WO2009114205A2 - Adsorption-enhanced compressed air energy storage - Google Patents
Adsorption-enhanced compressed air energy storage Download PDFInfo
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- WO2009114205A2 WO2009114205A2 PCT/US2009/001655 US2009001655W WO2009114205A2 WO 2009114205 A2 WO2009114205 A2 WO 2009114205A2 US 2009001655 W US2009001655 W US 2009001655W WO 2009114205 A2 WO2009114205 A2 WO 2009114205A2
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- energy storage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
- F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/005—Adaptations for refrigeration plants
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- 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
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- 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
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
-
- 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
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
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- 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
- F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
- F02C1/02—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being an unheated pressurised gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
- F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
- F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
- F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/50—Intrinsic material properties or characteristics
- F05D2300/514—Porosity
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- 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
- Y02E20/14—Combined heat and power generation [CHP]
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- 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
- Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
Definitions
- the present disclosure relates to the field of energy storage.
- the present disclosure is directed to an energy storage device that includes a pressure chamber containing a porous material that adsorbs air.
- CAES Compressed air energy storage
- the air compressor is driven by an electric motor, and subsequently used to drive an air motor or turbine connected to an electromagnetic generator, thereby forming the functional equivalent of an electrochemical battery. If the charge-discharge cycle is carried out slowly enough to be approximately isothermal, meaning that the heat generated by compression dissipates without raising the temperature of the air appreciably during compression, and the heat drawn in from the environment likewise keeps the air from cooling appreciably during expansion, this form of electricity storage can have good efficiency.
- CAES systems can also be engineered to have higher reliability, lower maintenance and longer operating lifetimes than chemical batteries, and their cost can be comparable to battery- based systems providing that an inexpensive means of storing the compressed air is available.
- the high cost, weight and large size of manufactured pressure vessels in which to store the air, such as steel tanks, prevents CAES devices from competing with batteries in all of their usual applications.
- CAES CAES has been used for three commercial purposes.
- the first and most widespread use is not as a means of energy storage per se, but to power pneumatic tools and machines in shops and factories.
- Pneumatic tools have higher weight-to-power ratios than electrically powered tools, and the small electric motors in such tools also tend to be inefficient compared to the larger motors that drive air compressors.
- the compressed air is stored in a tank big enough to serve as a buffer and ensure that the pressure in the system stays constant.
- the overall efficiency of these systems is limited by the fact that they discard the heat of compression and do not reheat the air during its rapid expansion. This inefficiency is limited by using modest pressures, usually less than ten atmospheres, which also reduces the capital costs of such CAES systems.
- CAES The second use of CAES is for temporary backup power to keep essential machinery running in the event of a power failure, for example in computer data centers or hospitals.
- floor space is at a premium, necessitating the use of pressures of a hundred or more atmospheres to attain a relatively high energy density, but the cost of the high-pressure steel storage tanks for the compressed air is justified by the high reliability of the system and the high power it can immediately deliver in the event of a power failure.
- a longer-term backup system like a diesel generator can be brought online if need be.
- a CAES system also requires less maintenance, has a longer lifetime, and does not have the disposal costs associated with environmentally hazardous chemicals.
- Other such short-term backup power solutions include supercapacitors and flywheels, which are likewise relatively costly.
- CAES third commercial use to which CAES has been put is to lower the cost of generating and/or distributing electric power by utility companies. This can be done in several ways, the most common of which is to enhance central generation capacity. Large central power plants such as coal and nuclear are expensive to stop and start, while smaller plants such as gas-fired turbines are readily turned off and on but are comparatively expensive to operate. Hence, if the energy from large plants can be stored when demand is low and used to produce electricity when demand is high, the need to install and operate small peak-load plants can be reduced, thereby also reducing the average or "levelized" cost of producing electricity.
- an energy storage device in an embodiment of the present disclosure, includes a porous material that adsorbs air and a compressor.
- the compressor converts mechanical energy into pressurized air and heat, and the pressurized air is cooled and adsorbed by the porous material.
- the energy storage device also includes a tank used to store the pressurized and adsorbed air and a motor. The motor is driven to recover the energy stored as compressed and adsorbed air by allowing the air to desorb and expand while driving the motor.
- another energy storage device is presented.
- the energy storage device includes a porous material, where a suitable fluid has been adsorbed.
- the device also includes a compressor that converts mechanical energy into pressurized air and heat and a barrier. The pressurized air is cooled by allowing the heat to flow through the barrier, the heat is transported to the porous material to which a fluid has been adsorbed, and the heat raises the temperature of the porous material, causing the fluid to desorb from it.
- the energy storage device includes a porous material that adsorbs air and a thermal energy storage system that stores heat.
- the device further includes a compressor that converts mechanical energy into pressurized air and heat.
- the pressurized air is cooled and adsorbed by the porous material and the temperature of the porous material and surrounding air is controlled by allowing the heat to flow through a barrier that prevents the pressurized and adsorbed air from escaping.
- the heat is directed to the thermal energy system and is stored there.
- the device includes a tank that stores the pressurized and adsorbed air, and the energy it contains is recovered when needed by allowing the air to desorb and expand.
- Figure 1 plots adsorption isotherms for the principal constituents of air
- Figure 2 plots the ratio of the number of nitrogen to the number of oxygen molecules versus nitrogen pressure where the ratio of nitrogen to oxygen pressures has a fixed value of 4.0;
- Figure 3 is a schematic diagram of mass and energy flow in an adsorption-enhanced compressed air energy storage embodiment, showing these flows during the first half of the charging process;
- Figure 4 is a schematic diagram of mass and energy flow in an adsorption-enhanced compressed air energy storage embodiment, showing these flows during the second half of the charging process;
- Figure 5 is a schematic diagram of mass and energy flow in an adsorption-enhanced compressed air energy storage embodiment, showing these flows during the first half of the discharging process
- Figure 6 is a schematic diagram of mass and energy flow in an adsorption-enhanced compressed air energy storage embodiment, showing these flows during the second half of the discharging process
- Figure 7 is a process flow diagram which illustrates in greater detail how an adsorption-enhanced compressed air energy storage embodiment operates during the first half of the charging process
- Figure 8 is a process flow diagram which illustrates in greater detail how an adsorption-enhanced compressed air energy storage embodiment operates during the second half of the discharging process.
- Figure 9 is a three-dimensional drawing of an array of air adsorption cylinders in a temperature- control chamber
- Figure 10 is a three-dimensional drawing of the adsorption heat pump that is primed and used to upgrade stored heat during the first half of the charging and second half of the discharging processes, respectively;
- Figure 11 is a three-dimensional drawing of the mixer-ejector air turbine used to recover the energy stored as compressed air, adsorbed air, and heat during the discharging process.
- the present disclosure provides two novel uses for the physical process of adsorption in porous materials, both of which greatly improve the economics of compressed air energy storage (CAES). Further the present disclosure provides several improvements to devices that store energy in the form of compressed air, and that may also store some of the energy in the form of sensible or latent heat.
- CAES compressed air energy storage
- the compressed air is presently stored in underground geological reservoirs such as natural aquifers or man-made depleted gas or oil wells, rather than in manufactured tanks.
- the economics is further improved by using the compressed air to turbo-charge a gas-fired turbine, thereby saving the turbine from having to expend energy compressing the air itself. This allows the energy stored in the compressed air to be recovered while at the same time generating additional energy from natural gas.
- turbocharging allows the stored energy to be delivered at a high power level and recovered with an overall efficiency of about 70%.
- AA-CAES A somewhat different approach to using CAES for utility purposes, which has yet to be commercially deployed, is known as “advanced adiabatic CAES.”
- AA-CAES the heat extracted from the air during compression is stored and used to reheat the air during expansion as it powers an air motor or turbine. In principle, this allows both the energy stored as heat and stored as compressed air to be recovered, so the efficiency of AA-CAES can approach 100% in principle. In practice, it is difficult to store and recover the heat of compression without significant losses especially at high power levels.
- the air is again to be stored in underground reservoirs at high pressure, and the heat is to be stored in sensible rather than latent form, usually at temperatures well above 200 0 C.
- Energy storage has the potential to reduce the operating costs of electric utilities in several other ways as well, although none have yet come into widespread use. These include transmission capacity deferral and congestion reduction, various ancillary services, bulk electricity price arbitrage, and load shifting or leveling at the end-user level. In the future, however, the most important such service is likely to be renewable capacity firming. Renewable energy sources such as wind and solar tend to be intermittent, so that their capacity varies in time and is often not sufficient to satisfy the demand for electricity. If the energy can be stored at times when capacity exceeds demand and used to produce electricity when demand exceeds capacity, these renewable energy sources will become much more cost effective.
- CAES central capacity generation
- suitable underground reservoirs are neither common nor transportable.
- a modular system that could be assembled anywhere and scaled to the size of the power plant there would, if cost effective, be much more useful for central generation capacity as well as renewable capacity firming.
- CAES could provide some or all of the other cost reduction services mentioned above.
- the main reason that such CAES systems are not presently cost-effective is, once again, the high cost of manufactured storage tanks for compressed air. It should be noted that, to a first-order approximation, the cost of the tank is independent of the pressure at which the air is stored, since raising the pressure allows the tank to be made smaller but requires its walls to become proportionately thicker, and vice versa.
- CAES systems are more economical, which has not received much attention, is to take advantage of the fact that the compression and expansion of air is a facile means of pumping heat from one place to another. This means that a CAES system could easily be developed to provide combined heat, cooling and power to end users. If such a CAES system were installed in a home or business where time of day electricity pricing is available, for example, it could be charged during the night when the electricity is relatively inexpensive while simultaneously providing heat to the building, and the electricity it produced used or sold back to the grid during peak daytime hours while also providing air conditioning.
- the heat released upon condensation of the desorbed vapor may be stored in sensible form, and recovered by using it to promote the evaporation of the condensate and then allowing the resulting vapor to re- adsorb.
- adsorption refrigerator or heat pump Such a device is commonly known as an adsorption refrigerator or heat pump. Nevertheless there have been no attempts to use the process of adsorption in any of these ways to make CAES systems less expensive, more efficient or transportable, better suited to combined heat-and-power applications, and / or safer to deploy.
- the present invention improves upon the economics of compressed air energy storage in four interrelated ways.
- the first is the use of an adsorbent for air in order to reduce the pressure in and/or volume of the vessel needed to store a given quantity of energy in the form of compressed air.
- the second is the desorption of water or some other suitable fluid, possibly combined with storage of the low-grade sensible heat released upon condensation of the vapor thereby produced, as a means of storing the heat of compression so as to make AA-CAES more economical.
- the third is to store the heat generated by adsorption of the air and to recover this energy at a later time by using it, possibly along with the heat of compression, to raise the temperature of the adsorbent material and/or the compressed air as it expands.
- the fourth is a new thermodynamic cycle for CAES, in which the temperature of the compressed air is varied so as to keep the pressure of the stored air approximately constant over the charge/discharge cycle.
- This "temperature-swing" cycle is especially advantageous when an adsorbent for air is utilized, as just described, and it is also applicable when the heat of compression and/or adsorption is stored for subsequent use, for example by means of an adsorbent for water or some other suitable fluid.
- the use of a temperature-swing cycle in adsorption-based gas separation processes is well established (see, for example, USPTO Pub. No. 2006/0230930).
- the present invention considers only the use of adsorbents for air in large-scale, stationary energy storage applications, the desorption of water or some other suitable fluid as a means of storing the heat of compression and / or adsorption of the air, and CAES systems that use a temperature-swing cycle. None of these processes are suitable for small-scale, mobile applications such as regenerative braking.
- an adsorption-enhanced CAES embodiment of the present invention utilizes a zeolite material for this purpose.
- zeolites adsorb nitrogen more strongly than oxygen, and so have been extensively utilized to separate the oxygen and nitrogen constituents of air for industrial and medical purposes.
- the temperature-pressure boundary at which the air in zeolites liquefies has not been mapped out in any detail.
- This process also called capillary condensation, is not normally observed at temperatures well above the critical point of the adsorbate gas, or about -140°C in the case of air. Such a low temperature would be difficult to achieve in a cost-effective adsorption-enhanced CAES device.
- a new use of adsorption in porous materials is as a means of reducing the volume of the tank needed to store a given mass of air at a given pressure and temperature, or alternatively, of reducing the thickness of the walls of the tank or the strength of the materials of which it is made, by reducing the pressure needed to store a given mass of air in a given volume and at a given temperature.
- Either of these two alternatives may be achieved by placing a suitable porous material inside the pressure chamber that holds the compressed air, where by suitable we mean that this porous material adsorbs a greater volume of air than the material itself occupies at the temperature and pressure of the compressed air in the chamber.
- Such porous materials exist by virtue of the fact that, at equilibrium with the temperature and pressure fixed at suitable values, air molecules in an adsorbed state have greatly reduced mobility and a much higher density than those in the gaseous air around them.
- another new use of adsorption in porous materials is as a means of storing the heat generated by the process of compressing the air, and/or the heat generated by the process of adsorption of the air as in the first new use above.
- This second new use is achieved by placing a porous material to which water or some other suitable fluid is adsorbed in thermal contact with, but outside of, the air compressor and/or pressure chamber.
- the porous material of the second new use need not be the same kind of material as that of the first new use. The heat increases the temperature of this porous material and so promotes desorption of the water or other fluid from it.
- this process converts kinetic energy into potential energy, which may then be stored indefinitely by preventing the vapor produced by desorption from coming back into contact with the porous material and being re-adsorbed.
- This may be described by saying that the heat has been stored in latent form.
- the transfer of heat from the compressed air to the porous material of the second new use reduces the temperature of the compressed air, thereby also reducing the work needed to further compress it, as well as the size or strength of the tank in which it is stored.
- the cooling of the porous material of the first new use which is concomitant upon transferring the heat of adsorption from it, increases the amount of air that it adsorbs at any given pressure.
- the vapor produced by desorption of the fluid must be available for re-adsorption when needed.
- the large volume occupied by the vapor makes it difficult to store in that form, and compressing or condensing it releases a smaller but still significant amount energy in the form of sensible heat. It is nevertheless possible to store this sensible heat, and to subsequently use the process of expansion of the vapor or evaporation of the liquid to harvest this heat and so regenerate the vapor.
- the advantage of doing this instead of storing the heat generated by compression and / or adsorption of the air directly in sensible form, lies in the fact that in the former case the sensible heat is contained in a material at a lower temperature that can be more easily insulated against losses.
- the latent heat may be recovered, along with the energy stored as compressed and / or adsorbed air, in mechanical form by placing the porous material of the second new use in thermal contact with the air motor or turbine and at the same time allowing the water or other fluid vapor to re-adsorb to it.
- the sensible heat generated as the water or other fluid re-adsorbs is conducted or otherwise transferred to the compressed air as it expands in the air motor or turbine, raising its temperature and pressure so that it does more useful work.
- this transfer of heat cools the porous material of the second new use and so further promotes the spontaneous re-adsorption of water or some other suitable fluid to it.
- the transfer of heat from this porous material to the porous material of the first new use promotes the desorption of air from it at the pressure in the chamber, and this compressed air may then be converted back to mechanical energy via the air motor or turbine as just described.
- porous materials When porous materials are incorporated into a CAES device for either of these two new uses, we shall refer to the resulting process as adsorption-enhanced CAES, or AE-CAES, and to the energy storage device itself as an AE-CAES device or AE-CAES system.
- the invention further provides a new use for the industrial process of temperature-swing adsorption, which has been widely employed as a means of separating mixtures of gases.
- This new use is actually applicable whether or not a porous material has been incorporated into a CAES device for the first new use of the physical process of adsorption.
- the temperature of the air and of the porous material to which air is adsorbed if the device incorporates a porous material for the first new use, is lowered when charging the CAES device with energy, and raised again when discharging it, all the while pumping air in or allowing air to escape from the pressure chamber at a rate that keeps the pressure of the compressed air therein approximately constant.
- a constant air pressure will simplify the construction and operation of any CAES device, but more important for the purposes of the present invention is the fact that the temperature- swing process is a convenient means of increasing the amount of air stored and released by any given quantity of porous material as in the first new use. It does this because the quantity of a gas adsorbed by the vast majority of known porous materials decreases as the temperature thereof is raised, and vice versa.
- V sys The volume of air in the system.
- P sys The pressure at which we maintain the air in the system by controlling its temperature.
- T ⁇ is The temperature of the air in the system when it is in its discharged (minimum energy) state.
- T- Ch9 The temperature of the air in the system when it is in its charged state (7 " chg ⁇ T dis ). • Pa tm ' The pressure against which the system does work while being discharged (here taken to be 100,000 Pascal, approximately one atmosphere).
- ⁇ dis and n chg be the number of moles of air in the system (i.e. multiples of Avogadro's number of air molecules) in its discharged and charged states
- V 31111 be the volume of air at pressure P atm needed to charge the system
- the ideal gas law and the definition of molar volume then imply that the following relations among these variables hold:
- V atm Psys V sys (1 / 7 " chg - 1 / 7 dis ) V M I R
- W sys ((P sys / Pat m ) ⁇ - 1 - 1 ) P*n Va n , / ( ⁇ - 1 )
- zeolite known as NaX.
- Faujasite-type zeolite containing sodium ions which is commonly sold under the commercial name of 13X.
- Dry air is about 78% nitrogen, 21% oxygen and 1 % argon by mole fraction.
- NaX adsorbs nitrogen more strongly than oxygen or argon, i.e. on a molar basis it adsorbs more nitrogen than oxygen or argon when placed under these pure gases at a given pressure and temperature — at least at the relatively low pressures usually considered for the purpose of purifying oxygen or nitrogen.
- oxygen and argon are largely adsorbed at chemically identical sites on the NaX pore walls and also have similar adsorption isotherms, while nitrogen is largely adsorbed at distinct sites which do not overlap with those of oxygen and argon.
- Figure 1 plots adsorption isotherms for the principal constituents of air, namely nitrogen and oxygen, with the commercially available zeolite widely known as NaX or 13X, at four different temperatures and at pressures of up to 20 atmospheres.
- the isotherms for nitrogen, obtained from the Sips isotherm formula are plotted with solid lines, while those for oxygen are obtained from the Langmuir isotherm, a special case of the Sips, and are plotted with dashed lines.
- the plots shown thus extrapolate Miller's data to the higher pressures needed for a cost-effective adsorption-enhanced compressed air energy storage device.
- Figure 2 plots the ratio of the number of nitrogen molecules to the number of oxygen molecules adsorbed to NaX against pressure at the same four temperatures as in Figure 1 , where the pressure of oxygen at each point on the plot is 25% that of nitrogen and hence approximately equal to the partial pressure of oxygen in air at 125% of the nitrogen pressure. These ratios are calculated using the extrapolated isotherms shown in Figure 1. The dashed horizontal line shows where this ratio has the value 4.0, so that the ratio adsorbed is approximately equal to the ratio of the partial pressures of nitrogen and oxygen in air.
- the corresponding pressure at a temperature of -40 0 C 1 indicated by the dashed vertical line is expected to be a reasonably cost-effective nitrogen partial pressure for an embodiment of adsorption-enhanced compressed air energy storage based on a temperature-swing cycle with a minimum temperature of -40 0 C. This is because going to higher pressures or lower temperatures would increase the amount of air adsorbed at a lower rate than had been achieved at lower pressures and higher temperatures, so that the cost-benefit ratio obtained from the use of the NaX adsorbent would become less favorable.
- FIGS. 3 through 8 show schematic diagrams of the complete AE-CAES (adsorption- enhanced compressed air energy storage) embodiment. These diagrams are graphic versions of the well-known process flow diagrams and the associated symbols for the common mechanical, fluidic and electrical components of chemical and materials processing systems, which are widely used by the engineering community. Process flow diagrams are not intended as blue-prints for a specific design, but rather to allow one skilled in the art of chemical and materials processing to design a system that can reproduce a specific process using such standard components. The diagrams thus provide a suitable means of describing the invention, which provides processes by which CAES systems may be enhanced using adsorption in porous materials, rather than a specific device or design. In those parts of the embodiment in which the components employed are not perfectly standard, more detailed drawings are given, and these have been enlarged in Figures 9 through 11.
- Figures 3 through 6 give high-level views of the principal mass and energy fluxes through an exemplary embodiment of an AE-CAES system at four points in its charge - discharge cycle.
- Figure 3 shows these fluxes at the beginning of the charging process, when the pressurized NaX bed 1 is near 100 0 C and so has the minimum quantity of air adsorbed to it, while the unpressurized NaX bed 41 is largely saturated with water.
- Figure 4 shows how the fluxes are altered about halfway through the charging process, when the temperature of the pressurized NaX bed 1 has fallen to the prevailing ambient air temperature and the unpressurized NaX bed 41 is has lost most of its water.
- Figure 5 shows the fluxes at the beginning of the discharging process, when the pressurized NaX bed 1 is at -40 0 C and so has the maximum amount of air adsorbed to it, while the unpressurized NaX bed 41 is still hot and dry.
- Figure 6 shows how these fluxes are altered about halfway through the discharging process, when the temperature of the pressurized NaX bed 1 is approaching the ambient air temperature and water vapor is now being carried into the unpressurized NaX bed 41 to produce the heat needed for complete discharge.
- Figure 7 shows a more detailed view of an AE-CAES embodiment in the beginning of the process of being charged with energy (cf. Fig. 3), when the unpressurized NaX bed 41 of the adsorption heat pump is being heated to drive off the adsorbed water.
- Figure 8 shows the same embodiment following the halfway point of the discharging process (cf. Fig. 6), when water vapor is being passed through the unpressurized NaX bed 41 to generate the high temperatures needed for full discharge.
- Figure 9 shows a cutaway enlargement of a compressed air storage module, which contains cylinders 2 packed with zeolite pellets 1 , within the condensation / vaporization chamber 4 used to control the temperature.
- Figure 10 shows an enlargement of the adsorption heat pump 40 containing the zeolite bed 41 used to store the heat generated by the compression and adsorption of air, including the baffles 42 used to ensure that the atmospheric air, which carries water vapor out of it during charging, roughly reverses the flow of the air, which carries water vapor into it during discharging, for maximum efficiency.
- Figure 11 shows an enlargement of the mixer / ejector air turbine, including the components labeled 53, 54 and 55, used to efficiently convert both the energy stored as pressure and as heat back into mechanical energy during the discharging process.
- an AE-CAES embodiment utilizes a maximum temperature, attained when the device is fully discharged, of 100 0 C, which as just argued implies a duty cycle of at least 80% in an AE-CAES embodiment.
- the NaX is necessary to form the NaX into pellets that will allow air to flow readily through the zeolite beds used in the device, by means of a thermally conducting binder that will also enable rapid heat transfer through the beds.
- the heat of adsorption will be considerably smaller than the sensible heat needed to cool and reheat the NaX bed itself over the 140 0 C temperature swing.
- the specific heat capacity of the bed will vary with the how the pellets are prepared and to some extent with temperature, but is typically of order 1 KJ / (Kgr K), which together with the above assumptions concerning the pellets' packing density implies a volumetric heat capacity of about 1 MJ / (M 3 K). Multiplying this by 140 and converting to kilowatt-hours gives 38.9, which is about 50% larger than the energy to be stored and recovered per cubic meter.
- the NaX zeolite pellets 1 of an AE-CAES embodiment are packed into cylinders 2, with a perforated hollow tube 3 extending from a hole at the bottom of each cylinder all the way to the other end of the cylinder.
- This tube allows the compressed air (right-upwards slanted hatching in the diagrams) to pass rapidly from the vent at the bottom of the cylinder through its entire length when charging the AE-CAES device, and back out again when discharging it.
- the length of the cylinders is not critical, but their diameters should be small enough to allow the rapid diffusion of air from the holes in the tube 3 through the NaX bed 1 to the surface of the cylinder 2, as well as the rapid diffusion of the heat generated as the air is adsorbed.
- an AE- CAES embodiment uses cylinders similar to, but longer than, the aluminum cans in which beverages like Coca Cola ® are commonly packaged.
- Aluminum is more costly than steel, but is more easily formed into such cylinders, more corrosion resistant and has a higher thermal conductivity, although slightly thicker walls than those of typical aluminum cans will be needed in order to contain ten atmospheres of pressure.
- the diameter of the cylinders 2 in an embodiment will be 6.0 centimeters, while the perforated tubes 3 down their centers need be no more than 0.5 centimeters in inner diameter and are made from steel in order to provide structural support to the packed cylinders.
- the cylinders 2 in turn are contained in a chamber with thermally insulated walls 4 that can withstand modest pressures and be evacuated over the temperature swing of an AE-CAES embodiment.
- This chamber serves to contain a heat transfer fluid, which in turn is used to control the temperature of the compressed air and NaX bed 1 inside the cylinders 2 and so implement the temperature-swing cycle utilized.
- a heat transfer fluid which in turn is used to control the temperature of the compressed air and NaX bed 1 inside the cylinders 2 and so implement the temperature-swing cycle utilized.
- Neither the geometry of the chamber nor the way in which the cylinders 2 are arranged within it are critical, but for the sake of economy the packing should be as dense as possible while allowing the heat transfer fluid to flow freely around the cylinders.
- a temperature-control chamber 1.25 M in diameter is shown, which contains 108 cylinders each 1.0 M long and arranged on a square grid with its points 0.1 M apart, for a total of about 0.25 M 3 of NaX bed per chamber.
- One hundred sixty such chambers would be needed to store a megawatt-hour of energy.
- the fluid that carries heat to and from the chamber with walls 4 is methanol. This is a liquid at ambient pressures and -4O 0 C, the lowest temperature reached over the temperature-swing cycle, while it is a gas at ambient pressures and 100 0 C, the highest temperature reached. It also has a high heat of vaporization, averaging about 36 kJ / mole over this temperature range, and its exact boiling point can be set to any value between -40 and 100 0 C by controlling the pressure in the chamber with walls 4.
- the boiling point of methanol at a pressure of one atmosphere is 64.7 0 C, and if we assume that its heat of vaporization does not depend on pressure, we may use the Clausius-Clapyron equation to show that its boiling point will be 100°C at 3.6 atmospheres and -40 0 C at 231.5 Pascal (about 0.2% of an atmosphere).
- These modest temperatures and pressures allow the walls 4 of the chamber to be made out of an inexpensive fiberglass composite formed from a heat-resistant phenolic resin or epoxy, which will also provide some of the requisite thermal insulation.
- fluids besides methanol are utilized to transfer the heat, and / or other materials are used for the walls 4 of the chamber.
- liquid methanol (heavier left-downwards slanted hatching) is sucked from a hermetically sealed and thermally insulated tank 15 through the control valve 10 and sprayed at a programmed rate from nozzles 8 in the top of the chamber 4 with walls 4, as indicated in Fig. 7. A portion of this methanol vaporizes and exits the chamber through vents 9 interspersed with the nozzles while the remaining liquid methanol, now at its boiling point for the pressure in the chamber, flows down the sides of the cylinders 2 and boils off of them as it does so, thereby cooling them along with the NaX beds 1 which they contain.
- the additional methanol vapor (lighter left-downwards slanted hatching) generated by this process rises and exits the chamber through the vents 9 as before, while any liquid methanol that makes it to the bottom of the chamber flows into a drain 6 in the bottom and thence back to a small sealed holding tank 7 for reuse.
- valve 10 when discharging an AE-CAES embodiment, the valve 10 is closed, another control valve 11 opened, and the methanol in the storage tank 15 is heated by the passage of hot water (heavier diagonal cross-hatching in the diagrams) through a heat exchanger 16 inside the tank.
- the resulting methanol vapor exits the tank 15 through a vent 14 in its top and flows through a pipe that leads to a network of perforated tubes 5 at the bottom of the chamber with walls 4.
- the methanol vapor then rises and condenses on the surfaces of the cylinders 2, transferring its heat of vaporization to them at the temperature determined by the prevailing pressure in the chamber.
- the pressure in the chamber with walls 4 is reduced via a compressor 19 into which the methanol vapor flows from the vents 9 through the valve 18, as indicated in Fig. 7. It exits the compressor 19 at a high pressure and temperature, and flows into a heat exchanger 21 in a thermally insulated tank 20, where it is cooled by a stream of water at ambient pressure to a temperature of about 100 0 C.
- the methanol vapor then passes through the pressure-reducing valve 24, which allows it to expand .further cool and largely condense, and from there back through the open valve 17 to the storage tank 15 for reuse.
- the compressed methanol vapor should have a temperature well above that, say 150 0 C.
- an adiabatic index for methanol of 1.3 it follows that early in the charging process, when the methanol vapor enters the compressor 19 with a pressure of 3.6 atmospheres and a temperature of 100 0 C, it will only need to increase the pressure by a factor of about 1.7, or to 6.2 atmospheres. Late in the charging process, however, as the pressure and temperature in the chamber with walls 4 fall to 231.5 Pascal and to -40 0 C, respectively, it would need to increase the methanol vapor pressure by a factor of almost 13.3, resulting in a pressure that is still only 0.03 atmosphere.
- the air is cooled as it exits the each of the two compressors 26 and 28. This is done using the pump 39 to drive a stream of cool water through the countercurrent heat exchangers 27 and 29 in the exits of the compressors 26 and 28, respectively. In this way the heat of compression preheats the water, which in turn is directed through a pipe to the nozzle 22 where, during the first half of the charging process (see Fig. 3), it is boiled by the compressed methanol vapor, as previously described. Later in the charging process, i.e. once the theoretical coefficient of performance of the methanol heat pump has fallen below 3 or so, the compression ratio of the compressor 19 is lowed so that the methanol vapor is raised to at most 100 0 C.
- the high-grade heat contained in the steam exiting the tank 20 is used to prime an adsorption heat pump that uses NaX-water as its adsorbent-adsorbate pair.
- This open adsorption system is modeled after one recently demonstrated by Andreas Hauer in the Federal Republic of Germany, where it was used to reduce the cost of heating buildings by desorbing water from the NaX at night and using the re- adsorption of water vapor to upgrade waste heat during the day when the demand for heating is greater (see section 2 of chapter 25 by A. Hauer, pp. 409-27 in "Thermal Energy Storage for Sustainable Energy Consumption," NATO Sci. Ser. II: Math., Phys. and Chem., vol. 234, H. O.
- This open adsorption heat pump is simply a thermally insulated tank 40, constructed in an embodiment from a heat-resistant fiberglass composite as before, which is filled with NaX pellets 41 similar, but not necessarily identical in form, to those used to adsorb the air.
- an AE-CAES embodiment also utilizes the NaX zeolite for the second new use of adsorption in porous materials of the invention.
- porous materials such as silica gel
- the water-NaX adsorbate-adsorbent pair used here is chosen because, like the air-NaX pair, the adsorbate is inexpensive and environmentally benign, while the adsorbent is well understood, not prone to degradation with repeated use (when a suitable binder is used for the pellets; see G. Storch, G. Reichenauer, F. Scheffler and A.
- a further advantage of the water-NaX system lies in the fact that the differential heat of adsorption of water vapor to NaX increases from a value close of that of the heat of vaporation of water, or 44 KJ / mole, to about twice that value as the amount of water adsorbed to the NaX falls from 30 to 0% by weight. This means that in addition to providing a means of upgrading heat to higher temperatures, the NaX bed 41 of the heat pump will also store a significant amount of heat in latent (as well as sensible) form, even after deducting the heat needed to evaporate water during discharge.
- the amount of NaX needed for this adsorption heat pump is less than one fourth that which is required to adsorb the air itself.
- the steam from the tank 20 passes through vents 23 in its top to another compressor 31 , which raises the steam's pressure by a factor of 2.8 and, since the adiabatic index of water is also about 1.3, its temperature to about 200 0 C. It then passes via the open valve 32 to a heat exchanger 36, where the steam is cooled by a countercurrent stream of atmospheric air which is blown over the heat exchanger by the fan 37, heating the air to a temperature of about 150 0 C in the process.
- the Carnot limit on the coefficient of performance for this heat pump is 7.5, which should be comparable to the average coefficient of performance of the methanol compressor 19 over the first half of the charging process. It should be noted that the energy needed by the compressors 19 and 31 also winds up as stored heat, and may subsequently be recovered thereby making up for losses elsewhere in the system; the energy needed to run the fan 37 is not significant by comparison.
- the hot air from the heat exchanger 36 flows into the thermally insulated tank 40 and through the unpressurized bed of NaX zeolite pellets 41 , which initially have about 30% of their weight in water adsorbed to them (see Fig. 10).
- the hot air raises the temperature of the NaX pellets 41 , causing this water to desorb from them in the form of water vapor and cooling the air in the process.
- This water vapor is carried by the air through the NaX-pellet-packed container 40 and exits from its other end in the form of moist air at a temperature of about 40 0 C.
- the steam used to heat the air entering the NaX bed 41 exits from the heat exchanger 36 through the pressure-reducing valve 38, whereupon it also cools down well below the normal boiling point of water and largely condenses. Because no heat transfer is ever complete, this water still holds a portion of the heat it contained entering the heat exchanger. The energy contained in this sensible heat is stored by returning the water to the surface of the reservoir 43 from which it originated.
- the warm moist air exiting from the NaX bed 41 passes over a condenser 47 through which water is passed via the action of the pump 44.
- This water flows from the cool bottom of the reservoir 43 through the condenser 47 and back through the open valve 50 to the warm surface of the reservoir 43.
- the heat of condensation is thereby likewise transferred to the surface water of the reservoir.
- the need to use the heat of condensation for efficiency's sake has been stressed by A. Hauer (Joe. cit.), and the option to store it in a reservoir has also been claimed in a more recent patent (US 6,820,441).
- the condensed water itself collects in the basin 49, and may be discarded or added to the reservoir 43 once an AE-CAES embodiment is fully charged.
- warm water from the surface of the reservoir is directed through the heat exchanger 16 by closing the valve 50 and opening the valve 51.
- the fan 37 is used to blow ambient air through the NaX bed 41 of the adsorption heat pump, where it picks up sensible heat from the bed but not much of the latent heat because it does not contain much moisture to re- adsorb. Some of this heat will be transferred to the water flowing through the heat exchanger 47 at the exit, whence it continues to the heat exchanger 16, but most of the heat will be carried along with the air into the exit chamber 48 at a still elevated temperature.
- This warm air is directed via the duct 52 to an air turbine, which includes components 53, 54 and 55, by rearranging the baffling in the exit chamber 48, as indicated schematically in Figs. 7 and 8. It will be used there to keep the expanding compressed air from cooling, as will be described presently.
- the warm water flowing through the heat exchanger 16 boils the methanol in the storage tank 15, which is initially under a pressure of a fraction of an atmosphere.
- the resulting methanol vapor is then used to heat the cylinders 2 containing the NaX pellet beds 1 to which air is adsorbed, as previously described.
- This compressed air is also directed as it is generated by desorption through the now- open valve 56 to the air turbine with components 53, 54 and 55, as shown in Fig. 8.
- the mass and energy fluxes during this first half of the discharging process are illustrated in Fig. 5.
- valve 45 is opened to let warm water from the surface of the reservoir 43 pass through a vaporizer 46, which dispenses it as a mist over the heat exchanger 36.
- warm water from the reservoir 43 is driven by the pump 39 through the heat exchanger 36 via the open valve 34, and prevented from getting to the air compressors 26 and 28 by closing valves 32, 33 and 35, so as to keep the evaporating water from cooling the air around it.
- the efficiency of the AE-CAES embodiment is also improved by passing the air during discharge through the unpressurized NaX pellet bed 41 in approximately the reverse of the direction in which hot air was passed through it in order to desorb moisture from the unpressurized NaX bed during charging. This increases the efficiency because otherwise some of the sensible heat picked up by the air entering the bed during the first half of the discharge process, or generated by the adsorption of moisture from the air during the second half, will be lost to the cooler and / or less dry NaX bed before it reaches the far end.
- baffles 42 depicted by heavy solid lines in the drawings, which are arranged so that during charging the air enters the near end through the center of the bed but exits the far end around the periphery, and then rearranged during discharging so that the air enters the periphery on the near end but exits through the center on the far end, as indicated schematically in Figs. 7 and 8 (see also Fig. 10).
- the far end includes a second fan, enabling the air to take exactly the opposite path back through the NaX bed 41 while the roles of the heat exchangers 36 and 47 are swapped while discharging the device.
- This air turbine which includes the components labeled 53, 54 and 55 in Figs. 7 and 8, is designed so that the stream of compressed air entering it expands and accelerates through a venturi with twisted vanes running in parallel along its length (see Fig 11). This creates a vortex which generates a vacuum behind it, which in turn draws the warm air from the duct 52 through a larger-in-diameter annulus of static blades 54 slightly up-wind of the blades 53.
- This second vortex of warm air merges with the vortex of cold expanding air from the blades 53 and is rapidly and thoroughly mixed with it by this process.
- the principles behind this turbine are in fact similar to those of the mixer-ejector wind turbine designs recently disclosed in USPTO Pub. No. 2008/023957 A1 , from which we have drawn inspiration.
- the now rapidly moving air vortex hits the blades of the air turbine rotor 55 and thereby converts the energy stored in the compressed air and a portion of the energy stored as heat into mechanical form for external use.
- many other devices are available, such as reciprocating air motors, by which heat and compressed air may be converted into mechanical energy in various alternative embodiments, although these will generally not be as efficient as the mixer-ejector air turbine just described.
- the compressed air must be released at flow rate of about 700 M 3 per hour, measured at ambient temperature and pressure.
- the actual temperature of the compressed air will start out at -40 0 C and gradually rise to near 100 0 C over the six hour period, and air at -40 0 C is 1.6 times more dense than air at 100 0 C at any given pressure. It follows that the air at ten atmospheres must be released at a rate of 54 M 3 per hour at the beginning of discharge period and 86 M 3 per hour at the end.
- this air would cool as it expands to -152 0 C at the beginning and -80 0 C at the end of the discharge period, which in turn would reduce the flow due to the release of compressed air to 283 and 454 M 3 per hour respectively.
- it To return air at those temperatures to ambient temperatures, it must be mixed with about 8.87 and 5.25 times the same mass of air at a temperature of 45°C, the approximate temperature of the air entering the air turbine through the duct 52.
- the required flow rate of 45 0 C air through the duct thus varies from 6628 to 3920 M 3 per hour over the six hour discharge period.
- the resulting air will enter the duct 52 at a temperature somewhat below the 45°C assumed above, but its flow rate into the turbine will also be greater than the 6628 M 3 per hour found above at 45°C.
- the pump 44 is slowed so that by the end of the discharge period the temperature of the water exiting the heat exchanger 47 approaches that of the air passing over it, or 100 0 C.
- the rate of humidified air flow through the NaX pellet bed 41 is gradually slowed, so that near the end of the discharging process the temperature of the air entering the turbine through the duct 52 will be somewhat larger than 45°C while its flow rate will also be less than the 3920 M 3 per hour estimated above at 45°C.
- the pressure in the chamber with walls 4 and the rate at which methanol enters it during charging and discharging must be regulated so that compressed air is converted to and from adsorbed air at the same rate that it is produced by the compressors 26 and 28 or fed to the turbine including the components labeled 53, 54 and 55, respectively, thereby keeping the pressure of the gaseous air in the cylinders 2 approximately constant throughout.
- This task although not trivial, is nevertheless a perfectly standard systems integration problem in chemical process engineering that can be accomplished by one skilled in that art.
- an AE-CAES device and/or a temperature-swing CAES device, could also employ a variety of other established chemical processes without materially deviating from the intent of the inventors.
- the water-NaX heat pump 40 and 41 of an embodiment could be based on other adsorbate-adsorbent pairs, the absorption of a gas in a liquid medium, or even be replaced by a wide variety of solid-liquid phase-change materials, which can also store heat in latent form. It is further possible to supplement or replace the heat storage subsystem entirely by waste heat recovery or thermal energy harvesting in a variety of ways.
- an AE-CAES device were located at a power plant that produces heat as a by-product, such as a coal or nuclear power plant, then this heat could be used to reheat the expanding air and/or the adsorbent for air.
- a passive solar thermal collector could also readily generate the modest temperatures needed when discharging an AE-CAES device, installed for example at a wind turbine farm. The main point is that the heat utilized by any component of an AE-CAES device during discharge need not have been produced by the inverse process while charging it.
Abstract
Description
Claims
Priority Applications (10)
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JP2010550706A JP2011518270A (en) | 2008-03-14 | 2009-03-16 | Adsorption enhanced compressed air energy storage |
EP09721173.4A EP2262993A4 (en) | 2008-03-14 | 2009-03-16 | Adsorption-enhanced compressed air energy storage |
CA2716776A CA2716776A1 (en) | 2008-03-14 | 2009-03-16 | Adsorption-enhanced compressed air energy storage |
CN2009801073524A CN101970833A (en) | 2008-03-14 | 2009-03-16 | Adsorption-enhanced compressed air energy storage |
AU2009223725A AU2009223725A1 (en) | 2008-03-14 | 2009-03-16 | Adsorption-enhanced compressed air energy storage |
BRPI0909360A BRPI0909360A2 (en) | 2008-03-14 | 2009-03-16 | advanced adsorption of compressed air energy storage |
GB1015869A GB2470337A (en) | 2008-03-14 | 2009-03-16 | Adsorption-enchanced compressed air energy storage |
US12/854,969 US8136354B2 (en) | 2008-03-14 | 2010-08-12 | Adsorption-enhanced compressed air energy storage |
IL207938A IL207938A0 (en) | 2008-03-14 | 2010-09-02 | Adsorption - enhanced compressed air energy storage |
US13/422,465 US8621857B2 (en) | 2008-03-14 | 2012-03-16 | Adsorption-enhanced compressed air energy storage |
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Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8037679B2 (en) | 2009-06-29 | 2011-10-18 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
US8061132B2 (en) | 2009-06-29 | 2011-11-22 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
EP2435679A2 (en) * | 2009-05-27 | 2012-04-04 | Energy Compression LLC | Adsorption-enhanced compressed air energy storage |
US8247915B2 (en) | 2010-03-24 | 2012-08-21 | Lightsail Energy, Inc. | Energy storage system utilizing compressed gas |
US8436489B2 (en) | 2009-06-29 | 2013-05-07 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
US8621857B2 (en) | 2008-03-14 | 2014-01-07 | Energy Compression Inc. | Adsorption-enhanced compressed air energy storage |
US10830504B2 (en) | 2012-04-26 | 2020-11-10 | Lawrence Livermore National Security, Llc | Adsorption cooling system using metal organic frameworks |
US10994258B2 (en) | 2012-04-26 | 2021-05-04 | Lawrence Livermore National Security, Llc | Adsorption cooling system using metal organic frameworks |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011088380A1 (en) | 2011-12-13 | 2013-06-13 | Siemens Aktiengesellschaft | Energy storage device with open charging circuit for storing seasonal excess electrical energy |
US20140369857A1 (en) * | 2012-01-25 | 2014-12-18 | General Compression, Inc. | Device for improved heat transfer within a compression and/or expansion system |
JP6857075B2 (en) * | 2017-04-19 | 2021-04-14 | 株式会社神戸製鋼所 | Compressed air storage power generation device and compressed air storage power generation method |
CN108644607A (en) * | 2018-04-02 | 2018-10-12 | 全球能源互联网研究院有限公司 | A kind of cryogenic liquefying air energy storage systems and method |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4027993A (en) * | 1973-10-01 | 1977-06-07 | Polaroid Corporation | Method and apparatus for compressing vaporous or gaseous fluids isothermally |
US4767938A (en) * | 1980-12-18 | 1988-08-30 | Bervig Dale R | Fluid dynamic energy producing device |
US4392062A (en) * | 1980-12-18 | 1983-07-05 | Bervig Dale R | Fluid dynamic energy producing device |
JPH02119638A (en) * | 1988-10-28 | 1990-05-07 | Takenaka Komuten Co Ltd | Energy storage system using compressed air |
JPH02188628A (en) * | 1989-01-12 | 1990-07-24 | Sumitomo Rubber Ind Ltd | Compressed air storage device |
JPH03258925A (en) * | 1989-11-20 | 1991-11-19 | Nkk Corp | Compressed air storage tank in compressed air storage power generating system |
JPH07119485A (en) * | 1993-10-22 | 1995-05-09 | Central Res Inst Of Electric Power Ind | Compressed air storage generating system |
DE19511215A1 (en) * | 1995-03-27 | 1996-10-02 | Ppv Verwaltungs Ag | Heat engine working according to the Stirling principle |
KR100544381B1 (en) * | 2003-11-13 | 2006-01-23 | 김기선 | Noise reducing structure of storage tank for an air compressor |
-
2009
- 2009-03-16 CA CA2716776A patent/CA2716776A1/en not_active Abandoned
- 2009-03-16 CN CN2009801073524A patent/CN101970833A/en active Pending
- 2009-03-16 GB GB1015869A patent/GB2470337A/en not_active Withdrawn
- 2009-03-16 WO PCT/US2009/001655 patent/WO2009114205A2/en active Application Filing
- 2009-03-16 RU RU2010139758/06A patent/RU2010139758A/en not_active Application Discontinuation
- 2009-03-16 EP EP09721173.4A patent/EP2262993A4/en not_active Withdrawn
- 2009-03-16 AU AU2009223725A patent/AU2009223725A1/en not_active Abandoned
- 2009-03-16 JP JP2010550706A patent/JP2011518270A/en active Pending
- 2009-03-16 BR BRPI0909360A patent/BRPI0909360A2/en not_active IP Right Cessation
-
2010
- 2010-09-02 IL IL207938A patent/IL207938A0/en unknown
Non-Patent Citations (1)
Title |
---|
See references of EP2262993A4 * |
Cited By (24)
Publication number | Priority date | Publication date | Assignee | Title |
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US8353156B2 (en) | 2009-06-29 | 2013-01-15 | Lightsail Energy Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
US8436489B2 (en) | 2009-06-29 | 2013-05-07 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
US8061132B2 (en) | 2009-06-29 | 2011-11-22 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
US8037677B2 (en) | 2009-06-29 | 2011-10-18 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
US8247915B2 (en) | 2010-03-24 | 2012-08-21 | Lightsail Energy, Inc. | Energy storage system utilizing compressed gas |
US10830504B2 (en) | 2012-04-26 | 2020-11-10 | Lawrence Livermore National Security, Llc | Adsorption cooling system using metal organic frameworks |
US10994258B2 (en) | 2012-04-26 | 2021-05-04 | Lawrence Livermore National Security, Llc | Adsorption cooling system using metal organic frameworks |
US11786883B2 (en) | 2012-04-26 | 2023-10-17 | Lawrence Livermore National Security, Llc | Adsorption cooling system using metal organic frameworks |
Also Published As
Publication number | Publication date |
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IL207938A0 (en) | 2010-12-30 |
CA2716776A1 (en) | 2009-09-17 |
EP2262993A2 (en) | 2010-12-22 |
GB201015869D0 (en) | 2010-10-27 |
BRPI0909360A2 (en) | 2015-09-29 |
GB2470337A (en) | 2010-11-17 |
RU2010139758A (en) | 2012-04-20 |
AU2009223725A1 (en) | 2009-09-17 |
EP2262993A4 (en) | 2013-12-18 |
WO2009114205A3 (en) | 2010-02-04 |
CN101970833A (en) | 2011-02-09 |
JP2011518270A (en) | 2011-06-23 |
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