CN115013269B - Solar-assisted intermediate-deep geothermal heat pipe energy system and control method thereof - Google Patents
Solar-assisted intermediate-deep geothermal heat pipe energy system and control method thereof Download PDFInfo
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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
- F03G4/00—Devices for producing mechanical power from geothermal energy
- F03G4/023—Devices for producing mechanical power from geothermal energy characterised by the geothermal collectors
- F03G4/029—Devices for producing mechanical power from geothermal energy characterised by the geothermal collectors closed loop geothermal collectors, i.e. the fluid is pumped through a closed loop in heat exchange with the geothermal source, e.g. 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
- 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
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
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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
- F03G4/00—Devices for producing mechanical power from geothermal energy
- F03G4/037—Devices for producing mechanical power from geothermal energy having other power cycles, e.g. Stirling, transcritical or supercritical cycles; combined with other power sources, e.g. wind, gas or nuclear
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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
- F03G6/068—Devices for producing mechanical power from solar energy with solar energy concentrating means having other power cycles, e.g. Stirling or transcritical, supercritical cycles; combined with other power sources, e.g. wind, gas or nuclear
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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
- F03G6/098—Components, parts or details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D11/00—Central heating systems using heat accumulated in storage masses
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D18/00—Small-scale combined heat and power [CHP] generation systems specially adapted for domestic heating, space heating or domestic hot-water supply
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2101/00—Electric generators of small-scale CHP systems
- F24D2101/10—Gas turbines; Steam engines or steam turbines; Water turbines, e.g. located in water pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/11—Geothermal energy
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D2200/00—Heat sources or energy sources
- F24D2200/14—Solar energy
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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
- Y02E10/44—Heat exchange systems
Abstract
The invention provides a solar-assisted middle-deep geothermal heat pipe energy system and a control method thereof, belonging to the technical field of middle-deep geothermal heat pipe energy; the technical problem to be solved is as follows: the improvement of the hardware structure of the solar-assisted intermediate-deep geothermal heat pipe energy system is provided; the technical scheme for solving the technical problems is as follows: the solar heat exchange branch is arranged at the upper end of the ground part of the main medium-deep geothermal heat exchange path, wherein a connecting pipeline between the cold working medium tank and the hot working medium tank forms a circulating pipeline system with the solar heat exchange branch and the main medium-deep geothermal heat exchange path respectively, and the cold working medium tank and the hot working medium tank are also connected with a heat supply system through pipelines; the invention is applied to the energy system of the intermediate-deep geothermal heat pipe.
Description
Technical Field
The invention provides a solar-assisted medium-deep geothermal heat pipe energy system and a control method thereof, belonging to the technical field of medium-deep geothermal heat pipe energy.
Background
The heat pump heating system with buried pipes in middle and deep layers is a new geothermal energy utilization mode, and is characterized in that the buried depth of a drill hole is generally 1000-3000 m, the heat pump heating system has good winter heat exchange and heat storage performance, and is suitable for winter heating in northern cold areas or buildings with narrow buried pipe spaces.
The prior heat pump system for the buried pipe of the middle-deep geothermal floor has the following defects:
(1) the heat exchange efficiency of the buried pipe needs to be improved;
(2) free solar energy light and heat cannot be reasonably utilized, and carbon emission cannot be further reduced;
(3) the model selection of the system working medium is limited by inverse Carnot cycle, and the system working medium cannot generate high-temperature heat energy output above 200 ℃ and cannot be applied to steam turbine power generation in an expanded way;
(4) the regulation and control guarantee design of the cogeneration needs to be improved, and a technical design of peak regulation and energy storage, no stop of operation during system maintenance and improvement of the regulation and control safety and stability of the system is required.
Therefore, the invention provides a solar-assisted intermediate-deep geothermal heat pipe energy system and a control method thereof, which can solve the four problems, do not need additional power to consume energy and can fully utilize free solar energy and heat. The system components of the invention all use the existing mature technologies and products, the technical feasibility is stronger, and the safety and the stability of the product functions are better.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention aims to solve the technical problems that: the improvement of the hardware structure of the solar-assisted intermediate-deep geothermal heat pipe energy system is provided.
In order to solve the technical problems, the technical scheme adopted by the invention is as follows: the utility model provides a deep geothermal heat pipe energy system in solar energy is supplementary, includes cold working medium jar, hot working medium jar, solar energy heat transfer branch road, deep geothermal heat transfer main road in, solar energy heat transfer branch road sets up in deep geothermal heat transfer main road in the upper end of ground part, wherein between cold working medium jar and the hot working medium jar connecting tube respectively with solar energy heat transfer branch road, deep geothermal heat transfer main road in formation circulation pipe-line system, still pass through pipe connection heating system between cold working medium jar and the hot working medium jar.
The main medium-deep geothermal heat exchange path comprises geothermal heat pipes, geothermal heat pipe heat exchange fins, a geothermal heat exchanger and a geothermal heat exchange temperature sensor, wherein the geothermal heat pipes are arranged on a medium-deep stratum and extend to the ground;
the first main pipeline is provided with a working medium pump, the first branch pipeline is provided with a geothermal heat exchange regulating valve, the ground output end, close to the geothermal heat exchanger, of the second main pipeline is provided with a geothermal heat exchange temperature sensor, and the third main pipeline is provided with a working medium bypass valve.
The solar heat exchange branch comprises a solar heat exchange platform, the solar heat exchange platform is placed on the ground part of the geothermal heat pipe, a solar heat pipe heat exchanger, a solar heat pipe and a solar heat pipe heat exchanger temperature sensor are arranged on the solar heat exchange platform, the first main pipeline is connected with one end of the solar heat pipe through a second branch pipeline, the other end of the solar heat pipe is connected with a thermal working medium tank through a second main pipeline, and a solar heat exchange adjusting valve is arranged on the second branch pipeline.
The heat supply system comprises a steam turbine generator, a heat supply phase-change heat storage module and a heat supply heat exchanger, wherein the steam turbine generator is arranged on a fourth main pipe connected with the cold working medium tank and the hot working medium tank, the fourth main pipe is connected with the heat supply phase-change heat storage module through a third branch pipe, the heat supply phase-change heat storage module is connected with the heat supply heat exchanger, and the heat supply heat exchanger is connected with a heat exchange pipeline;
and a steam turbine generator power regulating valve is arranged on the fourth main pipe close to the cold working medium tank end, and a heat supply power regulating valve is arranged on the third branch pipe close to the cold working medium tank end.
A working medium tank phase change heat storage module is arranged inside the hot working medium tank;
the material of the working medium tank phase-change heat storage module and the material of the heat supply phase-change heat storage module both adopt ternary molten salt, namely mixed nitrate consisting of 53 mass percent of potassium nitrate, 40 mass percent of sodium nitrite and 7 mass percent of sodium nitrate, and the melting point is 142 ℃ and the gasification point is 500 ℃.
The part of the geothermal heat pipe, which is contacted with the ground, is provided with a pressure-resistant sealing protective layer and a ground hardening protective layer.
A control method of a solar-assisted intermediate-deep geothermal heat pipe energy system adopts the solar-assisted intermediate-deep geothermal heat pipe energy system and comprises the following steps:
the control steps for cogeneration as a conventional one are as follows:
the working medium in the cold working medium tank is driven by the working medium pump to carry out system circulation, the opening degrees of the geothermal heat exchange regulating valve and the solar heat exchange regulating valve are respectively regulated according to the parameter proportion of a geothermal heat exchange temperature sensor and a solar heat pipe heat exchanger temperature sensor, and the flow of the working medium in the cold working medium tank flowing through the solar heat exchange branch and the geothermal heat pipe is controlled;
after being heated, working media in the cold working medium tank enter the hot working medium tank for pressure stabilization and storage, one path of working media is used for heating high-pressure steam by the steam turbine generator to drive the generator to generate electricity, the other path of working media enters the heat supply phase change heat storage module to be used as auxiliary flow to participate in heat energy regulation, and the opening degrees of the steam turbine generator power regulating valve and the heat supply power regulating valve are regulated according to the output power proportion of the steam turbine generator;
the control logics of the geothermal heat exchange regulating valve and the solar heat exchange regulating valve are as follows:
(1) Firstly, the operation of the working medium pump is protected to be safe and stable, and the total opening sectional area of the geothermal heat exchange regulating valve and the solar heat exchange regulating valve is always equal to the section of an outlet pipeline of the working medium pumpArea, initial opening degree of geothermal heat exchange regulating valve is phi 1 The sectional area of an outlet pipeline of the working medium pump is adopted, and the solar heat exchange regulating valve is initially and fully closed;
(2) Opening phi of geothermal heat exchange regulating valve 3 =a(T s -T 11 ) 2 +b(T s -T 11 ) + c, wherein, T s For a set temperature, T, of the working medium at the outlet of the geothermal heat exchanger 11 The measured temperature of the working medium at the outlet of the geothermal heat exchanger is fed back at intervals, and a, b and c are proportionality constants which are different according to the model of equipment and the temperature interval of geothermal heat;
(3) Opening phi of solar heat exchange regulating valve 4 =Φ 1 -Φ 3 Wherein phi is 1 The cross section of the outlet pipeline of the working medium pump is ensured 1 ≥Φ 3 ；
The control logics of the power regulating valve and the heat supply power regulating valve of the steam turbine generator are as follows:
(1) Initial opening degree of power regulating valve of steam turbine generator is phi 2 The heat supply power regulating valve is initially and fully closed;
(2) Opening phi of power regulating valve of steam turbine generator 21 =e(P s -P 22 ) 2 +f(P s -P 22 ) + g wherein P s For rated output power of the generator, P 22 The measured output power of the generator is fed back at intervals, and e, f and g are proportionality constants which are different according to the model of equipment and the temperature interval of geothermal heat;
(3) Opening phi of heat supply power regulating valve 23 =Φ 2 -Φ 21 Wherein phi is 2 The sectional area of the outlet pipeline of the hot working medium tank is ensured to be phi 2 ≥Φ 21 。
The working medium in the geothermal heat pipe and the cold working medium tank adopts naphthalene with a chemical formula of C 10 H 8 Melting point at one atmosphere: 80 to 82 ℃, boiling point: 217.9 ℃, critical temperature: 475.2 ℃;
the working medium of the solar heat pipe adopts methanol with a chemical formula of CH 3 OH, melting point at one atmosphere: boiling at-97.8 deg.CPoint: 64.7 ℃, critical temperature: 240 ℃;
the solar heat pipe comprises a solar heat pipe heat exchanger and is characterized in that a high-light-transmission resin sheath, a graphene solar energy absorbing coating and a copper heat pipe are sequentially arranged from outside to inside in the structure of the solar heat pipe heat exchanger, the high-light-transmission resin sheath, the graphene solar energy absorbing coating and the copper heat exchanger are sequentially arranged from outside to inside in the structure of the solar heat pipe heat exchanger, and naphthalene conveyed by a pipeline absorbs heat released from a condensation section of the solar heat pipe heat exchanger and also absorbs solar photo-heat absorbed by a shell of the solar heat pipe heat exchanger.
A control method of a solar-assisted intermediate-deep geothermal heat pipe energy system adopts the solar-assisted intermediate-deep geothermal heat pipe energy system and comprises the following steps:
the peak regulation and energy storage control steps for cogeneration are as follows:
when the steam turbine generator cannot meet the power load of a downstream user under the current working condition or rated output power, the peak shaving function of the combined heat and power generation is started through manual control;
firstly, checking and confirming that a geothermal heat exchange regulating valve is fully opened and a solar heat exchange regulating valve is fully closed, a power regulating valve of a steam turbine generator is fully opened and a heat supply power regulating valve is fully closed, so that a system pipeline is switched to a full power supply function;
starting the phase change heat storage module of the working medium tank, so that the phase change heat storage module of the working medium tank at the temperature of more than 250 ℃ can fully heat the working medium, and the output power of the steam turbine generator is improved;
when the temperature of the working medium in the daily hot working medium tank is more than 200 ℃, the working medium of the working medium tank phase change heat storage module is heated to melt and store the working medium, and the working medium is started when the peak regulation function of cogeneration is started by manual operation;
and when the electric power peak regulation is finished or the temperature of the phase change heat storage module of the working medium tank is reduced to 150 ℃ or below and is maintained for a set time, the system is reset to the working state before the peak regulation function.
The working medium in the geothermal heat pipe and the cold working medium tank adopts naphthalene with a chemical formula of C 10 H 8 Melting point at one atmosphere: 80 to 82 ℃, boiling point: 217.9 ℃, critical temperature: 475.2℃；
the working medium of the solar heat pipe adopts methanol with a chemical formula of CH 3 OH, melting point at one atmosphere: -97.8 ℃, boiling point: 64.7 ℃, critical temperature: 240 ℃;
the structure of the solar heat pipe comprises a high-light-transmission resin sheath, a graphene solar energy absorption coating and a copper heat pipe from outside to inside in sequence, the structure of the solar heat pipe heat exchanger comprises the high-light-transmission resin sheath, the graphene solar energy absorption coating and the copper heat exchanger from outside to inside in sequence, and naphthalene conveyed by a pipeline absorbs heat generated in a condensation section of the solar heat pipe and also absorbs solar photo-heat absorbed by a shell of the solar heat pipe heat exchanger.
Compared with the prior art, the invention has the beneficial effects that:
(1) the heat exchange efficiency of the geothermal heat pipe reaches more than 98%, no additional power is needed, the fluid resistance is small, the structure is simple, the processing is easy, the cost is low, and the work is reliable; the heat exchange efficiency of a common ground heat exchanger is about 95 percent.
(2) The free solar energy light and heat are fully utilized, and the carbon emission is further reduced.
(3) The type selection of the system working medium is flexible, and the working medium with the adaptive melting point, boiling point and critical temperature can be selected according to different ground temperature intervals, so that the system working medium is expanded and applied to power generation and heat supply of the steam turbine.
(4) The method has the advantages of improving the regulation and control guarantee design of cogeneration, increasing peak regulation and energy storage, avoiding the stop of operation during system maintenance, and improving the safety and stability of system regulation and control.
Drawings
The invention is further described below with reference to the accompanying drawings:
FIG. 1 is a schematic diagram of the system of the present invention;
in the figure: 1. a cold working medium tank; 2. a working medium pump; 3. a geothermal heat exchange regulating valve; 4. a solar heat exchange regulating valve; 5. a solar heat pipe heat exchanger; 6. a solar heat pipe; 7. a solar heat pipe heat exchanger temperature sensor; 8. a solar heat exchange platform; 9. geothermal heat pipe heat exchange fins; 10. a geothermal heat exchanger; 11. a geothermal heat exchange temperature sensor; 12. a geothermal heat pipe condensing section; 13. a compression-resistant sealing protective layer; 14. hardening the protective layer on the ground; 15. a geothermal heat pipe evaporation section; 16. a geothermal heat pipe; 17. a middle deep stratum; 18. a hot working medium tank; 19. the working medium tank phase change heat storage module; 20. a working medium tank bypass valve; 21. a steam turbine generator power regulating valve; 22. a steam turbine generator; 23. a heat supply power regulating valve; 24. a heat supply phase change heat storage module; 25. a heat supply heat exchanger; 26. a heat supply pipeline;
100 is a first main pipe, 101 is a first branch pipe, 102 is a second main pipe, 103 is a third main pipe, 104 is a second branch pipe, 105 is a fourth main pipe, and 106 is a third branch pipe.
Detailed Description
As shown in figure 1, the invention provides a solar-assisted intermediate-deep geothermal heat pipe energy system, which comprises a cold working medium tank 1, a hot working medium tank 10, a solar heat exchange branch and an intermediate-deep geothermal heat exchange main path, wherein the solar heat exchange branch is arranged at the upper end of the ground part of the intermediate-deep geothermal heat exchange main path, a connecting pipeline between the cold working medium tank 1 and the hot working medium tank 18 forms a circulating pipeline system with the solar heat exchange branch and the intermediate-deep geothermal heat exchange main path respectively, and a heat supply system is also connected between the cold working medium tank 1 and the hot working medium tank 18 through a pipeline.
The main medium-deep geothermal heat exchange path comprises geothermal heat pipes 16, geothermal heat pipe heat exchange fins 9 and a geothermal heat exchanger 10, wherein the geothermal heat pipes 16 are arranged on a medium-deep stratum and extend to the ground, a geothermal heat pipe evaporation section 15 is arranged in the middle of each geothermal heat pipe 16, a geothermal heat pipe condensation section 12 is arranged on the ground in the middle of each geothermal heat pipe 16, a main outlet of each cold working medium tank 1 is connected with a first main pipeline 100, the first main pipeline 100 is connected with an input end of the geothermal heat exchanger 10 through a first branch pipeline 101, an output end of the geothermal heat exchanger 10 is connected with a main inlet of a hot working medium tank 18 through a second main pipeline 102, and a first outlet of the hot working medium tank 18 is connected with a first inlet of the cold working medium tank 1 through a third main pipeline 103;
the first main pipeline 100 is provided with a working medium pump 2, the first branch pipeline 101 is provided with a geothermal heat exchange regulating valve 3, the ground output end of the second main pipeline 102 close to the geothermal heat exchanger 10 is provided with a geothermal heat exchange temperature sensor 11, and the third main pipeline 103 is provided with a working medium bypass valve 20.
The solar heat exchange branch comprises a solar heat exchange platform 8, the solar heat exchange platform 8 is placed on the ground part of the geothermal heat pipe 16, a solar heat pipe heat exchanger 5, a solar heat pipe 6 and a solar heat pipe heat exchanger temperature sensor 7 are arranged on the solar heat exchange platform 8, the first main pipeline 100 is connected with one end of the solar heat pipe 6 through a second branch pipeline 104 and is connected with the other end of the solar heat pipe 6 through a second main pipeline 102 and a thermal working medium tank 18, and a solar heat exchange regulating valve 4 is arranged on the second branch pipeline 104.
The heat supply system comprises a steam turbine generator 22, a heat supply phase-change heat storage module 24 and a heat supply heat exchanger 25, wherein the steam turbine generator 22 is arranged on a fourth main pipeline 105 connected with the cold working medium tank 1 and the hot working medium tank 18, the fourth main pipeline 105 is connected with the heat supply phase-change heat storage module 24 through a third branch pipeline 106, the heat supply phase-change heat storage module 24 is connected with the heat supply heat exchanger 25, and the heat supply heat exchanger 25 is connected with a heat exchange pipeline 26;
wherein, a steam turbine generator power regulating valve 21 is arranged on the fourth main pipeline 105 near the end of the cold working medium tank 1, and a heat supply power regulating valve 23 is arranged on the third branch pipeline 106 near the end of the cold working medium tank 1.
And a working medium tank phase change heat storage module 19 is arranged inside the hot working medium tank 18.
The part of the geothermal heat pipe 16 contacting with the ground is provided with a pressure-resistant sealing protective layer 13 and a ground hardening protective layer 14.
Naphthalene is selected as the working medium of the geothermal heat pipe 16 and the cold working medium tank 1, and the chemical formula is C 10 H 8 Melting point at one atmosphere: 80 to 82 ℃, boiling point: 217.9 ℃, critical temperature: 475.2 ℃, and is suitable for the middle-deep geothermal temperature range of 200-400 ℃. The physicochemical property of the single component working medium is stable, which is beneficial to the system to give full play to design parameters and functions, and avoids the disturbance of the system function due to fluctuation of the physicochemical property of the working medium caused by the easy change of the component proportion of the mixture working medium.
The invention relates to solar energyThe working medium of the heat pipe 6 is methanol with a chemical formula of CH 3 OH, melting point at one atmosphere: 97.8 ℃, boiling point: 64.7 ℃, critical temperature: 240 ℃ is suitable for the solar photo-thermal temperature range of about 100 ℃, and also gives consideration to outdoor anti-freezing in winter and manual maintenance-free. The solar heat pipe 6 is sequentially provided with a high-light-transmission resin sheath, a graphene solar energy absorption coating and a copper heat pipe from outside to inside, and the highest solar energy radiation absorption rate reaches more than 98%. The structure of the solar heat pipe exchanger 5 is sequentially provided with a high-light-transmittance resin sheath, a graphene solar energy absorption coating and a copper heat exchanger from outside to inside, and naphthalene conveyed by a pipeline absorbs heat released in a condensation section of the solar heat pipe 6 and also absorbs solar energy photo-heat absorbed by a shell of the solar heat pipe exchanger 5 in the solar heat pipe exchanger 5. The solar heat exchange branch circuit has the functions of heating and preheating the shunted naphthalene and providing heat supply. The installation angle of the solar module platform 8 is the optimum azimuth angle and inclination angle of the local solar radiation receiving surface.
The material of the working medium tank phase-change heat storage module 19 and the heat supply phase-change heat storage module 24 is ternary molten salt, namely mixed nitrate consisting of 53 mass percent of potassium nitrate, 40 mass percent of sodium nitrite and 7 mass percent of sodium nitrate, the melting point of the mixed nitrate is 142 ℃, and the gasification point of the mixed nitrate is 500 ℃.
The main functions realized by the system of the invention comprise: (1) conventional cogeneration; (2) peak regulation energy storage of cogeneration; (3) the operation is not stopped when the system is maintained; (4) the system regulates and controls the design of the position of a regulating valve of safety and stability.
(1) Conventional cogeneration: the working medium pump 2 drives naphthalene in the cold working medium tank 1 to perform system circulation, the opening degrees of the geothermal heat exchange regulating valve 3 and the solar heat exchange regulating valve 4 are respectively regulated according to the parameter proportion of the geothermal heat exchange temperature sensor 11 and the solar heat pipe heat exchanger temperature sensor 7, and the flow of naphthalene flowing through the solar heat exchange branch and the geothermal heat pipe 16 is controlled. Naphthalene is heated and enters the hot working medium tank 18 for pressure stabilization and storage, one path of naphthalene enters the steam turbine generator 22 to heat high-pressure steam to drive the generator to generate electricity, the other path of naphthalene enters the heat supply phase change heat storage module 24 to be used as auxiliary flow and heat energy regulation, and the opening degrees of the steam turbine generator power regulating valve 21 and the heat supply power regulating valve 23 are regulated according to the output power proportion of the steam turbine generator 22.
Control logics of the geothermal heat exchange regulating valve 3 and the solar heat exchange regulating valve 4 are as follows: (1) Firstly, the operation of the working medium pump 2 is protected to be safe and stable, the total opening sectional area of the geothermal heat exchange regulating valve 3 and the solar heat exchange regulating valve 4 is always equal to the sectional area of an outlet pipeline of the working medium pump 2, so that the output pressure of the working medium pump 2 is protected to be stable, and the safety of a pump body is protected. The initial opening degree of the geothermal heat exchange regulating valve 3 is phi 1 And the solar heat exchange regulating valve 4 is initially and fully closed. (2) Opening phi of geothermal heat exchange regulating valve 3 3 =a(T s -T 11 ) 2 +b(T s -T 11 ) + c, wherein, T s For a set temperature, T, of naphthalene at the outlet of the geothermal heat exchanger 10 11 The measured temperature of the naphthalene at the outlet of the geothermal heat exchanger 10 is fed back every 5min, and a, b and c are proportionality constants which are different according to the model of equipment and the temperature interval of geothermal heat. (3) Opening phi of solar heat exchange regulating valve 4 4 =Φ 1 -Φ 3 Wherein phi is 1 Is the cross section of the outlet pipeline of the working medium pump 2. Guarantee phi 1 ≥Φ 3 。
Control logic for steam turbine generator power regulating valve 21 and heating power regulating valve 23: (1) The initial opening degree of the power regulating valve 21 of the steam turbine generator is phi 2 The heating power regulating valve 23 is initially fully closed. (2) Opening phi of power regulating valve 21 of steam turbine generator 21 =e(P s -P 22 ) 2 +f(P s -P 22 ) + g wherein P s For rated output power of the generator, P 22 The feedback is carried out once every 5min for the actually measured output power of the generator, and e, f and g are proportionality constants which are different according to the model of equipment and the temperature interval of geothermal heat. (3) Opening phi of heat supply power regulating valve 23 23 =Φ 2 -Φ 21 Wherein phi is 2 The cross-sectional area of the outlet pipe of the hot working medium tank 18. Guarantee phi 2 ≥Φ 21 。
(2) Peak regulation energy storage of cogeneration: under the condition of normal operation of the system, the heat supply function can meet the heat load of a user. If the steam turbine generator 22 cannot meet the power load of the downstream users under the current working condition or rated output power, the peak shaving function of the cogeneration is started by manual operation. Firstly, checking and confirming that the geothermal heat exchange regulating valve 3 is fully opened, the solar heat exchange regulating valve 4 is fully closed, the power regulating valve 21 of the steam turbine generator is fully opened, and the heat supply power regulating valve 23 is fully closed, so that the system pipeline is switched to the function of full power supply. And opening the phase change heat storage module 19 of the working medium tank, so that the phase change heat storage module 19 with the temperature of more than 250 ℃ can heat naphthalene fully, and the output power of the steam turbine generator 22 is improved. The material of the working medium tank phase change heat storage module 19 is ternary molten salt, namely mixed nitrate consisting of 53 mass percent of potassium nitrate, 40 mass percent of sodium nitrite and 7 mass percent of sodium nitrate, the melting point is 142 ℃, the gasification point is 500 ℃, and the application of medium-deep geothermal power generation at 200-400 ℃ is met. The working medium tank phase change heat storage module 19 heats the ternary fused salt to melt, preserve heat and store when the temperature of naphthalene in the daily hot working medium tank 18 is above 200 ℃, and is started when the peak regulation function of cogeneration is started by manual operation. When the electric power peak regulation is finished or the temperature of the phase change heat storage module 19 of the working medium tank is reduced to 150 ℃ or below and is maintained for 30min, the system is reset to the working state before the peak regulation function. If the power peak regulation is finished, manually controlling and resetting; if the temperature of the working medium tank phase change heat storage module 19 is reduced to 150 ℃ or below and maintained for 30min, the system automatically resets.
(3) The operation is not stopped when the system is maintained: and when 2-17 parts are damaged and need to be maintained, closing the geothermal heat exchange regulating valve 3 or the solar heat exchange regulating valve 4 or the geothermal heat exchange regulating valve 3 and the solar heat exchange regulating valve 4, and ensuring that the cold and hot working medium tanks are communicated through the cogeneration equipment by combining maintenance of damaged parts. And starting the phase change heat storage module 19 of the working medium tank to heat the naphthalene in the hot working medium tank 18. And the power generation and heat supply are continued while the equipment is maintained. If the cold and hot working medium tank is communicated only through the cogeneration equipment, then in the later stage of this function maintenance, the pressure in the cold working medium tank 1 rises gradually, then opens the working medium tank bypass valve 20, balances the pressure in the cold and hot working medium tank, guarantees the safety of generating electricity. And in the pressure balancing process, the bypass valve 20 of the working medium tank is closed until the output power of the steam turbine generator 22 is reduced to 20% of the rated output power, so that the function is stopped, and the time interval from the restart of the system to the recovery of the normal operation is ensured to be within 1.5 hours.
(4) The technical design of the safety and stability of system regulation and control comprises the following steps: (1) The arrangement position of the working medium pump 2 is shown in figure 1, so that the pump head is used for directly overcoming the internal flow resistance of the geothermal heat exchanger 10 and the solar heat pipe heat exchanger 5, and the heat pump is stable and efficient. (2) The arrangement positions of the geothermal heat exchange regulating valve 3 and the solar heat exchange regulating valve 4 are shown in figure 1, the flow distribution proportion is regulated at the low-temperature and low-pressure stage of naphthalene, the safety of a regulating valve body is protected, the service life is prolonged, and the functional parameter regulation compatibility with the working medium pump 2 is better. (3) The arrangement positions of the power regulating valve 21 and the heat supply power regulating valve 23 of the steam turbine generator are shown in figure 1, the design intentions are the same as those of the geothermal heat exchange regulating valve 3 and the solar heat exchange regulating valve 4, namely, the flow distribution proportion is regulated at the low-temperature and low-pressure stage of naphthalene, so that the safety of the valve body of the regulating valve is protected, and the service life is prolonged. (4) The arrangement position of the working medium tank bypass valve 20 is shown in figure 1, and the working medium tank bypass valve is used for the function of no stop of operation during system maintenance and can also be used for the safety and stability of the pressure in the cold working medium tank 1 and the hot working medium tank 18 during maintenance. (5) The solar heat pipe heat exchanger temperature sensor 7 and the geothermal heat exchange temperature sensor 11 have a pipeline self-checking function, and system pipeline leakage is mainly likely to occur in a pipeline section from the cold working medium tank 1 to the geothermal heat pipe 16 and the solar heat pipe heat exchanger 5. For the solar heat pipe heat exchanger temperature sensor 7, T is measured if the daytime system is initially started 0 If the real value of the temperature sensor 7 of the solar heat pipe exchanger reaches T within 30min 0 +10 deg.C (when the solar radiation intensity is less than 120W/m) 2 ) Or if the measured value of the temperature sensor 7 of the solar heat pipe heat exchanger reaches T within 30min 0 +25 deg.C (when 120W/m) 2 The solar radiation intensity is less than or equal to 300W/m 2 ) Or if the measured value of the temperature sensor 7 of the solar heat pipe heat exchanger reaches T within 30min 0 +35 ℃ (when 300W/m 2 Less than or equal to the solar radiation intensity), the solar heat exchange branch may leak or be blocked, and the leak detection needs to be checked; if the system normally runs, in the normal day, if the actual measurement value of the temperature sensor 7 of the solar heat pipe heat exchanger rises by 10 ℃ within 30min (when the solar radiation intensity is less than 120W/m) 2 ) Or the heat exchange of the solar heat pipe within 30minThe measured value of the temperature sensor 7 rises by 25 ℃ (when 120W/m) 2 The solar radiation intensity is less than or equal to 300W/m 2 ) Or the measured value of the temperature sensor 7 of the solar heat pipe heat exchanger rises by 35 ℃ (when the measured value is 300W/m) within 30min 2 Not more than the solar radiation intensity), the solar heat exchange branch may leak, and the leak detection needs to be checked. For the geothermal heat exchange temperature sensor 11, if the system is initially started, the measured value T is 00 If the measured value of the geothermal heat exchange temperature sensor 11 does not reach T within 1.5 hours 00 At +100 ℃, leakage or pipeline blockage may exist and need to be checked; if the feedback value of the geothermal heat exchange temperature sensor 11 drops by 60 ℃ within 1.5 hours in the normal operation process of the system, leakage or pipeline blockage may exist, and inspection is needed.
The geothermal heat pipe 16 of the present invention adopts a gravity heat pipe, and the academic name of the gravity heat pipe is called as a "two-phase closed thermosiphon", which is called as a "thermosiphon" for short. The copper pipe is vacuumized and then filled with a certain amount of working medium, the working medium is repeatedly circulated in the copper pipe in an evaporation-condensation phase change process, and the heat of an evaporation section is continuously transferred to a condensation section, so that the heat transfer process of transferring the heat is completed. The basic working principle of the gravity heat pipe is as follows, the vacuum unit is used for vacuumizing the interior of a welded and sealed pipe shell, then a proper amount of working medium is filled in the pipe shell, and then cold welding and ultrasonic welding sealing are carried out. The complete gravity heat pipe is divided into three parts: an evaporation section (heating section), a condensation section (cooling section) and a heat insulation section. The working medium is vaporized and gasified when the evaporation section of the gravity heat pipe is heated, and simultaneously absorbs a large amount of latent heat of vaporization, the steam flows to the condensation section quickly under a small pressure difference, the steam is condensed on the inner wall of the condensation section, a large amount of latent heat of vaporization is released in the period, and the condensed working medium flows to the evaporation section along the pipe wall under the action of gravity. Thus, the heat is continuously transferred from one end of the gravity heat pipe to the other end by the high-speed circulation. The gravity heat pipe has the biggest characteristic that no liquid absorption core exists in the pipe cavity, so the gravity heat pipe has the advantages of simple structure, easiness in processing, low cost, reliability in working and the like. The working medium of the gravity assisted heat pipe can be flexibly adjusted according to the difference of the working environment temperature of the heat pipe, and the working medium with the boiling point, the melting point and the critical point which are suitable for the corresponding temperature range can be flexibly adjusted.
It should be noted that, regarding the specific structure of the present invention, the connection relationship between the modules adopted in the present invention is determined and can be realized, except for the specific description in the embodiment, the specific connection relationship can bring the corresponding technical effect, and the technical problem proposed by the present invention is solved on the premise of not depending on the execution of the corresponding software program.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.
Claims (4)
1. A control method of a solar-assisted middle-deep geothermal heat pipe energy system adopts the solar-assisted middle-deep geothermal heat pipe energy system, the system comprises a cold working medium tank, a hot working medium tank, a solar heat exchange branch and a middle-deep geothermal heat exchange main path, the solar heat exchange branch is arranged at the upper end of the middle-deep geothermal heat exchange main path positioned on the ground part, wherein a connecting pipeline between the cold working medium tank and the hot working medium tank forms a circulating pipeline system with the solar heat exchange branch and the middle-deep geothermal heat exchange main path respectively, and a heat supply system is also connected between the cold working medium tank and the hot working medium tank through a pipeline;
the main medium-deep geothermal heat exchange path comprises geothermal heat pipes, geothermal heat pipe heat exchange fins and geothermal heat exchangers, wherein the geothermal heat pipes are arranged on a medium-deep stratum and extend to the ground, a geothermal heat pipe evaporation section is arranged in the middle of each geothermal heat pipe on the medium-deep stratum, a geothermal heat pipe condensation section is arranged in the middle of each geothermal heat pipe on the ground, a main outlet of each cold working medium tank is connected with a first main pipeline, the first main pipeline is connected with an input end of each geothermal heat exchanger through a first branch pipeline, an output end of each geothermal heat exchanger is connected with a main inlet of each hot working medium tank through a second main pipeline, and a first outlet of each hot working medium tank is connected with a first inlet of each cold working medium tank through a third main pipeline;
the first main pipeline is provided with a working medium pump, the first branch pipeline is provided with a geothermal heat exchange regulating valve, the ground output end of the second main pipeline close to the geothermal heat exchanger is provided with a geothermal heat exchange temperature sensor, and the third main pipeline is provided with a working medium bypass valve;
the solar heat exchange branch comprises a solar heat exchange platform, the solar heat exchange platform is placed on the ground part of the geothermal heat pipe, a solar heat pipe heat exchanger, a solar heat pipe and a solar heat pipe heat exchanger temperature sensor are arranged on the solar heat exchange platform, the first main pipeline is connected with one end of the solar heat pipe through a second branch pipeline, the other end of the solar heat pipe is connected with a hot working medium tank through a second main pipeline, and a solar heat exchange regulating valve is arranged on the second branch pipeline;
the heat supply system comprises a steam turbine generator, a heat supply phase-change heat storage module and a heat supply heat exchanger, wherein the steam turbine generator is arranged on a fourth main pipe connected with the cold working medium tank and the hot working medium tank, the fourth main pipe is connected with the heat supply phase-change heat storage module through a third branch pipe, the heat supply phase-change heat storage module is connected with the heat supply heat exchanger, and the heat supply heat exchanger is connected with a heat exchange pipeline;
the steam turbine generator power regulating valve is arranged on the fourth main pipe close to the cold working medium tank end, and the heat supply power regulating valve is arranged on the third branch pipe close to the cold working medium tank end;
the method is characterized in that: the method comprises the following steps:
the control steps for cogeneration as a conventional one are as follows:
the working medium in the cold working medium tank is driven by the working medium pump to carry out system circulation, the opening degrees of the geothermal heat exchange regulating valve and the solar heat exchange regulating valve are respectively regulated according to the parameter proportion of a geothermal heat exchange temperature sensor and a solar heat pipe heat exchanger temperature sensor, and the flow of the working medium in the cold working medium tank flowing through the solar heat exchange branch and the geothermal heat pipe is controlled;
after being heated, working media in the cold working medium tank enter the hot working medium tank for pressure stabilization and storage, one path of working media is used for heating high-pressure steam by the steam turbine generator to drive the generator to generate electricity, the other path of working media enters the heat supply phase change heat storage module to be used as auxiliary flow to participate in heat energy regulation, and the opening degrees of the steam turbine generator power regulating valve and the heat supply power regulating valve are regulated according to the output power proportion of the steam turbine generator;
the control logic of the geothermal heat exchange regulating valve and the solar heat exchange regulating valve is as follows:
(1) Firstly, the operation of the working medium pump is protected to be safe and stable, the total opening sectional area of the geothermal heat exchange regulating valve and the solar heat exchange regulating valve is always equal to the sectional area of an outlet pipeline of the working medium pump, and the initial opening of the geothermal heat exchange regulating valve is phi 1 The sectional area of an outlet pipeline of the working medium pump is adopted, and the solar heat exchange regulating valve is initially and fully closed;
(2) Opening phi of geothermal heat exchange regulating valve 3 =a(T s -T 11 ) 2 +b(T s -T 11 ) + c, wherein, T s For a set temperature, T, of the working medium at the outlet of the geothermal heat exchanger 11 The measured temperature of the working medium at the outlet of the geothermal heat exchanger is fed back at intervals, and a, b and c are proportionality constants which are different according to the model of equipment and the temperature interval of geothermal heat;
(3) Opening phi of solar heat exchange regulating valve 4 =Φ 1 -Φ 3 Wherein phi is 1 The cross section of the outlet pipeline of the working medium pump is ensured 1 ≥Φ 3 ；
The control logics of the power regulating valve and the heat supply power regulating valve of the steam turbine generator are as follows:
(1) Initial opening degree of power regulating valve of steam turbine generator is phi 2 The heat supply power regulating valve is initially and fully closed;
(2) Opening phi of power regulating valve of steam turbine generator 21 =e(P s -P 22 ) 2 +f(P s -P 22 ) + g wherein P s For rated output power of the generator, P 22 Feeding back the measured output power of the generator at intervals, wherein e, f and g are proportionality constants which are different according to the model of equipment and the temperature interval of geothermal heat;
(3) Opening phi of heat supply power regulating valve 23 =Φ 2 -Φ 21 Wherein phi is 2 The sectional area of the outlet pipeline of the hot working medium tank is ensured to be phi 2 ≥Φ 21 。
2. The method for controlling the solar-assisted intermediate-deep geothermal heat pipe energy system according to claim 1, wherein the method comprises the following steps: the working medium in the geothermal heat pipe and the cold working medium tank adopts naphthalene with a chemical formula of C 10 H 8 Melting point at one atmosphere: 80 to 82 ℃, boiling point: 217.9 ℃, critical temperature: 475.2 ℃;
the working medium of the solar heat pipe adopts methanol with a chemical formula of CH 3 OH, melting point at one atmosphere: -97.8 ℃, boiling point: 64.7 ℃, critical temperature: 240 ℃;
the structure of the solar heat pipe comprises a high-light-transmission resin sheath, a graphene solar energy absorption coating and a copper heat pipe from outside to inside in sequence, the structure of the solar heat pipe heat exchanger comprises the high-light-transmission resin sheath, the graphene solar energy absorption coating and the copper heat exchanger from outside to inside in sequence, and naphthalene conveyed by a pipeline absorbs heat generated in a condensation section of the solar heat pipe and also absorbs solar photo-heat absorbed by a shell of the solar heat pipe heat exchanger.
3. The method for controlling the solar-assisted intermediate-deep geothermal heat pipe energy system according to claim 1, wherein the method comprises the following steps: a working medium tank phase change heat storage module is arranged inside the hot working medium tank;
the material of the working medium tank phase-change heat storage module and the material of the heat supply phase-change heat storage module both adopt ternary molten salt, namely mixed nitrate consisting of 53 mass percent of potassium nitrate, 40 mass percent of sodium nitrite and 7 mass percent of sodium nitrate, and the melting point is 142 ℃ and the gasification point is 500 ℃.
4. The method for controlling a solar-assisted geothermal heat pipe energy system according to claim 3, wherein the method comprises the following steps: the part of the geothermal heat pipe, which is contacted with the ground, is provided with a pressure-resistant sealing protective layer and a ground hardening protective layer.
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