[go: up one dir, main page]

WO2014123537A1 - Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation - Google Patents

Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation Download PDF

Info

Publication number
WO2014123537A1
WO2014123537A1 PCT/US2013/025400 US2013025400W WO2014123537A1 WO 2014123537 A1 WO2014123537 A1 WO 2014123537A1 US 2013025400 W US2013025400 W US 2013025400W WO 2014123537 A1 WO2014123537 A1 WO 2014123537A1
Authority
WO
WIPO (PCT)
Prior art keywords
solar
steam
segment
transfer fluid
heat transfer
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.)
Ceased
Application number
PCT/US2013/025400
Other languages
English (en)
Inventor
Randall C. Gee
David White
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.)
SkyFuel Inc
Original Assignee
SkyFuel Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SkyFuel Inc filed Critical SkyFuel Inc
Priority to PCT/US2013/025400 priority Critical patent/WO2014123537A1/fr
Publication of WO2014123537A1 publication Critical patent/WO2014123537A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/06—Devices for producing mechanical power from solar energy with solar energy concentrating means
    • F03G6/065—Devices for producing mechanical power from solar energy with solar energy concentrating means having a Rankine cycle
    • F03G6/067—Binary cycle plants where the fluid from the solar collector heats the working fluid via a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/071—Devices for producing mechanical power from solar energy with energy storage devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/098—Components, parts or details
    • F03G6/108—Components, parts or details of the heat transfer system
    • F03G6/111—Heat transfer fluids
    • F03G6/114—Molten salts
    • 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
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines

Definitions

  • This invention is in the field of solar/gas hybrid power systems, and relates to system configurations and methods of operation designed to optimize the solar- generated fraction of power produced by the hybrid systems.
  • Solar/gas hybrid power systems use both solar energy and energy liberated by the combustion of natural gas to generate electricity.
  • solar/gas hybrid systems offer a practical and efficient approach to deploying solar energy in power generation markets.
  • solar/gas hybrid plants have previously either used natural gas with poor efficiency or required that the amount of solar energy be relatively small (e.g., under 1 5%) compared to the natural gas contribution.
  • HTF heat transfer fluid
  • auxiliary boiler combusts natural gas to heat the HTF to a temperature ranging from 350 5 C to 390 5 C, which is then used to make superheated steam that drives a steam turbine to generate electricity.
  • This system uses natural gas less efficiently than it could be used in a modern standalone combined cycle plant.
  • the exhaust heat from a 40 MW gas turbine is used to heat the HTF to 395 °C, matching the solar field exit temperature.
  • the gas turbine exhaust heats the HTF to the same temperature as the solar field, so "looks" like additional solar collectors to the steam/power generation equipment.
  • the solar fraction of the proposed system (illustrated in FIG. 2) is reported to be 57% with a high gas usage efficiency that rivals a combined cycle plant.
  • This type of hybrid system also has a lower installed cost than a comparable solar-only plant, and results in a higher conversion efficiency of solar energy to electricity.
  • it requires either off-design lower-performance operation of the gas turbine or operation of the gas turbine at full output and dumping/wasting some thermal energy when the solar plus waste heat total exceeds the steam turbine capacity.
  • TES thermal energy storage
  • Fig. 3 shows a typical concentrated solar power (CSP) system configuration incorporating indirect two-tank TES.
  • CSP concentrated solar power
  • HX heat exchanger
  • the supply temperature to the steam generator can be 15 °C to 20 °C below the solar field outlet temperature. This large temperature drop results in part load operation (e.g. 90%) of the steam turbine whenever storage is discharged.
  • Turchi, C.S. and Ma, Z. "Gas Turbine/Solar Parabolic Trough Hybrid Design Using Molten Salt Heat Transfer Fluid", NREL, SolarPACES 201 1 , September 20-23, 201 1 ; Turchi, C; Mehos, M.; Ho, C.K.; and Kolb, G.J., "Current and Future Costs for Parabolic Trough and Power Tower Systems in the US Market", NREL, SolarPACES 2010, September 21 -24, 201 0; Turchi, C.S. ; Ma, Z. and Erbes, M.
  • the present invention provides solar/gas hybrid concentrating solar power (CSP) systems that use both natural gas and concentrated solar thermal energy to provide electricity.
  • the solar/gas hybrid configurations described herein comprise three segments: a solar segment, a thermal storage segment, and a water/steam segment that incorporates waste heat from a gas turbine. Each of these segments is physically isolated from the other segments.
  • the hybrid CSP systems are highly efficient due, at least in part, to a solar segment comprising a first heat transfer fluid and a thermal segment comprising a second heat transfer fluid.
  • the second heat transfer fluid heat exchanges with a steam segment to produce steam that drives a steam turbine.
  • the solar and thermal segments perform the "heavy lifting" of producing steam from water. Once the steam is produced, it enters a superheater of the steam segment.
  • the superheater which does not heat exchange directly with the thermal storage segment, is heated by a gas turbine positioned downstream from the thermal storage segment.
  • a gas turbine/solar trough hybrid configuration (illustrated in FIG. 5) is described herein that incorporates thermal energy storage (TES) in which the solar heat is used for steam generation and exhaust heat from a gas turbine is used to superheat the solar-generated steam.
  • TES thermal energy storage
  • This solar/gas hybrid system is designed to keep the operation of both turbines (the gas turbine and the steam turbine) at, or very near, their design points, which maximizes efficiencies and also uses the exhaust heat from the gas turbine to superheat the steam in order to maximize the cycle efficiency of the steam turbine.
  • the TES provides a thermal energy "buffer". Energy from a storage tank is withdrawn only when it is capable of producing sufficient steam to operate the steam turbine at (or near) its design point.
  • the gas turbine runs at its design capacity whenever energy is being withdrawn from storage (e.g., two-tank storage or thermocline TES). Just one or two hours of TES is sufficient to maintain operation at the design points of the two turbines, and also eliminates dumped/wasted energy. Without TES, energy must be dumped/wasted at times when the solar segment is producing more energy than the steam turbine can accept. TES provides a place for the excess solar heat to be stored, so the excess heat is not wasted.
  • storage e.g., two-tank storage or thermocline TES.
  • heat from the solar troughs is stored within a thermal storage segment so that when heat is withdrawn from the thermal storage segment it can generate steam within the water/steam segment.
  • Exhaust heat from the gas turbine superheats the solar-generated steam.
  • the use of gas turbine exhaust for superheat increases the cycle efficiency of the steam turbine. With saturated steam provided by the solar segment, and superheat provided by the gas turbine exhaust, the turbine inlet temperature can be increased above the solar field exit temperature. With the 450 °C exhaust temperature of a typical gas turbine, the steam turbine cycle efficiency can be increased from about 37% to at least 39%. This improves the solar-to-electricity conversion, and also the conversion efficiency of the exhaust heat from the gas turbine to electricity.
  • the molten salt supply temperature to the steam boiler is
  • the solar/gas hybrid system design described herein provides dispatchable power in a thermally efficient way and consumes natural gas more effectively than prior solar/gas hybrids when operating at a high solar fraction.
  • the steam turbine and gas turbine both operate at their design output levels, and the use of a gas turbine for steam superheating increases conversion efficiencies.
  • the solar/gas hybrid system described herein allows operation at full capacity during early evening (on-peak) hours, and use of TES eliminates any dumped energy from the solar field.
  • the solar-to-molten salt heat exchanger temperature drop penalty is only incurred once, and the solar/gas hybrid power system allows for high solar fractions.
  • Temperatures, pressures, and flow rates, as well as gas turbine selections, solar multiples, and TES sizes may be varied and/or optimized according to the needs of a particular system. There are also some modifications to the system configuration that are available, such as adding the capability of heating the hot tank and/or feedwater with gas turbine exhaust.
  • the solar contribution provides the dominant portion of the energy (i.e., greater than 50% of the electricity produced by the system is provided by solar energy).
  • the amount of thermal energy required to produce saturated steam i.e., the heat of vaporization
  • the heat of vaporization is in general significantly larger than the amount of thermal energy required to superheat the saturated steam for efficient use in a steam turbine.
  • the heat of vaporization is 1 1 70 Btu per pound
  • superheating the saturated steam another 100 5 C e.g., 313 5 C to 413 5 C
  • solar/gas hybrid power systems disclosed herein may have high solar contributions and small natural gas contributions.
  • the solar contribution will generally be above 60%, in some embodiments above 65%, in some embodiments above 70%, in some embodiments above 75%, and in some embodiments above 80%.
  • a hybrid concentrated solar power (CSP) system comprises a solar segment comprising at least one solar reflector optically coupled to a first conduit for a first heat transfer fluid; a thermal storage segment configured to store solar heat energy produced by the solar segment; wherein the thermal storage segment comprises a second conduit for a second heat transfer fluid; a steam segment configured to receive the solar heat energy stored by the thermal storage segment and to generate electric power when steam from the steam segment operates a steam turbine; and a gas turbine configured to generate electric power and to exhaust heat to a superheater of the steam segment, wherein the superheater does not heat exchange directly with the thermal storage segment.
  • CSP concentrated solar power
  • a solar segment is a concentrating solar array, or a concentrating solar reflector, or one or more parabolic concentrating solar devices.
  • the fluids of the solar segment, thermal storage segment and/or steam segment of the hybrid CSP system are thermally coupled (e.g., by way of a heat exchanger) but physically isolated from one another.
  • the first heat transfer fluid and the second heat transfer fluid are generally in thermal contact and physically isolated from one another
  • the second heat transfer fluid and the steam are generally in thermal contact and physically isolated from one another.
  • Thermal contact may be provided, in some embodiments, by a heat exchanger configured to transfer energy between the physically isolated segments of the hybrid CSP system.
  • a heat exchanger may be configured to transfer solar heat energy between the solar segment and the thermal storage segment, or to transfer energy stored in the thermal storage segment to the steam segment.
  • first and second heat transfer fluids having appropriate freezing points, boiling points, heat capacity, viscosity, corrosivity, cost, stability, and availability are important to the operation of the hybrid CSP systems.
  • the first heat transfer fluid has a different composition than the second heat transfer fluid.
  • the first heat transfer fluid is selected from the group consisting of water, molten salt, Therminol® VP-1 , oils, and combinations thereof.
  • the molten salt HTF may be a salt or salt blend selected from the group consisting of NaCI, KCI, NaN0 3 , KN0 3 , CaCI 2 , Ca(N0 3 )2 and combinations thereof.
  • the molten salt HTF may be a ternary blend, such as a blend of approximately 7% NaN0 3 , 45% KN0 3 and 48% Ca(N0 3 ) 2 with a melting point near 1 20 5 C.
  • the second heat transfer fluid is selected from the group consisting of molten salt, Therminol® VP-1 , oils, and combinations thereof.
  • the molten salt HTF may be a salt or salt blend selected from the group consisting of NaCI, KCI, NaN0 3 , KN0 3 , CaCI 2 , Ca(N0 3 ) 2 and combinations thereof.
  • the molten salt HTF may be a ternary blend, such as a blend of approximately 7% NaN0 3 , 45% KN0 3 and 48% Ca(N0 3 ) 2 with a melting point near 120 5 C.
  • Therminol® VP-1 is a synthetic vapor phase/liquid phase heat transfer fluid with a vapor phase operating temperature range of 257 5 C to 400 5 C, and a liquid phase operating temperature range of 12 5 C to 400 5 C.
  • Therminol® VP-1 is a eutectic mixture of 73.5% diphenyl oxide and 26.5% biphenyl. It can be used as a liquid heat transfer fluid or as a boiling-condensing heat transfer fluid up to its maximum use temperature, and it is miscible with other similarly constituted diphenyl- oxide/biphenyl fluids.
  • the properties of VP-1 are further described in the product literature, available at www.therminol.com/pages/products/vp-1 .asp, accessed 10/16/201 2, which is expressly incorporated by reference herein.
  • Molten salt is a non-toxic, readily available material that retains thermal energy effectively over time and can operate at temperatures greater than 550 5 C, which matches well with the most efficient steam turbines. For comparison, oil has a maximum temperature of about 400 5 C. Molten salt also costs a fraction (e.g., 1 /10 th ) of what traditional HTFs, such as synthetic oils, cost. However, oil is preferred as the HTF for use in a parabolic trough solar collection field because molten salt has a high freezing point, and energy is required to prevent it from freezing at night. (T.
  • the maximum temperature of the first heat transfer fluid is less than 450 °C, or less than 425 °C, or less than 400 °C, or less than 385 °C.
  • the maximum temperature of the first heat transfer fluid may be selected from the range of 350 °C to 450 °C, or selected from the range of 385 °C to 425 °C.
  • the maximum temperature of the second heat transfer fluid is less than 565 °C, or less than 525 °C, or less than 500 °C, or less than 475 °C, or less than 442 °C, or less than 425 °C.
  • the temperature of the second heat transfer fluid may be selected from the range of 400 °C to 565 °C, or selected from the range of 425 °C to 550 °C, or selected from the range of 425 °C to 500 °C.
  • a difference in temperature between the first heat transfer fluid as it exits the solar reflector and the second heat transfer fluid is selected from the range of 8 °C to 40 °C, or selected from the range of 10 °C to 30 °C, or selected from the range of 12 °C to 25 ⁇ ⁇ .
  • a difference in temperature between the second heat transfer fluid and the steam prior to superheating by the exhaust heat of the gas turbine is greater than or equal to 10°C.
  • the pressure of superheated steam entering the steam turbine is greater than 650 psia (45 bar), or greater than 800 psia, or greater than 1000 psia, or greater than 1250 psia, or greater than 1500 psia.
  • the pressure of the steam may be selected from the range of 650 psia to 1 600 psia, or selected from the range of 800 psia to 1500 psia, or selected from the range of 1000 psia to 1 250 psia.
  • cycle efficiency of a steam turbine is increased about 5% when the steam turbine is operated at a temperature of 425 °C compared to operating the steam turbine at 375°C.
  • the solar reflector is a linear parabolic reflector.
  • the thermal storage segment comprises at least one storage tank for storing the second heat transfer fluid, and in an embodiment, the storage tank may be in a direct configuration with the second conduit. In most embodiments, the second conduit is cyclical such that it forms a continuous circuit.
  • the storage tank is a single-tank thermocline energy storage subsystem.
  • the storage tank is selected from the group consisting of a hot tank and a cold tank; typically both a hot tank and a cold tank are present.
  • a hot tank may have a size capable of holding sufficient thermal energy to operate the steam turbine for at least 30 minutes, or at least 60 minutes, or at least 120 minutes, or at least 180 minutes.
  • the steam segment of the present hybrid CSP systems comprises a superheater for receiving exhaust heat directly from a gas turbine.
  • the superheater is directly thermally coupled with the gas turbine, but not with the thermal storage segment.
  • the steam segment receives solar heat energy stored by the thermal storage segment through a steam generator or through a steam generator and a solar preheater.
  • the steam segment further comprises a condenser for recycling the steam as it exits the steam turbine.
  • Water exiting the condenser is heated by a feedwater heater, and the feedwater heater may be heated by a source selected from the group consisting of exhaust heat from said gas turbine, said solar heat energy from said solar segment, said solar heat energy from said thermal storage segment and combinations of these.
  • the gas turbine of the present hybrid CSP systems may, in some embodiments, be an aeroderivative gas turbine.
  • the gas turbine is, in most embodiments, configured to exhaust heat to a superheater of the steam segment.
  • the thermal storage segment of the hybrid CSP system is upstream from the gas turbine.
  • the gas turbine may, in some embodiments, be additionally configured to exhaust heat to a storage tank.
  • a hybrid CSP system may comprise a second gas turbine configured to exhaust heat to the thermal storage segment.
  • exhaust gas from the natural gas turbine has a temperature selected over the range of 350 5 C to 650 5 C, in some embodiments selected over the range of 400 5 C to 650 5 C, and in some embodiments selected over the range of 460 5 C to 600 5 C.
  • the average fraction of energy produced by solar gain is at least 50%, or at least 60%, or at least 70%, or at least 80%, or at least 85%, or at least 90%.
  • the average fraction of energy produced by solar gain may be selected from the range of 50% to 90%, or selected from the range of 60% to 90%, or selected from the range of 70% to 90%, or selected from the range of 80% to 90%.
  • a hybrid CSP power system of the present invention has an electricity production capacity selected from the range of 5 MW to 250 MW, or selected from the range of 25 MW to 150 MW, or selected from the range of 50 MW to 100 MW.
  • a hybrid CSP power system includes a gas turbine and a steam turbine, where a ratio of the capacity of the gas turbine to the capacity of the steam turbine is between 1 :1 0 and 3:10.
  • the capacity of the gas turbine is less than the capacity of the steam turbine.
  • the capacity of the gas turbine may be at least three times less than the capacity of the steam turbine, in some embodiments, at least five times less than the capacity of the steam turbine, and in some embodiments, at least ten times less than the capacity of the steam turbine.
  • a method for producing electricity from a hybrid CSP system comprises the steps of: collecting solar heat energy using a solar segment comprising at least one solar reflector optically coupled to a first conduit for a first heat transfer fluid; thermally coupling the solar segment to a thermal storage segment configured to store the solar heat energy produced by the solar segment; wherein the thermal storage segment comprises a second conduit for a second heat transfer fluid; transferring the solar heat energy stored in the thermal storage segment to a steam segment configured to receive the solar heat energy; generating electric power using steam from the steam segment to operate a steam turbine; and generating electric power from a gas turbine to supplement the electric power produced by the steam turbine, wherein the gas turbine is configured to exhaust heat to the steam segment.
  • the step of thermally coupling comprises exchanging heat between the first heat transfer fluid and second heat transfer fluid.
  • FIG. 1 provides a schematic of a prior art CSP system that uses an auxiliary boiler to combust natural gas and warm a heat transfer fluid (HTF) within the solar field when sunlight is not available in the desired amount.
  • HTF heat transfer fluid
  • Figure 2 provides a schematic of a prior art solar/gas hybrid system in which exhaust heat from a gas turbine directly heats the solar field HTF.
  • FIG. 3 provides a schematic of a prior art non-hybrid concentrated solar power (CSP) system configuration incorporating indirect two-tank TES.
  • CSP non-hybrid concentrated solar power
  • Figure 4 provides a schematic of a prior art solar/gas hybrid system, often referred to as an Integrated Solar Combined Cycle (ISCC) system.
  • ISCC Integrated Solar Combined Cycle
  • Figure 5 provides a schematic of a solar/gas hybrid power system with a solar segment, a thermal storage segment, and a water/steam segment that incorporates the waste heat from a gas turbine, according to an exemplary embodiment.
  • a “concentrated solar power (CSP)” system uses mirrors, lenses or reflectors to concentrate or focus sunlight onto a small area.
  • the focused solar energy is converted to heat, which is used to produce steam that drives a steam turbine, to produce electricity.
  • a “hybrid CSP system”, as used herein, is a CSP system that integrates at least two sources of energy, solar energy and at least a secondary energy source that is a non-solar energy source.
  • the secondary energy source may not directly produce electricity (e.g., the secondary energy source may heat a HTF that provides thermal energy for electricity production).
  • the secondary energy source may directly produce electricity.
  • the secondary energy source may fuel an electricity-producing component, such as a gas turbine.
  • the hybrid CSP system may be a
  • Rankine-Brayton system particularly, a natural gas/solar system.
  • a “component” is used broadly to refer to an individual part of a system.
  • a gas turbine, a parabolic trough or a solar segment may be a component of a hybrid CSP system.
  • a "maximum temperature" of a heat transfer fluid is an operating
  • the maximum temperature may be the operating temperature achieved at the highest electricity production capacity of the system, or the maximum temperature may be an optimal operating temperature for a
  • a maximum temperature is a temperature that the system does not exceed during operation, for example, to preserve the mechanical integrity of the system and to ensure safety.
  • a maximum temperature of a heat transfer fluid is a temperature below a phase transition temperature of the heat transfer fluid, e.g., below a boiling point of the heat transfer fluid.
  • Hybrid CSP systems and methods of making and using the systems will now be described with reference to the figures. For clarity, multiple items within a figure may not be labeled and the figures may not be drawn to scale.
  • FIG. 1 provides a schematic of a prior art concentrated solar power (CSP) system that uses an auxiliary boiler to combust natural gas to warm a heat transfer fluid (HTF) within the solar collector field when sunlight is not available in the desired amount.
  • the system contains a solar segment and a steam segment, but there is no thermal storage capacity in the configuration of Figure 1 .
  • the HTF of the solar segment a synthetic oil (VP-1 ), circulates from a series of parabolic troughs toward a heat exchanger coupled to a superheater of the steam segment, which contains a steam turbine for generating electricity.
  • VP-1 synthetic oil
  • FIG. 2 provides a schematic of a prior art solar/gas hybrid system in which exhaust heat from a gas turbine directly heats the solar field HTF.
  • the system contains a solar segment and a steam segment, but no thermal storage capacity.
  • a synthetic oil HTF (VP-1 ) circulates through a series of parabolic troughs then through a gas/HTF heat exchanger that receives exhaust heat from a natural gas turbine that generates electricity.
  • the HTF then heat exchanges with a superheater, steam generator and preheater of the steam segment.
  • Steam from the superheater drives a steam turbine that produces electricity.
  • Steam exiting the turbine enters a condenser/cooling tower where it is converted to water which cycles or is pumped to a feedwater heater.
  • the feedwater heater is heated by exhaust from the gas/HTF heat exchanger.
  • the water from the feedwater heater is fed to the preheater, steam generator and superheater in a countercyclical direction relative to the flow of the HTF
  • FIG 3 provides a schematic of a prior art non-hybrid concentrated solar power (CSP) system incorporating indirect two-tank TES.
  • a synthetic oil HTF e.g., VP-1
  • the thermal storage segment includes a hot tank and a cold tank for storing a molten salt HTF.
  • the hot and cold tanks are positioned at opposite ends of a non-cyclical conduit (i.e., they are not in a conduit loop).
  • the thermal storage segment is "charged” when the molten salt HTF is transferred from the cold tank to the hot tank through an oil-to-salt heat exchanger that is warmed by the oil HTF from the parabolic troughs.
  • the thermal storage segment is "discharged” by transferring molten salt HTF from the hot tank to the cold tank, thereby reheating the oil HTF, which is transferred to the steam segment.
  • the molten salt HTF of the thermal storage segment need not be in motion for heat to be transferred to the steam segment.
  • the HTF may be held in the hot tank until it is needed.
  • the molten salt HTF stored in the hot tank is needed (e.g., during nighttime hours) to warm the oil HTF that is heat exchanging with steam in the steam segment
  • the molten salt HTF is pumped out of the hot tank to the cold tank through the oil-to-salt heat exchanger.
  • the oil HTF is heated by this "discharge" process, and pumped toward the superheater of the steam segment.
  • the HTFs are heat exchanged twice (once during charging and once during discharging) in the indirect two-tank TES configuration.
  • Steam within the steam segment drives a steam turbine that produces electricity. Steam exiting the turbine enters a condenser/cooling tower and is converted to water that enters a preheater and steam generator before re-entering the superheater.
  • FIG 4 provides a schematic of a prior art hybrid system that is commonly referred to as an Integrated Solar Combined Cycle (ISCC) system.
  • the ISCC system has a solar segment comprising a plurality of parabolic troughs.
  • Synthetic oil HTF e.g., VP-1
  • HRSG heat recovery steam generator
  • a natural gas turbine e.g., an aeroderivative turbine
  • the ISCC system can operate without any solar input, using exclusively natural gas, or it can operate using natural gas plus solar heat.
  • Steam exiting the steam turbine enters a condenser/cooling tower and is converted into water.
  • the water enters the economizer, for preheating then flows to the solar steam generator.
  • FIG. 5 provides a schematic of a solar/gas hybrid power system with a solar segment, a thermal storage segment, and a water/steam segment that incorporates the waste heat from a gas turbine, according to an exemplary embodiment.
  • a solar segment includes a collector field made up of a plurality of parabolic troughs connected in series and/or parallel by cyclical conduits containing a synthetic oil HTF (e.g., VP-1 ).
  • HTF e.g., VP-1
  • the oil HTF heat exchanges with a molten salt HTF of a thermal storage segment by way of an oil-to-salt heat exchanger.
  • this system unlike in the indirect storage system, there is no way to directly heat the steam segment using the oil HTF.
  • the thermal storage segment contains a cyclical conduit having at least one storage tank in a direct configuration.
  • the thermal storage tank may, for example, be a hot tank, a cold tank or a thermocline tank.
  • the thermal storage segment may be operated as a continuous flow loop wherein molten salt HTF exiting the heat exchanger flows to a hot tank, then to one or more heat exchangers coupled to a steam segment, followed by a cold tank and back to the oil-to-salt heat exchanger.
  • the molten salt HTF used within the thermal storage segment is in motion throughout the entire thermal storage segment conduit. This enables heat to be transferred from the solar segment to the thermal storage segment while simultaneously transferring heat from the thermal storage segment to the water/steam segment.
  • Another operational mode can occur when there is solar collection within the solar segment but it is not desirable to generate steam or make electricity.
  • molten salt HTF can be pumped from the cold tank, heated via exchange with the oil/salt heat exchanger, and then stored within the hot tank.
  • the molten salt is not simultaneously pumped from the hot tank for heat exchange with the water/steam segment, so no steam is made and no electricity is generated.
  • the solar/gas hybrid power system configuration of Figure 5 also includes a natural gas turbine (e.g., an aeroderivative turbine) that produces electricity from the combustion of fossil fuel. Waste heat from the gas turbine is thermally coupled to a superheater of a steam segment. Superheated steam drives a steam turbine that produces electricity, and steam exiting the steam turbine enters a condenser/cooling tower where it is converted into water. The water enters a feedwater heater, followed by a solar preheater and a steam generator which both heat exchange with the thermal storage segment.
  • a natural gas turbine e.g., an aeroderivative turbine
  • Waste heat from the gas turbine is thermally coupled to a superheater of a steam segment.
  • Superheated steam drives a steam turbine that produces electricity, and steam exiting the steam turbine enters a condenser/cooling tower where it is converted into water.
  • the water enters a feedwater heater, followed by a solar preheater and a steam generator which both heat exchange
  • isotopic variants of compounds disclosed herein are intended to be encompassed by the disclosure.
  • any one or more hydrogens in a molecule disclosed can be replaced with deuterium or tritium.
  • Isotopic variants of a molecule are generally useful as standards in assays for the molecule and in chemical and biological research related to the molecule or its use. Methods for making such isotopic variants are known in the art. Specific names of compounds are intended to be exemplary, as it is known that one of ordinary skill in the art can name the same compounds differently.
  • ranges specifically include the values provided as endpoint values of the range.
  • ranges specifically include all the integer values of the range. For example, a range of 1 to 1 00 specifically includes the end point values of 1 and 100. It will be understood that any subranges or individual values in a range or subrange that are included in the description herein can be excluded from the claims herein.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention concerne des systèmes à énergie solaire à concentration (CSP) hybrides soleil/gaz et des procédés d'utilisation des systèmes CSP. Les systèmes CSP hybrides sont très efficaces en raison, au moins en partie, d'un segment solaire comprenant un premier fluide de transfert de chaleur et d'un segment de stockage thermique comprenant un second fluide de transfert de chaleur. Le second fluide de transfert de chaleur échange la chaleur avec un segment vapeur pour produire la vapeur qui entraîne une turbine à vapeur. Ainsi, les segments solaire et thermique réalisent la « difficile tâche » consistant à produire de la vapeur à partir d'eau. Une fois que la vapeur est produite, elle entre dans un surchauffeur du segment vapeur. Le surchauffeur, qui n'échange pas directement la chaleur avec le segment de stockage thermique, est chauffé par une turbine à gaz positionnée en aval du segment de stockage thermique.
PCT/US2013/025400 2013-02-08 2013-02-08 Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation Ceased WO2014123537A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US2013/025400 WO2014123537A1 (fr) 2013-02-08 2013-02-08 Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2013/025400 WO2014123537A1 (fr) 2013-02-08 2013-02-08 Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation

Publications (1)

Publication Number Publication Date
WO2014123537A1 true WO2014123537A1 (fr) 2014-08-14

Family

ID=51300011

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2013/025400 Ceased WO2014123537A1 (fr) 2013-02-08 2013-02-08 Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation

Country Status (1)

Country Link
WO (1) WO2014123537A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105299922A (zh) * 2015-11-17 2016-02-03 绍兴文理学院 一种槽式太阳能制药热能系统
WO2016207449A1 (fr) * 2015-06-23 2016-12-29 Acs Servicios, Comunicaciones Y Energía, S. L. Installation solaire hybride
CN109059312A (zh) * 2018-07-06 2018-12-21 中国电建集团西北勘测设计研究院有限公司 一种光热电站熔盐储罐的多罐式储热装置及方法
WO2019109012A1 (fr) * 2017-12-03 2019-06-06 Glasspoint Solar, Inc. Dispositifs de stockage thermique de génération solaire de vapeur, comprenant la recirculation et le dessalement, systèmes et procédés associés
CN109958593A (zh) * 2019-03-11 2019-07-02 西安交通大学 一种太阳能燃煤耦合灵活发电系统及运行方法
US10411180B2 (en) 2013-01-07 2019-09-10 Glasspoint Solar, Inc. Systems and methods for selectively producing steam from solar collectors and heaters for processes including enhanced oil recovery
CN111108078A (zh) * 2017-01-16 2020-05-05 亚拉国际有限公司 硝酸钙和硝酸钾肥料粒子
CN113432099A (zh) * 2021-06-04 2021-09-24 西安交通大学 光热电站启动过程的预热器入口给水温度控制系统及方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090121495A1 (en) * 2007-06-06 2009-05-14 Mills David R Combined cycle power plant
US20100295306A1 (en) * 2009-05-21 2010-11-25 Advanced Solar Power Israel Ltd. System for converting solar radiation into electricity
US20110277469A1 (en) * 2008-09-17 2011-11-17 Avraham Brenmiller Solar thermal power plant

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090121495A1 (en) * 2007-06-06 2009-05-14 Mills David R Combined cycle power plant
US20110277469A1 (en) * 2008-09-17 2011-11-17 Avraham Brenmiller Solar thermal power plant
US20100295306A1 (en) * 2009-05-21 2010-11-25 Advanced Solar Power Israel Ltd. System for converting solar radiation into electricity

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10411180B2 (en) 2013-01-07 2019-09-10 Glasspoint Solar, Inc. Systems and methods for selectively producing steam from solar collectors and heaters for processes including enhanced oil recovery
WO2016207449A1 (fr) * 2015-06-23 2016-12-29 Acs Servicios, Comunicaciones Y Energía, S. L. Installation solaire hybride
CN105299922A (zh) * 2015-11-17 2016-02-03 绍兴文理学院 一种槽式太阳能制药热能系统
CN111108078A (zh) * 2017-01-16 2020-05-05 亚拉国际有限公司 硝酸钙和硝酸钾肥料粒子
US11485689B2 (en) 2017-01-16 2022-11-01 Yara International Asa Calcium nitrate and potassium nitrate fertiliser particles
US12103896B2 (en) 2017-01-16 2024-10-01 Yara International Asa Calcium nitrate and potassium nitrate fertiliser particles
WO2019109012A1 (fr) * 2017-12-03 2019-06-06 Glasspoint Solar, Inc. Dispositifs de stockage thermique de génération solaire de vapeur, comprenant la recirculation et le dessalement, systèmes et procédés associés
CN109059312A (zh) * 2018-07-06 2018-12-21 中国电建集团西北勘测设计研究院有限公司 一种光热电站熔盐储罐的多罐式储热装置及方法
CN109059312B (zh) * 2018-07-06 2020-03-17 中国电建集团西北勘测设计研究院有限公司 一种光热电站熔盐储罐的多罐式储热装置及方法
CN109958593A (zh) * 2019-03-11 2019-07-02 西安交通大学 一种太阳能燃煤耦合灵活发电系统及运行方法
CN113432099A (zh) * 2021-06-04 2021-09-24 西安交通大学 光热电站启动过程的预热器入口给水温度控制系统及方法

Similar Documents

Publication Publication Date Title
US20140223906A1 (en) Solar/gas hybrid power system configurations and methods of use
Yang et al. Thermodynamic analysis and optimization of a solar organic Rankine cycle operating with stable output
González-Roubaud et al. Review of commercial thermal energy storage in concentrated solar power plants: Steam vs. molten salts
Pitz-Paal Concentrating solar power
WO2014123537A1 (fr) Configurations de système à énergie hybride soleil/gaz et procédés d'utilisation
Tempesti et al. Thermodynamic analysis of two micro CHP systems operating with geothermal and solar energy
CN101413719B (zh) 带有双级蓄热的塔式太阳能热发电系统
US20120102950A1 (en) Solar thermal power plant with the integration of an aeroderivative turbine
US20140366536A1 (en) High temperature thermal energy for grid storage and concentrated solar plant enhancement
CN108291532B (zh) 太阳能发电装置及其控制方法
McTigue et al. Assessing geothermal/solar hybridization–Integrating a solar thermal topping cycle into a geothermal bottoming cycle with energy storage
EP3130770A1 (fr) Système intégré optimisé pour production d'électricité hybride solaire-biomasse
Pitz-Paal Solar Energy–Concentrating solar power
Li et al. Impacts of solar multiples on the performance of integrated solar combined cycle systems with two direct steam generation fields
CN110573699B (zh) 生成电能的发电所和运行发电所的方法
CN103890490A (zh) 混合式太阳能场
WO2011053863A2 (fr) Système de circuit de fluide double pour générer un fluide de travail vaporeux à l'aide d'énergie solaire
CN103670554B (zh) 发电供热装置
US20150167647A1 (en) Concentrating solar power plant with hybrid collector field
Turchi et al. Concentrating solar power
US11661857B2 (en) Electricity generating systems with thermal energy storage coupled superheaters
Wang et al. Thermodynamic and economic analyses of a parabolic trough concentrating solar power plant under off-design conditions
Chen et al. Techno-economic performance of the solar tower power plants integrating with 650° C high-temperature molten salt thermal energy storage
WO2013018014A2 (fr) Systèmes, dispositifs et procédés de stockage thermique d'énergie solaire
US20130312413A1 (en) Steam rankine cycle solar plant and method for operating such plants

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13874648

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13874648

Country of ref document: EP

Kind code of ref document: A1