CN108506177B - Solar cascade organic Rankine cycle power generation system based on gas-liquid two-phase heat collector - Google Patents
Solar cascade organic Rankine cycle power generation system based on gas-liquid two-phase heat collector Download PDFInfo
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- 238000010248 power generation Methods 0.000 title claims abstract description 95
- 239000007788 liquid Substances 0.000 title claims abstract description 24
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 179
- 238000005338 heat storage Methods 0.000 claims abstract description 77
- YXFVVABEGXRONW-UHFFFAOYSA-N Toluene Chemical compound CC1=CC=CC=C1 YXFVVABEGXRONW-UHFFFAOYSA-N 0.000 claims description 12
- OFBQJSOFQDEBGM-UHFFFAOYSA-N Pentane Chemical compound CCCCC OFBQJSOFQDEBGM-UHFFFAOYSA-N 0.000 claims description 4
- OHMHBGPWCHTMQE-UHFFFAOYSA-N 2,2-dichloro-1,1,1-trifluoroethane Chemical compound FC(F)(F)C(Cl)Cl OHMHBGPWCHTMQE-UHFFFAOYSA-N 0.000 claims description 2
- MSSNHSVIGIHOJA-UHFFFAOYSA-N pentafluoropropane Chemical compound FC(F)CC(F)(F)F MSSNHSVIGIHOJA-UHFFFAOYSA-N 0.000 claims description 2
- 238000000034 method Methods 0.000 abstract description 7
- 238000006243 chemical reaction Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 150000003839 salts Chemical class 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000002427 irreversible effect Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000005514 two-phase flow Effects 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
- F03G6/065—Devices for producing mechanical power from solar energy with solar energy concentrating means having a Rankine cycle
- F03G6/067—Binary cycle plants where the fluid from the solar collector heats the working fluid via a heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
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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
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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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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention relates to a solar cascade organic Rankine cycle power generation system based on a gas-liquid two-phase heat collector. The solar energy heat collection and storage system comprises a solar heat collection and storage loop, a primary organic Rankine cycle power generation loop and a secondary organic Rankine cycle power generation loop. Solar irradiation in daytime is more than 400W/m 2 When the system is in operation modes of heat collection, heat storage and power generation; and at night or on overcast days, the system continues to perform a power generation operation mode by utilizing the heat stored by the high-temperature heat storage water tank. The two-stage organic Rankine cycle adopts the steam turbine, and the system can realize large-scale application of more than 10 MW; the steam turbine adopts dry organic working medium, and the working medium is in an overheat state in the expansion process, so that liquid drops are not generated; indirect heat exchange is adopted between the heat collection field, the heat storage unit and the organic Rankine cycle unit, water vapor generated by the heat collection field is only a heat transfer medium, does not enter a steam turbine to expand and do work, and the quality requirements of the system on heat collection and heat storage hydraulic working media are effectively reduced.
Description
Technical Field
The invention belongs to the technical field of solar thermal power generation, and particularly relates to a solar cascade organic Rankine cycle power generation system based on a gas-liquid two-phase heat collector.
Background
Photo-thermal power generation is an important way to exploit solar energy on a large scale. Unlike conventional photo-thermal power station, which adopts heat conducting oil, fused salt and other mediums, the direct steam solar thermal power generation technology has the advantages of relatively simple system structure, easy cost reduction and the like because water is used as heat absorbing medium, heat accumulating medium and heat-power converting working medium of the heat collecting field.
The direct steam generation type solar thermal power generation technology has two key problems to be solved: firstly, the water working medium has phase change in the heat absorption process in the heat collector field, the control of two-phase flow is more complex than that of single-phase flow, and the external solar irradiation has obvious fluctuation characteristic. In this case, if the superheated steam is to be produced from the heat collection field outlet, the degree of superheat of the steam is difficult to control, so that the stability of the steam output is poor and the reliability is low, and therefore, a relatively simple scheme for directly producing saturated steam is generally adopted in practical application. Second, the heat storage design matching the superheated steam cycle is complex and typically includes multiple stages of heat storage (preheat stage, phase change stage, and superheat stage). The conventional molten salt cold and hot tank switching operation mode can cause great irreversible heat transfer loss, and needs a large heat exchange area, so that the practicability is poor. Therefore, an economic and efficient direct expansion solar thermal power generation and heat storage technology is not available at present.
The direct expansion type solar thermal power generation technology based on the screw expander can solve the problems to a certain extent. Compared with a steam turbine, the screw expander can process a gas-liquid two-phase mixture without causing mechanical damage and is rapid in start and stop. The greatest advantage of screw expanders over steam turbines in terms of thermodynamic properties is their good variable operating capacity, which has also been demonstrated experimentally by numerous students. For example, for a screw expander with a built-in ratio volume ratio of 5, when the actual pressure ratio becomes three times the built-in pressure ratio, the isentropic efficiency is reduced by only 10% compared to the maximum value. Therefore, when the screw expander is adopted, the steam generated by the heat collection field of the direct expansion solar thermal power generation system can be in gas-liquid two phases without overheating. Particularly, when a two-stage heat storage water tank is adopted, the direct expansion solar thermal power generation system performs heat-power conversion by utilizing different heat release modes; the annual working time of the organic Rankine cycle is prolonged, the heat storage capacity of the system is greatly improved (compared with a single-tank system, the heat storage capacity can be improved by 5-8 times), and the investment recovery period of the system is shortened; and effectively avoid the expander to run under the condition of seriously deviating from the design working condition, ensure the high-efficient operation of the system.
On the other hand, the screw expander at the present stage has several significant drawbacks: first, the stand-alone capacity is smaller. The single unit capacity of commercial screw expanders is typically less than 2.5 MW. For a solar thermal power generation system, if the installed capacity is small, the cost proportion of the thermal power conversion unit in the whole system increases, and the system economy decreases. In view of this, solar thermal power generation systems are typically 10MW or greater in scale, which presents challenges for screw expanders. Second, the efficiency of saturated or wet steam screw expanders is not high compared to mainstream dry steam turbines. The isentropic efficiency of the screw expander is between 60% and 75%, and the isentropic efficiency of the dry steam turbine is between 80% and 89%.
One potential solution to the above problem is to implement the top heat power conversion of an cascade rankine cycle with a steam turbine based on dry organic working medium (dry organic fluid).
Disclosure of Invention
In order to further improve thermodynamic performance and technical feasibility of the solar cascade organic Rankine cycle power generation system, the invention provides a solar cascade organic Rankine cycle power generation system based on a gas-liquid two-phase heat collector.
The solar cascade organic Rankine cycle power generation system based on the gas-liquid two-phase heat collector comprises a solar heat collection and storage loop, a primary organic Rankine cycle power generation loop and a secondary organic Rankine cycle power generation loop;
the solar heat collection and storage loop comprises a solar heat collection field 1, a high-temperature heat storage water tank 2, a low-temperature heat storage water tank 3, a low-temperature heat collection water pump 12, a medium-temperature water pump 13 and a high-temperature heat exchange water pump 14, wherein an outlet of the solar heat collection field 1 is connected with the high-temperature heat storage water tank 2 in series, and an inlet of the solar heat collection field 1 is connected with the low-temperature heat storage water tank 3 in series;
the first-stage organic Rankine cycle power generation loop comprises a first-stage evaporator 4, an intermediate heat exchanger 5, a first-stage turbine 8, a first-stage generator 10 and a first-stage organic working medium pump 15, wherein the first-stage evaporator 4, the first-stage turbine 8, the intermediate heat exchanger 5 and the first-stage organic working medium pump 15 are connected in series to form the first-stage organic working medium loop;
the secondary organic Rankine cycle power generation loop comprises an intermediate heat exchanger 5, a second-stage condenser 6, a second-stage evaporator 7, a second-stage steam turbine 9, a second-stage generator 11 and a second-stage organic working medium pump 16, wherein the intermediate heat exchanger 5 and the second-stage evaporator 7 are respectively connected with the second-stage steam turbine 9, the second-stage condenser 6 and the second-stage organic working medium pump 16 in series to form a second-stage organic working medium loop;
one side of the first-stage evaporator 4 is a water working medium, the other side of the first-stage evaporator 4 is an organic working medium, the first-stage evaporator 4 on one side of the water working medium is connected in series on one side of a high-temperature heat storage water tank 2 of a solar heat collection and storage loop, and the first-stage evaporator 4 on one side of the organic working medium is connected in series in a first-stage organic Rankine cycle power generation loop;
one side of the second-stage evaporator 7 is water working medium, the other side of the second-stage evaporator 7 is organic working medium, the second-stage evaporator 7 on one side of the water working medium is connected in series on one side of the low-temperature heat storage water tank 3 of the solar heat collection and storage loop, and the second-stage evaporator 7 on one side of the organic working medium is connected in series in the second-stage organic Rankine cycle power generation loop;
the two sides of the intermediate heat exchanger 5 are both organic working media, one side of the intermediate heat exchanger 5 is connected in series in the primary organic Rankine cycle power generation circuit, and the other side of the intermediate heat exchanger 5 is connected in series in the secondary organic Rankine cycle power generation circuit;
solar irradiation in daytime is more than 400W/m 2 When the system is in a working mode, the system performs heat collection, heat storage and power generation simultaneously;
at night or on cloudy days, the system continues to perform the power generation operation mode by using the heat stored in the high-temperature heat storage water tank 2.
The further defined technical scheme is as follows:
the outlet of the solar heat collection field 1 is connected with the inlet at the lower part of the high-temperature heat storage water tank 2, the outlet at the lower part of the high-temperature heat storage water tank 2 is connected with the inlet of the high-temperature heat exchange water pump 14, the outlet of the high-temperature heat exchange water pump 14 is connected with the inlet at the water working medium side of the first-stage evaporator 4, the outlet at the water working medium side of the first-stage evaporator 4 is connected with the inlet at the upper part of the high-temperature heat storage water tank 2, the outlet at the bottom of the high-temperature heat storage water tank 2 is connected with the inlet of the medium-temperature water pump 13, the outlet of the medium-temperature water pump 13 is respectively connected with the inlet of the medium-temperature heat collection water valve 18 and the inlet of the medium-temperature heat exchange water valve 19, the outlet of the medium-temperature heat collection water valve 18 is connected with the inlet at the water working medium side of the second-stage evaporator 7, the outlet at the water working medium side of the second-stage evaporator 7 is connected with the inlet of the throttle valve 20, the outlet of the throttle valve 20 is connected with the inlet at the upper part of the low-temperature water tank 3, the outlet at the bottom of the low-temperature heat storage water tank 3 is connected with the inlet of the low-temperature heat collection water pump 12, the outlet of the low-temperature heat collection water pump 12 is connected with the inlet of the low-temperature heat collection water valve 17, and the outlet of the low-temperature heat collection water valve 17 is connected with the inlet of the solar heat collection field 1;
the outlet of the first-stage evaporator 4 on the organic working medium side is connected with the inlet of the first-stage steam turbine 8, the outlet of the first-stage steam turbine 8 is connected with the inlet of the intermediate heat exchanger 5 on the side, the outlet of the intermediate heat exchanger 5 on the side is connected with the inlet of the first-stage organic working medium pump 15, and the outlet of the first-stage organic working medium pump 15 is connected with the inlet of the first-stage evaporator 4 on the organic working medium side;
the outlet of the other side of the intermediate heat exchanger 5 is connected with the inlet of the first heat exchange outlet valve 22, the outlet of the first heat exchange outlet valve 22 is connected with the inlet of the second-stage steam turbine 9, the outlet of the second-stage steam turbine 9 is connected with the inlet of the second-stage organic working medium pump 16, the outlet of the second-stage organic working medium pump 16 is connected with the inlet of the first heat exchange inlet valve 21 and the inlet of the second heat exchange inlet valve 23, the outlet of the first heat exchange inlet valve 21 is connected with the inlet of the other side of the intermediate heat exchanger 5, the outlet of the second heat exchange inlet valve 23 is connected with the inlet of the second-stage evaporator 7, the outlet of the second-stage evaporator 7 is connected with the inlet of the second heat exchange outlet valve 24, and the outlet of the second heat exchange outlet valve 24 is connected with the inlet of the second-stage steam turbine 9.
The solar heat collection field 1 is one of a parabolic trough heat collection field, a linear Fresnel heat collection field and a tower heat collection field.
The organic working medium in the primary organic Rankine cycle power generation loop is one of toluene and pentane; the organic working medium in the first-stage evaporator 4 and the organic working medium on one side of the intermediate heat exchanger 5 are the same as the organic working medium in the first-stage organic Rankine cycle power generation loop.
The organic working medium in the secondary organic Rankine cycle power generation loop is one of trifluoro dichloroethane (R123) and pentafluoropropane (R245 fa); the organic working medium at the other side of the intermediate heat exchanger 5, the organic working medium in the second-stage condenser 6 and the organic working medium in the second-stage evaporator 7 are the same as the organic working medium in the second-stage organic Rankine cycle power generation loop.
The working temperature of the high-temperature heat storage water tank 2 is 180-280 ℃, and the working temperature of the low-temperature heat storage water tank 3 is 30-150 ℃.
Compared with the prior art, the invention has the beneficial technical effects that:
1. the invention adopts the gas-liquid two-phase heat collector, the steam generated by the heat collection field is condensed in the high-temperature heat storage tank, and the released heat is used for driving the organic Rankine cycle to generate power. The heat collection field directly generates steam, and the generated steam does not enter a steam turbine or other expansion machines to perform heat-power conversion, so that the technical scheme of heat-power conversion is not reported in the existing solar thermal power generation system.
2. In the invention, in the first stage of heat release power generation, the heat with the height of Wen Shuiguan is used for driving the cascade organic Rankine cycle power generation, and in the second stage of heat release power generation, the water with the height of Wen Shuiguan flows into the low-temperature water tank, and the heat is used for driving the bottom organic Rankine cycle power generation. This direct expansion solar thermal power generation system with unique heat release pattern is only reported in the invention application CN 201710608229.7. The present invention differs significantly from invention CN 201710608229.7: the invention has the advantages that (1) a turbine is adopted instead of a screw expander in the top cycle, the heat work conversion process has higher efficiency, the output power is higher, and the like, (2) the turbine adopts a dry organic working medium, the working medium is in an overheated state in the expansion process, no liquid drops are generated, and therefore, the efficiency of the expander is higher than that of a wet steam turbine, and no mechanical damage occurs.
3. According to the invention, the first-stage and second-stage organic Rankine cycle all adopt steam turbines, and the system can realize large-scale application of more than 10 MW. Aiming at a 10MW system adopting a wet steam turbine, the humidity of the steam at the outlet of the wet steam turbine is about 11-14%, the isentropic expansion efficiency can reach about 80%, and the overall power generation efficiency of the system is about 21% when the heat collection temperature is 250 ℃; when the organic Rankine cycle based on dry working media is adopted in the top thermodynamic cycle, the isentropic efficiency of the steam turbine can be maintained at about 85%, and the power generation efficiency of the system is above 25%.
4. Indirect heat exchange is adopted among the heat collection field, the heat storage unit and the organic Rankine cycle unit, water vapor generated by the heat collection field is only a heat transfer medium, does not enter a steam turbine to expand and do work, and the quality requirements of a system on heat collection and heat storage hydraulic working media are effectively reduced. The heat collection and heat storage adopt water working media, so that the method is economical and environment-friendly.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention.
Fig. 2 is a schematic diagram of the simultaneous heat collection, heat storage and power generation modes.
Fig. 3 is a schematic diagram of a first stage exothermic power generation mode.
Fig. 4 is a schematic diagram of a second stage exothermic power generation mode.
FIG. 5 is a graph of saturation temperature-entropy (T-s plot) of R123 and water.
Number in fig. 1: the solar heat collection field 1, the high-temperature heat storage water tank 2, the low-temperature heat storage water tank 3, the first-stage evaporator 4, the intermediate heat exchanger 5, the second-stage condenser 6, the second-stage evaporator 7, the first-stage steam turbine 8, the second-stage steam turbine 9, the first-stage generator 10, the second-stage generator 11, the low-temperature heat collection water pump 12, the medium-temperature water pump 13, the high-temperature heat exchange water pump 14, the first-stage organic working medium pump 15, the second-stage organic working medium pump 16, the low-temperature heat collection water valve 17, the medium-temperature heat collection water valve 18, the medium-temperature heat exchange water valve 19, the first heat exchange inlet valve 21, the first heat exchange outlet valve 22, the second heat exchange inlet valve 23, the second heat exchange outlet valve 24 and the throttle valve 20.
Detailed Description
The invention is further described by way of examples with reference to the accompanying drawings.
Referring to fig. 1, a solar cascade organic rankine cycle power generation system based on a gas-liquid two-phase heat collector comprises a solar heat collection and storage loop, a first-stage organic rankine cycle power generation loop and a second-stage organic rankine cycle power generation loop.
The solar heat collection and storage loop comprises a solar heat collection field 1, a high-temperature heat storage water tank 2, a low-temperature heat storage water tank 3, a low-temperature heat collection water pump 12, a medium-temperature water pump 13 and a high-temperature heat exchange water pump 14, wherein the solar heat collection field 1 is a parabolic trough type heat collection field.
The first-stage organic Rankine cycle power generation loop comprises a first-stage evaporator 4, an intermediate heat exchanger 5, a first-stage turbine 8, a first-stage generator 10 and a first-stage organic working medium pump 15, wherein the first-stage evaporator 4, the first-stage turbine 8, the intermediate heat exchanger 5 and the first-stage organic working medium pump 15 are connected in series to form the first-stage organic working medium loop; one side of the first-stage evaporator 4 is water working medium, the other side of the first-stage evaporator 4 is organic working medium, the first-stage evaporator 4 on one side of the water working medium is connected in series on one side of the high-temperature heat storage water tank 2 of the solar heat collection and storage loop, and the first-stage evaporator 4 on one side of the organic working medium is connected in series in the first-stage organic Rankine cycle power generation loop; the organic working medium in the primary organic Rankine cycle power generation loop is toluene; the organic working medium in the first-stage evaporator 4 and the organic working medium on one side of the intermediate heat exchanger 5 are the same as the organic working medium in the first-stage organic Rankine cycle power generation loop.
The secondary organic Rankine cycle power generation loop comprises an intermediate heat exchanger 5, a second-stage condenser 6, a second-stage evaporator 7, a second-stage turbine 9, a second-stage generator 11 and a second-stage organic working medium pump 16, wherein the intermediate heat exchanger 5 and the second-stage evaporator 7 are respectively connected with the second-stage turbine 9, the second-stage condenser 6 and the second-stage organic working medium pump 16 in series to form the second-stage organic working medium loop. Both sides of the intermediate heat exchanger 5 are organic working media, one side of the intermediate heat exchanger 5 is connected in series in the primary organic Rankine cycle power generation circuit, and the other side of the intermediate heat exchanger 5 is connected in series in the secondary organic Rankine cycle power generation circuit. One side of the second-stage evaporator 7 is water working medium, the other side of the second-stage evaporator 7 is organic working medium, the second-stage evaporator 7 on one side of the water working medium is connected in series on one side of the low-temperature heat storage water tank 3 of the solar heat collection and storage loop, and the second-stage evaporator 7 on one side of the organic working medium is connected in series in the second-stage organic Rankine cycle power generation loop; the organic working medium in the secondary organic Rankine cycle power generation loop is R123; the organic working medium at the other side of the intermediate heat exchanger 5, the organic working medium in the second-stage condenser 6 and the organic working medium in the second-stage evaporator 7 are the same as the organic working medium in the second-stage organic Rankine cycle power generation loop.
The specific connection relation of each component of the solar cascade organic Rankine cycle power generation system is as follows:
the outlet of the solar heat collection field 1 is connected with the inlet at the lower part of the high-temperature heat storage water tank 2, the outlet at the lower part of the high-temperature heat storage water tank 2 is connected with the inlet of the high-temperature heat exchange water pump 14, the outlet of the high-temperature heat exchange water pump 14 is connected with the inlet at the water working medium side of the first-stage evaporator 4, the outlet at the water working medium side of the first-stage evaporator 4 is connected with the inlet at the upper part of the high-temperature heat storage water tank 2, the outlet at the bottom of the high-temperature heat storage water tank 2 is connected with the inlet of the medium-temperature water pump 13, the outlet of the medium-temperature water pump 13 is respectively connected with the inlet of the medium-temperature heat collection water valve 18 and the inlet of the medium-temperature heat exchange water valve 19, the outlet of the medium-temperature heat collection water valve 18 is connected with the inlet at the water working medium side of the second-stage evaporator 7, the outlet at the water working medium side of the second-stage evaporator 7 is connected with the inlet of the throttle valve 20, the outlet of the throttle valve 20 is connected with the inlet at the upper part of the low-temperature heat storage water tank 3, the outlet at the bottom of the low-temperature heat storage water tank 3 is connected with the inlet of the low-temperature heat collection water pump 12, the outlet of the low-temperature heat collection water pump 12 is connected with the inlet of the low-temperature heat collection water valve 17, and the outlet of the low-temperature heat collection water valve 17 is connected with the inlet of the solar heat collection field 1;
the outlet of the first-stage evaporator 4 on one side of the organic working medium is connected with the inlet of the first-stage steam turbine 8, the outlet of the first-stage steam turbine 8 is connected with the inlet of the intermediate heat exchanger 5 on one side, the outlet of the intermediate heat exchanger 5 on one side is connected with the inlet of the first-stage organic working medium pump 15, and the outlet of the first-stage organic working medium pump 15 is connected with the inlet of the first-stage evaporator 4 on one side of the organic working medium;
the outlet of the other side of the intermediate heat exchanger 5 is connected with the inlet of the first heat exchange outlet valve 22, the outlet of the first heat exchange outlet valve 22 is connected with the inlet of the second-stage steam turbine 9, the outlet of the second-stage steam turbine 9 is connected with the inlet of the second-stage organic working medium pump 16, the outlet of the second-stage organic working medium pump 16 is connected with the inlet of the first heat exchange inlet valve 21 and the inlet of the second heat exchange inlet valve 23 respectively, the outlet of the first heat exchange inlet valve 21 is connected with the inlet of the other side of the intermediate heat exchanger 5, the outlet of the second heat exchange inlet valve 23 is connected with the inlet of the second-stage evaporator 7 on the organic working medium side, the outlet of the second-stage evaporator 7 is connected with the inlet of the second heat exchange outlet valve 24, and the outlet of the second heat exchange outlet valve 24 is connected with the inlet of the second-stage steam turbine 9.
The working principle of the invention is described as follows:
(1) When the sun irradiation is sufficient in daytime, such as more than 400W/m 2 The system simultaneously performs three operation modes of heat collection, heat storage and power generation, as shown in fig. 2. The low-temperature heat collecting water pump 12, the medium-temperature water pump 13, the high-temperature heat exchange water pump 14, the first-stage organic working medium pump 15 and the second-stage organic working medium pump 16 are operated, and the low-temperature heat collecting water valve 17, the medium-temperature heat collecting water valve 18, the first-stage heat exchange inlet valve 21 and the first-stage heat exchange outlet valve 22 are opened. The low-temperature water in the low-temperature heat storage water tank 3 enters the solar heat collection field 1 to be heated to a set temperature through the low-temperature heat collection water pump 12 and the low-temperature heat collection water valve 17 and then enters the high-temperature heat storage water tank 2, wherein part of the high-temperature water enters the first-stage evaporator 4 through the high-temperature heat exchange water pump 14 to be cooled and released and then returns to the high-temperature heat storage water tank 2 to be mixed with the rest of the high-temperature water, the cooled high-temperature water enters the solar heat collection field 1 through the medium-temperature water pump 13 and the medium-temperature heat collection water valve 18 to be heated to the set temperature and then is stored in the high-temperature heat storage water tank 2 again, and the high-temperature water in the high-temperature heat storage water tank 2 can be always kept through the coordinated operation of the low-temperature heat collection water pump 12 and the medium-temperature water pump 13Maintaining at the set temperature. The dry organic working medium in the first-stage organic Rankine cycle absorbs heat and evaporates in the first-stage evaporator 4, the high-temperature dry organic working medium steam enters the first-stage turbine 8 to expand and do work and output electric energy through the first-stage generator 10, the dry organic working medium steam at the outlet of the expanded and cooled first-stage turbine 8 enters the intermediate heat exchanger 5 to be condensed and released into liquid, and the intermediate-temperature liquid enters the first-stage evaporator 4 again through the first-stage organic working medium pump 15 to complete the first-stage organic Rankine cycle. The dry organic working medium in the second-stage organic Rankine cycle absorbs heat and evaporates in the intermediate heat exchanger 5, medium-temperature dry organic working medium steam enters the second-stage steam turbine 9 through the first-stage heat exchange outlet valve 22 to do expansion work and is output by the second-stage generator 11, the expanded and cooled dry organic working medium steam enters the second-stage condenser 6 to be condensed and released into liquid, and low-temperature liquid enters the intermediate heat exchanger 5 through the second-stage organic working medium pump 16 and the first-stage heat exchange inlet valve 21 to complete the second-stage organic Rankine cycle.
(2) In cloudy days or at night, the system continues the power generation mode by using the heat stored in the high-temperature heat storage water tank 2. In the first-stage exothermic power generation mode, as shown in fig. 3, the high-temperature heat exchange water pump 14, the first-stage organic working medium pump 15 and the second-stage organic working medium pump 16 are operated, and the first-stage heat exchange inlet valve 21 and the first-stage heat exchange outlet valve 22 are opened. The high-temperature water in the high-temperature heat storage water tank 2 enters the first-stage evaporator 4 through the high-temperature heat exchange water pump 14 to cool and release heat, the cooled medium-temperature water enters the high-temperature heat storage water tank 2 again, and the flow of the water working medium entering the first-stage evaporator 4 is controlled by adjusting the high-temperature heat exchange water pump 14 so as to maintain the heat exchange temperature to be reduced within 70 ℃. The working processes of the first-stage organic Rankine cycle and the second-stage organic Rankine cycle are the same as those when the three modes of heat collection, heat storage and power generation are operated together.
In the second-stage exothermic power generation mode, as shown in fig. 4, the medium-temperature water pump 13 and the second-stage organic working medium pump 16 are operated, and the medium-temperature heat exchange water valve 19, the throttle valve 20, the second-stage heat exchange inlet valve 23 and the second-stage heat exchange outlet valve 24 are opened. The rest medium-temperature water in the high-temperature heat storage water tank 2 enters the second-stage evaporator 7 through the medium-temperature water pump 13 and the medium-temperature heat exchange water valve 19 to cool and release heat, enters the low-temperature heat storage water tank 3 through the throttle valve 20, the dry organic working medium in the second-stage organic Rankine cycle absorbs heat and evaporates in the second-stage evaporator 7, the medium-temperature dry organic working medium steam enters the second-stage steam turbine 9 through the second-stage heat exchange outlet valve 24 to expand and do work and output electric energy through the second-stage generator 11, the low-temperature organic working medium steam at the outlet of the expanded and cooled second-stage steam turbine 9 enters the second-stage condenser 6 to condense and release heat to form liquid, and the low-temperature liquid enters the second-stage evaporator 7 again through the second-stage organic working medium pump 16 and the second-stage heat exchange inlet valve 23 to complete the second-stage organic Rankine cycle.
When the embodiment is in the design working condition, the relevant parameters are as follows: the irradiation intensity of direct solar radiation is 800W/m 2 The solar irradiation time length is 6 hours, the ambient temperature is 25 ℃, the ambient wind speed is 2.5m/s, the rated power of the first-stage turbine 8 is 10MW, the rated power of the second-stage turbine 9 is 15.3MW, the efficiencies of the first-stage turbine 8 and the second-stage turbine 9 are 85%, the efficiencies of the first-stage generator 10 and the second-stage generator 11 are 95%, the efficiencies of the low-temperature heat collecting water pump 12, the medium-temperature heat collecting water pump 13, the high-temperature heat exchanging water pump 14, the first-stage organic working medium pump 15 and the second-stage organic working medium pump 16 are 80%, the heat accumulating temperature of the high-temperature heat accumulating water tank 2 is 250 ℃, the pressure is 4.5MPa, the heat storage temperature of the low-temperature heat storage water tank 3 is 50 ℃, the pressure is 1.5MPa, the heat storage duration of the high-temperature heat storage water tank 2 and the low-temperature heat storage water tank 3 is 4 hours, the water temperature in the high-temperature heat storage water tank 2 in the first-stage heat release power generation mode is gradually reduced from 250 ℃ to 180 ℃, the water temperature in the high-temperature heat storage water tank 2 in the second-stage heat release power generation mode is gradually reduced from 180 ℃ to 50 ℃, the evaporation temperature of the first-stage organic Rankine cycle is 240 ℃, the evaporation temperature of the second-stage organic Rankine cycle is 150 ℃, the condensation temperature of the first-stage organic Rankine cycle is 160 ℃, and the condensation temperature of the second-stage organic Rankine cycle is 35 ℃;
according to the parameters, the European tank ET150 and the Schottky PTR70 heat collecting pipes commonly adopted by the solar photo-thermal power station at present are selected to form a solar heat collecting field, and the calculation result shows that: the net output power of the first-stage organic Rankine cycle is 9.6MW, and the power generation efficiency is 10.1%; net output of second stage organic Rankine cycle14.6MW and 17.1% of power generation efficiency; the total output power of the cascade organic Rankine cycle system is 24.2MW, and the total power generation efficiency is 25.5%; when the system is in rated operation, the solar heat collection field 1 is required to collect heat to heat the water temperature from 180 ℃ to 250 ℃, the heat collection efficiency is 75.7%, the heat collection power is 95.0MW, and the required heat collection field area is 156856m 2 . In addition, if the first-stage exothermic power generation mode is continuously operated for four hours, the high-temperature heat storage water tank 2 needs to store 4263 tons of high-temperature water; in the second-stage exothermic power generation mode, the residual medium-temperature water in the high-temperature heat storage water tank 2 can drive the second-stage organic Rankine cycle to operate for 7.6 hours; when collecting heat required by four hours of heat accumulation, an additional solar heat collection field 1 is needed to heat low-temperature water at 50 ℃ in a low-temperature heat accumulation water tank 3 to 250 ℃, the heat collection efficiency is 76.1%, and the required heat collection field area is 281577m 2 。
The detailed calculation results are as follows:
first-stage organic rankine cycle: rated power generation 10.0MW, first-stage organic working medium pump power consumption 414.4kW, toluene working medium flow 218.1kg/s, water working medium flow 296.1kg/s, heat absorption power 95.0MW and power generation efficiency 10.1%;
second-stage organic rankine cycle: rated power 15.3MW, second-stage organic working medium pump power 653.5KW, R123 working medium flow 381.6kg/s, hydraulic medium flow 154.9kg/s, heat absorption power 85.4MW and power generation efficiency 17.1%.
Claims (6)
1. Solar cascade organic Rankine cycle power generation system based on gas-liquid two-phase heat collector, its characterized in that: the system comprises a solar heat collection and storage loop, a primary organic Rankine cycle power generation loop and a secondary organic Rankine cycle power generation loop;
the solar heat collection and storage loop comprises a solar heat collection field (1), a high-temperature heat storage water tank (2), a low-temperature heat storage water tank (3), a low-temperature heat collection water pump (12), a medium-temperature water pump (13) and a high-temperature heat exchange water pump (14), wherein an outlet of the solar heat collection field (1) is connected with the high-temperature heat storage water tank (2) in series, and an inlet of the solar heat collection field (1) is connected with the low-temperature heat storage water tank (3) in series;
the first-stage organic Rankine cycle power generation loop comprises a first-stage evaporator (4), an intermediate heat exchanger (5), a first-stage turbine (8), a first-stage generator (10) and a first-stage organic working medium pump (15), wherein the first-stage evaporator (4), the first-stage turbine (8), the intermediate heat exchanger (5) and the first-stage organic working medium pump (15) are connected in series to form a first-stage organic working medium loop;
the secondary organic Rankine cycle power generation loop comprises an intermediate heat exchanger (5), a second-stage condenser (6), a second-stage evaporator (7), a second-stage steam turbine (9), a second-stage generator (11) and a second-stage organic working medium pump (16), wherein the intermediate heat exchanger (5) and the second-stage evaporator (7) are respectively connected with the second-stage steam turbine (9), the second-stage condenser (6) and the second-stage organic working medium pump (16) in series to form a second-stage organic working medium loop;
one side of the first-stage evaporator (4) is water working medium, the other side of the first-stage evaporator (4) is organic working medium, the first-stage evaporator (4) on one side of the water working medium is connected in series on one side of a high-temperature heat storage water tank (2) of a solar heat collection and storage loop, and the first-stage evaporator (4) on one side of the organic working medium is connected in series in a first-stage organic Rankine cycle power generation loop;
one side of the second-stage evaporator (7) is water working medium, the other side of the second-stage evaporator (7) is organic working medium, the second-stage evaporator (7) on one side of the water working medium is connected in series on one side of a low-temperature heat storage water tank (3) of a solar heat collection and storage loop, and the second-stage evaporator (7) on one side of the organic working medium is connected in series in a second-stage organic Rankine cycle power generation loop;
both sides of the intermediate heat exchanger (5) are organic working media, one side of the intermediate heat exchanger (5) is connected in series in the primary organic Rankine cycle power generation circuit, and the other side of the intermediate heat exchanger (5) is connected in series in the secondary organic Rankine cycle power generation circuit;
solar irradiation in daytime is more than 400W/m 2 When the system is in a working mode, the system performs heat collection, heat storage and power generation simultaneously;
and at night or on overcast days, the system continues to perform a power generation operation mode by utilizing the heat stored by the high-temperature heat storage water tank (2).
2. The gas-liquid two-phase heat collector-based solar cascade organic rankine cycle power generation system according to claim 1, wherein: the outlet of the solar heat collection field (1) is connected with the inlet at the lower part of the high-temperature heat storage water tank (2), the outlet at the lower part of the high-temperature heat storage water tank (2) is connected with the inlet of the high-temperature heat exchange water pump (14), the outlet of the high-temperature heat exchange water pump (14) is connected with the inlet at the water working medium side of the first-stage evaporator (4), the outlet at the water working medium side of the first-stage evaporator (4) is connected with the inlet at the upper part of the high-temperature heat storage water tank (2), the outlet at the bottom of the high-temperature heat storage water tank (2) is connected with the inlet of the medium-temperature water pump (13), the outlet of the medium-temperature water pump (13) is respectively connected with the inlet of the medium-temperature heat collection water valve (18) and the inlet of the medium-temperature heat exchange water valve (19), the outlet of the medium-temperature heat exchange water valve (18) is connected with the inlet at the water working medium side of the second-stage evaporator (7), the outlet at the water working medium side of the second-stage evaporator (7) is connected with the inlet of the throttle valve (20), the outlet of the throttle valve (20) is connected with the inlet at the low-temperature water inlet (3) of the low-temperature heat collection water pump (12), and the outlet of the low-temperature water pump (17) is connected with the inlet of the low-temperature heat collection water pump (12;
the outlet of the first-stage evaporator (4) on one side of the organic working medium is connected with the inlet of the first-stage steam turbine (8), the outlet of the first-stage steam turbine (8) is connected with the inlet of the intermediate heat exchanger (5) on one side, the outlet of the intermediate heat exchanger (5) on one side is connected with the inlet of the first-stage organic working medium pump (15), and the outlet of the first-stage organic working medium pump (15) is connected with the inlet of the first-stage evaporator (4) on one side of the organic working medium;
the outlet of the other side of the intermediate heat exchanger (5) is connected with the inlet of a first heat exchange outlet valve (22), the outlet of the first heat exchange outlet valve (22) is connected with the inlet of a second-stage steam turbine (9), the outlet of the second-stage steam turbine (9) is connected with the inlet of one side of an organic working medium of a second-stage condenser (6), the outlet of one side of the organic working medium of the second-stage condenser (6) is connected with the inlet of a second-stage organic working medium pump (16), the outlet of the second-stage organic working medium pump (16) is respectively connected with the inlet of a first heat exchange inlet valve (21) and the inlet of a second heat exchange inlet valve (23), the outlet of the first heat exchange inlet valve (21) is connected with the inlet of the other side of the intermediate heat exchanger (5), the outlet of the second heat exchange inlet valve (23) is connected with the inlet of one side of an organic working medium of the second-stage evaporator (7), the outlet of the second-stage evaporator (7) is connected with the inlet of the second heat exchange outlet valve (24).
3. The gas-liquid two-phase heat collector-based solar cascade organic rankine cycle power generation system according to claim 1, wherein: the solar heat collection field (1) is one of a parabolic trough heat collection field, a linear Fresnel heat collection field and a tower heat collection field.
4. The gas-liquid two-phase heat collector-based solar cascade organic rankine cycle power generation system according to claim 1, wherein: the organic working medium in the primary organic Rankine cycle power generation loop is one of toluene and pentane; the organic working medium in the first-stage evaporator (4) and the organic working medium at one side of the intermediate heat exchanger (5) are the same as the organic working medium in the first-stage organic Rankine cycle power generation loop.
5. The gas-liquid two-phase heat collector-based solar cascade organic rankine cycle power generation system according to claim 1, wherein: the organic working medium in the secondary organic Rankine cycle power generation loop is one of trifluoro dichloroethane (R123) and pentafluoropropane (R245 fa); the organic working medium at the other side of the intermediate heat exchanger (5), the organic working medium in the second-stage condenser (6) and the organic working medium in the second-stage evaporator (7) are the same as the organic working medium in the second-stage organic Rankine cycle power generation loop.
6. The gas-liquid two-phase heat collector-based solar cascade organic rankine cycle power generation system according to claim 1, wherein: the working temperature of the high-temperature heat storage water tank (2) is 180-280 ℃, and the working temperature of the low-temperature heat storage water tank (3) is 30-150 ℃.
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