• 专利附录
  • 专利说明
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    • 专利摘要:
    High efficiency solar power plant and its operating procedure. High efficiency solar power plant comprising a closed and regenerative main brayton cycle (14) that works with a supercritical fluid and at least one closed tail cycle, which can be a rankine cycle (15) or a brayton cycle (16). The main brayton cycle (14) comprises a heat source comprising a solar receiver (1), an expander (2), a generator (3) of electric current, a primary heat recuperator (4), optionally a heat exchanger (5), a secondary heat recovery unit (6), a refrigerator (7), a compressor (8) and a pump (9). In a preferred embodiment, a tail rankine cycle (15) is connected to the main cycle (14) through the heat exchanger (5), while a tail brayton cycle (16) is connected to the main cycle (14). ) by means of the primary heat recovery unit (4). (Machine-translation by Google Translate, not legally binding)
    公开号:ES2595552A1
    申请号:ES201530754
    申请日:2015-05-29
    公开日:2016-12-30
    发明作者:Irene ORDÓÑEZ BARREIRO
    申请人:Abengoa Solar New Technologies SA；
    IPC主号:
    专利说明:

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    HIGH EFFICIENCY SOLAR POWER PLANT AND ITS PROCEDURE
    FUNCTIONING
    Technical sector of the invention
    The present invention relates to a high efficiency solar power plant and its operating procedure for solar applications by using fluids, at least one of them in supercritical conditions.
    Background of the invention
    At present, the development of supercritical cycle plants of both CO2 and steam is being deepened. The main advantage of these cycles is the high temperature and pressure at the turbine inlet, which increases the overall efficiency of the cycle. In this line the integration of solar thermal technology in supercritical cycles is being studied. In previous developments, although not particularly for solar applications, is US2013 / 0269334 patent where a combination of Brayton and Rankine cycles is presented. Both in the Brayton cycle, which uses supercritical CO2, and in the Rankine cycle, which uses superheated steam, the heat input comes from the same external source by using at least one heat exchanger. The heat source consists of the exhaust gases of a conventional gas turbine and the heat supplied comes exclusively from fossil fuels. With respect to the supercritical CO2 cycle, the pressure increase is carried out using exclusively compressors.
    In the field of solar-gas hybridization of supercritical CO2 cycles is US2013 / 0118145. The proposed supercritical CO2 cycle consists of a simple regenerative Brayton cycle. The heat input is made firstly in a solar receiver and secondly in a natural gas combustor, using solar energy to supplement combustion. In case the solar radiation is not enough or void the operation will be 100% gas. This invention includes a single turbine, in which the working fluid will be supercritical CO2, so that the efficiency obtained will be lower than the case proposed in the present invention, where a supercritical tail Rankine cycle is incorporated.
    A development related to the integration between solar energy and combined cycles is described in US2011 / 0233940. This configuration consists of a combined cycle where solar energy is incorporated following different schemes. In a first scheme the solar contribution is integrated both in the open Brayton cycle and in the
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    Rankine independently. In the second and third cases both receivers are interconnected. Finally, in the fourth case, solar energy is used exclusively in the Brayton cycle. In this case the Brayton cycle is not regenerative, that is, none of the energy available in the exhaust gases is used to preheat the entrance to the same Brayton cycle. Another limitation is found in the type of fluid to be used; as there is no pump after the compressor, the use of supercritical fluids in the Brayton cycle is limited. In this same area, the integration of solar energy in combined cycles, is the patent ES2480915A1. As in the previous invention, the heat input is performed sequentially: first in a solar receiver and then in a combustion chamber, however, this case also presents the limitation in the type of fluid to be used in the Brayton cycle, not allowing the use of supercritical fluids.
    The solution described in the present invention consists of a plant configuration whose purpose is, on the one hand, to be able to operate at partial load with 100% solar input (and provided there is sufficient radiation), being able in that case to be independent of the fuel supply fossils (only used in auxiliary boiler for specific cases of transients, that is, passing clouds etc.) and, on the other hand, to maximize production without reducing the efficiency of the plant.
    Description of the invention
    The high efficiency solar power plant consists of at least two cycles for the production of electrical energy: a closed and regenerative main Brayton cycle whose working fluid is a supercritical fluid and at least one tail cycle, which can be a Brayton cycle or a closed Rankine cycle that employs a working fluid that may be the same or different from the working fluid of the main Brayton cycle.
    The main Brayton cycle consists of the following elements: at least one heat source comprising a solar receiver to increase the temperature of its previously compressed supercritical working fluid, an expander connected to the heat source configured to convert the thermal energy contained in the supercritical fluid into mechanical energy, a generator that converts said mechanical energy into electrical energy, a primary recuperator of the thermal energy contained in the exhaust gases of the expander, a secondary recuperator located after the primary heat recuperator to take advantage of the fluid energy . Next to the secondary recuperator, there is a refrigerator where the fluid is cooled to room temperature, a compressor and a pump that allows the fluid to be boosted again (already in liquid state) to the heat source.
    Both the primary and secondary recuperators are heat exchangers that
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    They allow heat transfer between fluids.
    Optionally, the main Brayton cycle may include a heat exchanger between the primary recuperator and the secondary recuperator, said exchanger being configured to exchange heat between the output current of the primary recuperator and a working fluid of a tail cycle.
    The fact of using a supercritical fluid has the advantage that, when compressed, it has liquid properties and can be easily boosted with a pump, which implies energy savings when compared to the energy required to compress and drive a gas. Therefore, the pump used allows to reduce the self-consumption of the plant. Also, when using a fluid in supercritical conditions, the energy available at the inlet of the expander is greater than the energy of the same fluid in non-supercritical conditions, allowing to increase both the power and efficiency obtained in the cycle.
    In the main Brayton cycle, the expander is an independent equipment to the compressor, the main difference with the gas turbines where the same housing envelops the compressor and expander, and that necessarily has a combustion chamber. This plant is, therefore, conceived in its main Brayton cycle without a gas turbine and, therefore, without a combustion chamber, being replaced by an expander and a compressor, which allows it to operate in conditions of sufficient radiation with 100% solar input. and reduce as! greenhouse gas emissions. As it is also a closed cycle, it reduces the electrical self-consumption of the cycle, as it does not have to compress the working fluid from ambient pressure conditions, but from the pressure conditions of the expander. In addition, the exhaust gases of the expander have a double function: the first function is to preheat the fluid before entering the receiver, thus recovering! part of the energy contained at the exit of the expander having as! to perform a lower heating in the solar receiver to reach the desired temperature, which translates into smaller solar fields and lower costs; and a second function that is to heat the fluid of at least one tail cycle, which allows to increase the production. On the other hand, the use of fluids in supercritical conditions increases the overall efficiency of the system. Optionally, the heat source comprising a solar receiver can also include an auxiliary heat source located parallel to the solar receiver, in this way the plant allows the cycle to be operated in the moments in which the radiation is insufficient or zero to avoid stops in the operation of the plant. This heat source may be a combustion chamber, but it is not limited to this equipment.
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    exclusively, as we have mentioned an auxiliary support team only for certain circumstances.
    The tail cycle could be a Brayton cycle or a Rankine cycle, using a working fluid equal to or different from the main Brayton cycle fluid. In the event that the plant includes a Rankine tail cycle, the main Brayton cycle will include a heat exchanger between the primary and secondary recuperator, as discussed above. The Rankine tail cycle will consist of at least the following elements: a heat exchanger that shares with the main Brayton cycle, said element being the connection point between both cycles, a turbine to convert the thermal energy contained in the working fluid of the Rankine tail cycle in mechanical energy, an electricity generator connected to the turbine to convert said mechanical energy into electric energy, a refrigerator located next to the turbine and a pump that drives the fluid of the Rankine tail cycle from the refrigerator to the heat exchanger.
    In the heat exchanger, the supercritical fluid of the main Brayton cycle yields its thermal energy to the fluid of the Rankine tail cycle, then said heat exchanger constitutes a source of heat for said tail cycle.
    Optionally, the Rankine tail cycle may include a source of heat comprising a solar receiver, said source being located between the heat exchanger and the turbine to make an extra supply of heat to the fluid.
    In the event that the plant includes a tail Brayton cycle, the working fluid will also be a supercritical fluid, which may be the same or different from that used in the main Brayton cycle. In the case of having a Brayton tail cycle, the primary recuperator of the main Brayton cycle will be the element that connects both cycles. In the primary recuperator, the supercritical fluid of the main Brayton cycle gives heat to the supercritical fluid of the tail Brayton cycle.
    This tail Brayton cycle comprises a new expander, optionally it can include a solar receiver before and / or after the primary recuperator to complement the heat input and will also include at least one refrigerator, a heat recuperator located between the expander and the refrigerator, said recuperator being configured to receive the exhaust gases from the expander and to preheat the tail Brayton cycle fluid before entering the primary recuperator, a compressor and a pump.
    Optionally, in the supercritical fluid cycles, intermediate cooling may be performed in the compression train, that is, optionally there may be at least
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    an intermediate refrigerator between the compressor and the pump or additional cooling within the body of the compressor itself.
    In the event that the plant comprises two tail cycles, these will preferably be a Brayton cycle and a Rankine cycle that will comprise the elements mentioned above for each of them.
    In the described plant, either with a single tail cycle or with two tail cycles connected to the main cycle, the fluid that circulates through the solar receiver in each of the cycles can be the same that is subsequently expanded in the expander or in the turbine, that is, the fluid that circulates through each solar receiver is the working fluid of each cycle in question. Another option is to use solar receivers through which thermal storage materials circulate (either thermal storage fluids, solid particles and / or carbonated salts) that transfer their thermal energy through heat exchangers to the working fluid that circulates through each of cycles . In this case, the different sources of heat will include, in addition to a solar receiver to heat a thermal storage material, a thermal storage system connected to the solar receiver and a heat exchanger connected to the storage system configured said exchanger to heat the working fluid of the cycle in question from the thermal storage material.
    The storage of heat in a fluid other than the working fluid of the tail cycles allows storage at lower pressures, which translates into lower technical risks, as well as lower costs.
    The operating procedure of the plant for the production of electric energy comprises at least the following stages:
    - heating of the working fluid of the previously compressed Brayton main cycle; said heating occurs by means of a heat source comprising a solar receiver. The heating can be carried out directly or indirectly by means of solar energy; directly in the solar receiver or indirectly through a heat storage material previously heated with solar energy in the solar receiver;
    - conduction of the previously heated fluid to an expander that converts the thermal energy contained in the working fluid into mechanical energy, which is transformed into electric energy in a generator;
    - the flow of fluid (or exhaust gases) at the outlet of the expander is passed through a primary recuperator where the fluid loses part of its thermal energy,
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    transferring it either to the working fluid of the main Brayton cycle before entering the heat source or to a working fluid of a Brayton tail cycle,
    - optionally the working fluid stream of the main Brayton cycle at the outlet of the primary recuperator is passed through the heat exchanger where part of its thermal energy is transferred to a working fluid of a Rankine tail cycle;
    - Next, the fluid flow is passed through the secondary recuperator where it again loses part of its thermal energy, thereby preheating the working fluid of the main Brayton cycle before entering the heat source,
    - thereafter, the fluid is conducted after the secondary recuperator exits to a refrigerator, then to a compressor and from the compressor, already in a liquid state, the fluid is pumped to the heat source to start the cycle again.
    Then, in the main Brayton cycle, the flow of the working fluid of said cycle leaving the expander is cooled until it enters the liquid state in the compressor, which allows said fluid to be pumped to the heat source comprising a solar receiver. The heat yielded by the fluid stream when cooled is used to preheat the working fluid of said Brayton cycle before entering the heat source or to heat the working fluid of a tail cycle.
    As mentioned above, in the event that the main Brayton cycle comprises a heat exchanger, this will constitute the heat source of a Rankine tail cycle, since in said heat exchanger the working fluid of the main Brayton cycle yields heat to the working fluid of the Rankine tail cycle. In the case where the main cycle is connected to a Rankine tail cycle through the heat exchanger, the working fluid of the tail cycle is directed from the heat exchanger to a turbine and a generator for the production of electricity. The working fluid flow of the Rankine tail cycle (exhaust gases) at the outlet of the turbine is passed through a refrigerator and from there it is pumped back into the heat exchanger.
    Optionally, before entering the turbine, the working fluid of the Rankine tail cycle can be passed through a heat source comprising a solar receiver. In this case, the heating can be carried out directly or indirectly by means of solar energy; directly in a solar receiver or indirectly through an intermediate fluid or heat storage material previously heated with
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    Solar energy in the solar receiver.
    In the event that the heat input to the working fluid of both the main Brayton cycle and the Rankine tail cycle is done indirectly, the procedure would include an additional stage of heating a thermal storage material (eg a thermal storage fluid, carbonated salts or solid particles) to later be directed to a heat exchanger where the heating of the working fluid of each one of the cycles takes place.
    In the event that the main Brayton cycle is connected to a tail Brayton cycle that also uses a supercritical fluid, the primary recuperator of the main Brayton cycle constitutes a source of heat for the tail Brayton cycle, so that, in said recuperator , the supercritical fluid of the main Brayton cycle yields energy to the supercritical fluid of the tail Brayton cycle.
    Subsequently, in the Brayton tail cycle, the supercritical fluid expands in an expander connected to a generator for the production of electricity. The fluid flow at the outlet of the expander is passed through a heat regenerator. After the heat regenerator, the fluid is passed through a refrigerator and a compressor and from there it is pumped to the primary recuperator, which is where the transfer of thermal energy takes place from the working fluid of the main Brayton cycle to the working fluid of the Brayton tail cycle.
    Optionally, before arrival at the primary recuperator, the tail Brayton cycle fluid is heated in a heat source that includes a solar receiver.
    Finally, in the event that the plant includes two tail cycles (one Brayton and one Rankine), in addition to the main one, the operation procedure of the plant will include the stages of the three cycles as described above.
    Brief description of the drawings
    Figure 1. Schematic representation of an example of a solar power plant with two power cycles: a supercritical Brayton main cycle and a Rankine tail cycle.
    Figure 2. Schematic representation of an example of a solar power plant with three supercritical power cycles: a main Brayton cycle and a Rankine tail cycle and a Brayton tail cycle
    Figure 3. Schematic representation of an example of a solar power plant with three power cycles as in the previous case (figure 2), but with indirect solar energy input.
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    Figure 4. Schematic representation of an example of a solar power plant with two power cycles: a supercritical Brayton main cycle and a supercritical Brayton tail cycle.
    The following elements are listed in correspondence with the figures:
    I, 1 ’, 1’ .- Solar receivers
    2, 2 ’‐ Supercritical CO2 expander
    3, 3 ’, 3” .- Electric current generators
    4, - Primary recuperator 42.- Heat regenerator
    5, - Heat exchanger
    6, - Secondary recovery
    7, 7 ’, 7’ ‐ Refrigerators
    8, 8 ”.- Compressors
    9, 9 ’, 9” - Pumps
    10, - Auxiliary heat source
    II. -Steam turbine
    12,12 ’, 12’ ’.- Heat exchangers connected to a solar receiver 13,13’, 13 ”.- Thermal storage system
    14. - Main Brayton Cycle
    15. - Rankine tail cycle
    16. - Brayton tail cycle Description of a preferred realization
    In order to achieve a greater understanding of the invention, four preferred embodiments of the power plant of the present invention are described below based on the figures presented.
    In a first preferred embodiment, the plant includes a main Brayton cycle (14) of supercritical CO2 consisting of a simple, closed and regenerative Brayton cycle, and a Rankine tail cycle (15) whose working fluid is steam, well superheated steam or supercritical steam (15), where the thermal input comes from the main Brayton cycle (14) of supercritical CO2. Said preferred embodiment is represented in Figure 1.
    The heat input in the main cycle (14) is carried out in a heat source comprising a solar receiver (1), (preferably a central solar receiver tower system). In parallel to the solar receiver (1) an auxiliary heat source (10) is included, which could be a combustion chamber or a fuel cell although
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    limited to it. This auxiliary heat source (10) will be used to avoid plant shutdowns when the radiation is not sufficient to maintain the operation. The supercritical CO2 expander (2) connected to the electric current generator (3) receives, for the production of electricity, the fluid from the heat source (1 or 10) at a temperature between 700 and 1200 ° C, preferably higher than 750 ° C and pressure greater than 200 bar. The energy contained in the output current of the expander (2), that is, in the exhaust gases of the cycle, is used in the primary recuperator (4), thus preheating the CO2 before entering the heat source ( 1 or 10). At the outlet of the primary recuperator (4), the fluid is at a temperature around 600 ° C and pressure between 20 and 60 bar and is passed through the heat exchanger (5), which will be the source of Rankine tail cycle heat. After the heat exchanger (5), the main cycle fluid (14) is passed through a secondary recuperator (6) where part of its thermal energy yields, thereby preheating the CO2 before entering the heat source (1 or 10). After the secondary recuperator (6), the fluid is passed through a refrigerator (7) and a compressor (8). In the refrigerator (7) the necessary heat is extracted to ensure the conditions of entry to the compressor (8), these conditions are of a temperature around 25 ° C and pressure between 20 and 60 bar. Given the supercritical characteristics of the working fluid of the main cycle (14), a pump (9) is integrated into the process after the compressor. The pressure at the pump outlet will be greater than 200 bar. In order to preheat it, the pumped fluid is passed back through the secondary recuperator (6) and the primary one (4) entering it at an approximate temperature of 250 ° C and pressure between 200 and 300 bar; finally, it is directed to the heat source (1 or 10) to start the cycle again.
    As for the Rankine tail cycle (15), the thermal input is made in the heat exchanger (5). An additional body can optionally be included in the heat exchanger (5) for reheating by this. To complement the thermal contribution of steam, a solar receiver (1 ’) located after the heat exchanger (5) can be included. The steam can be turbinated in superheated steam or supercritical steam conditions. In the case of supercritical steam conditions, the steam that leaves the solar receiver (1 ') at temperature conditions between 600 ° C and 900 ° C, and pressure equal to or greater than 200 bar is expanded in a steam turbine (11) connected to an electric current generator (3 '). The steam stream from the turbine (11) (exhaust gases) is passed through a refrigerator (7 ’) where the heat needed to condition the air is extracted.
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    steam at the necessary conditions for the pump inlet (9 ’): approximate temperature of 25 ° C and pressure equal to or less than 0.14 bar.
    In a second preferred embodiment depicted in Figure 2, the primary recuperator (4) of the main Brayton cycle (14) is used to heat the working fluid of a Brayton tail cycle (16) consisting of a simple regenerative Brayton cycle that works with supercritical CO2, where the CO2 is heated in the primary recuperator (4) to a temperature between 700 ° C and 900 ° C and at a pressure greater than 200 bar and will be directed to a supercritical CO2 expander (2 '') connected to an electric current generator (3 '') for the production of electricity. At the exit the expander (2 ''), the CO2 current that is at a temperature in an approximate range of 500-600 ° C and pressure between 20-30 bar, is passed through a heat regenerator (42) to heat the input current to the primary recuperator (4). From the heat regenerator (42), the fluid stream is directed to the refrigerator (7 ”) where the necessary heat is extracted up to a temperature around 25 ° C and pressure between 20-30 bar. From there, it goes to the compressor (8 ”) and to the pump (9”) that drives the fluid flow to the primary recuperator (4) previously passing through the heat regenerator (42) where the fluid is preheated. Optionally, before the primary recuperator (4), a solar receiver (1 ”) is included to preheat the fluid to a temperature around 600 ° C and a pressure greater than 200 bar.
    In a third preferred embodiment represented in Figure 3, the heat sources include, in addition to the solar receivers (1, 1 'and 1 "), heat exchangers connected to said solar receivers (12, 12' and 12") . In this case, the working fluid of the different cycles circulates through the heat exchangers (12, 12 'and 12 ”), while a heat storage material circulates through the solar receivers (1, 1' and 1”) (be it fluid, molten metals, solid particles, etc.), which will be the one that, once heated with solar energy, yields heat to the working fluid of the cycles in the corresponding heat exchanger (12, 12 'and 12 "). The storage material can be stored in a storage system (13,13 ', 13' ') located between the corresponding solar receiver (1, 1' and 1 ”) and the corresponding heat exchanger (12, 12 'and 12 ").
    In the solar receiver (1) of the main Brayton cycle (14), the heat storage material is heated to temperature conditions above 750 ° C and pressure equal to or less than 30 bar. Said material gives heat to the working fluid of the main Brayton cycle (supercritical CO2), so that said working fluid enters the expander (2) at a temperature greater than 750 ° C and pressure greater than 200 bar.
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    In the Rankine glue cycle (15), in the case where the working fluid is supercritical steam, the heat storage material is heated to a maximum temperature of 800 ° C and pressure equal to or less than 30 bar in the solar receiver (1 ') to later be directed to the exchanger (12') where supercritical steam overheating occurs from a temperature higher than 550 ° C and pressure greater than 200 bar to a maximum temperature of 750 ° C and a pressure greater than 200 bar, turbine inlet conditions (11).
    In the Brayton cycle of supercritical CO2 glue, the storage material is heated in the solar receiver (1 ”) to a maximum temperature of 600 ° C and a pressure lower than 30 bar, to be subsequently directed to the exchanger (12”) where Preheating of supercritical CO2 takes place up to a temperature of 600 ° C and a pressure of 200 bar, before entering the primary recuperator (4). The CO2 of the Brayton tail cycle is heated in the primary recuperator (4) to a temperature between 700 ° C and 900 ° C and at a pressure greater than 200 bar and is subsequently directed to a supercritical CO2 expander (2 '') connected to an electric current generator (3 '') for the production of electricity. At the outlet of the expander (2 ''), the CO2 current that is at a temperature in an approximate range of 500-600 ° C and pressure between 20-60 bar, is passed through a heat regenerator (42) before entering either the solar receiver, or the primary recuperator.
    In a fourth preferred embodiment represented in Figure 4, the plant is constituted by a main Brayton cycle of supercritical CO2 (14), and a Brayton tail cycle of supercritical CO2 (16). The primary recuperator (4) of the main Brayton cycle (14) is used to heat the working fluid of the tail Brayton cycle (16) consisting of a simple closed and regenerative Brayton cycle, where the CO2 of the tail Brayton cycle is heated in The primary recuperator (4) up to a temperature between 700 ° C and 900 ° C and at a pressure greater than 200 bar and is directed to a supercritical CO2 expander (2 '') connected to an electric current generator (3 '' ) for the production of electricity. At the outlet of the expander (2 ''), the CO2 current that is at a temperature in an approximate range of 500-600 ° C and pressure between 20-60 bar, is passed through a heat regenerator (42) to heat the input current to the primary recuperator (4). From the heat regenerator (42), the fluid stream is directed to the refrigerator (7 ”) where the necessary heat is extracted up to a temperature around 25 ° C and pressure between 20-60 bar. From here it goes to the compressor (8 ”) and the pump (9”) that drives the fluid flow to the primary recuperator
    (4) previously passing through the heat regenerator (42) where the fluid is preheated. Optionally, and for non-nominal operating conditions, before the primary recuperator (4), a solar receiver (1 ”) is included to preheat the fluid to a temperature around 600 ° C and a pressure greater than 200 5 Pub.
    At the exit of the primary recuperator (4), the CO2 of the main Brayton cycle of supercritical CO2 (14) crosses the secondary recuperator (6) to yield part of its thermal energy and preheat the supercritical CO2 current before entering the source of heat (1 or 10).
    10 In this preferred embodiment, the heat exchanger (5) and the cycle are dispensed with
    tail Rankine (15).
    权利要求:
    Claims (26)
    [1]
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    1. - High efficiency solar power plant for the production of electric energy characterized in that it comprises:
    i) a closed and regenerative main Brayton cycle (14), which employs a supercritical working fluid and
    ii) at least one closed tail cycle, selected between a Rankine cycle (15) and a Brayton cycle (16), and where the main Brayton cycle (14) comprises the following elements:
    - at least one heat source comprising a solar receiver (1) to increase the temperature of the working fluid of the main Brayton cycle,
    - an expander (2) connected to the heat source and configured to convert the thermal energy contained in the working fluid of the main Brayton cycle into mechanical energy,
    - an electric current generator (3) connected to the expander (2) to convert said mechanical energy into electric energy,
    - a primary heat recuperator (4) configured to receive the exhaust gases from the expander (2),
    - a secondary heat recuperator (6) located after the primary heat recuperator (4)
    - a refrigerator (7) located next to the secondary recuperator (6),
    - a compressor (8) arranged behind the refrigerator (7) and
    - a pump (9) configured to push the working fluid of the main Brayton cycle (14) back to the heat source.
    [2]
    2. - High efficiency solar power plant according to revindication 1 characterized in that the main Brayton cycle (14) comprises a heat exchanger (5) located between the primary heat recuperator (4) and the secondary heat recuperator (6) and The solar power plant comprises a Rankine tail cycle (15) that uses steam as a working fluid, selected from supercritical steam and superheated steam, and that shares the heat exchanger (5) with the main Brayton cycle (14) of the plant, said heat exchanger (5) being the element that connects both cycles and where the tail Rankine cycle (15) also comprises:
    - a turbine (11) to convert the thermal energy contained in the working fluid of the Rankine tail cycle (15) into mechanical energy,
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    - an electric current generator (3 ’) connected to the turbine (11) to convert said mechanical energy into electric energy,
    - a refrigerator (7 ’) located next to the turbine (11) and
    - a pump (9 ’) that drives the Rankine tail cycle fluid (15) from the refrigerator (7’) to the heat exchanger (5).
    [3]
    3. - High efficiency solar power plant according to claim 1 characterized in that the heat source comprising a solar receiver (1) also includes an auxiliary heat source (10) located parallel to the solar receiver (1).
    [4]
    4. - High efficiency solar power plant according to claim 3 characterized in that the auxiliary heat source (10) is a combustion chamber.
    [5]
    5. - High efficiency solar power plant according to claim 2 characterized in that the tail Rankine cycle (15) includes a heat source comprising a solar receiver (1 ') located between the heat exchanger (5) and the turbine ( eleven).
    [6]
    6. - High efficiency solar power plant according to claim 1 characterized in that the plant comprises a tail Brayton cycle (16) which uses a supercritical fluid as a working fluid and shares the primary recuperator (4) with the main Brayton cycle ( 14), said primary recuperator (4) being the element that connects both cycles and where the tail Brayton cycle (16) further comprises:
    - an expander (2 ”) to convert the thermal energy contained in the working fluid of the tail Brayton cycle (16) into mechanical energy,
    - an electric current generator (3 ") connected to the expander (2") to convert said mechanical energy into electric energy,
    - a heat regenerator (42) configured to receive the working fluid current of the tail Brayton cycle (16) at the outlet of the expander (2 ”) and preheat the working fluid of the tail Brayton cycle (16) before your entry in the primary recuperator
    (4),
    - a refrigerator (7 ”) located next to the heat regenerator (42)
    - a compressor (8 ”) arranged behind the refrigerator and
    - a pump (9 ”) configured to push the working fluid of the tail Brayton cycle (16) back to the primary recuperator (4).
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    [7]
    7. - High efficiency solar power plant according to claim 6 characterized in that the tail Brayton cycle (16) includes a heat source comprising a solar receiver (1 ") configured to heat the working fluid before entering the primary recuperator (4).
    [8]
    8. - High efficiency solar power plant according to claim 2 characterized in that it comprises the Brayton tail cycle (16) described in claim 6.
    [9]
    9. - High efficiency solar power plant according to claim 2, 6 or 8 characterized in that the heat sources include, in addition to a solar receiver (1, 1 ', 1 ") for heating a thermal storage material, a system of thermal storage (13, 13 ', 13 ") connected to the solar receiver (1, 1, 1") and a heat exchanger (12,12', 12 ") connected to the thermal storage system (13, 13 ', 13 ") said exchanger (12,12 ', 12") configured to heat the working fluid of each of the cycles from the thermal storage material.
    [10]
    10. - Operating procedure of the plant described in claim 1 for the production of electric energy, characterized in that it comprises at least the following steps:
    - heating of the working fluid of the main Brayton cycle (14) previously compressed; said heating is produced by means of a heat source comprising a solar receiver (1);
    - conduction of said previously heated working fluid to an expander (2) that converts its thermal energy into mechanical energy, which is transformed into electric energy into a generator (3);
    - the fluid flow at the outlet of the expander (2) is passed through a primary heat recuperator (4) where the fluid loses part of its thermal energy;
    - subsequently, the flow of the fluid is passed through the secondary heat recuperator (6) where it again loses part of its thermal energy, thereby preheating the fluid before entering the heat source,
    - the fluid is conducted after the secondary recuperator (6) exits to the refrigerator (7), then to the compressor (8) and from the compressor (8), already in a liquid state, the fluid is pumped to the heat source to start the cycle again
    5
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    twenty
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    35
    [11]
    11. - Procedure of operation of the plant, according to claim 10, characterized in that:
    - the fluid stream at the outlet of the primary recuperator (4) is passed through a heat exchanger (5) so that the fluid of the main Brayton cycle (14) gives energy to the working fluid of a Rankine tail cycle ( 15) that uses steam selected from superheated steam and supercritical steam as a working fluid; - Once the working fluid of the Rankine tail cycle (15) in the primary recuperator (4) has been heated, said fluid is conducted to the turbine (11) connected to the generator for the production of electricity;
    - the working fluid stream of the Rankine tail cycle (15) at the outlet of the turbine (11) is passed through the refrigerator (7 ’) and from there it is pumped back to the steam generator (5).
    [12]
    12. - Procedure of operation of the plant, according to claim 11,
    characterized in that the working fluid of the main Brayton cycle (14) is preheated
    in the primary recuperator (4) before entering the heat source by taking advantage of the heat lost by said fluid from the main Brayton cycle (14) at the outlet of the expander (2).
    [13]
    13. - Procedure of operation of the plant, according to claim 11,
    characterized in that the Rankine tail cycle (15) includes an additional stage in which the working fluid of the Rankine tail cycle (15) at the exit of the heat exchanger (5) and before entering the turbine (11) is heats in a heat source comprising a solar receiver (1 ').
    [14]
    14. - Procedure of operation of the plant, according to claim 10,
    characterized because
    - the working fluid of a Brayton tail cycle (16) that uses a supercritical fluid (16) as the working fluid is heated in the primary recuperator (4) by harnessing the heat lost by the working fluid of the main Bryton cycle (14),
    - the working fluid of the heated Brayton tail cycle (16) is directed to the expander (2 ”) which converts the thermal energy contained in said working fluid of the Brayton tail cycle (16) into mechanical energy, which is transformed into electric energy in the electric current generator (3 ”);
    5
    10
    fifteen
    twenty
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    35
    - the fluid stream of the tail Brayton cycle (16) at the outlet of the expander (2 ”) is passed through the heat regenerator (42) where heat yields which is used by said working fluid of the tail Brayton cycle ( 16) before entering the primary recuperator (4),
    - the working fluid stream of the Brayton tail cycle (16) at the outlet of the heat regenerator (42) is passed through the refrigerator (7 ”) and the compressor (8”) and from there it is pumped to the recuperator primary (4).
    [15]
    15. - Procedure of operation of the plant, according to claim 14,
    characterized in that the fluid stream of the tail Brayton cycle (16) is heated in a heat source that includes a solar receiver (1 ”) before entering the primary recuperator (4).
    [16]
    16. - Procedure of operation of the plant, according to claim 11,
    characterized in that it also includes the stages of the tail Brayton cycle (16) described in claim 14.
    [17]
    17. - Procedure of operation of the plant, according to claim 11,
    characterized in that the working fluid of the main Brayton cycle (14) is supercritical CO2.
    [18]
    18. - Procedure of operation of the plant, according to claim 14,
    characterized in that the working fluid of the main Brayton cycle (14) and the working fluid of the tail Brayton cycle (16) is supercritical CO2.
    [19]
    19. - Procedure of operation of the plant, according to claim 11,14 or 16 characterized in that the working fluids of each cycle are directly heated in the heat source by passing them through the solar receiver (1, 1 ', 1 ” ).
    [20]
    20. - Procedure for operating the plant, according to claim 11,14 or 16, characterized in that the working fluids of each cycle are indirectly heated in the heat source, so that it is passed through the solar receiver (1, 1 ', 1 ") a thermal storage material that, once heated, gives energy to the working fluid of the corresponding cycle in a heat exchanger (12,12', 12") connected to a solar receiver (1, 1 ' and 1 ”).
    5
    10
    fifteen
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    [21]
    21. - Procedure for operating the plant, according to claim 17, characterized in that in the main Brayton cycle (14) the expander (2) receives the supercritical CO2 of the main Brayton cycle (14) at a temperature above 750 ° C and pressure greater than 200 bar; at the outlet of the primary recuperator (4), the working fluid of the main Brayton cycle (14) is at a temperature around 600 ° C and pressure between 20 and 60 bar; at the outlet of the refrigerator (7) and before entering the compressor (8) said fluid is at a temperature around 25 ° C and pressure between 20 and 60 bar and the fluid pressure of the main Brayton cycle ( 14) at the pump outlet (9) it is greater than 200 bar; in the Rankine tail cycle (15), the supercritical steam of said Rankine tail cycle (15) entering the turbine (11) has a temperature between 600 and 900 ° C and pressure equal to or greater than 200 bars, the Rankine tail steam (15) leaving the refrigerator (7 ') has an approximate temperature of 25 ° C and pressure equal to or less than 0.14 bar.
    [22]
    22. - Procedure of operation of the plant, according to claim 18,
    characterized in that the CO2 of the tail Brayton cycle (16) is heated in the
    primary recuperator (4) up to a temperature between 700 ° C and 900 ° C, being at a pressure greater than 200 bar; at the exit of the expander (2 ’), the CO2 current of the Brayton tail cycle (16) is at a temperature in the approximate range of 500-600 ° C and pressure between 20-30 bar; at the outlet of the refrigerator (7 ”) said fluid is at a temperature around 25 ° C and pressure between 20-30 bar.
    [23]
    23. - Procedure of operation of the plant, according to claim 22,
    characterized in that the CO2 of the Brayton tail cycle (16) is heated before entering the primary recuperator (4) in a solar receiver (1 ”) to a temperature around 600 ° C, being at a pressure greater than 200 bar
    [24]
    24. - Procedure of operation of the plant, according to claim 20
    characterized in that in the solar receiver (1), the heat storage material is heated to temperature conditions above 750 ° C and pressure equal to or less than 30 bar and said material yields heat to the supercritical CO2 of the main Brayton cycle ( 14) which enters the expander (2) at a temperature higher than 750 ° C and pressure greater than 200 bar; and in the Rankine cycle of supercritical steam tail (15), the heat storage material is heated to conditions of maximum temperature of 800 ° C and pressure equal to or less than 30 bar in the solar receiver (1 ') for later heat the steam from a temperature above 550 ° C and
    pressure greater than 200 bars up to a maximum temperature of 750 ° C and a pressure greater than 200 bars which are the conditions of the turbine inlet (11).
    [25]
    25. - Procedure of operation of the plant, according to claim 18 5 characterized in that the CO2 of the Brayton tail cycle (16) is heated in the
    Primary recuperator (4) up to a temperature between 700 ° C and 900 ° C and at a pressure greater than 200 bar and is directed to a supercritical CO2 expander (2 '') connected to an electric current generator (3 '') for the production of electricity; at the outlet of the expander (2 ''), the CO2 current that is at a temperature in an approximate range of 500-600 ° C and pressure between 20-60 bar, is passed through a heat regenerator (42 ) to heat the input current to the primary recuperator (4); From the heat regenerator (42), the CO2 stream of the Brayton tail cycle (16) is directed to the refrigerator (7 ”) where the necessary heat is extracted up to a temperature around 25 ° C and pressure between 20-60 Pub; from there, it is directed to the compressor (8 ”) and the pump (9”) that drives the CO2 current to the primary recuperator (4), previously passing through the heat regenerator (42) where the CO2 of the tail Brayton cycle is preheated (16).
    [26]
    26. - Procedure of operation of the plant, according to claim 25, characterized in that the CO2 of the tail Brayton cycle (16) is preheated in the
    solar receiver (1 ”) up to a temperature around 600 ° C and a pressure greater than 200 bar before the primary recuperator (4).
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    引用文献:
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    US9500185B2|2014-08-15|2016-11-22|King Fahd University Of Petroleum And Minerals|System and method using solar thermal energy for power, cogeneration and/or poly-generation using supercritical brayton cycles|
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    CN104832229A|2015-04-29|2015-08-12|南京瑞柯徕姆环保科技有限公司|Britten-organic Rankine type solar thermal power generation method and device|CN107829893A|2017-11-04|2018-03-23|肇庆市高新区晓靖科技有限公司|A kind of multistage heat generating system|
    CN108915964A|2018-07-03|2018-11-30|华北电力大学|A kind of Bretton distributing-supplying-energy system driven using tower type solar|
    IT201900000823A1|2019-01-18|2020-07-18|Univ Della Calabria|Concentrating solar plant that creates a closed Joule-Brayton cycle|
    CN112922685A|2021-03-29|2021-06-08|西安交通大学|Closed air Brayton-organic Rankine combined cycle system|
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