WO2013038563A1 - Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur - Google Patents

Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur Download PDF

Info

Publication number
WO2013038563A1
WO2013038563A1 PCT/JP2011/071268 JP2011071268W WO2013038563A1 WO 2013038563 A1 WO2013038563 A1 WO 2013038563A1 JP 2011071268 W JP2011071268 W JP 2011071268W WO 2013038563 A1 WO2013038563 A1 WO 2013038563A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat medium
heat
heating
amount
gas
Prior art date
Application number
PCT/JP2011/071268
Other languages
English (en)
Japanese (ja)
Inventor
秀明 大田
Original Assignee
川崎重工業株式会社
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 川崎重工業株式会社 filed Critical 川崎重工業株式会社
Priority to AU2011377040A priority Critical patent/AU2011377040A1/en
Priority to PCT/JP2011/071268 priority patent/WO2013038563A1/fr
Publication of WO2013038563A1 publication Critical patent/WO2013038563A1/fr

Links

Images

Classifications

    • 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
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/05—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly characterised by the type or source of heat, e.g. using nuclear or solar energy
    • 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
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • 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
    • 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
    • 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]

Definitions

  • the present invention relates to a solar thermal power generation facility and a solar thermal power generation method that use solar heat while using a heat medium that changes phase between a liquid phase and a gas phase.
  • the present invention also relates to a heat medium supply device and a heat medium heating device that can be used for a solar power generation facility or a facility that requires a gas phase heat medium.
  • a solar thermal power generation facility is known as an example of a facility that uses a heat medium and solar heat.
  • the first heat medium heated by solar heat transmits solar heat to the heat storage tank, and the solar heat is stored in the heat storage tank.
  • the second heat medium is heated by the heat stored in the heat storage tank, and further heated by the boiler device to be vaporized.
  • the vaporized second heat medium drives the steam turbine power generator.
  • the parabolic trough type heat collecting apparatus has a parabolic trough mirror 1010 having a parabolic cross section.
  • the parabolic trough mirror 1010 is arranged at the focal position of the parabola, and is configured to reflect sunlight toward the heat absorption pipe 1012 through which the heat medium flows. And the inclination angle of the parabolic trough mirror 1010 is changed according to the movement of the sun.
  • the Fresnel type heat collecting apparatus has a plurality of flat plate mirrors 1022 as shown in FIG.
  • a heat absorption pipe is disposed above the flat mirror 1010 in parallel with the flat mirror.
  • the flat mirror is configured to reflect sunlight toward the heat absorption pipe 1012 in accordance with the movement of the sun. Then, the inclination angle of each flat mirror 1022 is changed.
  • the tower-type heat collecting apparatus includes a tower 1032 having a tip 1030 through which a heat medium flows, and a plurality of concentric circles, concentric semi-centric circles having different distances from the tower 1032 to the tower 1032, or It has a plurality of flat mirrors 1034 (referred to as heliostats) arranged on concentric polygons. As the sun moves, each heliostat 1034 is configured to reflect sunlight toward the tip 1030 of the tower 1032. Then, the inclination angle of each heliostat 1034 is changed.
  • a vacuum pipe or a non-vacuum pipe is used as a heat absorption pipe irradiated with reflected sunlight (that is, heated by solar heat).
  • the vacuum pipe is less likely to dissipate heat and therefore has less heat loss.
  • the vacuum pipe includes a steel tube through which a heat medium flows and a glass tube surrounding the steel tube. The space between the steel tube and the glass tube is evacuated.
  • the coating film which can selectively absorb the sunlight of a specific wavelength is formed on the outer surface of the steel pipe.
  • Such a vacuum pipe is often employed when oil is used as a heat medium and a parabolic trough heat collector is used as a heat collector.
  • the non-vacuum pipe is, for example, a simple steel pipe.
  • Non-vacuum pipes have more heat dissipation than vacuum pipes, but have the advantage of simple structure, low manufacturing cost and easy handling.
  • Such a non-vacuum pipe is often employed when water is used as a heat medium and a Fresnel heat collector is used as a heat collector.
  • Patent Document 4 discloses a pipe through which a heat medium flows and stores heat of the heat medium.
  • the solar thermal power generation facility described in Patent Literature 4 is configured to store the heat of a heat medium in a heat storage medium provided in a pipe, and to heat the heat medium with the heat stored in the heat storage medium.
  • a main supply pipe thermally connected to the heat storage medium
  • a bypass pipe thermally separated from the heat storage medium
  • a control valve for flowing the heat medium through either the supply pipe or the bypass pipe is provided.
  • the solar heat energy intensity reaching the ground (Direct sunshine intensity: Direct Normal Irradiance or DNI for short) varies depending on the season, time, weather, location, etc. For example, as shown in FIG. 17, the change in direct sunlight intensity in Denver, USA, the sunshine time varies depending on the calendar day, and the direct sunlight intensity varies depending on the time. In addition, the direct sunlight intensity changes suddenly due to sudden changes in weather, such as clouds blocking the sun. That is, there is a possibility that the heat medium cannot be sufficiently heated by solar heat. Therefore, in the case of solar power generation using a heat medium sufficiently heated by solar heat, that is, a gas phase heat medium (for example, water vapor), there is a possibility that sufficient electric power cannot be generated.
  • a gas phase heat medium for example, water vapor
  • the present invention can sufficiently heat the heating medium without increasing the scale of the facility, even when the sunshine duration is short, the direct sunlight intensity is low, and / or even when the direct sunlight intensity changes rapidly.
  • the task is to do.
  • the present invention is configured as follows.
  • a solar thermal power generation facility that uses a heat medium that changes phase between a liquid phase and a gas phase, wherein the heat medium is heated by solar heat that is first heat.
  • a second heating device that increases the proportion of the gas phase of the heating medium by heating the heating medium after being heated by the first heating device with a second heat different from solar heat, and the second heating.
  • a turbine generator that is driven by the heat medium heated by the apparatus, and the second heating apparatus is configured to use the heat held by another heat medium as the second heat for heating the heat medium.
  • a solar thermal power generation facility is provided.
  • a solar thermal power generation method using a heat medium that changes phase between a liquid phase and a gas phase, wherein the heat medium is heated by solar heat that is first heat, and the solar heat is used.
  • the heated heat medium is heated by the second heat different from the solar heat to increase the ratio of the gas phase of the heat medium, and the turbine power generator is driven by the heat medium heated by the second heat to generate electric power.
  • a solar thermal power generation method that uses heat held by another heat medium as second heat for heating the heat medium.
  • a heat medium supply device that supplies a heat medium that changes in phase between a liquid phase and a gas phase in a gas phase state, and the heat medium is generated by solar heat that is first heat.
  • a first heating device that heats the heating medium, and a second heating that increases a gas phase ratio of the heating medium by heating the heating medium heated by the first heating device with a second heat different from solar heat.
  • a second heating device configured to use the heat held by another heating medium as the second heat for heating the heating medium.
  • a heat medium heating device that heats a heat medium that changes phase between a liquid phase and a gas phase, and receives the heat medium heated by solar heat that is first heat.
  • the heating medium is configured to increase the gas phase ratio of the received heat medium by being heated by the second heat different from the solar heat, and receives another heat medium from the outside of the heat medium heating apparatus, and receives another heat medium.
  • a heat medium heating device configured to use the heat held by the heat medium as the second heat for heating the heat medium.
  • the heating medium is sufficiently heated even when the sunshine duration is short, when the direct sunlight intensity is low, and / or when the direct sunlight intensity changes abruptly without increasing the size of the facility. can do.
  • FIG. 1 conceptually shows the configuration of the combined solar thermal power generation facility according to Embodiment 1 of the present invention.
  • a solar combined power generation facility (ISCC: Integrated Solar Combined Cycle) 10 shown in FIG. 1 is an example of a solar thermal power generation facility that generates power using solar heat and a heat medium, and includes a plurality of power generation sources.
  • heat medium refers to a fluid that can flow while retaining heat.
  • inexpensive water is used as a heat medium that changes between a liquid phase and a gas phase.
  • a solar combined power generation facility 10 is heated by solar heat, a solar field (first heating device) 12 that vaporizes (generates steam) a liquid heat medium (water) by solar heat.
  • a second heating device 14 that heats the heated heat medium (heat medium with a low gas phase ratio) after heating to increase the gas phase ratio, and a heat medium (gas phase ratio) heated by the second heating device 14
  • a waste heat recovery boiler device 16 that superheats (a heat medium having a high heat capacity)
  • a steam turbine power generator 18 that is driven by a heat medium (gas phase heat medium) that is superheated by the exhaust heat recovery boiler device 16, and
  • a gas turbine power generator 20 that generates power while supplying high-temperature exhaust gas (another heat medium) to the second heating device 14 and the exhaust heat recovery boiler device 16 is provided.
  • the solar field 12, the second heating device 14, the exhaust heat recovery boiler device 16, and the gas turbine power generation device 20 supply a vapor phase heat medium to the steam turbine power generation device 18.
  • the liquid phase heat medium is heated by the exhaust gas discharged from the gas turbine power generation device 20 to be vaporized, and further A facility for generating electricity by heating it to a steam turbine power generator is called a gas turbine combined power generation facility (CCPP: Combined Cycle Power Plant).
  • CCPP Combined Cycle Power Plant
  • FIG. 2 shows a specific configuration of the solar thermal combined power generation facility 10. From here, a plurality of components of the solar combined power generation facility 10 will be described while explaining the flow of the heat medium. Each drawing shows only main components related to the present invention, and there are other components not shown. It should be noted that the components described below are components related to the present invention and are not all the components necessary for the combined solar thermal power generation facility 10.
  • the solar field 12 has the Fresnel heat collecting device 22 that heats the liquid heat medium by solar heat.
  • the Fresnel type heat collecting apparatus 22 includes a plurality of flat plate mirrors 22 a that heat a liquid phase heat medium flowing in the heat absorption pipe 24.
  • Each flat mirror 22 a is configured to reflect sunlight and irradiate the heat absorption pipe 24 with the reflected light. The inclination angle of each flat mirror 22a is adjusted according to the movement of the sun.
  • the Fresnel-type heat collector 22 may be called LFR (Linear Fresnel Reflector) or CLFR (Compact Linear Fresnel Reflector).
  • the Fresnel heat collector 22 having a plurality of flat mirrors 22a having a simple structure and being inexpensive is preferable.
  • the present invention does not limit the heat collecting device. Any heat collecting apparatus capable of vaporizing a liquid heat medium with solar heat can be used. For example, a parabolic trough heat collector (see FIG. 14) or a tower heat collector (see FIG. 16) may be used.
  • Parabolic trough heat collectors have good heat collection efficiency and are widely used in large-scale solar power generation facilities of 30 MW class or higher.
  • oil is used as the heat medium, so there is a limit to the use temperature (depending on the type of oil, for example, about 400 ° C). Further, the production cost is higher than that of the Fresnel type heat collecting apparatus.
  • the tower type heat collector has a high concentration. Therefore, when using a molten salt as a heating medium, the heating medium can be heated to a very high temperature (depending on the type of the molten salt, for example, in the case of a mixed salt of potassium nitrate and sodium nitrate, a temperature exceeding about 560 ° C. ). However, since the height is large, a tower 1030 that requires earthquake resistance and a high-power pump (not shown) that sends a heat medium to the tip 1030 of the tower 1032 are required.
  • the heat absorption pipe 24 of the present invention may be either a vacuum pipe or a non-vacuum pipe.
  • Vacuum pipes have high heat collection efficiency but high production costs.
  • non-vacuum pipes are advantageous in terms of equipment cost because they are less expensive than vacuum pipes but are less expensive.
  • the heat medium (vapor) vaporized by heating the solar field 12 flows out of the heat absorption pipe 24 and passes through the second heating device 14.
  • the heat medium is heated by the second heating device 14 so that the steam of the rated steam amount can be supplied to the steam turbine power generation device 18 to increase the ratio of the gas phase.
  • the heating medium is brought into a saturated state in which the gas phase and the liquid phase coexist with each other (saturated steam is generated) by the heating of the second heating device 14. Details of the second heating device 14 will be described later.
  • the heat medium heated by the second heating device 14 is separated into a gas phase (steam) and a liquid phase (water) by the gas-liquid separator 26.
  • the liquid phase heat medium is returned to the solar field 12.
  • the gas phase heat medium is sent to and stored in an air storage tank (buffer tank) 28.
  • the heat medium that has changed to the liquid phase while being stored in the air storage tank 28 is returned to the solar field 12.
  • the gas phase heat medium stored in the air storage tank 28 is adjusted to a steam amount corresponding to the rated steam amount of the steam turbine power generator 18 by the flow rate control valve 30 and supplied to the exhaust heat recovery boiler device 16.
  • the heat medium supplied from the air storage tank 28 to the exhaust heat recovery boiler device 16 merges with the heat medium vaporized by the evaporator (evaporator) 16b and flows into the super heater (superheater) 16c.
  • the heat medium (superheated steam) superheated by the super heater 16c drives the steam turbine 18a of the steam turbine power generator 18, and the steam turbine 18a drives the generator 18b. Thereby, the generator 18b generates power.
  • the gas phase heat medium after driving the steam turbine 18 a is converted into a liquid phase by the condenser 32.
  • the liquid phase heat medium is sent by the pump 34, heated by the feed water heater 36, and deaerated by the deaerator 38.
  • a part of the deaerated heat medium is sent to the exhaust heat recovery boiler apparatus 16 by the pump 40, and the rest is sent to the solar field 12 by the pump 42.
  • the heat medium sent to the exhaust heat recovery boiler device 16 is preheated by an economizer (preheater) 16a, vaporized by an evaporator 16b, and merges with the heat medium supplied from the air storage tank 28.
  • the exhaust heat recovery boiler unit 16 has a purpose of preheating the liquid heat medium by the economizer 16a, a purpose of vaporizing the liquid heat medium by the evaporator 16b, and a gas heat medium by the super heater 16c.
  • Exhaust gas discharged from the gas turbine 20a of the gas turbine power generator 20 is supplied as the heat for overheating.
  • the gas turbine 20a is driven by combustion gas generated by the combustion of fuel. Thereby, the gas turbine 20a drives the generator 20b. And the combustion gas after driving the gas turbine 20a is discharged
  • the exhaust gas of the gas turbine power generator 20 supplied to the exhaust heat recovery boiler device 16 is finally dissipated through the chimney 46. Further, a part of the exhaust gas of the gas turbine power generation device 20 is selectively supplied to the second heating device 14.
  • FIG. 3 schematically shows the configuration of the second heating device 14.
  • FIG. 4 shows a cross section (AA cross section) of the second heating device 14.
  • FIG. 5 shows the daily solar thermal energy intensity (DNI) (one-dot chain line), the amount of power generated by the steam turbine power generator 18 (solid line), and the solar thermal energy (two-dot chain line) acquired by the solar field 12. .
  • DNI daily solar thermal energy intensity
  • solid line the amount of power generated by the steam turbine power generator 18
  • solar thermal energy two-dot chain line
  • FIG. 5B the solar thermal energy acquired by the solar field 12 and the power generation amount that is electric energy obtained by converting the thermal energy do not completely match. This is because, in the process of converting solar thermal energy into electric energy, energy loss occurs due to, for example, copper loss, iron loss, windage loss, sliding friction, and the like of the steam turbine power generation device 18.
  • the rated power generation amount of the steam turbine power generator 18 is determined based on the average direct sunlight intensity at the place where the solar field 12 is laid. This is because the time zone in which the maximum direct sunlight intensity is obtained within a day is short, and the steam turbine power generator is partially loaded in most other time zones. In the partial load operation, the steam turbine efficiency is reduced, so that the power generation efficiency of the entire power generation facility is reduced. Therefore, it is reasonable to determine the rated power generation amount of the steam turbine power generator 18 based on the average direct sunlight intensity rather than the maximum direct sunlight intensity.
  • the “average direct sunshine intensity” as used herein refers to the direct power when it is assumed that the amount of power generated equal to the amount of power generated using the direct sunshine intensity that changes within the day is generated with a constant direct sunshine intensity.
  • sunshine intensity Specifically, first, the amount of the heat medium in the gas phase generated through the solar field 12 by the solar heat with the average direct sunlight intensity is calculated. Next, a possible power generation amount is calculated from the calculated gas phase heat medium amount. Then, the specification of the steam turbine power generator 18 is determined based on the calculated power generation amount.
  • FIG. 5 (A) shows a day in which part of the direct sunlight sunshine intensity that changes within a day is higher than the average direct sunlight intensity.
  • FIG. 5 (B) shows a day when the direct sunlight intensity changing within a day is lower than the average direct sunlight intensity.
  • the second heating device 14 is heated by solar heat (solar field 12) so that the steam turbine power generation device 18 can generate the rated power generation amount without wasting solar thermal energy.
  • the heating medium after heating is configured to be heated.
  • the second heating device 14 includes a heat medium flow path (first flow path) 50 through which a heat medium from the solar field 12 toward the gas-liquid separator 26 passes, and gas turbine power generation.
  • Exhaust gas flow path (second flow path) 52 through which high-temperature exhaust gas supplied from the apparatus 20 passes, heating material 54 capable of holding heat, and flow rate adjustment for adjusting the amount of exhaust gas flowing into the exhaust gas flow path 52
  • the flow rate control valve 56 is a part of a device that distributes the exhaust gas of the gas turbine power generation device 20 to the second heating device 14 and the exhaust heat recovery boiler device 16.
  • the heat medium flow path 50 and the exhaust gas flow path 52 are made of, for example, steel pipes capable of efficiently exchanging heat between the internal space through which the heat medium and the exhaust gas flow and the outside.
  • the heating material 54 that absorbs and holds heat from other objects and supplies the retained heat to the other objects is, for example, a material such as sand, molten salt, or ceramic powder.
  • the heating material 54 may be a gas such as sealed air.
  • the heating material 54 is directly thermally connected to the heat medium flow path 50 (that is, the heat medium), and is also directly thermally connected to the exhaust gas flow path 52 (that is, the exhaust gas). It is connected. Therefore, the heating material 54 can absorb and retain heat from the heat medium or exhaust gas, and can heat the heat medium by the retained heat (heat can be supplied to the heat medium). That is, the exhaust gas and the heat medium are indirectly thermally connected via the heating material 54.
  • the flow rate adjusting valve 56 is configured to adjust the amount of exhaust gas flowing into the exhaust gas flow channel 52 based on the amount of gas phase heat medium flowing into the heat medium flow channel 50.
  • a flow sensor 58, a pressure sensor 60, and a temperature sensor 62 are provided in order to measure the amount of the heat medium in the gas phase flowing into the heat medium flow path 50.
  • the amount of the heat medium in the gas phase flowing into the heat medium flow path 50 corresponds to the flow rate of the heat medium detected by the flow sensor 58, the pressure of the heat medium detected by the pressure sensor 60, and the temperature of the heat medium detected by the temperature sensor 62. Calculated based on
  • the calculation of the amount of the gas phase heat medium flowing into the heat medium flow path 50 of the second heating device 14 and the control of the flow rate adjustment valve 56 based on the calculation result are performed by the main computer (not shown) of the combined solar heat power generation facility 10. Is called.
  • the main computer controls the steam turbine power generation device 18, the gas turbine power generation device 20, the condensing device, the deaerator, the flow rate adjustment valve 30, the pumps 34, 40, 42, and the like.
  • another computer incorporated in the second heating device 14 is used to calculate the amount of the gas phase heat medium flowing into the heat medium flow path 50 and the flow rate adjustment valve 56 based on the calculation result. Control may be performed. By doing in this way, the 2nd heating apparatus 14 can be easily integrated in the existing installation.
  • the second heating device 14 When the amount of the heat medium in the gas phase supplied from the solar field 12 is larger than the specified amount, the second heating device 14 is configured to absorb the heat retained by the heat medium by the heating material 54. On the other hand, when the amount of the heat medium in the gas phase is smaller than the specified amount, the second heating device 14 is configured to heat the heat medium with the heat retained by the heating material 54.
  • the “specified amount” referred to here is the amount of the heat medium in the gas phase that is lost until it reaches the steam turbine power generator 18, the amount of the heat medium in the gas phase supplied from the evaporator 16b, and the rated steam amount. It is an amount calculated based on this.
  • the predetermined temperature is preferably set to a temperature at which heat transfer from the heat medium to the heating material 54 hardly occurs when the amount of the heat medium in the gas phase flowing through the heat medium flow path 50 is substantially a specified amount.
  • a temperature sensor 64 that detects the temperature of the heating material 54 is provided in the second heating device 14.
  • the temperature sensor 64 may be installed anywhere as long as it can detect the temperature correlated with the temperature of the heating material 54 (the amount of retained heat) inside the second heating device 14.
  • the amount of exhaust gas flowing into the exhaust gas passage 52 is reduced when the amount of the gas phase heat medium flowing through the heat medium passage 50 exceeds a specified amount.
  • the amount of heat retained by the heating material 54 decreases, and part of the heat retained by the heat medium is absorbed by the heating material 54.
  • the exhaust gas supply amount is increased.
  • the amount of heat retained by the heating material 54 increases, and part of the heat retained by the heat medium heating material 54 is supplied. Therefore, the amount of the gas phase heat medium output from the second heating device 14 can be maintained at a substantially specified amount.
  • the second heating device 14 When the operation of the solar combined power generation facility 10 is started, the second heating device 14 is heated for the purpose of increasing the amount of heat retained by the heating material 54 or for the purpose of warming the heat medium flow path 50 and the exhaust gas flow path 52.
  • the exhaust gas may be flowed into the exhaust gas passage 52 by operating the flow control valve 56.
  • exhaust gas can be used effectively, and as a result, the utilization of solar thermal energy, which is natural energy, is improved.
  • FIG. 6 shows a second heating device of a comparative example that heats the heat medium supplied from the solar field by using only the heating material without using exhaust gas.
  • the heating material 154 is the heat medium. Although there is no need to absorb heat, the heat of the heat medium is absorbed by the heating material 154. Therefore, it is necessary to provide a bypass channel 166 for avoiding thermal connection with the heating material 154 and for allowing the heat medium to flow.
  • the temperature of the heating material 54 (retained heat amount) is maintained constant by the exhaust gas. Heat is not absorbed.
  • the heating material 154 when the retained heat amount of the heating material 154 is near the lower limit and the amount of the heat medium in the gas phase supplied from the solar field 12 is lower than the specified amount, the heating material 154 The heat medium cannot be heated by holding heat. Therefore, the power generation amount of the steam turbine power generator 18 is reduced. Considering this, it is necessary to provide a large amount of heating material 154.
  • the temperature of the heating material 54 (retained heat amount) is kept constant by the exhaust gas, and therefore flows into the exhaust gas passage 52. Since the amount of exhaust gas to be increased can be increased, the heat medium can be heated.
  • the heating material 154 when the retained heat amount of the heating material 54 is near the upper limit and the amount of the heat medium in the gas phase supplied from the solar field 12 exceeds the specified amount, the heating material 154 is Can hardly absorb the heat of the heat medium. Further, since the second heating device 114 of the comparative example is configured to heat the heat medium with the heat retained by the heating material 154, the heating material 154 is thermally separated from the outside (the natural nature of the heating material 154). Heat dissipation is suppressed). Considering this, it is necessary to provide a large amount of heating material 154.
  • the second heating device 14 of the first embodiment when the retained heat amount of the heating material 54 is near the upper limit and the amount of the gas phase heat medium supplied from the solar field 12 exceeds the specified amount, the exhaust gas The supply of exhaust gas to the flow path 52 is stopped. As a result, the amount of heat retained by the heating material 54 can be reduced, and the heating material 54 can absorb the heat of the heat medium. That is, when the supply of the exhaust gas is stopped, a part of the heat retained by the heating material 54 moves into the exhaust gas passage 52 and is dissipated outside through the chimney 48.
  • the present invention does not require a bypass flow path for avoiding heat exchange between the heat medium and the heating material 54.
  • the second heating device 14 preferably includes a bypass flow path.
  • the heat medium flow path 50 ie, the heat medium
  • the exhaust gas flow path 52 ie, the exhaust gas
  • the direct sunlight intensity changes rapidly, that is, the amount of heat medium in the gas phase rapidly changes. Can respond quickly.
  • the amount of the heat medium in the gas phase flowing through the heat medium passage 50 sharply decreases due to a sudden change in weather
  • the amount of exhaust gas flowing through the exhaust gas passage 52 is increased, and a part of the retained heat of the exhaust gas (heat medium flow
  • the heat medium can be quickly heated by heat (moving to the path 50).
  • the amount of the heat medium in the gas phase is measured. (Calculated by the flow sensor 58, the pressure sensor 60, and the temperature sensor 62), but the present invention is not limited to this.
  • the amount of the heat medium in the gas phase may be measured after flowing out of the heat medium flow path 50, that is, after heat exchange is performed between the heat medium and the heating material 54. In this case, adjustment of the amount of exhaust gas flowing into the exhaust gas passage 52 based on the amount of the heat medium in the gas phase (control of the passage control valve 56) is feedback controlled.
  • the amount of heat medium in the gas phase is measured (calculated), but the present invention is not limited to this. It is also possible to adjust the amount of exhaust gas supplied to the exhaust gas passage 52 based on the measurement result of the liquid phase heat medium amount. For example, as shown in FIG. 2, a flow rate sensor 68 for detecting the amount of heat medium in the liquid phase separated by the gas-liquid separator 26 is provided, and based on the amount of heat medium in the liquid phase detected by the flow rate sensor 68, The amount of exhaust gas supplied to the exhaust gas passage 52 via the flow rate adjustment valve 56 is adjusted.
  • the amount of heat medium in the liquid phase detected by the flow sensor 68 increases, the amount of exhaust gas supplied to the exhaust gas flow path 52 via the flow control valve 56 increases.
  • the amount of the heat medium in the liquid phase detected by the flow rate sensor 68 decreases, the amount of exhaust gas supplied to the exhaust gas flow path 52 via the flow rate adjustment valve 56 decreases.
  • the amount of liquid phase heat medium detected by the flow sensor 68 and the amount of liquid phase heat medium before being heated by the solar field 12 that is, the heat medium supplied to the solar field 12 by the pump 42. If the amount is substantially the same, the supply of the exhaust gas to the exhaust gas passage 52 of the second heating device 14 may be stopped.
  • the amount of the heat medium in the liquid phase detected by the flow sensor 68 and the amount of the heat medium in the liquid phase before being heated by the solar field 12 are substantially the same. It means that it is hardly heated by the solar field 12. In other words, even if the heat medium is heated by the second heating device 14, it means that the amount of the heat medium in the gas phase hardly increases. Therefore, in this case, the exhaust gas supply to the second heating device 14 is stopped.
  • the amount of the liquid phase heat medium supplied to the solar field 12 (that is, the amount of the heat medium supplied to the solar field 12 by the pump 42) is adjusted. May be. For example, when the amount of the liquid phase heat medium detected by the flow sensor 68 increases, the amount of the liquid phase heat medium supplied to the solar field 12 via the pump 42 decreases. On the other hand, when the amount of the liquid phase heat medium detected by the flow sensor 68 decreases, the amount of the liquid phase heat medium supplied to the solar field 12 via the pump 42 increases. Thereby, the 2nd heating apparatus 14 can exhibit the heating capability.
  • the heat medium can be sufficiently heated.
  • the heat medium can be sufficiently vaporized, and as a result, the solar combined power generation facility 10 can generate sufficient power.
  • Embodiment 2 The combined solar heat power generation facility of the second embodiment is the same as that of the first embodiment except for the second heating device. Therefore, the 2nd heating apparatus concerning this Embodiment 2 is demonstrated.
  • FIG. 8 shows the second heating device 214 of the second embodiment. Unlike the second heating device 14 of the first embodiment, the second heating device 214 of the second embodiment does not have a heating material. Note that the heat medium flow path 250 (that is, the heat medium) and the exhaust gas flow path 252 (that is, the exhaust gas) are thermally connected.
  • the amount of heat medium in the gas phase supplied from the solar field 12 (that is, calculated based on the detection results of the flow sensor 258, the pressure sensor 260, and the temperature sensor 262). If the gas phase heat medium amount) exceeds the specified amount, the flow rate adjustment valve 256 stops the exhaust gas supply to the exhaust gas flow path 252. While the heat medium flows through the heat medium flow path 250, a part of the retained heat enters the exhaust gas flow path 252 and is dissipated to the outside through the chimney 48.
  • the amount of the exhaust gas supplied to the exhaust gas passage 252 is adjusted by the flow rate control valve 256 based on the amount of the heat medium in the gas phase. Is done.
  • the second heating device 214 of the second embodiment does not include a heating material
  • the second heating device 214 is more compact than the second heating device 14 of the first embodiment.
  • the heating material is not provided, the heat retained by the heat medium cannot be absorbed and retained. That is, when the amount of the heat medium in the gas phase supplied from the solar field 12 exceeds the specified amount, a part of the heat retained by the heat medium cannot be absorbed and retained by the heating material. Furthermore, the heat retained by the heating material cannot be used for heating the heat medium.
  • the second heating device 214 preferably includes a bypass flow channel thermally separated from the exhaust gas flow channel 252.
  • FIG. 9 shows the second heating device 314 of the third embodiment.
  • the heating material 354 and the exhaust gas passage 352 that is, the exhaust gas
  • the heating material 354 and the exhaust gas do not exchange heat.
  • the second heating device 314 includes a heat medium flow path 350a thermally connected only to the exhaust gas flow path 352, a heat medium flow path 350b thermally connected only to the heating material 354, and a heat medium. It has flow control valves 356b and 356c for supplying the heat medium to at least one of the flow path 350a or the heat medium flow path 350b.
  • the amount of the gas phase heat medium from the solar field 12 and the temperature sensor 368 calculated based on the detection results of the flow sensor 358, the pressure sensor 360, and the temperature sensor 362.
  • the three flow rate control valves 356a, 356b, and 356c are controlled based on the detection result (the amount of heat retained by the heating material 354).
  • the amount of the heat medium in the gas phase supplied from the solar field 12 is less than a specified amount, a part of the heat medium is supplied to the heat medium flow path 350a because it is heated by the exhaust gas, and the rest is supplied by the heating material 354. In order to be heated, it is supplied to the heat medium flow path 350b.
  • the second heating device 314 having such a configuration can control the amount of the gas phase heat medium supplied to the gas-liquid separation device 26 with high accuracy.
  • the second heating device 314 has a bypass channel thermally separated from the exhaust gas channel 352 and the heating material 354. It is preferable to provide.
  • Embodiment 4 The combined solar heat power generation facility of the fourth embodiment is the same as that of the first embodiment except for the second heating device. Therefore, the 2nd heating apparatus concerning this Embodiment 4 is demonstrated.
  • FIG. 10 shows the second heating device 414 of the fourth embodiment.
  • the heating material 454 and the exhaust gas passage 452 that is, the exhaust gas
  • the heating material 454 and the exhaust gas do not exchange heat.
  • the second heating device 414 includes a heat medium flow channel 450a thermally connected only to the exhaust gas flow channel 452, and a heat medium flow channel 450b thermally connected only to the heating material 454.
  • the second heating device 414 is configured so that the heat medium after passing through the heat medium flow path 450b always flows through the heat medium flow path 450a (this is different from the third embodiment).
  • the amount of gas phase heat medium from the solar field 12 and the temperature sensor 468 calculated based on the detection results of the flow sensor 458, the pressure sensor 460, and the temperature sensor 462. Based on the detection result (the amount of heat retained by the heating material 354), the flow rate adjustment valve 456 is controlled.
  • the heat medium is heated by the heating material 454 while passing through the heat medium flow path 450b, and further passes through the heat medium flow path 450a. However, it is heated by the exhaust gas flowing through the exhaust gas flow path 452.
  • the second heating device 414 configured as described above can control the amount of the gas phase heat medium supplied to the gas-liquid separation device 26 with high accuracy. Further, the structure of the second heating device 414 of the fourth embodiment is simpler than that of the second heating device 314 of the third embodiment.
  • the second heating device 414 when the frequency with which a substantially prescribed amount of vapor phase heat medium is supplied from the solar field 12 is high, the second heating device 414 includes a bypass channel thermally separated from the exhaust gas channel 452, and a heating material 454. And a bypass channel thermally separated.
  • the first embodiment is a solar combined power generation facility having a plurality of power generation sources
  • the fifth embodiment is a solar thermal power generation facility having one generation power source.
  • FIG. 11 shows a specific configuration of the solar thermal power generation facility 510 of the fifth embodiment.
  • the first difference from the first, second, third, and fourth embodiments described above is that no gas turbine power generation device is provided.
  • the second difference is that the configuration of the exhaust heat recovery boiler apparatus is different. Therefore, the points different from the first, second, third, and fourth embodiments will be mainly described.
  • the solar thermal power generation facility 510 of the fifth embodiment does not include the gas turbine power generation device, the high temperature gas turbine exhaust gas is not supplied to the boiler device 516.
  • the boiler device 516 includes a combustion device 516 that receives fuel and air and burns the fuel.
  • the liquid phase heat medium supplied from the pump 540 is preheated via the economizer 516a and then vaporized via the evaporator 516b by the combustion gas (exhaust gas) generated by the combustion device 516. Further, the gas phase heat medium supplied from the storage tank 528 and the gas phase heat medium supplied from the evaporator 516b are superheated by the exhaust gas via the super heater 516c.
  • the exhaust gas from the combustion device 516 is used for heating the heat medium, and then distributed from the boiler device 516 to the second heating device 514 and the chimney 546.
  • the exhaust gas that has flowed to the second heating device 514 heats the heat medium supplied from the solar field 512.
  • the solar thermal power generation facility 510 of the fifth embodiment is not enlarged in size, as in the case of the solar thermal combined power generation facility 10 of the first embodiment, when the sunshine duration is short, when the direct sunlight intensity is low, and / or Even when the direct sunlight intensity changes abruptly, the heat medium can be sufficiently heated. Thereby, the heat medium can be sufficiently vaporized. As a result, the solar thermal power generation facility 510 can generate sufficient power.
  • the sixth embodiment is a solar thermal composite thermoelectric supply facility that includes a plurality of power generation sources and can supply heat.
  • FIG. 12 conceptually shows the configuration of the solar thermal composite thermoelectric supply facility according to the sixth embodiment.
  • the solar thermal composite thermoelectric supply facility 610 of the sixth embodiment includes a solar field 612, a second heating device 614, and a diesel power generation device 662 as heat medium supply devices that supply a vapor phase heat medium to the steam turbine power generation device 618. It has a heat medium supply device. Moreover, it has the heat exchanger 664 which warms water using the exhaust heat of the diesel generator device 662.
  • the solar feed 612, the second heating device 614, and the steam turbine power generation device 618 are the same as those in the first, second, third, fourth, and fifth embodiments described above.
  • the diesel generator 662 has a diesel engine 662a and a generator 662b driven by the diesel engine 662a.
  • the diesel engine 662a receives the supply of fuel to drive the generator 662b and supplies high-temperature exhaust gas to the second heating device 614.
  • the heat exchanger 664 is configured to exchange heat between engine cooling water that has become a high temperature state by cooling the diesel engine 662a and another water. Thereby, warm water can be obtained.
  • the solar thermal complex thermoelectric supply facility 610 of the sixth embodiment is not enlarged, and when the sunshine duration is short, when the direct sunlight intensity is low, and Even if the direct sunlight intensity changes abruptly, the heat medium can be sufficiently heated. Thereby, the heat medium can be sufficiently vaporized. As a result, the solar thermal composite thermoelectric supply facility 610 can generate sufficient power. Moreover, heat (hot water) can be supplied.
  • the seventh embodiment is a solar thermal composite thermoelectric supply facility that includes one power generation source and can supply cold air.
  • FIG. 13 conceptually shows the configuration of the solar thermal composite thermoelectric supply facility according to the seventh embodiment.
  • the solar thermal composite thermoelectric supply equipment 710 according to the seventh embodiment includes a heat medium supply device including a solar field 712, a second heating device 714, and a gas turbine power generation device 720 as a heat medium supply device that supplies a gas phase heat medium.
  • a water supply type refrigerator 766 that receives supply of a gas phase heat medium from the heat medium supply device is provided.
  • the solar feed 712 and the second heating device 714 are the same as those of the above-described first, second, third, fourth, fifth and sixth embodiments, and the exhaust heat recovery boiler device 716 and the gas turbine power generation device 720 are the same as those described above. Are the same as those of the first, second, third, and fourth embodiments.
  • the gas phase heat medium that has passed through the solar field 712, the second heating device 714, and the exhaust heat recovery boiler device 716 is used not to generate power but to generate cold air. Therefore, an absorption refrigerator 766 that generates cold air using a high-temperature gas phase heat medium is provided.
  • the solar thermal complex thermoelectric supply facility 710 of the seventh embodiment is not enlarged, when the sunshine time is short, when the direct sunlight intensity is low, and Even if the direct sunlight intensity changes abruptly, the heat medium can be sufficiently heated. Thereby, the heat medium can be sufficiently vaporized. As a result, the solar thermal composite thermoelectric supply facility 710 can generate sufficient power. Moreover, cold air can be supplied.
  • the present invention is applicable to any solar thermal power generation facility and solar thermal power generation method that generate power using a heat medium heated by solar heat.
  • the heat medium supply device and the heat medium heating device according to the present invention are applicable to any facility that requires a gas phase heat medium.
  • a gas phase heat medium obtained by the heat medium supply device and the heat medium heating device according to the present invention can be used as a drive source of a turbo compressor that generates compressed air or as a heat source of a dryer.
  • Solar thermal power generation facility (solar thermal combined power generation facility) 12 First heating device (solar field) 14 Second heating device 18 Turbine power generation device (steam turbine power generation device)

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)
  • High Energy & Nuclear Physics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention se rapporte à une installation (10) de production d'énergie thermique solaire qui utilise un milieu caloporteur subissant un changement de phase entre une phase liquide et une phase gazeuse. L'installation (10) de production d'énergie thermique solaire comprend : un premier dispositif de chauffage (12) qui chauffe le milieu caloporteur à l'aide de chaleur solaire qui est une première chaleur ; un second dispositif de chauffage (14) qui augmente le rapport de la phase gazeuse dans le milieu caloporteur grâce au chauffage du milieu caloporteur à l'aide d'une seconde chaleur différente de la chaleur solaire, une fois que le milieu caloporteur a été chauffé par le premier dispositif de chauffage (12) ; et un générateur de puissance à turbine (18) entraîné par le milieu caloporteur qui a été chauffé par le second dispositif de chauffage (14). Le second dispositif de chauffage (14) est configuré de telle sorte que la chaleur retenue par un autre milieu caloporteur est utilisée comme seconde chaleur dans le but de chauffer le premier milieu caloporteur cité.
PCT/JP2011/071268 2011-09-16 2011-09-16 Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur WO2013038563A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2011377040A AU2011377040A1 (en) 2011-09-16 2011-09-16 Solar thermal energy electric power generation system, solar thermal energy electric power generation method, heating medium supplying system, and heating medium heating system
PCT/JP2011/071268 WO2013038563A1 (fr) 2011-09-16 2011-09-16 Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/071268 WO2013038563A1 (fr) 2011-09-16 2011-09-16 Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur

Publications (1)

Publication Number Publication Date
WO2013038563A1 true WO2013038563A1 (fr) 2013-03-21

Family

ID=47882821

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/071268 WO2013038563A1 (fr) 2011-09-16 2011-09-16 Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur

Country Status (2)

Country Link
AU (1) AU2011377040A1 (fr)
WO (1) WO2013038563A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150068205A1 (en) * 2013-09-06 2015-03-12 Kabushiki Kaisha Toshiba Steam turbine plant
WO2016002711A1 (fr) * 2014-07-01 2016-01-07 いすゞ自動車株式会社 Système de récupération de la chaleur perdue

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000161016A (ja) * 1998-11-19 2000-06-13 Takeshi Hatanaka ハイブリッドガスタ―ビンエンジンおよび推進装置
JP2000514149A (ja) * 1996-05-31 2000-10-24 エレクトリック パワー リサーチ インスチテュート インコーポレイテッド 太陽熱および燃料燃焼によるハイブリッド発電システム
JP2004232571A (ja) * 2003-01-31 2004-08-19 Takeo Saito 多種・多重サイクル発電システム
JP2008039367A (ja) * 2006-08-10 2008-02-21 Kawasaki Heavy Ind Ltd 太陽熱発電設備および熱媒体供給設備
JP2008121483A (ja) * 2006-11-10 2008-05-29 Kawasaki Heavy Ind Ltd 熱媒体供給設備および太陽熱複合発電設備なびにこれらの制御方法
WO2011089997A1 (fr) * 2010-01-21 2011-07-28 三菱重工業株式会社 Dispositif de production d'énergie à récupération de chaleur perdue et navire équipé de ce dernier

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000514149A (ja) * 1996-05-31 2000-10-24 エレクトリック パワー リサーチ インスチテュート インコーポレイテッド 太陽熱および燃料燃焼によるハイブリッド発電システム
JP2000161016A (ja) * 1998-11-19 2000-06-13 Takeshi Hatanaka ハイブリッドガスタ―ビンエンジンおよび推進装置
JP2004232571A (ja) * 2003-01-31 2004-08-19 Takeo Saito 多種・多重サイクル発電システム
JP2008039367A (ja) * 2006-08-10 2008-02-21 Kawasaki Heavy Ind Ltd 太陽熱発電設備および熱媒体供給設備
JP2008121483A (ja) * 2006-11-10 2008-05-29 Kawasaki Heavy Ind Ltd 熱媒体供給設備および太陽熱複合発電設備なびにこれらの制御方法
WO2011089997A1 (fr) * 2010-01-21 2011-07-28 三菱重工業株式会社 Dispositif de production d'énergie à récupération de chaleur perdue et navire équipé de ce dernier

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150068205A1 (en) * 2013-09-06 2015-03-12 Kabushiki Kaisha Toshiba Steam turbine plant
JP2015052427A (ja) * 2013-09-06 2015-03-19 株式会社東芝 蒸気タービンプラント
WO2016002711A1 (fr) * 2014-07-01 2016-01-07 いすゞ自動車株式会社 Système de récupération de la chaleur perdue

Also Published As

Publication number Publication date
AU2011377040A1 (en) 2014-05-01

Similar Documents

Publication Publication Date Title
WO2013098945A1 (fr) Appareil de production d'énergie solaire thermique
US8286429B2 (en) Solar hybrid combined cycle gas and steam power plant
JP5399565B2 (ja) 太陽熱利用コンバインドサイクル発電プラント
KR102030642B1 (ko) 태양 원천의 열 에너지의 저장 및 사용에 대한 에너지 효율성의 수준을 높이기 위한 장치, 시스템 및 방법
JP6340473B2 (ja) 太陽エネルギ及びバイオマスエネルギ一体型発電最適化結合システム
JP5602306B2 (ja) 太陽熱ボイラおよびそれを用いた太陽熱発電プラント
JP6223955B2 (ja) 太陽熱発電システム
US9638173B2 (en) Solar thermal power system
US20120240577A1 (en) Thermal generation systems
JP2011117447A (ja) 太陽エネルギーを用いた発電システム
US20130086904A1 (en) Solar Thermal Power Plant
US20130139807A1 (en) Thermal energy generation system
WO2010092584A1 (fr) Systèmes thermiques solaires
WO2013065492A1 (fr) Dispositif générateur d'électricité à turbine à chaleur solaire et procédé de commande pour ce dispositif
CN105247208B (zh) 具有蓄热器的太阳能集热器厂
WO2013038563A1 (fr) Installation de production d'énergie thermique solaire, procédé de production d'énergie thermique solaire, dispositif d'alimentation en milieu caloporteur et dispositif de chauffage de milieu caloporteur
US20150082792A1 (en) Solar and renewable/waste energy powered turbine with two stage heating and graphite body heat exchanger
WO2010067359A2 (fr) Systeme d'energie solaire a boucle fermee equipe d'un generateur electrique a poussoir
EP3055562B1 (fr) Procédé de chauffage contrôlé d'un fluide de traitement par le biais d'une centrale solaire thermique à concentration et d'un système caloporteur et appareil associé
JP6600605B2 (ja) 太陽熱発電システム及び太陽熱発電方法
JP2012127577A (ja) 太陽熱集熱装置およびその集熱量調整方法
WO2014065158A1 (fr) Installation de génération d'énergie combinée
JP2017101578A (ja) 複合タービンシステム及びその発電方法
Kalbhor Modified solar central receiver in concentrated solar power systems
Yang et al. Sanchez, M., Santana, D. & Pei, G.(2020). Performance investigation of solar tower system using cascade supercritical carbon dioxide Brayton-steam Rankine cycle. Energy Conversion and Management, 225, 113430.

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: 11872353

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2011377040

Country of ref document: AU

Date of ref document: 20110916

Kind code of ref document: A

122 Ep: pct application non-entry in european phase

Ref document number: 11872353

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP