CN109139400B - Solar thermal complementary combined cycle system capable of changing integration mode based on irradiation change - Google Patents
Solar thermal complementary combined cycle system capable of changing integration mode based on irradiation change Download PDFInfo
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- CN109139400B CN109139400B CN201810839133.6A CN201810839133A CN109139400B CN 109139400 B CN109139400 B CN 109139400B CN 201810839133 A CN201810839133 A CN 201810839133A CN 109139400 B CN109139400 B CN 109139400B
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- 230000000295 complement effect Effects 0.000 title claims abstract description 31
- 230000010354 integration Effects 0.000 title claims abstract description 29
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 74
- 230000001105 regulatory effect Effects 0.000 claims abstract description 71
- 230000005855 radiation Effects 0.000 claims abstract description 12
- 239000002918 waste heat Substances 0.000 claims abstract description 12
- 239000007789 gas Substances 0.000 claims description 39
- 238000002485 combustion reaction Methods 0.000 claims description 8
- 238000003303 reheating Methods 0.000 claims description 7
- 238000010438 heat treatment Methods 0.000 claims description 2
- 238000004458 analytical method Methods 0.000 description 6
- 238000010248 power generation Methods 0.000 description 6
- 238000006243 chemical reaction Methods 0.000 description 3
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 2
- 239000003546 flue gas Substances 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000012932 thermodynamic analysis Methods 0.000 description 2
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 150000003839 salts Chemical class 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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- 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
- F03G6/064—Devices for producing mechanical power from solar energy with solar energy concentrating means having a gas turbine cycle, i.e. compressor and gas turbine combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
- F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
- F22D1/003—Feed-water heater systems
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- 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
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- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses a solar heat complementation combined cycle system for changing an integration mode based on irradiation change, which comprises: the first regulating valve, the second regulating valve, the third regulating valve, the fourth regulating valve, the oil-water heat exchanger, the expansion tank, the oil pump and the groove type condenser field form a groove type solar subsystem; the solar heat complementary combined cycle system changes the integration mode based on the irradiation change, and changes the integration position of solar heat from a high-pressure evaporator of a waste heat boiler to a second-stage high-pressure economizer at the moment that the direct solar radiation intensity is lower; the solar heat complementary combined cycle system not only can realize the maximum utilization of solar heat and prolong the service life of the solar heat, but also can further improve the photoelectric efficiency and the acting output of a power plant.
Description
Technical Field
The invention relates to the technical field of combined power generation, in particular to a solar thermal complementary combined cycle system for changing an integration mode based on irradiation change.
Background
Fossil energy utilization has long been a major part of the world's energy utilization structure. However, with the excessive consumption of fossil energy and the increasingly prominent problem of environmental pollution, the large-scale efficient use of solar energy as the renewable energy with the largest reserves has become a necessary requirement for adjusting the world energy utilization structure and sustainable development. The solar heat complementary combined cycle system introduces solar energy into the efficient combined cycle system, thereby improving the photoelectric conversion efficiency of the solar energy, saving the cost and reducing the consumption of fossil energy.
The traditional solar heat complementary combined cycle system uses heat conduction oil or molten salt as a heat exchange working medium of a groove type solar subsystem and integrates the heat exchange working medium into a high-pressure evaporator of a waste heat boiler, and when a solar heat collecting mirror field works under low direct solar radiation intensity (DNI), the collected solar energy is not enough to enable the outlet temperature of heat conduction fluid to reach the temperature specified by the system, so that the direct solar radiation intensity with lower numerical value cannot be effectively utilized.
Therefore, the invention provides a solar thermal complementary combined cycle system with an integration mode changed based on irradiation change, which aims to solve the problems in the prior art.
Disclosure of Invention
The invention aims to provide a solar thermal complementary combined cycle system capable of changing an integration mode based on irradiation change, and the integration position of solar thermal is changed from a high-pressure evaporator of a waste heat boiler to a second-stage high-pressure economizer at the moment that the direct solar radiation intensity is lower.
The invention discloses a solar heat complementation combined cycle system for changing an integration mode based on irradiation change, which comprises: the system comprises a groove type solar subsystem and a gas turbine subsystem, wherein the groove type solar subsystem and the gas turbine subsystem are combined through a pipeline and a valve;
the gas turbine subsystem includes: the system comprises a gas turbine compressor (1), a gas turbine (2), a gas turbine combustion chamber (3), a steam turbine high-pressure cylinder (4), a steam turbine intermediate-pressure cylinder (5), a steam turbine low-pressure cylinder (6), a condenser (7), a low-pressure water feed pump (8), an intermediate-pressure water feed pump (9), a high-pressure water feed pump (10), a low-pressure economizer (11), a low-pressure evaporator (12), a first-stage high-pressure economizer (13), an intermediate-pressure economizer (14), an intermediate-pressure evaporator (15), a low-pressure superheater (16), a second-stage high-pressure economizer (17), an intermediate-pressure superheater (18), a high-pressure evaporator (19), a reheater (20), a high-pressure superheater (21), a low-pressure steam pocket (22), an intermediate-pressure steam pocket (23), a high-pressure steam pocket (24), a valve first generator (30), a second generator (31); the gas compressor (1) of the gas turbine is connected with the gas turbine (2) of the gas turbine through a combustion chamber (3) of the gas turbine; the gas turbine compressor (1), the gas turbine (2) and the second generator (31) are coaxially connected; the outlet of the combustion engine turbine (2) is connected with the inlet of a three-pressure reheating waste heat boiler (35); the outlet of the three-pressure reheating waste heat boiler (35) is connected with the atmosphere; an outlet of the steam turbine low-pressure cylinder (6) is connected with an inlet of the steam turbine low-pressure cylinder (6) sequentially through a condenser (7), a low-pressure water feed pump (8), a low-pressure economizer (11), a low-pressure steam drum (22), a low-pressure evaporator (12) and a low-pressure superheater (16); one path of the outlet of the low-pressure economizer (11) is connected with the inlet of the high-pressure cylinder (4) of the steam turbine sequentially through a high-pressure water feeding pump (10), a first-stage high-pressure economizer (13), a second-stage high-pressure economizer (17), a high-pressure steam pocket (24), a high-pressure evaporator (19) and a high-pressure superheater (21); the other path of the outlet of the low-pressure economizer (11) is connected with the inlet of a reheater (20) through a medium-pressure water feed pump (9), a medium-pressure economizer (14), a medium-pressure steam drum (23), a medium-pressure evaporator (15) and a medium-pressure superheater (18); and the outlet of the turbine high-pressure cylinder (4) is connected with the inlet of the reheater (20); the outlet of the reheater (20) is connected with the inlet of the turbine intermediate pressure cylinder (5); the outlet of the turbine intermediate pressure cylinder (5) is connected with the inlet of the turbine low pressure cylinder (6); the steam turbine high pressure cylinder (4), the steam turbine intermediate pressure cylinder (5), the steam turbine low pressure cylinder (6) and the first generator (30) are coaxially connected;
the trough solar subsystem includes: the device comprises a first adjusting valve (25), a second adjusting valve (26), a third adjusting valve (27), a fourth adjusting valve (28), an expansion tank (29), an oil-water heat exchanger (32), an oil pump (33) and a groove type condenser field (34); the outlet of the first regulating valve (25) and the outlet of the second regulating valve (26) are respectively connected with the inlet of the oil-water heat exchanger (32) through pipelines; the inlet of the third regulating valve (27) and the inlet of the fourth regulating valve (28) are connected with the outlet of the oil-water heat exchanger (32) through pipelines; the heat exchange working medium in the expansion tank (29) enters the groove type condenser field (34) through the oil pump (33) for heating, then enters the oil-water heat exchanger (32) for heat exchange, and finally enters the expansion tank (29).
Preferably, the connection mode of the trough solar subsystem and the gas turbine subsystem through a pipeline and a valve is as follows: the first path of the outlet of the high-pressure water feeding pump (10) is connected with the inlet of the high-pressure steam drum (24) through the first-stage high-pressure economizer (13), the first regulating valve (25), the oil-water heat exchanger (32) and the third regulating valve (27) in sequence; and the second path of the outlet of the high-pressure water feeding pump (10) is connected with the inlet of the high-pressure superheater (21) sequentially through the first-stage high-pressure economizer (13), the second-stage high-pressure economizer (17), the second regulating valve (26), the oil-water heat exchanger (32) and the fourth regulating valve (28).
Preferably, the groove type solar subsystem controls the flow of feed water entering the oil-water heat exchanger (32) through the opening and closing of the first regulating valve (25), the second regulating valve (26), the third regulating valve (27) and the fourth regulating valve (28).
Preferably, the groove type solar subsystem takes heat conduction oil as a heat exchange working medium.
Preferably, when the solar heat complementation combined cycle system works at low direct solar radiation intensity, the first regulating valve (25) and the third regulating valve (27) are opened, the second regulating valve (26) and the fourth regulating valve (28) are closed, the feed water at the outlet of the first-stage high-pressure economizer (13) is divided into two lines, and the feed water at the outlet of the first-stage high-pressure economizer (13) enters the second-stage high-pressure economizer (17) in one line; in the other line, the water supply at the outlet of the first-stage high-pressure economizer (13) flows through the oil-water heat exchanger (32) through the first regulating valve (25) to absorb the sunlight heat collected by the heat transfer oil in the groove type condenser mirror field (34), and when the temperature of the water supply at the outlet of the first-stage high-pressure economizer (13) is the same as that of the water supply at the outlet of the second-stage high-pressure economizer (17), the water supply at the outlet of the first-stage high-pressure economizer (13) and the water supply at the outlet of the second-stage high-pressure economizer (17) are mixed and enter the high-pressure evaporator (19).
Preferably, when the solar thermal complementary combined cycle system works at high direct solar radiation intensity, the second regulating valve (26) and the fourth regulating valve (28) are opened, the first regulating valve (25) and the third regulating valve (27) are closed, the feed water at the outlet of the second-stage high-pressure economizer (17) is divided into two lines, and the feed water at the outlet of the second-stage high-pressure economizer (17) enters the high-pressure evaporator (19) in one line; in the other line, the water supplied from the outlet of the second-stage high-pressure economizer (17) flows through the oil-water heat exchanger (32) through the second regulating valve (26) to absorb the sunlight heat collected by the heat transfer oil in the trough-type condenser field (34), and when the temperature of the water supplied from the outlet of the second-stage high-pressure economizer (17) is the same as that of the steam at the outlet of the high-pressure evaporator (19), the water supplied from the outlet of the second-stage high-pressure economizer (17) and the steam at the outlet of the high-pressure evaporator (19) are mixed and enter the high-pressure superheater (21) to be superheated.
The invention discloses a solar heat complementary combined cycle system capable of changing an integration mode based on irradiation change, which aims at the current situation that the thermodynamic advantage and the economic advantage of the traditional solar heat complementary combined cycle system are insufficient, the solar heat complementary combined cycle system capable of changing the integration mode based on irradiation change is provided, the integration position of solar heat on a waste heat boiler is changed through the control of an added valve according to the change of solar radiation, and the integration position of the solar heat is changed from a high-pressure evaporator of the waste heat boiler to a second-stage high-pressure economizer at the moment that the direct solar radiation intensity is lower. The solar heat utilization device not only can realize the maximum utilization of solar heat and prolong the service life of the solar heat, but also can further improve the photoelectric efficiency and the acting output of a power plant. Compared with the traditional integration mode, the method has remarkable thermodynamic advantage and economic advantage.
Drawings
FIG. 1 is a schematic diagram of a solar thermal complementary combined cycle system with integration mode change based on irradiance variation.
Detailed Description
In order to make the implementation objects, technical solutions and advantages of the present invention clearer, the technical solutions in the implementation examples of the present invention will be described in more detail below with reference to the accompanying drawings in the implementation examples of the present invention. In the drawings, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described are a part of the embodiments of the present invention, and not all embodiments. The embodiments described below with reference to the accompanying drawings are exemplary and intended to be illustrative of the present invention and are not to be construed as limiting the present invention. All other embodiments obtained by those skilled in the art without any creative effort based on the embodiments of the present invention belong to the protection scope of the present invention.
As shown in fig. 1, a gas turbine compressor 1 is connected with a gas turbine 2 through a gas turbine combustion chamber 3; the gas turbine compressor 1, the gas turbine 2 and the second generator 31 are coaxially connected; the outlet of the gas turbine 2 is connected with the inlet of a three-pressure reheating waste heat boiler 35; the outlet of the turbine low-pressure cylinder 6 is connected with the inlet of the turbine low-pressure cylinder 6 through a condenser 7, a low-pressure water feed pump 8, a low-pressure economizer 11, a low-pressure steam drum 22, a low-pressure evaporator 12 and a low-pressure superheater 16; the outlet of the low-pressure economizer 11 is connected with the inlet of the high-pressure cylinder 4 of the steam turbine through a high-pressure water feeding pump 10, a first-stage high-pressure economizer 13, a second-stage high-pressure economizer 17, a high-pressure steam pocket 24, a high-pressure evaporator 19 and a high-pressure superheater 21; the outlet of the high-pressure water-feeding pump 10 is connected with the inlet of the high-pressure steam drum 24 through a first-stage high-pressure economizer 13, a first regulating valve 25, an oil-water heat exchanger 32 and a third regulating valve 27; the outlet of the high-pressure water-feeding pump 10 is connected with the inlet of the high-pressure superheater 21 through a first-stage high-pressure economizer 13, a second-stage high-pressure economizer 17, a second regulating valve 26, an oil-water heat exchanger 32 and a fourth regulating valve 28; the outlet of the low-pressure economizer 11 is connected with the inlet of a reheater 20 through a medium-pressure water feed pump 9, a medium-pressure economizer 14, a medium-pressure steam drum 23, a medium-pressure evaporator 15 and a medium-pressure superheater 18; the outlet of the turbine high-pressure cylinder 4 is connected with the inlet of the reheater 20; the outlet of the reheater 20 is connected to the inlet of the turbine intermediate pressure cylinder 5; the outlet of the turbine intermediate pressure cylinder 5 is connected with the inlet of the turbine low pressure cylinder 6; the high turbine pressure cylinder 4, the medium turbine pressure cylinder 5, the low turbine pressure cylinder 6 and the first generator 30 are coaxially connected.
The system comprises a first adjusting valve 25, a second adjusting valve 26, a third adjusting valve 27, a fourth adjusting valve 28, an oil-water heat exchanger 32, an expansion tank 29, an oil pump 33 and a groove type condenser field 34, wherein the groove type solar subsystem is formed by the first adjusting valve 25, the second adjusting valve 26, the third adjusting valve 27, the fourth adjusting valve 28, the oil-water heat exchanger 32, the expansion tank 29, the oil pump 33; the groove type solar subsystem takes heat conduction oil as a heat exchange working medium; the flow of the feed water entering the oil-water heat exchanger 32 is controlled by controlling the opening and closing of the first regulating valve 25, the second regulating valve 26, the third regulating valve 27 and the fourth regulating valve 28.
The invention adopts a PG9351FA type gas turbine; air is compressed in a gas compressor 1 of the gas turbine and is discharged into a combustion chamber 3 of the gas turbine to be mixed and combusted with fuel; the generated high-temperature and high-pressure flue gas flows into the gas turbine 2 to do work, and then is discharged into the three-pressure reheating waste heat boiler 35 to recycle the flue gas waste heat.
6 exhaust steam of steam turbine low pressure jar, discharge three pressure reheat exhaust-heat boiler 35 after condenser 7 condensation and low pressure feed water pump 8 preliminary boost in, shunt behind the low pressure economizer 11 is flowed through to the feedwater: one feed water flows through the low-pressure steam drum 22, the low-pressure evaporator 12 and the low-pressure superheater 16, is converted from supercooled water into superheated steam, and is mixed with the exhaust steam of the steam turbine intermediate pressure cylinder 5 to enter the steam turbine low pressure cylinder 6 to do work; the other feed water is boosted by a medium-pressure feed water pump 9, then flows through a medium-pressure economizer 14, a medium-pressure steam pocket 23, a medium-pressure evaporator 15 and a medium-pressure superheater 18, is converted from supercooled water into superheated steam, is mixed with the exhaust steam of a high-pressure cylinder 4 of the steam turbine and then enters a reheater 20 for reheating, and the reheated steam flows through a medium-pressure cylinder 5 of the steam turbine to do work; the last feed water is boosted by the high-pressure feed water pump 10, then flows through the first-stage high-pressure economizer 13, the second-stage high-pressure economizer 17, the high-pressure steam pocket 24, the high-pressure evaporator 19 and the high-pressure superheater 21, is converted from a supercooled state to a superheated state, and flows through the high-pressure cylinder 4 of the steam turbine to do work.
The steam turbine low-pressure cylinder 6 is connected with a first generator 30 through a shaft to convert mechanical energy into electric energy; the gas turbine compressor 1 is connected with a second generator 31 through a shaft to convert mechanical energy into electric energy.
When the solar thermal complementary combined cycle system with the integration mode changed based on the irradiation change works at low direct solar radiation intensity, the first regulating valve 25 and the third regulating valve 27 are opened, the second regulating valve 26 and the fourth regulating valve 28 are closed, the feed water at the outlet of the first-stage high-pressure economizer 13 is divided into two parts, and one part flows into the second-stage high-pressure economizer 17; the other strand of the solar heat collected in the groove type condenser field 34 by the heat transfer oil flowing through the oil-water heat exchanger through the first adjusting valve 25 reaches the same temperature as the water supply at the outlet of the second stage high-pressure economizer 17, and then enters the high-pressure evaporator 19 after being mixed with the water supply at the outlet of the second stage high-pressure economizer 17.
When the solar thermal complementary combined cycle system with the integration mode changed based on the irradiation change works at high direct solar radiation intensity, the second regulating valve 26 and the fourth regulating valve 28 are opened, the first regulating valve 25 and the third regulating valve 27 are closed, the feed water at the outlet of the second-stage high-pressure economizer 17 is divided into two parts, and one part flows into the high-pressure evaporator 19; the other strand of the solar heat collected in the groove type condenser field 34 by the heat transfer oil flowing through the oil-water heat exchanger through the second regulating valve 26 reaches the same temperature as the steam at the outlet of the high-pressure evaporator 19, and then enters the high-pressure superheater 21 for superheating after being mixed with the steam at the outlet of the high-pressure evaporator 19.
The trough type light-gathering heat collector in the trough type light-gathering heat collecting mirror field is arranged in the east-west direction, the fuel is natural gas transported from west to east, and the weather data is typical annual data of Dunhuang; table 1 lists the thermodynamic analysis basis data and table 2 lists the economic analysis basis data.
TABLE 1 thermodynamic analysis of basic data
TABLE 2 economic analysis base data
Table 3 lists the thermodynamic results analysis of the solar thermal complementary combined cycle system, the baseline system and the conventional solar thermal complementary combined cycle system with the integration pattern changed based on the change in irradiance. Table 4 lists the economic results analysis of the solar thermal complementary combined cycle system and the conventional solar thermal complementary combined cycle system with varying integration patterns based on irradiance changes.
TABLE 3 analysis of the results of the thermal behavior of the system
TABLE 4 analysis of the System economics results
As can be seen from table 3, compared with the conventional solar thermal complementary combined cycle system, the solar thermal complementary combined cycle system with the integration mode changed based on the irradiation change has improved all parameters. Wherein the net efficiency of solar photoelectric conversion is improved by 1.1 percent, and the solar photoelectric conversion
The efficiency is improved by 1.1 percent, and the total power generation amount is high 1002.968MW & h.
As can be seen from table 4, the power generation cost of the conventional solar thermal complementary combined cycle system is 1.61 ￥/kW · h, while the power generation cost of the solar thermal complementary combined cycle system in which the integration mode is changed based on the change of the irradiation is 1.542 ￥/kW · h, and the power generation cost of the solar thermal complementary combined cycle system in which the integration mode is changed based on the change of the irradiation is saved by 0.07 ￥/kW · h compared with the power generation cost of the conventional solar thermal complementary combined cycle system.
The solar thermal complementary combined cycle system with the integration mode changed based on the irradiation change has obvious thermodynamic integration advantages and economic advantages.
Finally, it should be pointed out that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art will understand that: the technical solutions described in the foregoing embodiments can be modified, or some technical features can be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solution depart from the spirit and scope of the technical solution of the embodiments of the present invention.
Claims (3)
1. Solar thermal complementary combined cycle system for changing integration mode based on irradiation change, characterized in that the solar thermal complementary combined cycle system comprises: the system comprises a groove type solar subsystem and a gas turbine subsystem, wherein the groove type solar subsystem and the gas turbine subsystem are combined through a pipeline and a valve;
the gas turbine subsystem includes: the system comprises a gas turbine compressor (1), a gas turbine (2), a gas turbine combustion chamber (3), a steam turbine high-pressure cylinder (4), a steam turbine intermediate-pressure cylinder (5), a steam turbine low-pressure cylinder (6), a condenser (7), a low-pressure water feed pump (8), an intermediate-pressure water feed pump (9), a high-pressure water feed pump (10), a low-pressure economizer (11), a low-pressure evaporator (12), a first-stage high-pressure economizer (13), an intermediate-pressure economizer (14), an intermediate-pressure evaporator (15), a low-pressure superheater (16), a second-stage high-pressure economizer (17), an intermediate-pressure superheater (18), a high-pressure evaporator (19), a reheater (20), a high-pressure superheater (21), a low-pressure steam pocket (22), an intermediate-pressure steam pocket (23), a high-pressure steam pocket (24), a first generator (30), a second generator (31); the gas compressor (1) of the gas turbine is connected with the gas turbine (2) of the gas turbine through a combustion chamber (3) of the gas turbine; the gas turbine compressor (1), the gas turbine (2) and the second generator (31) are coaxially connected; the outlet of the combustion engine turbine (2) is connected with the inlet of a three-pressure reheating waste heat boiler (35); the outlet of the three-pressure reheating waste heat boiler (35) is connected with the atmosphere; an outlet of the steam turbine low-pressure cylinder (6) is connected with an inlet of the steam turbine low-pressure cylinder (6) sequentially through a condenser (7), a low-pressure water feed pump (8), a low-pressure economizer (11), a low-pressure steam drum (22), a low-pressure evaporator (12) and a low-pressure superheater (16); the other path of the outlet of the low-pressure economizer (11) is connected with the inlet of a reheater (20) through a medium-pressure water feed pump (9), a medium-pressure economizer (14), a medium-pressure steam drum (23), a medium-pressure evaporator (15) and a medium-pressure superheater (18); and the outlet of the turbine high-pressure cylinder (4) is connected with the inlet of the reheater (20); the outlet of the reheater (20) is connected with the inlet of the turbine intermediate pressure cylinder (5); the outlet of the turbine intermediate pressure cylinder (5) is connected with the inlet of the turbine low pressure cylinder (6); the steam turbine high pressure cylinder (4), the steam turbine intermediate pressure cylinder (5), the steam turbine low pressure cylinder (6) and the first generator (30) are coaxially connected; one path of the outlet of the low-pressure economizer (11) is connected with the inlet of the high-pressure cylinder (4) of the steam turbine sequentially through a high-pressure water feeding pump (10), a first-stage high-pressure economizer (13), a second-stage high-pressure economizer (17), a high-pressure steam pocket (24), a high-pressure evaporator (19) and a high-pressure superheater (21);
the trough solar subsystem includes: the device comprises a first adjusting valve (25), a second adjusting valve (26), a third adjusting valve (27), a fourth adjusting valve (28), an expansion tank (29), an oil-water heat exchanger (32), an oil pump (33) and a groove type condenser field (34); the outlet of the first regulating valve (25) and the outlet of the second regulating valve (26) are respectively connected with the inlet of the oil-water heat exchanger (32) through pipelines; the inlet of the third regulating valve (27) and the inlet of the fourth regulating valve (28) are connected with the outlet of the oil-water heat exchanger (32) through pipelines; the heat exchange working medium in the expansion tank (29) enters the groove type condenser field (34) through the oil pump (33) for heating, then enters the oil-water heat exchanger (32) for heat exchange, and finally enters the expansion tank (29);
the feed water at the outlet of the first-stage high-pressure economizer (13) is controlled by opening the first regulating valve (25) and the third regulating valve (27) and closing the second regulating valve (26) and the fourth regulating valve (28), and the feed water at the outlet of the first-stage high-pressure economizer (13) enters the second-stage high-pressure economizer (17) in one line; in the other line, the water supply at the outlet of the first-stage high-pressure economizer (13) is connected with the inlet of the high-pressure steam drum (24) through a first regulating valve (25), an oil-water heat exchanger (32) and a third regulating valve (27), and the heat collection temperature of a heat exchange working medium in a groove type condenser field (34) is changed; the feed water at the outlet of the second-stage high-pressure economizer (17) is controlled by opening the second regulating valve (26) and the fourth regulating valve (28) and closing the first regulating valve (25) and the third regulating valve (27), and the feed water at the outlet of the second-stage high-pressure economizer (17) enters the high-pressure evaporator (19) in a line; in the other line, the water supply at the outlet of the second-stage high-pressure economizer (17) is connected with the inlet of the high-pressure superheater (21) through a second regulating valve (26), an oil-water heat exchanger (32) and a fourth regulating valve (28), and the heat collection temperature of a heat exchange working medium in a groove type condenser field (34) is changed;
the trough type solar subsystem controls the integration position of the water supply flow entering the oil-water heat exchanger (32) and solar energy through the opening and closing of the first regulating valve (25), the second regulating valve (26), the third regulating valve (27) and the fourth regulating valve (28), and changes the heat collection temperature of a heat exchange working medium in the trough type condenser field (34);
the groove type solar subsystem takes heat conduction oil as a heat exchange working medium.
2. A solar thermal complementary combined cycle system with integrated mode change based on irradiance change according to claim 1, wherein: when the solar heat complementation combined cycle system works at low direct solar radiation intensity, the first regulating valve (25) and the third regulating valve (27) are opened, the second regulating valve (26) and the fourth regulating valve (28) are closed, the integration position of solar energy is integrated into the second-stage high-pressure economizer (17), and the heat collection temperature of a heat exchange working medium in the groove type condenser field (34) is adjusted.
3. A solar thermal complementary combined cycle system with integrated mode change based on irradiance change according to claim 1, wherein: when the solar heat complementation combined cycle system works at high direct solar radiation intensity, the second regulating valve (26) and the fourth regulating valve (28) are opened, the first regulating valve (25) and the third regulating valve (27) are closed, the integration position of solar energy is integrated to the high-pressure evaporator (19), and the heat collection temperature of a heat exchange working medium in the groove type condenser field (34) is adjusted.
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| CN102454440A (en) * | 2010-10-20 | 2012-05-16 | 中国科学院工程热物理研究所 | Board slot combined solar energy and thermal power station complementary generating system |
| CN103452611A (en) * | 2013-09-05 | 2013-12-18 | 上海电气电站设备有限公司 | Combined-cycle combined heat and power system |
| CN104963776A (en) * | 2015-07-17 | 2015-10-07 | 华北电力大学 | Solar heat-complementary combined cycle power generation system |
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| CN102454440A (en) * | 2010-10-20 | 2012-05-16 | 中国科学院工程热物理研究所 | Board slot combined solar energy and thermal power station complementary generating system |
| CN103452611A (en) * | 2013-09-05 | 2013-12-18 | 上海电气电站设备有限公司 | Combined-cycle combined heat and power system |
| CN104963776A (en) * | 2015-07-17 | 2015-10-07 | 华北电力大学 | Solar heat-complementary combined cycle power generation system |
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