In some embodiments, the conduit is distributed non-uniformly within the thermal energy storage medium. The conduit may be placed more densely in one region within the thermal energy storage medium than in another region. In some embodiments, the conduit is serpentine, and the spacing period varies. In some embodiments, the conduit has a larger cross-sectional area in one region of the thermal energy storage medium than in another region. In some embodiments, the system may comprise a different volume (e.g. larger or smaller diameter) of thermal energy storage medium surrounding the conduit along its length as the conduit extends through or traverses the thermal energy storage medium.
  • a different volume e.g. larger or smaller diameter
  • the method comprising: (a) flowing steam into a conduit disposed within and in thermal contact with a thermal energy storage medium, whereby heat is transferred from the steam to the medium for storage; and (b) forming a temperature gradient in the medium longitudinally along a length of the conduit, the temperature gradient in operation translating along the length of the conduit according to heat transfer between the steam and the medium.
  • sufficient heat is transferred from the steam to the medium such that water exits the conduit.
  • sufficient heat is transferred from the steam to the medium such that substantially no steam exits the conduit.
  • the temperature gradient is comprised of a superheat zone, a latent heat zone, and a preheat zone.
  • the temperature gradient is comprised of a superheat zone and a latent heat zone.
  • superheated steam may be extracted from the thermal energy storage system at a later time point.
  • at least a portion of the thermal energy storage medium within the superheat zone is fully saturated with thermal energy upon charging the system and the medium has a substantially uniform temperature along at least a portion of the conduit within the superheat zone.
  • a method for storing thermal energy comprising: (a) flowing steam into a conduit disposed within and in thermal contact with a thermal energy storage medium, whereby heat is transferred from the steam to the medium for storage; and (b) thermally saturating a zone of the medium with heat so that the zone has a substantially uniform temperature, wherein substantially no condensation of the steam occurs within the conduit in thermal contact with the medium in the zone.
  • any of the thermal energy storage systems as described herein may be used in a method of storing thermal energy as described herein, and any of the methods of storing thermal energy as described herein may be used in conjunction with a thermal energy storage system as described herein. Accordingly, in additional aspects of the invention are: a method of storing thermal energy by use of a thermal energy storage system as described herein, and a thermal energy storage system for use in any of the methods as described herein.
  • thermal energy power plant comprising a thermal energy storage system as described herein.
  • FIGS. IA- IB provide general graphical illustrations of the temperature of a thermal energy storage medium in thermal contact with a conduit as a function of position along the conduit for an example of a thermal energy storage system as described herein.
  • FIGS. 2A-2B provide side cross-sectional views of an example of a thermal energy storage system.
  • FIGS. 3A-3B provide illustrations of an example of a thermal energy storage system comprising first and second annular thermal energy storage regions.
  • FIG. 4 provides a schematic illustration of a variation of a thermal energy storage system in which a cross-sectional diameter of conduits within the system vary along the length of the conduits.
  • FIG. 5 provides a schematic illustration of a variation of a thermal energy storage system in which the conduits comprise multiple conduits feeding into a single conduit.
  • FIG. 6 provides a schematic illustration of a variation of a thermal energy storage system in which a mass or thermal mass of thermal energy storage medium surrounding and in thermal contact with a conduit varies along the length of the thermal conduit.
  • FIG. 7 provides a schematic illustration of a variation of a thermal energy storage system in which a packing density of a serpentine conduit varies along the length of the conduit.
  • FIG. 8 provides a schematic illustration of a variation of a thermal energy storage system in which two coiled conduits are embedded in a thermal energy storage medium, and the pitch of the coils varies along the length of the system, and the thermal properties of the medium vary along the length of the system.
  • FIGS. 9A-9C provide illustrations of examples of thermal energy storage systems in which the thermal energy storage medium is contained within a long cylinder, multiple cylinders positioned axially along the length of the conduit, or multiple coaxial cylinders.
  • a thermal energy storage system comprising: (a) a conduit arranged to carry a working fluid; and (b) a thermal energy storage medium; wherein the conduit is disposed within and in thermal contact with the thermal energy storage medium; wherein during charging or discharging of the thermal energy storage system with thermal energy, a temperature gradient is created in the thermal energy storage medium longitudinally along the length of the conduit.
  • the temperature gradient may shift along the length of the conduit as the system continues to charge and/or discharge.
  • the thermal energy storage system may generate superheated working fluid (e.g. superheated steam) upon discharge of the system.
  • the thermal energy storage medium has a substantially homogeneous composition and/or structure along the length of the conduit.
  • the thermal energy storage medium composition and/or structure varies (e.g. in two or more discernible regions) along the length of the conduit.
  • the physical distribution of a thermal energy storage medium varies along the length of the conduit, e.g. so that a volume or mass of the medium in contact with the conduit at one end of the system is less than a volume or mass of the medium in contact with the conduit at an opposing end of the system.
  • the thermal energy storage medium is not pumped or otherwise moved under an external force.
  • the thermal energy storage medium comprises a highly viscous liquid or slurry, where convective heat exchange is low due to the high viscosity, and where conductive heat exchange is also low as compared to a metal such as iron or steel.
  • one or more regions of the thermal energy storage medium are physically separated from each other, for example by a thermally insulating material having a thermal conductivity much less than adjacent material.
  • the conduit may be linear and/or follow a serpentine or coiled (e.g. helical) or other non-linear path within the thermal energy storage medium.
  • a conduit may be substantially in one plane (e.g. linear, serpentine), or may be three- dimensional (e.g. coiled). In some embodiments, the conduit is linear.
  • the conduit is serpentine. In some embodiments, the conduit is coiled. In some embodiments, the conduit is distributed non-uniformly within the thermal energy storage medium. The conduit may be placed more densely in one region within the thermal energy storage medium than in another region. In some embodiments, the conduit is serpentine, and the spacing period varies. In some embodiments, the conduit has a larger cross-sectional area in one region of the thermal energy storage medium than in another region. In some embodiments, the system may have a different volume or mass (e.g. larger or smaller diameter) of thermal energy storage medium surrounding the conduit along its length as the conduit traverses or extends through the thermal energy storage medium.
  • a different volume or mass e.g. larger or smaller diameter
  • the method comprising: (a) flowing steam into a conduit disposed within and in thermal contact with a thermal energy storage medium, whereby heat is transferred from the steam to the medium for storage; and (b) forming a temperature gradient in the medium longitudinally along a length of the conduit, the temperature gradient in operation translating along the length of the conduit according to heat transfer between the steam and the medium.
  • sufficient heat is transferred from the steam to the medium such that water exits the conduit.
  • sufficient heat is transferred from the steam to the medium such that substantially no steam exits the conduit.
  • the temperature gradient is comprised of a superheat zone, a latent heat zone, and a preheat zone.
  • the temperature gradient is comprised of a superheat zone and a latent heat zone.
  • superheated steam may be extracted from the thermal energy storage system at a later time point.
  • at least a portion of the thermal energy storage medium within the superheat zone is fully saturated with thermal energy upon charging the system and the medium has a substantially uniform temperature along at least a portion of the conduit within the superheat zone.
  • in another aspect of the invention is a method for storing thermal energy, the method comprising: (a) flowing steam into a conduit disposed within and in thermal contact with a thermal energy storage medium, whereby heat is transferred from the steam to the medium for storage; and (b) thermally saturating a zone of the medium with heat so that the zone has a substantially uniform temperature, wherein substantially no condensation of the steam occurs within the conduit in thermal contact with the medium in the zone.
  • thermal power plant e.g. a Rankine cycle plant
  • thermal energy storage systems described herein may also be used in the context of a steam plant (e.g. for industrial process heat, absorption cooling, food processing, sterilization, water desalination, chemical processing, or enhanced oil recovery), and the like.
  • steam plant e.g. for industrial process heat, absorption cooling, food processing, sterilization, water desalination, chemical processing, or enhanced oil recovery
  • other heating systems such as fossil fuel fired boilers, package boilers, geothermal boilers, or a nuclear-reactor powered plant arranged to exchange thermal energy (heat) with a working fluid may be used to provide thermal energy to the storage system.
  • the thermal energy storage system 100 may in some variations have at least two zones while charging: a superheat zone 110, a latent heat zone 120, and optionally a preheat zone 130. Dashed lines in FIGS. 2A-2B indicate differentiation of the zones. These zones shift (to the right for this particular illustration) as additional steam is added to the thermal energy storage system (Fig. 2B) and additional heat is transferred into the thermal energy storage medium. Additionally, a subzone of thermal energy storage medium may be created within the superheat zone (e.g. "TS" in Figure IB) which is thermally saturated, such that the thermal energy storage medium within this subzone is at a substantially uniform temperature after charging.
  • TS superheat zone
  • Limited heat is transferred within the thermal energy storage medium in a longitudinal direction along the length of the conduit by way of convective heat transfer, or by way of conductive heat transfer, especially as compared to a metal such as iron or steel in contact with another piece of iron or steel.
  • the heat transfer properties of the thermal energy storage medium may be selected so that sufficient heat transfer occurs to enable a desired amount of energy storage in the medium for a desired conduit length, but limited so that a thermal gradient formed along the length of the conduit during charging is substantially preserved during a desired storage period so that at least some of the storage medium is at a high enough temperature to allow superheated steam to be recovered at the operating pressure.
  • the desired storage period may be selected according to source of steam and eventual application for stored thermal energy.
  • the storage period may be about 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, or 14 hours, or even longer.
  • the limited convective and conductive heat transfer may be due at least in part to intrinsic material properties such as high viscosity and/or low thermal conductivity of the materials within the thermal energy storage medium, and/or the limited heat transfer may be due at least in part to physical barriers, for example intervening thermally insulating material 140 positioned at various locations within the thermal energy storage medium along the length of the conduit.
  • intervening thermally insulating material 140 positioned at various locations within the thermal energy storage medium along the length of the conduit.
  • the thermal energy storage medium has a substantially homogeneous composition along the length of the conduit, e.g.
  • the storage medium in thermal contact with the conduit in zones 110, 120, and 130 as shown in FIGS. 2A-2B has substantially the identical composition.
  • the mass or volume of the thermal energy storage medium in thermal contact with the conduit may differ between zones, e.g. the mass or volume of thermal energy storage medium in contact with the conduit in at least part of the superheat zone 110 may be smaller than that of the mass or volume of thermal energy storage medium in contact with the conduit in at least part of the latent heat zone 120 or the preheat zone 130.
  • the composition of the thermal energy storage medium may be different for different zones.
  • compositions, structure, or volume or mass of the storage medium may be selected to provide improved performance of the system, e.g. efficiency, amount of superheat steam recovered upon discharge, and/or temperature of superheat steam recovered upon discharge.
  • superheated fluid such as superheated steam passes into a conduit 111 SH disposed within the thermal energy storage medium, and thermal energy from the superheated fluid is exchanged with and stored at a temperature T 1 , wherein Ti is greater than the temperature of condensation for the fluid at operating pressure (creating superheat zone 110).
  • the operating pressure may be selected based on the source of the steam and/or the intended use of the steam. In some variations, the operating pressure may be, for example, about 50bar, about lOObar, about 150 bar, or about 200bar.
  • the temperature Ti of the thermal energy storage medium within the superheat zone 110 may be a range of temperatures above the fluid condensation temperature.
  • the temperature of the superheated fluid decreases due to heat exchange with the thermal energy storage medium, and eventually the fluid reaches its saturation temperature so that vapor and liquid are both conveyed through the conduit 11 ILAT.
  • Thermal energy from the saturated fluid exchanges with thermal energy storage medium (creating latent heat zone 120 at T 2 ), causing additional vapor to condense. Since the thermal energy transferred by the saturated fluid is from latent heat, T 2 is substantially the same throughout the latent heat zone.
  • the temperature T 3 of the medium in the preheat zone is therefore less than the temperature T 2 in the latent heat zone, and as shown in Figure IB, T 3 may vary over the length of the preheat zone 130.
  • these zones shift towards the exit of the system (to the right as illustrated in Figs. IB and 2B).
  • the superheat region may extend the full length of the thermal energy storage system, two zones (superheat and latent heat) may be present in the thermal energy storage system, three zones (superheat, latent heat, and preheat), or more than three zones (e.g. superheat, latent heat, preheat, and unheated) may be present in the thermal energy storage system.
  • liquid e.g. water
  • the thermal energy storage system flows into the thermal energy storage system at a desired operating pressure in order to extract the thermal energy.
  • the liquid flows into the thermal energy storage system in the reverse direction from the charging mode, in some embodiments, the liquid may flow into the thermal energy storage system in the same direction as in the charging mode.
  • the optional preheat zone 130 is present upon initiating the discharge mode. The liquid flows through the conduit 11 IPRE into the preheat zone 130 where the liquid is heated to a temperature near its boiling point.
  • the heated liquid continues traversing to the conduit 11 ILAT and passes through the latent heat zone 120, in which the liquid receives heat from the thermal energy storage medium of the latent heat zone and boils to form a saturated fluid stream.
  • the saturated fluid subsequently passes to conduit 11 ISH through the superheat zone 110 of the thermal energy storage medium.
  • the fluid exiting the latent heat zone and entering the superheat zone via the conduit may be saturated, may be superheated, or may be at the point where essentially all or all liquid has vaporized but has not yet been superheated.
  • the fluid passing through the conduit within the superheat zone receives thermal energy from the superheat zone, and ultimately superheated fluid exits the superheat zone.
  • the zones will shift along the length of the conduit towards the exit of the system (e.g. in this embodiment to the left in Figure 2B).
  • This configuration and method of operation may provide more efficient and effective utilization of stored heat.
  • Thermal energy is stored at a higher temperature(s) Ti in the superheat zone of the thermal energy storage medium than would otherwise be possible if the thermal energy storage medium of the superheat zone had high thermal conductivity with the thermal energy storage medium of the latent heat zone.
  • the latent heat zone may be larger than would otherwise be possible if the thermal energy storage medium of the latent heat zone had high thermal conductivity with the thermal energy storage medium of the preheat zone.
  • the thermal energy storage system of the invention may increase the maximum temperature of the extracted working fluid (e.g. superheated steam) upon system discharge and/or may increase the length of time in which superheated fluid (e.g. superheated steam) may be extracted from the thermal energy storage system.
  • superheated fluid e.g. superheated steam
  • temperatures of the thermal energy storage medium in the superheat zone, latent heat zone, and preheat zone may also be near the temperature of the fluid exchanging heat with the thermal energy storage medium in each of the zones as well as near the temperature of the fluid heated or cooled by the thermal energy storage medium in each of the zones in later use.
  • the small temperature differential may also improve efficiency of heat transfer.
  • a thermal energy storage medium varies along the length of the conduit so as to comprise one or more discernible regions in the storage medium. While such regions of thermal energy storage medium along the length of the conduit do not need to be thermally isolated from one another (i.e. allowing essentially no heat transfer between the regions), they should be sufficiently thermally isolated and/or thermal convection and conduction along the length of the conduit should be sufficiently suppressed such that the thermal energy storage medium can maintain a thermal gradient for a sufficient length of time during storage and subsequent discharge of the system such that fluid heated to the desired temperature (e.g. superheated steam) may be extracted from the thermal energy storage system for the desired length of time (e.g. a steady flow).
  • fluid heated to the desired temperature e.g. superheated steam
  • the thermal energy storage medium can maintain a thermal gradient for a sufficient length of time during discharge of the system such that fluid heated to the desired temperature (e.g. superheated steam) may be extracted from the thermal energy storage system for the desired length of time (e.g. a steady flow). While the thermal gradient within the medium may in some instances decrease substantially during the storage period, the thermal gradient is maintained sufficiently during the discharge period such that fluid heated to the desired temperature (e.g. superheated steam) may be extracted from the thermal energy storage system for the desired length of time.
  • fluid heated to the desired temperature e.g. superheated steam
  • the desired length of time e.g. a steady flow
  • the thermal energy storage medium is substantially homogenous or comprises a substantially homogenous mixture, and may be comprised of one or more materials and/or components distributed in a uniform manner along the length of the conduit and/or extending radially outward from the conduit.
  • the materials and/or components of the thermal energy storage medium are distributed in a non-uniform manner along the length of the conduit and/or extending radially outward from the conduit.
  • the thermal energy storage system part 200 of which is depicted in Figures 3 A and 3B, may have two or more different thermal energy storage materials or components surrounding a pipe or other conduit 210.
  • a first material 220 in contact with the conduit may have about the same thermal conductivity as or a higher thermal conductivity than a second material 230 contacting the first material.
  • the first material provides a larger heat-exchange surface to contact the second material, which may store most of the thermal energy transferred from the working fluid.
  • the first material may also provide better thermal contact with the conduit (e.g. by comprising a liquid or having a smaller particle size) than the second material.
  • the thermal energy storage medium may be the same along the full length of the conduit, or the thermal energy storage medium may vary along the length of the conduit. When the thermal energy storage medium is non-uniform (e.g.
  • the non-uniformity may be present as a smooth (e.g. gradual) or step gradient of materials (e.g. a gradient from material A to material B, either continuously or in multiple discrete steps) and/or be present as a sharp division between the materials. Further variations are described in more detail below.
  • a conduit may comprise multiple interconnected segments arranged in various configurations.
  • a conduit may be substantially linear through the thermal energy storage medium, or a conduit may follow any of a number of nonlinear paths, including coiled (e.g. helical), spiral, serpentine, and other winding or turning configurations.
  • a serpentine portion of a conduit oscillates substantially within a plane, and may have, for example, angular or curved turns (see e.g. top and bottom figures in Figure 7, respectively).
  • multiple conduits may be used, e.g. arranged in a side-by-side manner or arranged in a nested or interpenetrating manner.
  • two or more substantially linear conduits may be arranged parallel to one another.
  • Two or more serpentine conduits may be arranged in a side-by side manner.
  • Two or more coiled conduits may be arranged in an interpenetrating manner.
  • the conduits may have the same or differing configurations.
  • connections between multiple conduits may be changed in operation using valves or the like, e.g. so that multiple conduits may be charged in parallel but discharged in series.
  • Conduit size and spacing within the thermal energy storage medium affects density of conduit and conduit surface area (and thus heat exchange area).
  • the desired density and surface area of conduit may be determined by, for example, the thermal energy storage medium used (e.g. thermal conductivity), particular working fluid, fluid flow rate, operating temperature range, and the like.
  • the conduits are sized and spaced uniformly throughout the thermal energy storage medium. In some or all regions of the thermal energy storage medium, the conduits may also be sized and/or spaced non-uniformly. For example, in one instance as depicted in Fig. 4, conduits 330 in a first region 310 of the thermal energy storage system may have a smaller diameter than conduits in a second region 320 of the thermal energy storage system. Alternatively or additionally, as depicted in Fig. 5, some or all of the small diameter conduits 401, 402, 403, 404 of the first region 410 may merge into larger diameter conduits 405, 406 of the second region 420 of the thermal energy storage system. In this instance, the second region has fewer conduits than the first region has.
  • the amount (e.g., thermal mass as defined by the product of mass and heat capacity) of thermal energy storage medium around and in thermal contact with a particular section of a conduit may vary.
  • the conduit 501 of Fig. 7 may follow a nonlinear path in a region, and the packing density (e.g. pitch of a coiled, helical, or serpentine configuration) of conduit in a first region 510 may differ from a packing density of conduit in a second region 520.
  • a conduit 502 may have a serpentine (or coiled, helical, etc.) configuration with uniform spacing period, so that adjacent conduit portions are spaced the same distance from one another.
  • the conduit spacing period in a first region 510 may differ from the conduit spacing period in a second region 520.
  • use of longer conduits within the superheat zone may permit the use of smaller-diameter conduits within that zone, thus increasing the length of the conduit within the superheated zone and thus increasing the dwell time of the working fluid and more efficient heat exchange in the zone.
  • the smaller-diameter conduits may increases fluid velocity in comparison with a larger-diameter conduit.
  • Increasing a ratio of surface area of conduit to unit thermal mass of thermal energy storage medium and/or adjusting dwell time within the conduit may ensure rapid heat transfer in the superheat zone, allowing the superheat zone to be more compact with better utilization of the medium than it would otherwise have to be if conduit of the same diameter were used throughout the thermal energy storage system.
  • decreasing the amount (e.g. thermal mass) of thermal energy storage medium around and in contact with a particular section of a conduit e.g. by increasing the packing density of conduit or by directly decreasing the volume or mass or thermal mass of thermal energy storage medium around the conduit) within the superheat zone may facilitate creation of the thermal saturation subzone.
  • the conduit within the latent heat zone may be of larger diameter and/or surrounded by a greater volume or mass or thermal mass of thermal energy storage medium than in another zone (e.g. the superheat zone).
  • another zone e.g. the superheat zone.
  • the relative surface area of the conduit per unit volume of the working fluid may be decreased, and thus the conduit may be of larger diameter.
  • a greater amount (e.g. thermal mass) of thermal energy storage medium may be present surrounding and in thermal contact with the conduit in the latent heat zone (e.g. by decreasing the packing density of conduit or by directly increasing the radius of thermal energy storage medium around the conduit).
  • a third zone (e.g. preheat zone), if present, may have the same or different density of conduits, conduit spacing period, and/or heat exchange area per unit volume of conduit and/or thermal energy storage medium as either of the first and second zones of the thermal energy storage system.
  • a third zone has a higher ratio of mass, thermal mass, or volume of thermal energy storage medium per unit surface area of a conduit within that zone.
  • conduit configurations were discussed above with respect to zones, it is to be understood that these zones are not static regions within the thermal energy storage system, but may shift along the length of the conduit during charging and discharging of the system. Thus, discussion of having certain conduit configurations within a particular "zone" indicates that the configuration may be present in at least a portion of the zone during at least a portion of the charging or discharging time.
  • Fig. 8 depicts an example of a thermal energy storage system 800 in which two coiled conduits (e.g. pipes) 801 depicted by the solid and dotted lines having varying spacing or period between adjacent courses of the pipe as the pipe winds its way from one side of the thermal energy storage system to the other side of the thermal energy storage system.
  • the conduits may be displaced from each other and/or interpenetrating.
  • the two coils in Fig. 8 may be, for example, displaced from each other horizontally and offset vertically, or may be interpenetrating.
  • the thermal energy storage medium 813 in the lower region 830 where a pipe has larger period spacing differs from the thermal energy storage medium 812 in the middle region 820, and each thermal energy storage medium differs from the thermal energy storage medium 811 in top region 810.
  • the composition, mass, thermal mass, or volume of thermal energy storage medium for each region may be selected based on the available thermal energy to be captured, temperature, and size of the region, for instance.
  • the composition of the thermal energy storage medium may be substantially constant along the length of the conduit, but the volume or mass of the storage medium may be less in one region compared to another region.
  • the thermal energy storage mediums may comprise more than one different dry materials, or one or more of the thermal energy storage mediums may comprise a liquid, e.g. molten salt, at operating temperature.
  • adjacent pipes may be displaced linearly so that one of the pipes is spaced apart from the other pipe in portions of each region of the thermal energy storage medium in order to increase or maximize contact with and thermal energy conduction into all areas of the thermal energy storage medium.
  • the pipes may be spaced to help provide a reasonably even temperature distribution in a cross-section of each region.
  • a subzone is created within at least a portion of the superheat zone (see “TS" in Figure IB).
  • the thermal energy storage medium is saturated with heat, such that the subzone is substantially isothermal (i.e. at a substantially uniform temperature), both radially from the conduit as well as lengthwise along the conduit.
  • creation of the thermal saturation subzone may permit more efficient heat extraction from the medium, and higher maximum temperature of the extracted working fluid.
  • the working fluid is a gas, and it is generally more difficult to transfer heat into a gas than into a liquid.
  • the thermal saturation subzone increases the length (and thus dwell time) of conduit in thermal contact with thermal energy storage medium at its maximum temperature. Additionally, since in these embodiments there in no thermal gradient radially out from the conduit, there may be a more rapid flow of heat into the working fluid, since there is no radial thermal gradient to work against such heat flow.
  • the packing density of conduit e.g. increasing density
  • thermal energy storage medium materials e.g. increasing thermal conductivity and/or thermal contact
  • size e.g. decreasing amount such as mass, thermal mass or volume of thermal energy storage medium around and in thermal contact with the conduit
  • thermal interface between the fluid and thermal energy storage medium e.g.
  • the radius of the thermal energy storage medium around the conduit is smaller in the thermal saturation subzone than in another zone (e.g. latent heat zone).
  • another zone e.g. latent heat zone.
  • the thermal energy storage medium may reach thermal saturation more quickly and readily.
  • the conduit(s) may be made from any material and in any configuration suitable for transporting the working fluid to be used in the thermal energy storage system. Any suitable diameter or closed cross-sectional shape may be used, and the conduits further may be made out of any material suitable for transferring heat from the working fluid to the medium and vice versa.
  • the conduits may be metal, a polymeric material, silicon carbide, fused zirconia or other very high strength ceramics.
  • Non- limiting examples of metal conduits include those comprising carbon steel, low carbon steel, medium carbon steel, stainless steel, black iron, carbon-manganese steel, mild steel, and low alloy steels containing nickel chromium, molybdenum, vanadium, copper, niobium, or titanium.
  • the conduits comprise low carbon steel. In some embodiments, the conduits comprise medium carbon steel. In some embodiments, the conduits comprise pipes. In some embodiments, the conduits are ASTM Al 06 Grade B seamless steel pipes or ASTM A210 carbon steel pipes. In some embodiments, the conduits meet local code requirements for the temperature and pressure ranges of intended use (e.g. boiler code such as promulgated by a standards setting organization such as ASTM, ASME or ISO). In some embodiments, the external surface of the conduits are corrosion resistant with regards to the storage medium. In some instances, the conduits may be conduits formed in or bored through the thermal energy storage medium. The conduits may optionally comprise the fluid channeling devices as described in U.S. Patent Application Serial No.
  • the conduits comprise pipes.
  • the pipes may have a diameter of about 0.25" to about 16".
  • Pipe diameters listed herein indicate the nominal inside diameter of the pipe.
  • the diameter of the pipes is about 0.25" to about 4".
  • the diameter of the pipes is about 0.5" to about 2.0".
  • the diameter of the pipes is about 0.5" to about 1.0".
  • the diameter of the pipes is about 0.25" to about 0.5".
  • the diameter of the pipes is about 1" or less.
  • the diameter of the pipes is about 0.75" or less.
  • the diameter of the pipes is about 0.5" or less.
  • the diameter of the pipes is about 0.5". In some embodiments, the diameter of the pipes is at least about 0.5". In some embodiments, the thickness of the pipe walls is about 1 to about 16 mm, for example about 1 to about 3 mm. In some embodiments, the thickness of the pipe walls is about 2.1 mm. In some embodiments, the thickness of the pipe walls is at least about 0.75 mm. In some embodiments, the pipes are Schedule 5 pipes. In some embodiments, the pipes are Schedule 10 pipes. In some embodiments, the pipes are Schedule 40 pipes. Generally, smaller diameter pipes are more effective at transfer of heat between the working fluid and the thermal storage medium, due to their greater surface area per unit volume. However, the lower limit of effective pipe size may be controlled by corrosion limits.
  • the conduit(s) may be configured within the thermal energy storage medium in any arrangement suitable for transporting the working fluid, in order to store thermal energy within the medium.
  • the conduit(s) are horizontal.
  • the conduit(s) are vertical.
  • the conduit(s) are linear.
  • the conduit(s) are serpentine.
  • the conduit(s) are curved.
  • the conduit(s) are coiled.
  • a conduit arrangement that is not linear from entry to exit of a thermal energy storage system, especially where the conduits are pipes, may be adopted to allow the pipe to flex or twist somewhat during thermal cycles. This configuration distributes stresses from thermal expansion and contraction along much more of the conduit length and limits the extent of conduit extension that must be accommodated at the thermal energy storage system's entry and exit.
  • a serpentine or coiled conduit path may therefore be adopted, and the conduit spacing period may be uniform or may vary as discussed previously.
  • a thermal energy storage system having pipes may also have one or more joints (e.g. swivel joints) incorporated along a length of pipes to form articulated piping, especially where the pipe is not linear from entry to exit of a thermal energy storage system.
  • a joint e.g. a swivel joint
  • Articulated piping may be incorporated into any thermal energy storage system described above.
  • a joint e.g. a swivel joint
  • a joint may be e.g. an area where two pipes were welded together. The dissimilar shape of the weld and imperfect alignment of the two pipes upon welding provide a natural point along a pipe for out of plane motion such as swiveling to take place.
  • the preferred length and density of the conduit(s) for a particular thermal energy storage system may depend on factors such as the particular thermal energy storage medium used (e.g. conductivity, heat capacity, thermal contact, etc), the diameter of the conduit(s), the total amount of energy to be stored by the system, the charging and/or discharging response time required by the system, the length of time for which constant output is desired, the particular materials that comprise the conduit(s), the particular working fluid used, the temperature range at which the working fluid operates, the flow rate of the working fluid, and the like. In some embodiments it is preferred that the conduit(s) be long enough (within the context of a particular thermal energy storage system) such that no working fluid vapor (e.g.
  • the height of the pipes is about 120 m.
  • the conduit is about 12 m along one or more axes.
  • the overall dimensions of a serpentine conduit within a thermal energy storage system may be about 12 m in height, and 12 m in width (with the length of the conduit being longer than 12 m).
  • the conduit(s) may be arranged and/or shaped in order to maximize conduit length within a particular size of a thermal energy storage system unit.
  • a thermal energy storage system unit comprised of the conduit disposed within a volume of thermal energy storage medium, may be 12m x 12m x 12m.
  • a conduit which is placed vertically within this thermal energy storage medium has a maximum of 12m in length.
  • a longer conduit may fit within the thermal energy storage medium.
  • a longer conduit may be made to fit within a particular size thermal energy storage system, and thermal energy storage may be optimized in three dimensions.
  • the working fluid may in various embodiments comprise a water mixture (e.g. water plus ammonia), a hydrocarbon (e.g. pentane), carbon dioxide, air, or other suitable fluid.
  • a water mixture e.g. water plus ammonia
  • a hydrocarbon e.g. pentane
  • carbon dioxide air, or other suitable fluid.
  • the working fluid may be used directly (e.g. to drive a turbine), or may exchange heat with a second fluid (e.g. an organic fluid used in organic Rankine-cycle turbines that is expanded through the turbine).
  • a second fluid e.g. an organic fluid used in organic Rankine-cycle turbines that is expanded through the turbine.
  • material when used in the context of an element of a thermal energy storage medium, “material” as used herein indicates e.g. rock, gravel, sand, silt, soil, ceramic, as well as specific types, chemical compositions, or isolated fractions thereof.
  • a “material” may be, for example, rock, quartzite rock, alumina, or clay (e.g. clay may be an isolated fraction of some soils).
  • component when used in the context of an element of a thermal energy storage medium, “component” as used herein indicates a particular material of a particular size class (i.e. having a particular size range for the component particles).
  • a component may be sand of about 0.1 to about 2 mm in size.
  • a component may be basalt rock of about 50 to about 60 mm in size.
  • "constituent” as used herein indicates a mixture of two or more components.
  • Non-limiting examples of materials which may be useful for thermal energy storage include, for example, aggregate (e.g. rock (e.g. quartzite, granite, basalt, silicates, limestone, shale, hematite, alumina, periclase (MgO), etc.), gravel (e.g. quartzite, granite, basalt, silicates, limestone, shale, hematite, alumina, periclase (MgO), etc.), concrete pieces), sand, soil (e.g. topsoil and/or subsoil), clay, silt, soil organic material, metals, metal oxides (e.g.
  • aggregate e.g. rock (e.g. quartzite, granite, basalt, silicates, limestone, shale, hematite, alumina, periclase (MgO), etc.
  • gravel e.g. quartzite, granite, basalt, silicates, limestone, shale, hematite,
  • Rock generally comprises particles which are greater than about 50 mm in size.
  • rock comprises granite, quartzite, basalt, a silicate, carbonate, nitrate, and/or oxide. In some embodiments, rock comprises granite, quartzite, basalt, and/or silicates. In some embodiments, rock comprises a carbonate, nitrate, and/or oxide which is naturally present in rock. In some embodiments, rock comprises a carbonate and/or oxide which is naturally present in rock. Gravel generally comprises the same materials as rock, with a size range of about 2 mm to about 50 mm. "Medium gravel” comprises gravel of about 25 mm. “Fine gravel” comprises gravel of about 6 mm.
  • Sand frequently comprises a high percentage of silicates, but may in addition to or instead of silicates, may comprise one or more of any of the materials of rock or gravel, with a size range of about 0.06 mm to about 2 mm.
  • Coarse sand comprises sand of about 1.5 mm.
  • Fluor sand comprises sand of about 0.3 mm.
  • Very fine sand comprises sand of about 0.08 mm.
  • Silt comprises particles of about 4 microns to about 60 microns, and may comprise organic material and/or any of the materials of rock, gravel, or sand.
  • soil may comprise one but in general soil comprises a mixture of two or more (e.g. three, four, or more) of the following: rock, gravel, sand, clay, silt, and organic material.
  • soil may be unwashed or washed (e.g. to remove organic material and/or clay).
  • the materials used in the thermal energy storage system do not decompose at the operating temperature range of the system.
  • Rock may in some embodiments be monolithic rock, crushed rock and/or quartzite.
  • Gravel may in some embodiments be monolithic gravel, crushed gravel and/or quartzite. Quartzite has the highest conductivity at 250 0 C of all the types of minerals reported by Clauser and Huenges in their 1995 paper titled "Thermal Conductivity of Rocks and Minerals", Rock Physics and Phase Relations, A Handbook of Physical Constants, American Geophysical Union (1995), the disclosure of which is herein incorporated by reference in its entirety.
  • the conductivity of the quartzitic minerals, at 250 0 C is between about 2.5 and about 4 W/(m.K).
  • the "size" of a particle of a material may be either the length of the longest dimension of the particle, or when the particle is spherical or approximately spherical, may be the diameter of the particle. In some embodiments, the size is the length of the longest dimension. In some embodiments, the size is the diameter.
  • the various materials may be used alone or be mixed, and may be used in their naturally occurring form, in crushed form, or in a consolidated form, such as in the form of bricks or blocks, provided that when the thermal energy storage medium is a "granular thermal energy storage medium", the consolidated forms are granular materials of the medium (i.e. the medium as a whole is not bound together, such as with conduits encased in concrete).
  • the medium materials when in consolidated form may comprise, for example, concrete blocks composed of low fraction cement, or bricks formed from, for example, bonded aluminium oxide particles.
  • the materials may in some embodiments be smoothed, either naturally (e.g. river pebbles) or artificially.
  • the medium may optionally be wet or dry compacted to maximize density and conductivity, but this compaction may be moderated to avoid frictional stress on the conduits, and additionally, in the case of granular thermal energy mediums, the medium will retain its granular integrity after exposure to water.
  • wet compaction the inclusion of the smallest particles, in particular of clays, of less than about 15 microns, in some embodiments less than about 10 microns, may facilitate compaction but may also lead to shrinkage on drying, causing high thermal stresses.
  • clay when clay is present, it is present in a low enough concentration such that if the medium gets wet, the medium will retain its granular integrity and the clay will not act as a binder.
  • the thermal energy storage medium may comprise one or more materials, components, and/or constituents.
  • Various examples of mediums are described below.
  • the medium When placed within a thermal energy storage system of the invention, the medium is arranged such that heat convection and conduction within the medium is suppressed along the length of the conduit, such that a temperature gradient is created in the thermal energy storage medium along the length of the conduit during thermal charging and/or discharging of the system.
  • the temperature gradient may be sustained over time to such an extent that superheated working fluid may be extracted from the system for a sustained period of time (e.g. at least about 30 minutes, at least about 1 hour, at least about 2 hours, at least about 3 hours, at least about 4 hours, at least about 6 hours, at least about 8 hours).
  • the medium itself may suppress convection and conduction longitudinally (e.g. solids or mixtures of solids having low overall conductivity, viscous molten salt slurries, etc. as described below), and/or through physical means (e.g. thermally insulating baffles and/or barriers placed within the medium and/or physical isolation of regions of medium). Examples of specific embodiments for physical separation of the medium are described below with reference to specific mediums. However, it is to be understood that the physical thermal isolation methods described herein may or may not be used in conjunction with other types of mediums described herein. Additionally, it is further to be understood that the examples of mediums described herein may be used in conjunction with one or more physical thermal isolation methods as described herein.
  • the thermal conductivity (at the operating temperature of the system) of each of the thermal energy storage medium materials is generally less than about 30, less than about 20, less than about 15, less than about 10, less than about 5, less than about 4, less than about 3, less than about 2, less than about 1, about 0.1 to about 5, about 0.3 to about 5, about 0.5 to about 5, about 0.5 to about 4, about 0.5 to about 3, about 1 to about 3, about 2 to about 3 W/(m-K).
  • the thermal conductivity of the bulk of the materials used in the thermal energy storage medium may fall within these ranges, and a smaller portion of one or more materials may have a higher conductivity, provided that the overall thermal conductivity of the thermal energy storage medium provides the useful thermal gradient characteristics as described herein.
  • the overall thermal conductivity of the medium when no physical thermal isolation barriers are present, is generally less than about 30, less than about 20, less than about 15, less than about 10, less than about 5, less than about 4, less than about 3, less than about 2, less than about 1, about 0.1 to about 5, about 0.3 to about 5, about 0.5 to about 5, about 0.5 to about 4, about 0.5 to about 3, about 1 to about 3, about 2 to about 3 W/(m-K).
  • the thermal energy storage medium comprises a viscous slurry (e.g. of one or more molten salts and one or more solid particulate materials such as sand or soil).
  • a viscous slurry e.g. of one or more molten salts and one or more solid particulate materials such as sand or soil.
  • materials having a higher thermal conductivity may optionally be used in the thermal energy storage medium, and the overall thermal energy storage medium conductivity may be increased.
  • the thermal energy storage medium comprises two or more components distributed heterogeneously within the medium such that one or more physical properties of the medium vary with distance from the one or more conduits.
  • the thermal energy storage medium may comprise a gradient of components, e.g. in thermal conductivity decreasing radially outward from the conduits.
  • suitable mediums include those described in U.S. Provisional Patent Application Serial No. 61/059,748 filed June 6, 2008, and titled "Thermal Energy Storage System Comprising Varying Physical Properties and Methods For Use” which is incorporated herein by reference in its entirety.
  • the thermal energy storage medium comprises: (a) a first annulus of a highly thermally conductive material in contact with the conduit and having a conductivity Kl and (b) a second (outer) annulus of a conductive material in contact with the first annulus and having a conductivity K2, which may be about equal to or lower than Kl (see e.g. Figures 3A and 3B, in which 220 represents the first annulus, and 230 represents the second annulus).
  • the first and/or the second annulus may comprise more than one material or component.
  • Kl may be at least about 1, at least about 2, at least about 3, at least about 5, at least about 10, at least about 15, at least about 20, or at least about 30 W/m- K
  • K2 may range from about 0.1 to about 4, about 0.3 to about 4, about 0.3 to about 3, about 0.3 to about 2, about 0.3 to about 1.5, about 0.1 to about 0.5 W/m-K, at the operating temperature range of the system.
  • the material in the first annulus may be selected for high thermal conductivity and additionally, may have high thermal contact with the conduit.
  • Use of more thermally conductive material(s) may further permit use of shorter lengths of the conduit(s), which lowers the costs of the conduit material (e.g. metal), since heat may be transferred into and out of the working fluid more efficiently.
  • High thermal contact may be achieved by using, for example, a small particle size of the material, in order to avoid gaps between the conduit and the medium.
  • liquid materials e.g. molten salts such as nitrate or nitrite salts of lithium, sodium, potassium or calcium
  • molten salts such as nitrate or nitrite salts of lithium, sodium, potassium or calcium
  • An example of material in the first annulus includes, for example, alumina (K of about 10-30 W/m- K). Having a first annulus comprised of a highly conductive material with high thermal contact with the conduit effectively increases the surface area of the conduit, permitting more efficient transfer of heat to the second annulus material.
  • first annulus materials may in some instances be prohibitively expensive to use for the entire thermal energy storage system (e.g. alumina)
  • a second annulus comprised of a less expensive material(s) which may have a lower conductivity, for example, sand or soil (K of approximately 0.3 to about 0.5 W/m-K), low-cost granulated ceramics, or a mixture thereof.
  • the materials themselves may be inexpensive, and additionally, may advantageously be found near to the site of the thermal energy storage system, minimizing transportation costs for the material(s) to the site of operation.
  • the relative radial cross-sectional thickness of the first and second annulus may vary depending on the specific thermal energy storage medium materials used, the costs of the materials used, the flow rate of the working fluid, the response time required by the system during charging and discharging, the amount of energy to be stored by the system, etc.
  • the second annulus may be thicker than the first annulus. In some embodiments, the second annulus is about two times thicker, or at least about two times thicker, than the first annulus. Poor thermal conductivity of a storage material can be matched with an appropriate radius ratio between a first and second annulus such that under peak heat flow conditions, heat will not be supplied or withdrawn too quickly for the outer annulus to conduct.
  • the volume, mass or thermal mass of the material(s) in the second annulus is about 2-3 times the volume, mass or thermal mass of the material(s) in the first annulus. In some embodiments, the volume, mass, or thermal mass of the material(s) in the second annulus is greater than about 3 times the volume, mass, or thermal mass of the material(s) in the first annulus.
  • the thermal energy storage medium materials may be present in various configurations, for example, a continuous long cylinder (see Figure 9A) or series of smaller cylinders/canisters (see Figure 9B) surrounding a conduit. The medium may directly contact the conduit and/or may contact the conduit via an inner cylinder wall.
  • the cylinders may have an inner wall between a first and a second annulus (see Figure 9C).
  • Any suitable storage mediums described herein or otherwise known may be used with such configuration variations.
  • a viscous slurry comprising one or more molten salts and a particulate filler such as sand or soil as described herein may be used to fill the cylinder surrounding and in thermal contact with the conduit.
  • a viscous slurry comprising one or more molten salts and a particulate filler such as sand or soil as described herein may be used to fill the cylinder surrounding and in thermal contact with the conduit.
  • a thermally conductive liquid such as one or more molten salts or a viscous slurry may be used to fill the volume of the first annulus around a conduit defined by the inner cylinder wall, and a storage medium that is a solid (e.g. particulate or granular) or a slurry may be used to fill the volume of the second outer annulus.
  • the cylinder(s) e.g. such as those shown in Figs. 9A-9C
  • additional thermal storage medium which may be the same or different from the medium(s) inside the cylinder(s).
  • the cylinder(s) may be surrounded by one or more of e.g.
  • the cylinder(s) are set into the ground, and are surrounded by a medium comprising the ground soil.
  • a medium comprising the ground soil.
  • such configurations may in some variations improve the efficiency of heat transfer from the working fluid to the storage medium.
  • the medium contained within the cylinder(s) may have high thermal conductivity, and the cylinder(s) provide a relatively larger surface area to the medium outside the cylinder(s), thus improving transfer of heat into the medium outside the cylinder(s).
  • a configuration incorporating a long cylindrical form of the storage medium in thermal contact with a cylinder such as illustrated in FIGS. 9A-9C
  • a cylinder such as illustrated in FIGS. 9A-9C
  • a long cylinder configuration may encourage local isolated circulation patterns with limited axial conductivity so as to enable formation of a sustainable axial thermal gradient within the thermal energy storage medium.
  • a highly viscous slurry may be used in a continuous long cylinder (e.g. as illustrated in FIGS.
  • a long cylindrical form may be physically subdivided so that convection along the length of the cylinder is limited to lengths of those subdivisions. Any type of subdivision may be used so as to effectively limit convection along the length of the cylinder, e.g. baffles, flow control devices, and the like.
  • a long cylindrical form may be subdivided into a series of discrete cylinders arranged in a generally colinear manner as illustrasted in FIG. 9B.
  • the series of individual cylinders may be used to permit convection within each cylinder, but sufficiently isolate the cylinders from each other so that substantially no inter-cylinder flow occurs, thus creating the thermal gradient along the length of the conduit.
  • the series of individual cylinders may advantageously be configured to accommodate linear thermal expansion.
  • the series of individual cylinders may be separated by a gap (e.g. about 1 cm), to allow for thermal expansion of the individual cylinders upon heating.
  • Any suitable thermal energy storage material may be disposed within the cylinders to effectively receive and store heat from a working fluid in the conduit during charging, and to provide heat to a working fluid upon discharge.
  • the individual cylinders may be at least partially filled with one or more molten salts (such as nitrate or nitrite salts of lithium, potassium, sodium or calcium) or, in some variations, a slurry (e.g. one or more molten salts mixed with soil or sand).
  • molten salts such as nitrate or nitrite salts of lithium, potassium, sodium or calcium
  • a slurry e.g. one or more molten salts mixed with soil or sand.
  • the series of individual cylinders may be surrounded by another thermal energy storage medium, e.g. soil, sand, rock, gravel, a slurry, or the like.
  • the gap may optionally comprise a band or other sealing means between the gaps, to prevent the thermal energy storage medium materials (e.g. sand, soil) from entering the gap zone.
  • the gap may help to maintain the temperature gradient, as the gaps act as thermal insulators.
  • the cylinders may be comprised of, for example, steel or ceramic tubes, e.g. steel pipes where the particular steel has been selected for the operational pressures and temperatures of the system.
  • the cylinders may optionally be surrounded by a thin wall sand- filled cylinder to modularize for easy installation and removal if a weld cracks.
  • the cylinder diameter is about 20 cm, for a conduit comprised of 1 to 2 inch diameter pipe.
  • the thermal energy storage medium in direct contact with the conduit comprises a slurry that is, in turn, comprised of a liquid (e.g. oil, molten salt) and one or more solid materials. Since liquids makes excellent contact with the conduit, a slurry that wets all surfaces avoids thermal contact problems associated with dry mediums. Molten salts convect like water at elevated temperatures, and additionally, unlike some liquids, molten salts do not have a vapor pressure, making them safer for use in a high temperature system, and are often cheaper than oils.
  • a liquid e.g. oil, molten salt
  • liquids such as oils
  • vapor pressure may be used in the slurry, optionally in conjunction with a N 2 blanket.
  • the molten salts are molten and preferably do not decompose at the operating temperatures of the storage system.
  • the operating temperature range is about 200 to about 500 0 C.
  • molten salts include, for example, nitrate and nitrite salts of lithium, sodium, potassium, and calcium.
  • Molten salts useful in the invention frequently have melting temperature of at least about 15O 0 C.
  • the molten salt comprises a 50/50 (by weight or volume) mixture OfNaNO 3 and KNO 3 (stable to 540 0 C). Addition OfCaNO 2 as a minor component to this mix will lower the melting point of the mixture.
  • One or more additional (solid) materials may be added to the molten salt, and in some variations, may be added in sufficient quantities so that the mixture has the properties of a viscous slurry. It may be preferred to increase the amount of solids relative to the amount of salt, provided that the surfaces of conduit(s) are wet: increasing the amount of e.g. sand in the slurry may reduce the cost of the thermal energy storage medium, and increase the overall conductivity of the slurry.
  • the overall K of the slurry is about 0.5 to about 4, about 0.5 to about 3, about 0.5 to about 2, about 1 to about 3, about 1.5 to about 3, about 2 to about 3 W/(m-K).
  • the ratio of solid: liquid e.g. sand:salt
  • the additional solid materials in some embodiments may be filtered or otherwise selected by particulate size; a uniform size of particulate is less like to ratchet or settle within the slurry.
  • the average particle size and particle size distribution may be selected so that the particles form a physically stable network or framework surrounded by the liquid component, wherein the particles in the network or framework generally do not move relative to each other.
  • the overall conductivity of the slurry medium may affect the conduit length required to efficiently extract the energy available from the working fluid. For example, when water/steam is the working fluid, a K of about 2.5 corresponds to a conduit length of about 120m. A lower K may require a longer length of conduit, and a higher K may effectively utilize a shorter length of conduit.
  • the slurry may be viscous, to suppress convection within the slurry but still yield sufficiently to accommodate thermal expansion of the conduit and to wet the surface of the conduit to ensure excellent thermal contact.
  • the slurry may have a viscosity of approximately 50,000 to about 250,000, or approximately 50,000 to about 500,000, or approximately 50,000 to about IxIO 6 centipoise at operating temperatures.
  • the slurry may have the viscosity approximating that of room temperature wet unset concrete, ketchup, or peanut butter.
  • the viscosity of the slurry can be affected by selecting the particle size of the solid, the type of solid, and the amount of solid. In some variations, increasing the amount of solids (e.g. sand) in the slurry will increase the viscosity. In some variations, decreasing the particle size of the solid will increase the viscosity.
  • the particular thermal energy storage medium used for a particular thermal energy storage system may depend on factors such as the operating temperature of the system, the total amount of energy to be stored by the system, the charging and/or discharging response time required by the system, the length of time for which constant output is desired, the particular materials that comprise the conduit(s), the diameter of the conduit(s), the particular working fluid used, the flow rate of the working fluid, and the like.
  • the thermal energy storage system may be located above ground level, below ground level, or partially below ground level.
  • the local soil available on site by digging the containment pit may advantageously be used in the thermal energy storage medium, thus lowering transportation costs of shipping materials to be used at the site of the system.
  • Such soil may be filtered to remove organic material and also to sort the material by grain radius.
  • various methods of containment of the medium such as concrete walls, may be used, as will be apparent to one of skill in the art.
  • the thermal energy storage system accepts superheated steam directly from the field, via the conduit(s). Reverse flow of the working fluid through the conduit is frequently used for discharging and extracting heat from the system. However, in some embodiments, the working fluid is flowed into the system in the same direction when charging as well as discharging the system. Additionally, by utilizing valves that operate various portions of the system, other flow configurations are possible. For example, multiple conduits may be charged and/or discharged in parallel or sequentially. Heat storage modules formed of multiple conduits connected by header systems can be arranged in parallel to accept the peak volume of superheated or saturated steam on charging, and provide the desired peak volume of steam upon discharge.
  • the interconnecting pipework can be rearranged with some of the modules in series on charging to change the effective length of the conduits.
  • the interconnecting pipework can be rearranged with some of the modules in series on discharging to change the output fluid flow rate characteristics for output time.
  • two conduits may be charged in parallel, and then discharged in antiseries, such that when discharging the working fluid flows in the reverse direction through the first conduit, but then flows in the original direction (compared with the charging direction) through the second conduit.
  • At least two superheated charged modules charged in parallel over a shorter period can be reconnected with the hot ends connected during discharge; fluid flow from the cold end to the hot end of the first, traveling then through the hot end of the second, will subsequently heat the colder end of the second and exit there, resulting in a steady flow of superheated steam at constant temperature for more hours than the charging time, although this constant temperature may be about 20 to about 50 0 C, or about 20 to about 60 0 C below the peak supply superheating temperature.
  • the thermal energy storage system can be tailored to seasonal energy output by valving off certain portions of the system. Other variations in interconnection of modules will be apparent to one of skill in the art.
  • the system When superheated steam is used as the working fluid, the system may be suitable for up to about 600° C in operation.
  • the system may be suitable for operation at pressures of about 25, about 50, about 75, about 100, about 150, or about 200 bar, or even higher pressures.
  • the system may deliver for some hours (e.g. at least about 0.5, at least about 1, at least about 2, at least about 3, at least about 4, at least about 6, at least about 8, at least about 10, at least about 12, at least about 14 hours) a constant volume and temperature of superheated steam close to but below the original superheated temperature of the steam from the field, provided the working fluid flow is held constant on discharge.
  • the change in temperature of the thermal energy storage medium contacting the conduit between charging and discharging is relatively uniform along the length of the conduit. Without wishing to be bound by theory, it is believed that this may increase the efficiency for transferring heat in and out of the thermal energy storage medium. In some embodiments, this change in temperature between charged and discharged states is about 60 0 C. In some embodiments, this change in temperature between charged and discharged states is about 100 0 C. In some embodiments, corrosion of the conduit(s) is reduced compared with other thermal energy storage systems, as the zone in which the working fluid boils is distributed over a relatively larger area.
  • the amount of energy to be stored and the rate at which energy must be extracted in operation affect the preferred embodiments for conduit length and diameter, particular thermal energy storage medium used, amount of thermal energy storage medium per unit length of the conduit, the flow rate and volume of the working fluid, etc.
  • thermal energy storage systems discussed above may be incorporated into a conventional, nuclear, or solar thermal energy power plant, or process or industrial steam plant, and may be utilized to capture heat from an appropriate fluid stream to store thermal energy for later use.
  • superheated steam is generated in a conventional power plant, e.g. coal or natural gas fired.
  • superheated steam is generated in a nuclear reactor.
  • superheated steam is generated using solar energy from a tower, linear Fresnel array, or trough collector.
  • superheated steam is generated using steam generated from a conventional power plant with a solar powered booster (e.g., admission of steam generated with solar energy into a portion of the steam circuit of the conventional plant to augment steam generated using other than solar energy).
  • a portion of the superheated steam may be used to drive a Rankine-cycle turbine to generate electricity, and a portion of the superheated steam may enter a thermal energy storage system as discussed above.
  • a portion of the generated steam may be used as process steam (e.g. for enhanced oil recovery, food processing, desalination, refrigeration and the like) and a portion of the steam may enter a thermal energy storage system as described above.
  • Thermal energy at high temperature is transferred to and stored in a superheat zone of the thermal energy storage system, while thermal energy from latent heat and optionally from superheated steam is stored in a latent heat zone of the thermal energy storage system.
  • Condensed hot water may leave the latent heat zone and be transferred directly to insulated hot water storage tanks, or heat may be extracted from the hot water and stored in a preheat zone of the thermal energy storage system.
  • the stored thermal energy may be used and superheated steam may be generated by supplying water to the optional preheat zone and/or to the latent heat zone of the thermal energy storage system to vaporize the water, and saturated steam may then pass to the superheat zone where the saturated steam is superheated.
  • One or more valves may be used to control pressure within the thermal energy storage system.
  • the superheated steam is therefore of high quality because of the high temperature that can be achieved by the inventive thermal energy storage system and can be used to drive a Rankine-cycle turbine or can be used in another process if desired.
  • Variations and modifications may be made in respect of the power plant and thermal energy storage system as above described without departing from the scope of the invention as described and as defined in the following claim.

Abstract

L'invention concerne un système de stockage d'énergie thermique pouvant être utilisé pour emmagasiner de l'énergie thermique issue de vapeur surchauffée. Le système de stockage d'énergie thermique comporte un long conduit et un milieu de stockage d'énergie thermique en contact thermique avec le conduit sur sa longueur. Le conduit peut être sensiblement linéaire ou non linéaire (par ex. en forme de serpentin ou de bobine). Les propriétés thermiques du milieu de stockage d'énergie thermique peuvent être choisies de manière à créer au sein dudit milieu un gradient thermique sur la longueur du conduit pendant le chargement, de telle sorte qu'au moins une zone du milieu de stockage d'énergie thermique maintienne une température suffisante pour que de la vapeur surchauffée puisse être récupérée à partir du système de stockage d'énergie thermique à son évacuation.
PCT/US2010/021675 2009-01-21 2010-01-21 Stockage d'énergie thermique pour applications en surchauffe WO2010085574A1 (fr)

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WO2014148894A1 (fr) * 2013-03-18 2014-09-25 Stamicarbon B.V. Acting Under The Name Of Mt Innovation Center Réservoir de stockage isolé de sels fondus
CN105980802A (zh) * 2013-12-20 2016-09-28 能源耐斯特公司 用于热能储存器的设备
CN107940477A (zh) * 2017-12-24 2018-04-20 江苏中研宜普科技有限公司 具有两环节能蓄热体的蓄热燃烧装置
US10914293B2 (en) 2018-06-20 2021-02-09 David Alan McBay Method, system and apparatus for extracting heat energy from geothermal briny fluid
US11661857B2 (en) 2020-06-16 2023-05-30 Cyrq Energy, Inc. Electricity generating systems with thermal energy storage coupled superheaters

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JP2014520243A (ja) * 2011-06-09 2014-08-21 ネスト アーエス 熱エネルギー貯蔵装置、並びにそのプラント、方法、及び使用
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WO2014148894A1 (fr) * 2013-03-18 2014-09-25 Stamicarbon B.V. Acting Under The Name Of Mt Innovation Center Réservoir de stockage isolé de sels fondus
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CN105980802A (zh) * 2013-12-20 2016-09-28 能源耐斯特公司 用于热能储存器的设备
CN107940477A (zh) * 2017-12-24 2018-04-20 江苏中研宜普科技有限公司 具有两环节能蓄热体的蓄热燃烧装置
CN107940477B (zh) * 2017-12-24 2023-10-13 江苏中研宜普科技有限公司 具有两环节能蓄热体的蓄热燃烧装置
US10914293B2 (en) 2018-06-20 2021-02-09 David Alan McBay Method, system and apparatus for extracting heat energy from geothermal briny fluid
US11225951B2 (en) 2018-06-20 2022-01-18 David Alan McBay Method, system and apparatus for extracting heat energy from geothermal briny fluid
US11692530B2 (en) 2018-06-20 2023-07-04 David Alan McBay Method, system and apparatus for extracting heat energy from geothermal briny fluid
US11661857B2 (en) 2020-06-16 2023-05-30 Cyrq Energy, Inc. Electricity generating systems with thermal energy storage coupled superheaters

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