EP2235341A1 - Appareil et procédé de stockage d'énergie thermique - Google Patents

Appareil et procédé de stockage d'énergie thermique

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Publication number
EP2235341A1
EP2235341A1 EP08864032A EP08864032A EP2235341A1 EP 2235341 A1 EP2235341 A1 EP 2235341A1 EP 08864032 A EP08864032 A EP 08864032A EP 08864032 A EP08864032 A EP 08864032A EP 2235341 A1 EP2235341 A1 EP 2235341A1
Authority
EP
European Patent Office
Prior art keywords
heat
fluid
steam
particles
temperature
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP08864032A
Other languages
German (de)
English (en)
Inventor
Reuel Shinnar
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
City University of London
Research Foundation of City University of New York
Original Assignee
City University of London
Research Foundation of City University of New York
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 City University of London, Research Foundation of City University of New York filed Critical City University of London
Publication of EP2235341A1 publication Critical patent/EP2235341A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • 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
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • 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
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • Y02E20/18—Integrated gasification combined cycle [IGCC], e.g. combined with carbon capture and storage [CCS]
    • 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

  • the present invention generally relates to method and apparatus for storing heat energy, and more particularly the present invention relates to method and apparatus for storing heat for use, especially in industrial power systems.
  • Electro-chemical cells are good for storing energy for later retrieval, for example electro-chemical "batteries", can be used for household items, small appliances and even for electric vehicles. But in size and cost, these are mostly small-scale applications. But larger power applications cannot be adequately served with electro-chemical storage batteries. These use include storage of power for power plants or for other large machinery to be driven with stored energy. We refer to these as “large-scale” applications or "industrial” applications.
  • hydroelectric power is often used to provide stored energy on-demand and enable fast load-following for regulation of grid variations.
  • Pumped storage which is similar to hydroelectricity, is widely practiced where the topology allows it but has only moderate efficiency. Compressed air can also be used but it only has moderate efficiency and relatively high costs. None are presently used to meet the large-scale demand in supporting the grid.
  • the ratio between the maximum capacity and the minimum capacity at which the power plant can operate without a significant loss in efficiency is called the turndown ratio.
  • the design specifications call for a minimum turndown ratio of
  • CCPP Combined cycle power plants
  • CCPP technology is based on a high temperature gas turbine, the hot exhaust of which is fed to a boiler creating steam for a steam turbine.
  • gas turbines have a very low turndown ratio, losing efficiency very rapidly when power is below maximum.
  • the only control is basically on-off, as they can be shutdown in an hour and started up in one or two hours. But they are not suitable for rapid load following for grid regulation and there is not enough overcapacity to enable such operation as a practical matter.
  • IGCC Integrated Gasification Combined Cycle
  • the present invention solves one or more of the problems associated with prior heat storage systems and is directed to these and other uses for stored energy.
  • the present invention provides method and apparatus for storing heat, most notably in industrial systems where large sources of stored energy are called upon to meet a work load, such as for driving a turbine in electric power generating plants.
  • the present invention overcomes thermal storage limitations and in fact enables storage of heat at practically any temperature at which most power plants can operate.
  • the present invention is simple in design and is more robust and is relatively less expensive to implement and operate than other methods of heat storage for large-scale applications.
  • the present invention teaches storing the heat content of that hot working fluid by using the hot working fluid as a heat transfer fluid in vapor form and depositing its heat content on a heat storage medium and then removing the now cooled and condensed liquid phase of that heat transfer fluid, perhaps to a holding tank.
  • the liquid heat transfer fluid is returned to the heated storage medium and is reheated as it passes through the hot storage medium and then is returned to the working system and is used as a hot working fluid as needed.
  • a systems and methods that provide stored heat using a heat transfer fluid at or about temperature Ta including: ceramic heat storage medium having an extended longitudinal section extending along a longitudinal axis, the medium formed with particles, the particles cooperating and defining voids between the particles to facilitate flow of a flow of heat transfer fluid in the longitudinal direction, the voids combining to define a longitudinal flow path along the longitudinal axis through the medium; the particles and voids enabling flow of the fluid along a plane perpendicular to the axis laterally across the medium, the particles configured to limit particle-to- particle heat transfer, the particles configured to promote and having an affinity for direct transfer of heat with the fluid in the plane and thus defining a heat front along the plane, wherein the medium and fluid cooperate to transfer heat between the fluid and the medium along the plane to form the heat front perpendicular to the axis and along the plane; the particles simultaneously resisting heat transfer by contact with each other and having an affinity for rapidly transferring heat by direct contact with
  • the particles further include heat storage material and heat insulating material, further including periodic insulating porous layers of the insulating material in the flow path to prevent at the front the reduction of the temperature gradient by heat conduction through the particles, and wherein preferably the insulating layer is a plate with passages, the plate made of an insulating heat resistant material and may be a layer of insulating heat resistant particles similar in size to the heat conducting material.
  • the flow path has the ability to store the heat of steam generated in a concentrating solar power plant, regenerating this steam by feeding water to the storage vessel, for delivery of the regenerated steam on demand.
  • this includes the ability to store the heat of steam generated in the steam boiler of a combined cycle power plant whenever the steam is not needed to generate electricity thereafter using the steam stored whenever needed in a separate turbine providing thereby load following capability and storage to a combined cycle plant; or wherein the extra steam turbine is larger than the steam turbine of the plant itself and providing larger short term load following capability to use to stabilize a power grid; or wherein the plant is an integrated coal gasification combined cycle power plant to provide it with better load following capability; or wherein the plant is a coal fired steam power plant; or wherein the flow path has the ability to store the heat of steam, where the steam for storage was withdrawn from the outlet of the high pressure turbine of a steam power plant after a reheater to reduce the pressure.
  • the method includes the steps of: providing a ceramic heat storage medium having an extended longitudinal section extending along a longitudinal axis, the medium formed with particles, the particles cooperating and defining voids between the particles to facilitate flow of a flow of heat transfer fluid in the longitudinal direction, the voids combining to define a longitudinal flow path along the longitudinal axis through the medium; providing the particles and voids enabling flow of the fluid along a plane perpendicular to the axis laterally across the medium, the particles configured to limit particle-to-particle heat transfer, the particles configured to promote and having an affinity for direct transfer of heat with the fluid in the plane and thus defining a heat front along the plane, wherein the medium and fluid cooperate to transfer heat between the fluid and the medium along the plane to form the heat front perpendicular to the axis and along the plane; providing the particles simultaneously resisting heat transfer by contact with each other and having an affinity for rapidly transferring heat by direct contact with the fluid
  • the particles further include heat storage material and heat insulating material, further including periodic insulating porous layers of the insulating material in the flow path to prevent at the front the reduction of the temperature gradient by heat conduction through the particles.
  • the insulating layer is a plate with passages, the plate made of an insulating heat resistant material or of insulating heat resistant particles similar in size to the heat conducting material.
  • a heat storage system for providing stored heat of a heat transfer fluid X at or about temperature Ta, the system including: a container having a heat transfer fluid cool input and heat transfer fluid superheat output, the container having a longitudinal section in communication with the input and output; a ceramic heat storage medium in the longitudinal section, the medium having a major longitudinal axis and a minor axis, the medium formed with particles and defining voids between the particles to facilitate fluid flow and heat transfer, the voids cooperating to define a major longitudinal flow path extending along the major axis in the longitudinal section; the flow path supplying a flow of fluid below boiling temperature to the boiling region for boiling, the flow path supplying the boiling flow to the superheat region for heating the flow to superheat; and a flow controller, the controller setting a flow rate of the fluid flow, the rate enabling heating by a sequence of thin slices of the boiling particles in the boiling region and the superheated particles in the superheated region, each the slice of particles being defined by a cross-section
  • These and other embodiments include various power applications, industrial processes and the like, and may be used in solar power plants, CCPP plants, ICGG plants, coal and gas fired plants, nuclear plants, geothermal plants, and other operations that use superheated fluid to do work, among other applications.
  • FIG. 1 shows a generic power plant with heat storage system according to the present invention
  • Figure 2 shows in cross-section an illustrative storage vessel of the invention in one practice of the embodiment of Figure 1;
  • Figures 3-5 illustrate comparison of heat propagation during steam regeneration in different embodiments of the present invention, wherein Figure 3 shows heat front propagation using a CO 2 heat transfer fluid system of the invention, compared with Figure 4 showing heat front propagation in H 2 O system of the invention, both at 1500 psi, and compared with Figure 5 showing heat front propagation in H 2 O system of the invention at 600 psi; and
  • Figure 6 illustrates application of a heat storage system according to the present invention to a small-scale solar steam power plant as one of many applications of the invention.
  • a reference to a compound or component includes the compound or component by itself, as well as in combination with other compounds or components, such as mixtures of compounds.
  • the singular forms “a,” “an,” and “the” include the plural reference unless the context clearly dictates otherwise.
  • the present invention provides method and apparatus for storing heat in systems, preferably industrial systems, such as in power plants.
  • the present invention overcomes thermal storage limitations and, in fact, enables storage of heat at practically any temperature at which most power plants can operate.
  • the present invention is simple in design, is more robust and is relatively less expensive to implement and operate than other practical methods of heat storage for large applications.
  • the present invention can be implemented in various systems, and particularly provides storage of heat content of a fluid, and more particularly, a hot working fluid.
  • the hot working fluid is a fluid which can be heated and in its heated state can be used to perform a work function, such as where water is heated to generate steam and the steam is used to drive a machine to get work done, or serves for other uses of stored heat energy.
  • the present invention provides for storage of the heat content of a hot working fluid by using the hot working fluid as a heat transfer fluid and depositing the heat content of the vapor phase of that heat transfer fluid onto a heat storage medium in a container and then the cooled vapor changes to a liquid and is removed from the container.
  • a supply of cold working fluid is returned as a heat transfer fluid to the heated storage medium and is reheated to its vapor phase and then taken from the container is used as a hot working fluid.
  • reheating takes the place of a boiler using the stored energy.
  • the present invention provides for storage of the heat content of a hot working fluid by using a hot working fluid that can undergo a phase transition as a heat transfer fluid and depositing the heat content of that heat transfer fluid onto a heat storage medium in a container and then the cooled fluid is removed from the container all as the fluid flows in a charging direction through the storage medium.
  • a supply of working fluid is returned as a heat transfer fluid to the heated storage medium, preferably counter-currently to the charging direction, and is reheated and then taken from the container and is returned to the working system to be used as a hot working fluid.
  • a working fluid in its heated vapor phase or its heat is stored from that phase and then heat is recovered utilizing the same type fluid first in the liquid phase as a heat transfer fluid and then in the vapor phase and returned as a working fluid.
  • the invention uses a steam working fluid and a steam heat transfer fluid, most preferably superheated pressurized steam.
  • the most important uses of steam in power plants is superheated steam, the free energy of which is strongly dependent upon the temperature of the steam.
  • the present invention can operate with thermal efficiency > 90% and perhaps even >95%.
  • the capability to store the heat content of the steam with high efficiency generates many technical opportunities with wide applications in many areas, such as for extending the capacity of power plants, to provide dispatchable energy, to provide a better control function to a power plant for grid regulation, and for other industrial purposes where stored heat or steam is used.
  • a heat source e.g., a boiler
  • a working circuit such as where steam drives a steam turbine to generate electricity.
  • this working fluid preferably superheated steam
  • this working fluid is available for the storage cycle, i.e., when capacity in excess of demand is available, typically at other than times of peak loading
  • the superheated working fluid steam is routed from the working circuit to a storage circuit that includes a storage medium, and now this fluid serves as a heat transfer fluid carrying the steam heat to the storage medium where the heat is transferred from the heat transfer fluid steam to the storage medium, wherein the steam condenses and the condensate liquid water is drained from the storage medium.
  • the heat is stored as desired and retrieved when needed.
  • the working circuit and the storage circuit are interconnect with appropriate valves to effect a closed circuit, and thus to conserve the fluid (water).
  • the invention includes depositing the heat content of the steam on a solid material, preferably with high heat capacity and high conductivity, such as for example alumina pebbles, in a way that we regenerate the steam at or about the original temperature at perhaps slightly lower pressure, preferably by feeding water counter-currently through the storage medium.
  • a solid material preferably with high heat capacity and high conductivity, such as for example alumina pebbles
  • This is rather equivalent, in terms of efficiency, to storing the steam directly.
  • Storing the heat content of steam and providing a second turbine to a power plant to utilize the stored heat can be of great help in meeting of national energy needs.
  • storage of steam heat content can help in the combined cycle power plant (CCPP), providing a reasonable turndown ratio and can improve load following capability.
  • CCPP combined cycle power plant
  • the steam power plant in general provides about 40-45% of the total plant electricity output, and the gas turbine can be operated all the time with a boiler at full capacity allowing the second (steam) turbine to load follow while diverting any excess steam to storage.
  • a supplementary turbine is driven with that stored steam in times of need which increase the total capacity of the CCPP for peak loads or otherwise to control grid fluctuations.
  • the question is, in each case, if storing the heat content of steam serves a purpose, such as if it is cheaper versus increasing capacity, in most cases it serves a purpose to provide this extra source of stored energy and it is cheaper.
  • storage of heat content of steam includes the concept of using any condensable vapor, and includes any two- phase system with one high temperature vapor phase and one cooler liquid phase. That system preferably operates in two phases and instead of water may also use propane, butane, and other condensable gases.
  • a counter-current pebble bed heat exchanger is provided with a storage function, where heat is exchanged non-cyclically, i.e., it is stored and available later on demand.
  • the hot vapor enters the storage vessel in one direction of travel preferably at the top of a vertically oriented vessel, and heats up the storage medium (preferably ceramic particles), and preferably the bottom end is left cool so as not to unnecessarily discharge heat energy as would lower efficiency of storage.
  • the pipes and the medium, as well as the flow are designed such that the heat progresses through the storage container as a relatively sharp front. Capacity is reached when further loading would discharge steam or boiling water.
  • the fluid that is to be heated (or cooled) flows slow enough such that its temperature completely equilibrates with the storage medium over a very short Distance (compared to the Total Length of the exchanger) most preferably at a factor of more than one in one hundred of (Distance to Total Length), or preferably at least a factor of one in ten, but to get a high efficiency the factor should be much larger than ten.
  • the heating up time of a particle, i.e., a pebble or stone, of the heat storage medium is very short compared to the residence time of the vapor.
  • the heat-up time is proportional to rV ⁇ , where ' ⁇ ' is the thermal conductivity of the medium and 'r' a characteristic length of the chosen filler material. Smaller particles with high conductivity are therefore preferable.
  • this heat-up time controls or limits the ideal maximum velocity permissible for a given storage vessel, both for heat loading and heat recovery.
  • the present invention provides a heat storage system capable of retrievably storing heat energy in various applications with great efficiency.
  • the heat storage system can be adapted for use with various power sources, such as a steam power source.
  • Embodiments of the invention teach storage of heat in various applications including concentrating solar power plants, steam power plants, coal-fired power plants, combined cycle power plants, small-scale solar power plants, and in other uses.
  • FIG. 1 shows an illustrative power generating system 10 including a power plant 1OA and heat storage system 1OB according to the present invention in which power plant 1OA generates a hot fluid 11 which can be used for doing work in the plant, or can be used for storing and retrieving heat into and out of heat storage system 1OB. From time to time the heat stored in storage system 1OB is returned to plant 1OA for doing additional work at the plant, also by use of fluid 11.
  • the hot fluid (e.g., superheated steam) 11 generated in a boiler 12 is used as working fluid 1 Ia for driving turbine 13 or alternatively this superheated steam is diverted from turbine 13 at valve 14 and is used as a heat transfer fluid 1 Ib in heat storage system 1OB.
  • the hot fluid e.g., superheated steam
  • the hot fluid / superheated steam 11 enters heat storage system 1OB as heat transfer fluid 1 Ia via input 15 of storage vessel 16 and flows through and heats heat storage medium 18 within the vessel. This stored heat is later retrieved from the storage medium 18 to regenerate the superheated steam 11 for return to and use at plant 1OB as needed.
  • storage vessel 16 is vertically oriented such that superheated steam 1 Ia is applied to charge heat the storage medium 18 from the top 38 of vessel 16 and flows in the charging direction along longitudinal axis I-II through the storage medium 18 on its journey down to the bottom 39 of vessel 16 where condensate water 20 is removed to holding tank 22. Water 20 is held in this tank and then is returned from holding tank 22 to boiler 12 for reheating or is reintroduced to vessel 16 in a countercurrent flow to regenerate superheated steam 11 as needed.
  • vessel 16 is vertical and superheated steam 11 is introduced at the vessel top 38 and travels through the storage medium 18 such that the heat propagates along a relatively sharp front in order to maximize efficiency of heat transfer, at least during retrieval, wherein the vessel top 38 is at maximum heat at the temperature of the inputted steam 11 while the exit end at bottom 39 of the vessel is kept cooler.
  • the relatively colder end is maintained for purposes of efficiency so that boiling water is not flowed out of the storage vessel to tank 22 wherein its heat would be wasted. This is not done where maximizing efficiency of storage is desired.
  • a section of the storage medium is heated to a very high temperature as delivered by the arriving heat transfer fluid.
  • the flow rate is controlled so that the heat propagates in a relatively sharp front allowing recovery of the stored heat at the highest temperature at which the heat was stored, preferably from superheated steam. It will be appreciated that if during recovery the front moves too fast, the total storage vessel will be cooled almost uniformly and the temperature of the steam recovered will decline continuously to the average temperature. The total heat recovered will remain constant but only a fraction of the steam will be recovered at the top temperature causing a large loss in free energy. This is avoided in practice of the invention because the highest stored temperature, not the average, is sought to be recovered.
  • the hot fluid 11 is a superheated gas vapor at an initial temperature and is flowed through vessel 16 until medium 18 is heated to that temperature. As the vapor passes through the medium, it cools and therefore it leaves the vessel at a lower temperature and with the vessel end 24 being at that lower temperature. When the lower temperature starts to rise, the charging process is stopped. . However, it is most preferred to keep the temperature at the hot end as close as possible and even constantly at the top temperature to maintain high thermal efficiency. Close control of the temperature at the cold end is not so important but it is at the hot end.
  • superheated steam heat transfer fluid 1 Ia is introduced from the top 38 of vessel 16 and heats region 18a to temperature Ta as it continues its flow until the fluid has released enough energy that it undergoes a phase change and condenses to boiling water and then it heats the storage medium in region 18b to boiling temperature Tb.
  • the condensed heat transfer fluid 11a continues to heat the medium in region 18b to boiling temperature as its flows toward the vessel bottom 39 and thereafter the further cooled heat transfer fluid 11a now at temperature Td reaches region 18c at the end of vessel 16 wherein there is inadequate heat energy remaining to bring the storage medium to boiling temperature for storage, and therefore the heat transfer fluid is discharged to tank 22 as a cooled discharge fluid 20 at temperature Td.
  • the discharge fluid 20 would be water at below boiling in this case.
  • the heat storage system 1OB can be controlled during charging by monitoring the temperature of the discharge water 20 and stopping the flow when the temperature either starts to rise or becomes too high, and preferably stops well below boiling (i.e., well below the boiling point of the water at the storage pressure).
  • the flow rate preferably is selected so that as much heat transfer as possible is achieved and with a preference for building a larger superheat region 18a so that upon steam regeneration a greater volume of steam can be regenerated at the superheated temperature Ta, with the rate of flow for regeneration being selected to maximize the delivery of superheated steam as working fluid 11a out of outlet 28 at the top of vessel 16, and the flow of regenerated superheated steam being stopped when the temperature is no longer at the desired temperature to be used as the working fluid 11a, unless an additional reheat is anticipated.
  • the hot heat transfer fluid 11a is a superheated vapor steam at an initial temperature Ta and is flowed through vessel 16 until a first region 18a of medium 18 is heated to that superheated temperature Ta.
  • the fluid passes through the medium, it cools and changes to a boiling water in a second region 18b of the medium at temperature Tb and at the vessel bottom 39 reaches a colder temperature Tc below boiling in a third region 18c and thereafter exits the vessel at outlet 21 at temperature Tc.
  • the flow rate is adequate where a majority of the medium 18 is heated to superheat temperature Ta and only a short region is at boiling and then the end is below boiling.
  • the level of heating can be detected by monitoring the outlet temperature Td of the fluid flow and as it reaches a designated "stop" temperature then the fluid flow and the charging process is stopped.
  • this stop temperature approaches but is below the boiling temperature Tb to minimize heat loss via the hot fluid exiting the vessel, since the heat loss affects overall system efficiency.
  • the superheated steam 11 at temperature Ta flows through the entire path I-II in the vessel and the flow is stopped only when the outlet temperature Td is at or approaches the initial temperature Ta as the steam flows out of the vessel.
  • This enables maximum storage utilization of the vessel 16 but is at a loss of heat energy carried by the out-flowing steam during the charging process, and therefore it is not done when efficiency matters most.
  • boiler 12 is solar-heated and provides superheated steam 11 to drive turbine 13 or as redirected to storage 1OB as described above.
  • the regenerated superheated steam 11 from storage 1OB drives the existing turbine 13 at night to provide additional electricity output 30.
  • turbine 13 is often operated at peak production, and therefore retrieved steam 11 is directed to drive an auxiliary turbine 32 to supply additional electricity output 30 to add to the output of turbine 13, as needed.
  • the storage medium 18 has high heat capacity to minimize storage volume, such as by using available, well-known materials, which can be mass produced to keep the cost down.
  • the heat storage medium 18 is formed as a bed 19 of alumina material parts 19', e.g., stones, pebbles or pellets, with the steam 11 traveling along flow path I-II (vertical in Figure 2) through the medium 18, flowing between the material parts 19'. It will be appreciated that when storing the heat of the superheated steam, there will be a superheated region 18a and a boiling region 18b and then a short cooler region 18c.
  • a sharp front implies that the superheated region is optimally heated and separated from the boiling region with the boundary moving with the flow accordingly.
  • a sharp front is not necessary in the charging cycle but is high preferred in the regeneration cycle.
  • the fluid flows perpendicular to the cross section through the vessel, with the intent to obtain complete temperature equalization between the steam and storage medium over a short distance, i.e., a few feet along the flow path, which we define as a sharp front as a plane P perpendicular to the longitudinal axis.
  • a sharp front relates to as 30' long transition region 18b over a 140' storage path.
  • Plane P is shown in Figure 2 coincident with boiling region 18b and will be appreciated to move with the fluid flow along the flow axis essentially parallel to the plates 40 in this embodiment.
  • alumina particles e.g., stones or pebbles
  • the preferred storage medium is selected because the heat transfer resistance in a steam system is low.
  • the latter means that the thermal conductivity of the alumina is high and their size is small so the time needed to reach the temperature of the hot fluid stream is very short compared to the fluid residence time, and the temperature of the alumina thus follows that of the surrounding hot fluid practically instantaneously.
  • a preferred design allows for charging from the top down and counter-current regenerating from the bottom up, preferably with even and uniform flow distribution laterally across the diameter with complete heat transfer and temperature equalization being reached over a very short distance of fluid flow (e.g., 30' of 140') along the flow axis I-II.
  • the system includes the solid filling, e.g., ceramic particles of high density in a design which enables fluid flow with low pressure drop.
  • the thermal conductivity of the filling should be high and the heating time of the filling should be as short as feasible, but too small particles can cause excessive pressure drops during fluid flow. Even so, as for the latter, low pressure drop in the storage vessels is not critical for steam storage as no recompression is needed.
  • Any design that fulfills the basic design concepts described herein and which allows storage of the heat of a vapor, as from steam, with high thermal efficiency (preferably using counter-current flow) can be used.
  • the size and structure of the particles will be a compromise between the acceptable heating time and the acceptable pressure drop.
  • the storage medium such as ceramic pebbles
  • this material is selected such that it can withstand these conditions, and materials with low porosity (generally ⁇ 5%) are preferable.
  • materials with low porosity generally ⁇ 5%
  • heat up time of the solid particles is short.
  • the rate of feeding the superheated steam or the water for regeneration is to be in a manner such that the heat propagates in a sharp front, especially during recovery.
  • FIG. 2 shows the assembled modules in side cross-section with the peddle bed 19 loaded and filling the vessel interior from the vessel top to the vessel bottom, with flow path I-II extending through the medium 18 between the pebble material 19' of pebble bed 19.
  • a single large storage vessel 16 can be used although preferably smaller modules are assembled to form the vessel.
  • a single such module (such as a 20-30 ft long section of pipe) is good for forming a small power plant, while a number of vessels can be assembled for a larger plant. For example seven 20 foot long modules can be stacked to form a 140 foot storage vessel with end caps, i.e., manifolds.
  • the storage vessel 16 includes preferably cylindrical modules 16A, with two modules 16Al and 16A2 being vertically stacked and the closed vessel 16 being formed by addition of manifold plates 16Bl and 16B2 at the top 38 and bottom 39 respectively of vessel 16 on the respect outer ends of modules 16Al and 16A2. Furthermore, Each module 16A is provided with a flange 41 at its top and bottom such that the mated modules can be and are sealed together at meeting adjacent flanges 41 to form seal 43, as indicated.
  • a manifold plate 16Bl is placed at the top end of module 16Al such that manifold plate rim 45 cooperates with adjacent flange 41 to form seal 47 thereat and manifold plate 16B2 is placed at the bottom end of module 16A2 such that plate rim 45 cooperates with adjacent flange 41 to form seal 49, thus to provide a sealed storage container 16, as shown in Figure 2.
  • the cylindrical modules 16A, 16B of Figure 2 preferably use sections of ready-made large diameter steel pipes such as those used for natural gas pipelines, each cut into a length that is easy to transport and to assemble (such as 20-30 ft long sections), and equipped with the flanges to assist assembly of the vessel on location.
  • modules 16A, 16B, etc. are preferably fitted with perforated plates 40 (Figure 2), the holes 44 of which are smaller than the diameter of the storage material 19', to retain it in place.
  • these plates 40 also serve as conventional flow distributors with a desired pressure drop. It will be further appreciated that preferably these plates are made of non-conducting ceramic to minimize heat conduction through the storage material, since heat transfer is ideally restricted to direct contact between fluid 11a and pebble material 19' and because equilibration between hotter and colder sections of storage could reduce the volume of highest temperature superheated steam that could be regenerated and delivered from the storage.
  • One example of a recommended ceramic filling material 19' is using small balls of non- porous alumina 1-10 mm in diameter (preferably 2-3 mm), with the desired outcome being a fast heating medium.
  • the configuration of the modular vessel and associated feed pipes forms a strong structure wherein the flanged pipe sections reinforce strength of the individual pipes to form a strong high structure that can be anchored to the ground.
  • pipe sections are available for pipelines in sizes up to about 5 ft diameter. This design avoids field construction and can be transported in trucks. These sections should be designed for easy assembly on location. For this purpose, the sections should be short enough, such that they can be made and filled with the ceramic in a shop, and transported completely ready for final assembly. This is less expensive than building large storage vessels on location.
  • the storage medium is suitable over a wide temperature range, preferably from ambient temperature to above the maximum temperature required for a given power technology. This temperature is about 1350 0 F for high efficiency steam power plants and between 2200-2500 0 F for gas turbines.
  • the maximum temperature achievable also determines the cost of the storage. In fact, while high temperatures may require more expensive materials, the storage volume needed, and therefore the cost of the system, is inversely proportional to the difference between the top and bottom temperatures of the power cycle, just as in a power plant.
  • the storage medium 18 is charged with heat preferably from superheated pressurized steam 11, and then the heat in the storage medium 18 remains stored until later demand-driven retrieval using cooler water 20.
  • the working fluid of the system e.g., steam
  • the heat transfer fluid e.g., steam
  • Using water/steam as the heat transfer fluid has the advantage of a high heat transfer coefficient.
  • superheated steam is used, preferably filling the storage vessel from the top down as described. Later, the heat can be recovered by feeding cold water at the bottom, regenerating in a counter-current way, and leaving from the top as superheated steam, practically at the same temperature and pressure as the originating storage.
  • a preferred process of the invention is: supply superheated gas vapor (e.g., steam) 11, store the heat in medium 18 which condenses the vapor (e.g., steam) and then discharge the condensate liquid 20 (e.g., water) to tank 22, wait for demand, and regenerate heated gas vapor (e.g., steam) 11 after reintroducing the cool liquid 20 into the vessel.
  • superheated gas vapor e.g., steam
  • medium 18 which condenses the vapor
  • the condensate liquid 20 e.g., water
  • the superheated steam input 15 and the regenerated steam output 28 are located above the storage medium 18 at the top 38 of vessel 16 and the liquid output 21 and input 25 are located below the storage medium at the bottom 39 of vessel 16.
  • the storage medium 18 and fluid flow are vertically oriented within vessel 16, such as would accommodate introduction of steam 11 at the top and allowing condensed liquid falling toward the outlet after heat transfer and phase change and would also accommodate steam rising after introduction of the cooler liquid 20 during steam regeneration. This arrangement assists in regeneration of superheated steam 11.
  • input/output 15 and 28 on the vessel top may actually be a single bi-directional port that from time to time serves the respective described inlet and outlet functions and likewise for inlet/outlet 21 and 25 at the vessel bottom may be another single bi-directional valve serving the respective described functions.
  • these port are open during charging of the storage medium and for regeneration and closed during storage.
  • the present invention enables use as heat transfer fluid the same gas used as working fluid.
  • FIG. 3 shows heat front propagation using a CO2 heat transfer fluid system, showing a plot of the progress of the heat front in the vessel at 1500 psi during heat recovery.
  • FIG 4 shows heat front propagation of superheated steam in a H2O system of the invention at 1500 psi and 1200F during heat recovery.
  • recovering steam with the same superheat is done in one embodiment with a lower pressure to avoid a "pinch” caused by the phase change (at "Z").
  • the effect of reducing pressure on efficiency is small. Looking at Figure 4 it is seen that there is a growing but short flat section of the temperature front as it progresses. As long this stays inside the completely heated section, the steam is superheated.
  • this short section at constant temperature can cause a "pinch" in the storage cycle.
  • One way to overcome the effect of this pinch is to carry out the recovery cycle at a lower pressure such that the flat section is below the boiling point of the steam used for the storage. This is demonstrated in Figure 5, by reducing the pressure to 600 psi (or even 400 psi) the temperature of this flat region Z is significantly reduced below the boiling point of the fresh steam that enters the storage. Since storage is not done below the boiling point, the pinch then does not matter.
  • insulating porous plates with holes small enough to retain the filling material, or alternatively we can use thin layers of insulating particles the same size as the storage particles.
  • the storage method itself has no temperature limitations, but above 1100 or 1150 0 F, the vessels and pipes should be made of stainless steel, which can be used up to 1500 0 F, though as a practical matter few applications of steam require storing at temperature higher than 1400 0 F.
  • standard steel vessels can be used at higher temperatures by insulating them from the inside with ceramic coating, and then insulating the outside is not done.
  • the heat propagates along a relatively sharp front in order to maximize heat transfer, wherein the hot exit always stays hot and the cold exit cold, by stopping or reversing the cycle before the thermal front reaches the exit.
  • the hot end of the storage vessel always stays at the maximum temperature of the steam or vapor to be stored.
  • the hot end of the storage vessel stays at a substantially constant temperature.
  • the cool end need only be at a temperature below the boiling point of the steam or vapor used for the charge. Thus, the temperature of the cool end can vary without preference for remaining at a substantially constant temperature.
  • the present invention takes advantage of the principle of a recuperative heat exchanger, which in the past has been used to improve the thermal efficiency of power plants by heat exchanging hot flue gas with fresh air fed to a combustor, in a cyclic process of heat and exchange.
  • the same principle has been used more recently in the development of cyclic catalytic reactors.
  • the cycles alternate and are of equal duration, while gas velocities are also equal in both directions.
  • the present invention includes recognition that these cyclic heat exchangers can be modified to provide added value to power generation, wherein charging of the storage medium is interrupted after heat storage, with the storage medium storing the heat until it is needed. This can be for any realistic period of time according to the capacity of the storage system.
  • the feed is made uniform across the cross-section, perpendicular to the direction of flow through the medium.
  • the storage medium is suitable over a wide temperature range, preferably from ambient temperature to above the maximum temperature required for a given power technology.
  • This temperature is about 1350 0 F for high efficiency steam power plants and between 2200-2500 0 F for gas turbines.
  • the maximum temperature achievable also determines the cost of the storage. In fact, while high temperatures may require more expensive materials, the storage volume needed, and therefore the cost of the system, is inversely proportional to the difference between the top and bottom temperatures of the power cycle, just as in a power plant.
  • the storage medium has high heat capacity to minimize storage volume, and preferably uses available, well-known materials, which can be mass produced to keep the cost down.
  • the heat storage medium uses small alumina pellets.
  • Figure 5 illustrates this, showing heat front propagation in H2O system at 600 psi.
  • the storage method itself has no temperature limitations, but above 1100 or 1150 0 F, the vessels and pipes should be made of stainless steel, which can be used up to 1500 0 F, though as a practical matter few applications of steam require storing at temperature higher than 1400 0 F.
  • standard steel vessels can be used at higher temperatures by insulating them from the inside with ceramic coating, and then insulating the outside is not wanted.
  • the length of each vessel and the number of vessels required depends on the specific design. The actual design depends on the load pattern and the physical constraints and it is preferred that the design be guided by assuring that under all conditions the heat front remains sharp enough to guarantee that the top temperature, at which the heated steam leaves the storage vessel, remains at all the time at the desired value.
  • CSP Concentrating Solar Power Plants
  • One known example is a solar tower operating at 600 0 F using a short-term storage method of storing pressurized boiling water in a vessel and generating steam by reducing the pressure. This is not efficient. But such a tower could be easily modified in practice of the invention to generate steam with a temperature of say 1200 0 F, and superheated steam has a large advantage in thermal efficiency over saturate steam.
  • the present steam system of the invention requires no boiler and therefore there is no temperature loss due to heat exchangers.
  • the design is simple and no compressors are needed; pressure drops in pipelines or collectors have very little impact, as at constant super heat, and no reheat, the efficiency is only a weak function of pressure.
  • Solar power plants with direct steam are advantageous for a number of uses. With direct steam there is no need to recompress any gas or pump a hot transfer fluid over large distances, both of which require parasitic power consumption. In a direct steam use without reheat there is still a higher temperature achieved without heat transfer being required. Higher temperature plus the lack of parasitic losses compensate for a significant part of the difference in efficiency versus added reheat.
  • One preferred application of direct steam is for small CSP plants, say below 100 MW and especially for smaller distributed CSP plants down to sizes of perhaps 50 kW. These are useful for remote locations.
  • Power plants have a significant size factor.
  • a 10 MW conventional coal power plant built with a given efficiency and pollution control is approximately three times more expensive per kWh than a 200 MW plant for the same conditions.
  • CSP collectors and the storage vessels for our method are an assembly of modules preferably mass produced and sized for easy shipping.
  • all we need are enough collectors, storage vessels, pumps, and a turbine, tied together, and the size effect is relevant only for the turbine and the pumps which are a small fraction of the total cost of a CSP.
  • the simplicity of a CSP with direct steam storage gives it a large advantage for small plants versus coal or for other types of CSP or solar energy.
  • the second application where solar direct steam storage has a decisive advantage is for CSP plants designed for either cogeneration of steam and electricity for large chemical plants and refineries, or for large-scale steam generation for heavy oil recovery or similar uses, in areas that have sufficient sun.
  • 24-hour operation is essential and the storage method of the present invention can supply this cheaper than any other CSP design.
  • superheated steam is preferable, which is important as storage of low temperature saturated steam is feasible according to the present invention, but would be more expensive.
  • the pressure of the steam should be chosen for the application, but for storage it is advisable to keep the pressure below 1500 psi, as high pressures give too high a storage cost.
  • high pressures For small CSP plants with direct steam generation such high pressures are not suitable anyway: 1000 psi is plenty in such case.
  • super heat at least above 1000 0 F provides for both efficiency and low storage cost.
  • FIG. 6 illustrates a further embodiment for a small-scale concentrating solar power plant 50.
  • Solar collectors 52 are provided with water 54 from a water tank 56 and generate superheated steam 58 in the collectors which is fed to steam turbine 60 via control 62 to generate electricity at output 64.
  • additional or spare superheated steam 58 is diverted at control 62 into heat storage 66, which stores heat from the diverted steam as earlier described.
  • the condensate water 55 is returned via control 62 to tank 56.
  • cold water 68 from tank 56 is introduced into the heat storage tank 66 preferably counter-currently from below. Water is converted to superheated steam 70 and taken from the top of the storage 66 and is applied to drive turbine 60 to produce electricity at output 64.
  • the embodiment of Figure 6 deals with a special need: supplying electricity to remote areas with abundant sunshine but no connection to the grid and possibly with fuel and water in short supply. This situation exists in many underdeveloped countries and in places where it is too expensive to build a connection to the grid. To supply small villages or cities, the size of such plant should be between perhaps 50 KW to 20 MW. These small plants are inherently more expensive on a kilowatt basis than large plants but they are certainly competitive in absence of a grid or fossil fuels, and are much cheaper than PV with storage batteries, and certainly are needed where the resources to build a larger plant are not available.
  • such small CSP plants should have low maintenance requirements and operate without needing a dedicated full time operator or many skilled personnel. Additionally, a relatively large store capacity is desired, preferably for more than one day. Water cooling should not be required.
  • the design according to the present invention fulfills all these requirements.
  • a preferred embodiment features parabolic trough collectors or other sets of collectors in which the heat exchange fluid is H 2 O based, e.g., water is fed to the collectors and heated to superheated steam).
  • H 2 O based e.g., water is fed to the collectors and heated to superheated steam.
  • These collectors are available from several companies (e.g., Schott) in a design that can be mass-produced.
  • the superheated steam can be fed directly into a steam turbine designed as a backpressure turbine with air cooling; the condensed water is recycled to a storage tank and then to the collector.
  • the CSP plant can serve a second function if turbine 60 is a back pressure turbine.
  • the steam 74 exiting backpressure turbine 60 can be used for purifying or desalinating a local water source.
  • steam 124 is applied to desalinization boiler 126, wherein inputted H 2 O is processed and outputted as potable water H 2 O*.
  • a storage system which can store the heat of superheated steam and when required can generate steam with the same superheat.
  • the system is simple. There are no compressors or boilers and only a few pumps. The entire system can be designed and manufactured for shipping by truck for easy assembly on location. Also, it can be designed for totally automatic control. It is also relatively low cost.
  • the present invention covers not only the unique storage method, but also its applications.
  • One application that has a large number of implementations is storage of steam in combined cycle power plants (CCPP).
  • CCPP combined cycle power plants
  • Combined cycle power plants which have a high temperature gas turbine, the hot exhaust of which is used to provide the heat for a companion steam power plant, are for gaseous fuel the most efficient power plants (up to 60% efficiency) a higher than any power plant based on fossil fuels. They can be fueled by natural gas, diesel oil, methanol and other lighter clean fuels, and are also used in IGCC power plants, which provides clean power from coal. Gas-fired CCPPs supply 20% of the electric power used in the US today. All CCPPs have, however, one disadvantage: they cannot rapidly load follow. For high efficiency the gas turbine has to operate at maximum load, and when the load goes below 80% they become very inefficient.
  • CCPPs are in wide use today.
  • the steam power plant part of the CCPP supplies between
  • the steam plant can be controlled separately by diverting any unneeded steam to a heat storage unit according to the present invention.
  • the gas turbine always operates at optimal capacity and all control of the output is done by controlling the amount of steam fed to the steam turbine, diverting the rest to storage.
  • an additional steam turbine in addition to the storage, there is provided an additional steam turbine, the size of which can be chosen based on the load following capability designed. Thus, it could be bigger than the steam turbine in the original plant to provide larger peak power or load following capability for a designed time period.
  • fast load following capability with a 40% turndown capability, and the capability to increase the power for short times by even a large ratio. This totally changes the capability of combined cycle plants to load follow.
  • all of the steam can be withdrawn for storage after the reheater, where it has a suitable lower pressure.
  • the high-pressure turbine will still generate electricity as electricity is needed even in periods of low demand.
  • the steam can be expanded adiabatically.
  • a reheat turbine for the stored steam is not practical as the steam is only needed when the load exceeds the maximum capacity, a point where the boiler is fully utilized; instead the storage unit acts as a "boiler" making steam available as needed.
  • the special turbine for the stored steam can be sized according to system needs and if the extra load is only used for short times, results in total output being temporarily much greater than the design capacity of the power plant. This method is a very cost effective tool to deal with peak loads and load fluctuations, allowing to add short-time extra capacity much cheaper than building new coal power plants, and cheaper that just increasing the bulk capacity of new power plants to greater than needed on a steady basis.
  • the present storage invention overcomes this problem for Geothermal as for other power plants.
  • the present system for storing the heat of steam allows the steam to be stored at times of low electricity demand and therefore, at low electricity prices.
  • electricity is recovered from storage when electricity is at a higher cost, i.e., when there is a strong demand, there is a large savings. This is so because the present storage invention cost per Kwh stored is much lower than the price differential between high and low demand.
  • the present invention solves a number of problems faced by prior art power plants and the power industry.
  • the invention enables storage of solar energy and enables power generation at times when solar energy is not available.
  • Conventional power plants can be equipped with heat storage capacity to store heat during off-peak time and use it for extra capacity during peak time or anytime when load following and control of grid fluctuations is needed. With this storage capability, these power plants provide an improved control function for the grid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un procédé et un appareil pour stocker de la chaleur dans des systèmes industriels qui font appel à des sources importantes d'énergie stockée pour répondre à une charge de travail, stocker la contenance thermique d'un fluide de travail chaud en utilisant le fluide de travail chaud comme fluide de transfert de chaleur sous forme de vapeur, en déposant sa contenance thermique sur un support de stockage de chaleur et en retirant ensuite la phase liquide refroidie et condensée de ce fluide de transfert de chaleur, et lorsqu'un fluide de travail chaud est de nouveau nécessaire, le fluide de transfert de chaleur liquide est renvoyé au support de stockage chauffé, est réchauffé lorsqu'il passe à travers le support de stockage chaud et est ensuite renvoyé au système de travail pour être utilisé comme fluide de travail chaud.
EP08864032A 2007-12-21 2008-12-19 Appareil et procédé de stockage d'énergie thermique Withdrawn EP2235341A1 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
US863507P 2007-12-21 2007-12-21
US6346708P 2008-01-31 2008-01-31
US6977908P 2008-03-17 2008-03-17
US6977808P 2008-03-17 2008-03-17
US8300508P 2008-07-23 2008-07-23
US8305108P 2008-07-23 2008-07-23
US8605508P 2008-08-04 2008-08-04
US9704308P 2008-09-15 2008-09-15
US11583108P 2008-11-18 2008-11-18
PCT/US2008/087820 WO2009082713A1 (fr) 2007-12-21 2008-12-19 Appareil et procédé de stockage d'énergie thermique

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EP2593742A2 (fr) * 2010-07-12 2013-05-22 Siemens Aktiengesellschaft Dispositif de récupération et stockage d'énergie thermique pourvu d'un aménagement d'échangeur de chaleur comportant une région d'interaction thermique étendue
GB2485836A (en) 2010-11-27 2012-05-30 Alstom Technology Ltd Turbine bypass system
GB201104867D0 (en) * 2011-03-23 2011-05-04 Isentropic Ltd Improved thermal storage system
CA2834938C (fr) 2011-05-02 2019-06-25 Hitesh BINDRA Stockage d'energie thermique pour centrales a cycle combine
CN102818468A (zh) * 2011-06-12 2012-12-12 北京兆阳能源技术有限公司 一种固体储热装置
WO2016050367A1 (fr) * 2014-09-30 2016-04-07 Siemens Aktiengesellschaft Système d'évacuation à système d'échange d'énergie thermique à haute température et procédé
EP3245389B1 (fr) * 2015-03-20 2020-07-15 Siemens Gamesa Renewable Energy A/S Centrale d'accumulation d'énergie thermique
CN105804817A (zh) * 2015-06-20 2016-07-27 韩少茹 发电系统及其运行控制方法
CN104929710B (zh) * 2015-06-25 2016-04-13 国家电网公司 一种余热利用的高效节能发电系统
CN105351018A (zh) * 2015-11-27 2016-02-24 上海援梦电力能源科技咨询中心 带有熔盐储能供电供热的火力发电系统及方法
CN106122758A (zh) * 2016-08-16 2016-11-16 陈恳 移动式蒸汽储存装置
CN112534201B (zh) * 2018-07-26 2022-08-12 苏黎世联邦理工学院 温跃层控制方法
FR3099821B1 (fr) * 2019-08-08 2022-04-29 Eco Tech Ceram Dispositif de stockage thermique amélioré
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IL206505A0 (en) 2010-12-30
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BRPI0819515A2 (pt) 2015-05-26
EA201001060A1 (ru) 2011-04-29

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