WO2014121711A1 - 太阳能自动均热聚热管、槽式组件、热发电系统和工艺 - Google Patents

太阳能自动均热聚热管、槽式组件、热发电系统和工艺 Download PDF

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Publication number
WO2014121711A1
WO2014121711A1 PCT/CN2014/071568 CN2014071568W WO2014121711A1 WO 2014121711 A1 WO2014121711 A1 WO 2014121711A1 CN 2014071568 W CN2014071568 W CN 2014071568W WO 2014121711 A1 WO2014121711 A1 WO 2014121711A1
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WO
WIPO (PCT)
Prior art keywords
steam
water
solar
power generation
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2014/071568
Other languages
English (en)
French (fr)
Inventor
陈义龙
杨清萍
张岩丰
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zhongying Changjiang International New Energy Investment Co Ltd
Original Assignee
Zhongying Changjiang International New Energy Investment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to MX2015010148A priority Critical patent/MX360583B/es
Priority to AU2014214382A priority patent/AU2014214382B2/en
Priority to RU2015137804A priority patent/RU2627613C2/ru
Priority to SI201430667T priority patent/SI2955460T1/en
Priority to MYPI2015702563A priority patent/MY175875A/en
Priority to LTEP14749382.9T priority patent/LT2955460T/lt
Priority to KR1020157022461A priority patent/KR101788730B1/ko
Priority to EP14749382.9A priority patent/EP2955460B1/en
Priority to BR112015018759A priority patent/BR112015018759A2/pt
Application filed by Zhongying Changjiang International New Energy Investment Co Ltd filed Critical Zhongying Changjiang International New Energy Investment Co Ltd
Priority to CA2899966A priority patent/CA2899966A1/en
Priority to DK14749382.9T priority patent/DK2955460T3/en
Priority to JP2015555576A priority patent/JP6059824B2/ja
Priority to SG11201506084YA priority patent/SG11201506084YA/en
Publication of WO2014121711A1 publication Critical patent/WO2014121711A1/zh
Priority to US14/818,301 priority patent/US9897077B2/en
Anticipated expiration legal-status Critical
Priority to ZA2015/06506A priority patent/ZA201506506B/en
Ceased legal-status Critical Current

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Classifications

    • 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
    • F03G6/061—Parabolic linear or trough concentrators
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/006—Methods of steam generation characterised by form of heating method using solar heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B33/00—Steam-generation plants, e.g. comprising steam boilers of different types in mutual association
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/40—Solar heat collectors using working fluids in absorbing elements surrounded by transparent enclosures, e.g. evacuated solar collectors
    • F24S10/45—Solar heat collectors using working fluids in absorbing elements surrounded by transparent enclosures, e.g. evacuated solar collectors the enclosure being cylindrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/70—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits
    • F24S10/75—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits with enlarged surfaces, e.g. with protrusions or corrugations
    • F24S10/754—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits with enlarged surfaces, e.g. with protrusions or corrugations the conduits being spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/20—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/20—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants
    • F24S20/25—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants using direct solar radiation in combination with concentrated radiation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/60—Solar heat collectors integrated in fixed constructions, e.g. in buildings
    • F24S20/61—Passive solar heat collectors, e.g. operated without external energy source
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/121—Controlling or monitoring
    • F03G6/127—Over-night operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/40—Solar heat collectors using working fluids in absorbing elements surrounded by transparent enclosures, e.g. evacuated solar collectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/70—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits
    • F24S10/75—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits with enlarged surfaces, e.g. with protrusions or corrugations
    • F24S2010/751—Special fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
    • F24S2080/03—Arrangements for heat transfer optimization
    • F24S2080/05—Flow guiding means; Inserts inside conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S23/00—Arrangements for concentrating solar-rays for solar heat collectors
    • F24S23/70—Arrangements for concentrating solar-rays for solar heat collectors with reflectors
    • F24S23/74—Arrangements for concentrating solar-rays for solar heat collectors with reflectors with trough-shaped or cylindro-parabolic reflective surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S90/00—Solar heat systems not otherwise provided for
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a thermal power generation process and a device/system and a process for directly passing water through a solar trough type heat collecting tube, and belongs to the technical field of solar thermal power generation. Background technique
  • the final drive motor generates electricity by using a steam turbine, and its work fluid is water vapor.
  • the medium for collecting solar thermal energy is a heat conducting oil (or molten salt), and then heating the water with a hot heat conducting oil (or molten salt). This produces steam to drive the turbine to generate electricity.
  • a solar vacuum heat collecting tube assembly including the above solar vacuum heat collecting tube; comprising a parabolic trough mirror lbl and a solar vacuum heat collecting tube at a focus thereof, the solar vacuum heat collecting tube is disposed by the glass tube lb2 and
  • the absorption tube lb3 coated with the light-sensitive heat absorbing layer is composed of a vacuum between the glass tube lb2 and the absorption tube lb3.
  • the solar heat is greatly affected by the weather.
  • the energy collection is unstable and discontinuous, and the use of heat transfer oil (or molten salt) is sufficient.
  • the thermal function just happens to offset the effects of weather changes.
  • the second is the existing vacuum heat collecting tube used in trough power generation, which cannot adapt to the physical properties of the working medium such as water. When the sunlight heats the water to a certain temperature and pressure, a tube bursting accident occurs.
  • the solar glare concentrated by the trough system mirror always illuminates the vacuum collector tube near the half of the mirror lbl (see the lower side of the glass tube lb2 in the cross section of the solar vacuum collector tube shown in Figure 1), the opposite half That is, the upper side of Figure 1 is forever receiving no concentrated glare, the convergence ratio of light is greater than 80: 1, the instantaneous temperature difference between the upper and lower sides of the absorption tube lb3 is as high as 300 ° C or more, and the vacuum between the glass tube lb2 and the absorption tube lb3 is vacuum.
  • the good thermal conductivity of the liquid medium causes the temperature in the absorption tube lb3 to be quickly balanced, and no excessive temperature difference is generated to generate internal stress.
  • the absorption tube lb3 is filled with water and the water temperature rises above 10 CTC, the water is easily vaporized to generate water vapor, and the vacuum collector tube of the trough system is long and horizontally placed.
  • the upper part of the tube in the absorption tube lb3 is steam, and the lower part is the two-phase flow state of water.
  • the thermal conductivity of steam differs greatly from the thermal conductivity of liquid water, which inevitably causes vacuum.
  • the temperature difference between the upper and lower sides of the heat collecting tube is large, and a large internal stress is generated due to thermal expansion and contraction, and a tube bursting accident that destroys the vacuum heat collecting tube occurs.
  • the technical problem to be solved by the present invention is to provide a solar energy automatic heat collecting and collecting heat pipe capable of directly passing water, and a trough type heat collecting component formed by the same, so that the solar automatic heat collecting heat collecting pipe can be directly filled with water for heating. It will not squib; it also provides a thermal power generation system and process for photothermal complementary power generation using a trough assembly with an automatic soaking heat collecting tube, so that the solar thermal hybrid power station is not affected by the weather, at night or in the sun When sufficient, it will continue to generate electricity stably, and it is energy-saving and environmentally friendly.
  • the technical solution adopted by the present invention is:
  • the utility model relates to a solar energy automatic heat collecting and heat collecting tube, which comprises a glass tube and an absorption tube which is disposed in the same and coated with a heat absorption layer, and a vacuum between the glass tube and the absorption tube; wherein the absorption tube is provided with an absorption tube in the inner cavity of the absorption tube; The intermediate fluid alternately tumbling and flowing the separator, the separator is spiral and fixed in the absorption tube.
  • the separator is spirally rotated and continuously distributed in the entire absorption tube, and the pitch is the same in the axial direction; or the separator is spirally rotated and distributed in a plurality of intervals in the entire absorption tube, and is axially
  • the pitch of the different sections is the same; along the axial direction of the absorption tube, one end of the isolation plate is fixed on the inner tube wall of the absorption tube, and the other end is free or the isolation plate is fixed on a shaft with a plurality of spiral blades and passes through one end of the shaft
  • the spiral blade is fixed in the inner cavity of the absorption tube, and the spiral blade on the other end of the shaft is a free end, the pitch of the spiral blade is equal and the spiral blades are evenly distributed.
  • a forced soaking trough assembly is characterized in that: the above-mentioned solar automatic homogenizing heat collecting tube is adopted, wherein the solar automatic homogenizing heat collecting tube is located at the focus of the parabolic trough mirror.
  • a thermal power generation system which is a thermal power generation system for photothermal complementary power generation, mainly comprising a solar concentrating heating module, a boiler heating module, and a steam turbine generator set; wherein: the solar concentrating heating module is preheated and Soda-water two-phase The evaporating sections are sequentially connected in series, the preheating section is composed of a solar vacuum collecting tube assembly, and the two-phase evaporating section is composed of a forced soaking trough assembly; in the two-phase evaporating section, at least at the end thereof
  • a steam-water separator is connected in series in the pipeline, and the steam output end of the steam-water separator converges with the output end of the boiler drum, and is connected to the steam turbine generator set through the superheater in the boiler heating module; the separated water output of the steam-water separator The end is connected to the solar automatic homogenizing heat collecting tube of the forced soaking trough assembly in any one of the two-phase evaporating sections; the steam turbine condenser
  • the steam output end of the last stage steam-water separator is merged with the boiler steam drum output end through the steam switching valve.
  • the photothermal complementary thermal power generation process using the above thermal power generation system is characterized in that: according to weather conditions, switching is performed in a boiler heating generation mode and a photothermal complementary power generation mode for continuous power generation; in a photothermal complementary power generation mode, a water supply line The water supply is sent to the solar concentrating heating module. First, it is preheated by solar energy in the solar vacuum heat collecting tube of the preheating section, and then enters the solar automatic heating heat collecting tube of the two-phase evaporation section to continue to be heated and heated, and in the absorption tube.
  • the mixed flow is forced to spirally roll by the partition plate in the absorption pipe, so that the temperature of the absorption pipe is quickly balanced, and then the two-phase mixed flow flows to the steam-water separator for steam-water separation;
  • the separated water is returned to the vapor-water two-phase flow evaporation section and then evaporated.
  • the separated saturated steam is combined with the saturated steam from the boiler drum, and then heated into the superheater of the boiler heating module to become superheated steam.
  • the boiler heating mode At night or when there is no sunlight, it is in the boiler heating mode; in the boiler heating mode, the water supply of the water supply module is only supplied to the boiler heating module, and the superheated steam is generated by the boiler, and then enters the steam turbine generator to generate electricity after passing through the heat;
  • the heating module stops working in the boiler heating mode, and the water in the solar automatic heat collecting tube stops flowing and is in a state of heat preservation.
  • a thermal power generation system which is a thermal power generation system for photothermal complementary power generation, mainly comprising a solar concentrating heating module, a boiler heating module, and a steam turbine generator set; wherein: the solar concentrating heating module is preheated, The two-phase flow evaporation section and the superheating section are sequentially connected in series, and the preheating section is composed of a solar vacuum heat collecting tube assembly, and the two-phase flow evaporation section and the superheating section are composed of a forced-heating type trough assembly; a steam-water separator connected in series with at least the output line at the end thereof, the steam output of the steam-water separator and the first forced-heating tank assembly of the superheating section
  • the solar energy automatic heat collecting heat collecting pipe is connected, and the last solar automatic heat collecting heat collecting pipe at the end of the superheating section is connected with the steam inlet of the steam turbine; the solar water automatic heat collecting heat collecting pipe of the separated water output end of the steam water separator and the two phase flow evapor
  • the output end of the solar energy automatic heat collecting and collecting tube at the last stage of the superheating section is merged with the superheater output end of the boiler through the steam switching valve, and the converging line is connected with the steam inlet of the steam turbine; before the convergence point, the superheater in the boiler A steam switching valve and a steam flow regulating valve are arranged on the output line.
  • the water supply module mainly comprises a deaerator and a feed water pump connected in sequence; the softened water storage tank is connected to the deaerator through the one-way water inlet pipeline; the steam turbine condenser output end of the steam turbine generator set is divided The oxygen pump is connected; the water pump outlet is respectively connected with two outlet pipes, and each of the outlet pipes is provided with an on-off valve, and a water supply regulating valve is also arranged on the outlet pipe.
  • the photothermal complementary thermal power generation process using the above-mentioned thermal power generation system is characterized in that: according to weather conditions, switching is continuously performed in a boiler heating generation mode, a solar power generation mode, and a photothermal complementary power generation mode; in the photothermal complementary power generation mode,
  • the water supply of the water supply pipeline is sent to the solar heating module. First, it is preheated by solar energy in the solar vacuum heat collecting tube of the preheating section, and then enters the two-phase flow evaporation section, and the solar automatic heating and collecting heat collecting tube continues to be heated and heated, and is in the absorption tube.
  • the two-phase mixed flow of water and steam is generated, and the mixed flow is forced to be spirally tumbling by the partition plate in the absorption pipe, so that the temperature of the absorption pipe is quickly balanced, and then the mixed flow flows to the steam separator for steam-water separation;
  • the water is returned to the vapor-water two-phase flow evaporation section and then evaporated;
  • the saturated steam separated in the separator continues to advance, reaches the superheated section of the solar automatic heat-collecting heat collecting tube, and continues to be heated to become superheated steam, and the superheated steam is
  • the spiral tumbling flow inside the absorption tube of the section makes the absorption tube temperature fast Value; the superheated steam and superheated steam output from the boiler superheater confluence and then into the turbogenerator power generation;
  • the water supply of the water supply module is only supplied to the boiler heating module, and the superheated steam is generated by the boiler, and after passing through the heat, it enters the steam turbine generator to generate electricity, and the solar energy
  • the heating module stops working in the boiler heating mode, and the water supply in the solar vacuum collecting tube and the solar automatic heat collecting tube stops flowing, and is in a state of heat preservation;
  • the sunlight is strong enough, it is in the solar power generation mode.
  • the water supply generates a two-phase mixed flow of water and steam after the solar heating module passes through the preheating section and the two-phase flow evaporation section, and the mixture flows through the separator to separate the saturation.
  • the steam is heated by the hot section solar energy to generate superheated steam.
  • the superheated steam is directly sent to the steam turbine generator set to generate electricity. Since the boiler needs to be started at night, in order to shorten the boiler start-up time, only a small amount of water is supplied to the boiler heating module in this mode. , to maintain the low load of the boiler (about 10% or so) operation.
  • the system feed water is preheated to about 90 °C by solar energy in the solar vacuum heat collecting tube of the preheating section.
  • the boiler of the boiler heating module of the invention is a conventional boiler, and the current coal-fired boiler, the oil-fired boiler, the biomass direct-fired boiler, the natural gas boiler, the coal-field gas boiler can be selected, and the biomass gasification gas boiler or the biomass direct combustion is preferred. boiler.
  • the trough solar heat collecting module of the present invention is provided with at least one steam water separator after the steam and water two-phase flow evaporation section; the separated saturated steam can be directly sent to the saturated steam turbine for power generation, or merged with the saturated steam generated by the boiler. Then, the superheater in the boiler is heated to be superheated steam and sent to the steam turbine for power generation; or the separated saturated steam is further superheated through the solar thermal collecting field of the hot section, and is combined with the superheated steam of the boiler and sent to the steam turbine for power generation; the steam separator The separated high-temperature water is sent to the two-phase evaporation section through the return water pump and then evaporated.
  • a variety of work modes can be flexibly selected according to the weather and the availability of sunlight, energy saving and environmental protection.
  • the solar automatic heat equalizing heat collecting tube of the invention can conveniently break the laminar flow state of the two-phase flow fluid flowing in the inner cavity of the absorption tube because the inner tube of the absorption tube is provided with a separating plate for alternately tumbling the fluid in the tube.
  • the ground causes the fluid in the tube to alternately roll up and down in the flow to form a self-stirring action to achieve thermal equilibrium between the upper and lower sides of the absorption tube to avoid a tube explosion accident.
  • FIG. 1 is a schematic structural view of a solar vacuum heat collecting tube assembly composed of a solar vacuum heat collecting tube in the prior art.
  • 2 is a schematic structural view of a first embodiment of a solar automatic heat equalizing heat collecting tube of the present invention.
  • FIG 3 is a schematic structural view of a second embodiment of the solar automatic heat equalizing heat collecting tube of the present invention.
  • Figure 4 is a cross-sectional view showing the forced heat equalizing trough assembly of the solar automatic heat collecting and collecting heat pipe of Figure 2 or Figure 3.
  • Intention the cross section of the solar automatic heat collecting heat collecting tube in the figure is the AA cross section of Fig. 2 or Fig. 3).
  • Fig. 5 is a structural schematic view showing a third embodiment of the solar automatic heat equalizing heat collecting tube of the present invention.
  • Fig. 6 is a schematic structural view showing a first embodiment of the thermal power generation system of the present invention.
  • Fig. 7 is a schematic structural view showing a second embodiment of the thermal power generation system of the present invention. detailed description
  • FIG. 2 is a schematic structural view of a first embodiment of a solar automatic heat equalizing heat collecting tube of the present invention.
  • lb2 is the glass tube of the outer layer of the solar automatic heat collecting heat collecting tube
  • lb3 is the absorption tube of the heat absorbing layer of the inner layer of the solar automatic heat collecting heat collecting tube
  • the lb3 is usually made of stainless steel, bismuth alloy (such as beryllium bronze) and the like.
  • the metal material, the space between lb2 and lb3 is vacuum
  • lb4 is the insulation plate provided in the inner cavity of the absorption tube lb3, and the lb4 is made of the same material or similar thermal properties as the lb3 material.
  • A-A indicates the position and view direction of the cross section of the forced heat-receiving trough assembly (ie, cut at the A-A and looking to the right, the solar automatic heat collecting and collecting tube shown in the center of Figure 4 can be seen).
  • the separating plate lb4 is a spiral with a proper pitch, and the outer diameter of the spiral is equal to or smaller than the inner diameter of the lb3, and can be installed in the inner cavity of the absorption tube lb3 and continuously distributed in the entire absorption tube, so that the rolling speed is uniform and the axial pitch is
  • one end of the partitioning plate lb4 is fixed in the inner cavity of the absorption tube lb3 of the solar vacuum heat collecting tube, and the other end is a free end.
  • FIG. 3 is a schematic structural view of a second embodiment of the solar automatic heat equalizing heat collecting tube of the present invention.
  • lb2 is the outer glass tube
  • lb3 is the inner layer of the heat absorbing layer of the absorption tube (lb3 is usually made of high temperature resistant metal such as stainless steel or tantalum alloy)
  • the space between lb2 and lb3 is vacuum
  • lb4 is absorption.
  • the two-section spacer plate (obviously, several segments are also provided) in the inner cavity of the tube, and the spacer plate lb4 is a spiral shape with a proper pitch (the outer diameter of the spiral outer diameter is equal to or smaller than lb3, and can be installed in the inner cavity of the absorption tube lb3).
  • the pitch of each segment along the axial direction is preferably the same.
  • the lb4 is made of the same material or similar thermal properties as the lb3 material.
  • A-A indicates the position and view direction of the cross section of the forced heat-receiving trough assembly (ie, the solar automatic segregation collector shown in the center of Figure 4 can be seen by cutting to the right at A-A).
  • the absorption tube Along the axial direction of the absorption tube, one end of each spacer is fixed to the absorber tube, and the other end is a free end.
  • FIG. 4 is a cross-sectional view of the forced heat equalizing trough assembly of the solar automatic heat collecting and collecting heat pipe of FIG. 2 or FIG. 3, wherein the cross section of the solar automatic heat collecting heat collecting pipe is the AA cross section of FIG. 2 or FIG. 3 . .
  • the solar automatic heat collecting heat collecting tube is placed at the center of the focus of the parabolic mirror.
  • Lbl is a parabolic mirror
  • lb2 is solar energy
  • lb3 is the absorption tube coated with the heat absorbing layer in the inner layer of the solar automatic heat collecting heat collecting tube
  • the lb3 is usually made of high temperature resistant metal material such as stainless steel or bismuth alloy, between lb2 and lb3
  • the space is vacuum
  • lb4 is the isolation plate set in the inner cavity of the absorption tube
  • the lb4 is made of the same material or similar thermal properties as the lb3 material.
  • the straight line with the arrow indicates the light path of the sunlight, and the solar automatic heat collecting heat collecting tube concentrated at the focus. .
  • Fig. 5 is a structural schematic view showing a third embodiment of the solar automatic heat equalizing heat collecting tube of the present invention.
  • Fig. 5 is a schematic view showing the structure of the partition plate in the inner cavity of the absorption tube after the glass tube and the absorption tube are cut along the central axis of the solar automatic heat collecting and collecting tube, and the part obscuring the line of sight of the observer is removed.
  • Lb2 is a glass tube
  • lb3 is an absorption tube
  • the space between lb2 and lb3 is a vacuum
  • lb5 is a shaft
  • lb4 is a spiral impeller blade welded or otherwise fixed on the shaft, the blades are equally spaced, each spiral
  • the cycle is arranged 2, or 3, or 4, or N. This figure shows 2 per spiral.
  • the structure of the forced heat-receiving trough assembly composed of the solar automatic heat-generating heat collecting tube of the structure is the same as that of the arrangement of Fig. 4 and will not be described again
  • la is a preheating section composed of a plurality of well-known solar vacuum heat collecting tube assemblies (shown in Fig. 1), and lb is a soda water composed of a series of forced heat equalizing trough components unique to the present invention.
  • Two-phase flow evaporation section lc is a steam-water separator
  • Id is a return water pump
  • le is a superheated section of a forced-heating tank type series connected (only in the system of Figure 7)
  • It is a boiler heating module consisting of a conventional boiler (conventional boilers are selected from known coal-fired boilers, oil-fired boilers, natural gas boilers, biomass direct-fired boilers, coal-fired gas boilers.
  • Preferred biomass gasification gas boilers or biomass direct-fired boilers 2a is the superheater in the boiler, 2b is the boiler drum, 3 is the steam turbine generator set, 3a is the steam turbine condenser, 3b and 3c are the switching valves; 3d is the steam flow regulating valve; 4 is the deaerator, 5 It is a feed pump, 5a, 5b are on-off valves, 5c is a feed water regulating valve, and 6 is a softened water storage tank (softened water from a chemical water treatment plant).
  • the water from the deaerator is mostly driven by the feed pump 5 to the la section of the solar light field.
  • the solar preheating is about 90 °C, and the lb two-phase flow evaporation section continues to be heated to produce a two-phase mixed flow of water and steam.
  • the mixed flow is forced by the separator and spirally flows to the steam separator lc.
  • the separated saturated steam merges with the saturated steam from the boiler drum 2b, and enters the superheater 2a of the boiler 2, and becomes superheated steam to enter the steam turbine 3 to generate electricity.
  • the water separated in the separator lc is driven by the return water pump Id, and is returned to the vapor-water two-phase flow evaporation section lb for evaporation.
  • the solar automatic superheated heat collecting tube Due to the lb two-phase flow evaporation section, the solar automatic superheated heat collecting tube is provided with a spiral isolation in the lb3 inner cavity. Plate lb4, the two-phase mixed fluid is driven by the feed water pump 5, and must spirally roll up and down in the absorption tube lb3, because the heat conduction performance of water is good, although the solar automatic heat collecting heat collecting tube is always the lower half of the absorption tube lb3 It is heated, but the water tumbling up and down will quickly transfer the heat to the upper part of the absorption tube lb3, so that the upper and lower parts of the solar absorption tube lb3 will soon reach a thermal equilibrium state, and the solar vacuum collector tube will be directly passed through the water. The disease of the tube is blocked.
  • the opening of the regulating valve 5c provided at the outlet of the water pump 5 is adjusted to reduce the opening of the 5c, and the flow of water to the solar heat collecting field is reduced, and the flow through the 5b switching valve is transmitted to
  • the water flow rate of the conventional boiler 2 is increased, the boiler load is increased, and the multi-product steam ensures that the output power of the turbine generator is constant.
  • the water from the deaerator is mostly driven by the feed pump 5 to the la section of the solar field, which is concentrated.
  • the solar preheating is about 90 °C, and then enters the lb two-phase flow evaporation section to continue heating, and produces a two-phase mixed flow of water and steam.
  • the mixed flow is forced by the separator and spirally flows to the steam separator.
  • the water separated in the separator is driven by the return water pump Id, and is refluxed to the vapor-water two-phase flow evaporation section lb and evaporated.
  • the saturated steam separated in the separator lc continues to advance, reaching the superheating section le of the forced soaking trough component in the trough solar field, and the saturated steam continues to be heated into superheated steam in the superheating section, overheating
  • the steam merges with the superheated steam from the conventional boiler superheater 2a, and then enters the steam turbine 3 to generate electricity.
  • a spiral isolation plate is arranged in the inner cavity of the solar automatic heat absorption heat collecting tube absorption tube, and the two-phase mixed fluid is driven by the feed water pump 5, and must be spirally rolled up and down in the tube. Because the heat transfer performance of water is very good, although the vacuum heat collecting tube is always heated by the lower half of the absorption tube, the water tumbling up and down will quickly transfer heat to the upper half of the absorption tube, thereby making the solar absorption tube lb3 The upper and lower parts quickly reach a state of thermal equilibrium, and the absorbing tube lb3 of the solar vacuum heat collecting tube is directly exposed to water to cause a tube rupture.
  • the opening of the regulating valve 5c provided at the outlet of the feed pump 5 is adjusted, so that the opening of the 5c is reduced, and the flow of water to the solar heat collecting field is reduced, and the flow through the 5b switching valve is transmitted to
  • the water flow rate of the boiler 2 is increased, the boiler load is increased, and the steam is produced to ensure that the output power of the steam turbine generator is constant.
  • the on-off valves 5a and lf are closed, and the return pump ld is stopped.
  • the water from the deaerator is driven by the feed pump 5 to the conventional boiler 2, and the boiler generates superheated steam and then enters the steam turbine to generate electricity.
  • the solar heat collecting field stops working at night, and the medium stops flowing in a kept state.
  • the trough solar heat collecting light field of the invention is composed of a preheating section composed of a solar heat collecting unit component and a vaporized water two-phase flow evaporating section (or is evaporated by a preheating section, a soda-water two-phase flow)
  • the segmental and superheated sections are composed of the solar automatic two-phase flow evaporation section and the superheating section, and the solar automatic multi-heating heat collecting tube and the forced uniform heat tank type component of the invention are used, and in the vapor-water two-phase flow evaporation section.
  • At least one steam-water separator is provided, which solves the problem of the complementary convergence of the steam directly generated by the solar water and the steam generated by the conventional boiler, and solves the problem that the solar energy is affected by the weather, unstable, and the power station cannot generate electricity at night.
  • the invention relates to the invention of a solar automatic heat equalizing heat collecting tube and a forced uniform heat tank type, and opens up a completely new technological technology path for the parabolic trough solar photovoltaic power generation directly flowing through water.

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Abstract

一种太阳能自动均热聚热管，包括玻璃管（1b2）和套置于其中且涂有吸热层的吸收管（1b3），玻璃管（1b2）和吸收管（1b3）间为真空。吸收管（1b3）内腔中设置有能够使吸收管（1b3）中流体上下交替翻滚流动的隔离板（1b4），隔离板（1b4）呈螺旋状，并固定在吸收管（1b3）内。一种光热互补发电的热发电系统和工艺，实现了太阳能光热互补电站不受天气影响，在夜晚或太阳光不充足时持续稳定发电。

Description

太阳能自动均热聚热管、 槽式组件、 热发电系统和工艺 技术领域
本发明涉及一种太阳能槽式集热管直接通水的热发电工艺及装置 /系统和工艺，属于 太阳能光热发电技术领域。 背景技术
太阳能具有分布广泛， 储量无限， 收集利用清洁， co2零排放的优点引起人们广泛 关注。 长期以来， 太阳能光热发电技术领域， 存在三种发电模式， 即塔式、 碟式、 槽式 (含抛物面反射镜槽式， 及菲涅耳反射镜槽式）。
现有技术槽式太阳能热发电系统中， 最终驱动电机发电的均使用汽轮机， 其做功工 质是水蒸汽。 但目前现有技术中， 槽式太阳能热发电系统的真空集热管中， 收集太阳能 光热使用的介质却是导热油 （或者熔融盐）， 再使用热的导热油 （或者熔融盐） 加热水， 从而产生蒸汽驱动汽轮机发电。 图 1所示是包含上述太阳能真空集热管的太阳能真空集 热管组件； 由抛物面槽式反射镜 lbl及位于其焦点的太阳能真空集热管组成， 太阳能真 空集热管由玻璃管 lb2和套置于其中且涂有光敏感吸热层的吸收管 lb3组成，玻璃管 lb2 和吸收管 lb3间为真空。
槽式太阳能热发电形成上述工艺模式有两个原因，其一，太阳光热受天气影响较大， 天气有云时能量汇集不稳定、 不连续， 而使用导热油 （或者熔融盐） 就具有蓄热功能， 恰好可抵消天气变化的影响。 其二是槽式发电使用的现有真空集热管， 不能适应水这种 工质的物理性能， 太阳光加热水到一定温度、 压力时就会发生爆管事故。
因为槽式系统反射镜汇聚的太阳强光总是照射在真空集热管靠近反射镜 lbl那一半 的（见图 1所示太阳能真空集热管横断面图中的玻璃管 lb2下侧面）， 相反的一半即图 1 的上侧面是永远接收不到会聚强光的， 光的会聚比大于 80： 1， 吸收管 lb3上下其间的 瞬间温差高达 300°C以上， 玻璃管 lb2和吸收管 lb3之间为真空， 如果吸收管 lb3内充 满导热油（或者熔融盐）， 其液态介质的良好导热性会使吸收管 lb3内温度很快均衡， 不 会形成过大温差而产生内应力。 而如果吸收管 lb3内充满水， 水温上升到 10CTC以上时， 水就很容易气化产生水蒸汽， 而槽式系统的真空集热管又很长， 且是水平放置的， 从真 空集热管横断面看，会在吸收管 lb3管内形成上半部是蒸汽，下半部是水的两相流状态， 蒸汽的导热性与液态水的导热性差别很大， 这就必然造成真空集热管内上下温差很大， 因热胀冷縮而产生很大內应力， 发生毁坏真空集热管的爆管事故。
因此寻找技术途径， 开发一种不同于现有槽式太阳能热发电技术装置、 组件及相适 应的工艺， 从而解决现有太阳能真空集热管存在的问题就很有必要。 发明内容
本发明要解决的技术问题是： 提供一种能够直接通水的太阳能自动均热聚热管、和 由其构成的槽式聚热组件、 使得太阳能自动均热聚热管中能够直接充水进行加热而不会 爆管； 同时提供一种利用带有自动均热聚热管的槽式组件进行光热互补发电的热发电系 统及工艺， 使得太阳能光热互补电站不受天气影响， 在夜晚或太阳光不充足时持续稳定 发电， 且节能环保。
为解决上述技术问题， 本发明采用的技术方案是：
一种太阳能自动均热聚热管， 包括玻璃管和套置于其中且涂有吸热层的吸收管， 玻 璃管和吸收管间为真空； 其特征在于： 吸收管内腔中设置有能够使吸收管中流体上下交 替翻滚流动的隔离板， 隔离板呈螺旋状， 并固定在吸收管内。
按上述技术方案， 隔离板呈螺旋状旋转并连续分布于整段吸收管内， 沿轴向螺距相 同； 或者隔离板呈螺旋状旋转并以多段间隔的方式分布于整段吸收管内， 且沿轴向不同 段螺距均相同； 沿吸收管轴向， 隔离板的一端固定在吸收管内腔管壁上， 另一端为自由 或者隔离板是在一根轴杆上固定若干螺旋状叶片，并通过轴杆一端的螺旋状叶片固 定在吸收管内腔中构成， 另一端轴杆上螺旋状叶片为自由端， 螺旋状叶片的螺距相等且 各螺旋状叶片均布。
一种强制均热式槽式组件， 其特征在于： 采用了上述的太阳能自动均热聚热管， 其 中， 太阳能自动均热聚热管位于抛物面槽式反射镜焦点上。
一种热发电系统， 为光热互补发电的热发电系统， 主要包括太阳能聚光供热模块、 锅炉供热模块、 汽轮发电机组； 其特征在于： 太阳能聚光供热模块由预热段和汽水两相 流蒸发段顺次串联而成， 预热段由太阳能真空集热管组件组成， 而两相流蒸发段是由强 制均热式槽式组件构成； 在两相流蒸发段， 至少在其末端的输出管路中串联一个汽水分 离器， 汽水分离器的蒸汽输出端与锅炉汽包输出端汇聚， 汇聚后并经锅炉供热模块中的 过热器与汽轮发电机组连通； 汽水分离器的分离水输出端与两相流蒸发段中的任一个强 制均热式槽式组件的太阳能自动均热聚热管回流连通； 汽轮发电机组的汽轮机冷凝器输 出端与供水模块连通； 供水模块还设置一路进水管线和两路出水管线， 一路出水管线与 预热段第一个太阳能真空集热管组件连通， 另一路出水管线与锅炉给水管路连通。
按上述技术方案，最后一级汽水分离器的蒸汽输出端经蒸汽开关阀后与锅炉汽包输 出端汇聚为一路。
采用上述热发电系统的光热互补热发电工艺， 其特征在于： 根据天气状况， 在锅炉 供热发电模式、 以及光热互补发电模式下切换进行持续发电； 光热互补发电模式下， 给 水管线的供水送往太阳能聚光供热模块， 首先在预热段的太阳能真空集热管中经太阳能 预热， 然后进入两相流蒸发段的太阳能自动均热聚热管中继续被加热升温， 并在吸收管 中产生水与蒸汽的两相混合流， 混合流被吸收管中的隔离板强制螺旋状地翻滚， 使得吸 收管温度快速均衡， 然后两相混合流流动到汽水分离器中进行汽水分离； 分离器中分离 出的水回流到汽水两相流蒸发段中再蒸发， 分离出的饱合蒸汽与来自锅炉汽包的饱合蒸 汽汇合， 再进入锅炉加热模块的过热器中升温， 成为过热蒸汽进入汽轮发电机组中进行 光热互补发电；
夜晚或无太阳光时， 处于锅炉供热发电模式； 锅炉供热发电模式下， 供水模块的供 水仅供给锅炉加热模块， 经锅炉产生过热蒸汽， 经过热器后进入汽轮发电机组发电； 而 太阳能供热模块在锅炉供热发电模式下停止工作， 太阳能自动均热聚热管中的水停止流 动， 处于保温状态。
一种热发电系统， 为光热互补发电的热发电系统， 主要包括太阳能聚光供热模块、 锅炉供热模块、 汽轮发电机组； 其特征在于： 太阳能聚光供热模块由预热段、 两相流蒸 发段和过热段顺次串联而成， 预热段由太阳能真空集热管组件组成， 而两相流蒸发段、 过热段均由强制均热式槽式组件构成； 在两相流蒸发段， 至少在其末端的输出管路中串 联一个汽水分离器， 汽水分离器的蒸汽输出端与过热段的第一个强制均热式槽式组件的 太阳能自动均热聚热管连通， 过热段末端的最后一个太阳能自动均热聚热管与汽轮机蒸 汽入口连通； 汽水分离器的分离水输出端与两相流蒸发段中的任一个太阳能自动均热聚 热管回流连通； 锅炉供热模块中， 锅炉汽包输出端经过热器后与汽轮机蒸汽入口连通， 汽轮机冷凝器输出端与供水模块连通； 供水模块还设置一路进水管线和两路出水管线， 一路出水管线与预热段第一个太阳能真空集热管组件的太阳能真空集热管连通， 另一路 出水管线与锅炉给水系统连通。
按上述技术方案，过热段最后一级太阳能自动均热聚热管输出端经蒸汽开关阀后与 锅炉中的过热器输出端汇聚， 汇聚管线与汽轮机蒸汽入口连通； 汇聚点前， 锅炉中的过 热器输出端管路上设置蒸汽开关阀和蒸汽流量调节阀。
按上述技术方案， 供水模块主要包括顺次连接的除氧器和给水泵； 软化水储罐经过 所述的一路进水管线与除氧器连通；汽轮发电机组的汽轮机冷凝器输出端与除氧器连通; 给水泵出口分别连接两路出水管线， 各出水管线上分别设置开关阀， 所述一路出水管线 上还设置给水调节阀。
采用上述热发电系统的光热互补热发电工艺， 其特征在于： 根据天气状况， 在锅炉 供热发电模式、 太阳能发电模式以及光热互补发电模式下切换进行持续发电； 光热互补 发电模式下， 供水管线的供水送往太阳能供热模块， 首先在预热段的太阳能真空集热管 中经太阳能预热， 然后进入两相流蒸发段太阳能自动均热聚热管中继续被加热升温， 并 在吸收管中产生水与蒸汽的两相混合流，混合流被吸收管中的隔离板强制螺旋状地翻滚， 使得吸收管温度快速均衡， 然后混合流流动到汽水分离器中进行汽水分离； 分离器中分 离出的水回流到汽水两相流蒸发段中再蒸发； 分离器中分离出的饱合蒸汽继续前进， 到 达过热段的太阳能自动均热聚热管中， 继续被加热升温成为过热蒸汽， 过热蒸汽在该段 的吸收管内螺旋状翻滚流动， 使得吸收管温度快速均衡； 过热蒸汽输出后与来自锅炉过 热器的过热蒸汽汇合， 再进入汽轮发电机组中发电；
夜晚或无太阳光时， 处于锅炉供热发电模式； 锅炉供热发电模式下， 供水模块的供 水仅供给锅炉加热模块， 经锅炉产生过热蒸汽， 经过热器后进入汽轮发电机组发电， 而 太阳能供热模块在锅炉供热发电模式下停止工作， 太阳能真空集热管和太阳能自动均热 聚热管中的供水停止流动， 处于保温状态； 阳光足够强时处于太阳能发电模式下， 此模式下， 供水在太阳能加热模块经预热段 和两相流蒸发段后产生水与蒸汽的两相混合流， 混合流经分离器分离出的饱合蒸汽经过 热段太阳能继续加热后产生过热蒸汽， 过热蒸汽直接输往汽轮发电机组中发电； 由于夜 晚来临时锅炉尚需启动工作， 为縮短锅炉启动时间， 此模式下仅少量供水给锅炉加热模 块， 维持锅炉的低负荷 （大约 10%左右） 运行。
按上述技术方案， 系统给水在预热段的太阳能真空集热管中经太阳能预热到 90°C 左右。
本发明中锅炉加热模块的锅炉为常规锅炉， 可选用目前的燃煤锅炉、 燃油锅炉、 生 物质直燃锅炉、 天然气锅炉、 煤田气锅炉均可， 优选生物质气化气锅炉或生物质直燃锅 炉。
本发明槽式太阳能聚热模块在汽水两相流蒸发段后至少设置一个汽水分离器； 分离 出的饱合蒸汽可以直接输往饱合蒸汽汽轮机进行发电，或者与锅炉产生的饱合蒸汽汇合， 再进入锅炉中的过热器中加热为过热蒸汽输往汽轮机发电； 或者分离出的饱合蒸汽经过 热段的太阳能聚热光场继续过热后与锅炉过热蒸汽汇合输往汽轮机中发电； 汽水分离器 分离出的高温水通过回水泵输往两相流蒸发段再蒸发。 多种工作模式可以根据天气和太 阳光是否充足进行灵活选择， 节能环保。
本发明的太阳能自动均热聚热管由于吸收管内腔中设置有可使管中流体上下交替翻 滚流动的隔离板， 可方便的打破两相流流体在吸收管内腔中流动的层流状态， 强制性地 使管中流体在流动中上下交替滚动， 形成自搅拌作用， 以达到吸收管上下热均衡， 避免 爆管事故。 附图说明
下面结合附图和实施例来说明本发明。
图 1是现有技术中的由太阳能真空集热管组成的太阳能真空集热管组件结构简图。 图 2是本发明的太阳能自动均热聚热管第一种实施方式结构示意图。
图 3是本发明的太阳能自动均热聚热管第二种实施方式结构示意图。
图 4是图 2或图 3的太阳能自动均热聚热管构成的强制均热式槽式组件的横断面示 意图 （图中太阳能自动均热聚热管横断面部分为图 2或图 3的 A-A横断面）。
图 5是本发明的太阳能自动均热聚热管第三种实施方式结构示意图。
图 6是本发明的热发电系统第一种实施方式的结构示意图。
图 7是本发明的热发电系统的第二种实施方式的结构示意图。 具体实施方式
下面结合附图和最佳实施方式具体说明本发明。
图 2是本发明的太阳能自动均热聚热管第一种实施方式结构示意图。 其中， lb2是 太阳能自动均热聚热管外层的玻璃管， lb3 是太阳能自动均热聚热管内层的涂吸热层的 吸收管（lb3通常采用不锈钢、 铍合金（如铍青铜）等耐高温金属材料， lb2与 lb3之间 的空间为真空）， lb4是吸收管 lb3内腔设置的隔离板， lb4采用与 lb3材质相同或热性 能相似的材料。 A-A表示强制均热式槽式组件横切面的位置及视图方向（即在 A-A处切 开朝右看， 可看到图 4中心部分所示的太阳能自动均热聚热管）。
隔离板 lb4为螺距适当的螺旋状， 螺旋外经等于或小于 lb3的内径， 可安装于吸收 管 lb3的内腔中， 并连续分布于整段吸收管内， 为使翻滚速度一致， 沿轴向螺距最好相 同； 沿吸收管轴向， 隔离板 lb4的一端固定在太阳能真空集热管的吸收管 lb3内腔中， 另一端为自由端。
图 3是本发明的太阳能自动均热聚热管第二种实施方式结构示意图。 其中， lb2是 外层的玻璃管， lb3是内层的涂吸热层的吸收管（lb3通常采用不锈钢、铍合金等耐高温 金属材料）， lb2与 lb3之间的空间为真空， lb4是吸收管内腔中设置的 2段隔离板 （显 然， 数段也可以）， 隔离板 lb4为螺距适当（螺旋外经等于或小于 lb3的内径， 可安装于 吸收管 lb3 的内腔中） 的螺旋状， 为使翻滚速度一致， 沿轴向各段螺距最好相同。 lb4 采用与 lb3材质相同或热性能相似的材料。 A-A表示强制均热式槽式组件横切面的位置 及视图方向（即在 A-A处切开朝右看， 可看到图 4中心部分所示的太阳能自动均热聚热 管）。 沿吸收管轴向， 每个隔离板的一端固定在吸收管上， 另一端为自由端。
图 4是图 2或图 3的太阳能自动均热聚热管构成的强制均热式槽式组件的横断面示 意图， 图中太阳能自动均热聚热管横断面部分为图 2或图 3的 A-A横断面。 其中， 太阳 能自动均热聚热管置于抛物面反射镜的焦点中心。 lbl是抛物面反射镜， lb2是太阳能自 动均热聚热管外层的玻璃管， lb3 是太阳能自动均热聚热管内层的涂有吸热层的吸收管 ( lb3通常采用不锈钢、 铍合金等耐高温金属材料， lb2与 lb3之间的空间为真空， lb4 是吸收管内腔设置的隔离板， lb4采用与 lb3材质相同或热性能相似的材料。 图中带箭 头的直线表示太阳光的光路， 汇聚于焦点处的太阳能自动均热聚热管。
图 5是本发明的太阳能自动均热聚热管第三种实施方式结构示意图。 图 5显示的是 沿太阳能自动均热聚热管中轴线切开玻璃管、吸收管，并拿开遮挡观察者视线的部分后， 所看到的吸收管内腔中隔离板的结构示意图。 lb2是玻璃管， lb3是吸收管， lb2与 lb3 之间的空间为真空， lb5是轴杆， lb4是螺旋状叶轮的叶片焊接或其他方式固定在轴杆上， 叶片的间距相等， 每个螺旋周期布置 2， 或 3， 或 4， 或 N个， 本图显示的是每螺旋 2 个。 由该结构的太阳能自动均热聚热管构成的强制均热式槽式组件的结构与图 4布置结 构相同， 不再赘述。
图 6及图 7中， la是多个现已公知太阳能真空集热管组件 （图 1中所示） 串联构成 的预热段， lb 是本发明特有的强制均热式槽式组件串联构成的汽水两相流蒸发段， lc 是汽水分离器， Id是回水泵， le 是强制均热式槽式组件串联构成的过热段 （仅在图 7 的系统中有设置）， If是蒸汽开关阀， 2是常规锅炉构成的锅炉加热模块（常规锅炉选自 已知的燃煤锅炉、 燃油锅炉、 天然气锅炉、 生物质直燃锅炉、 煤田气锅炉均可。 优选生 物质气化气锅炉或生物质直燃锅炉）， 2a是锅炉中的过热器， 2b是锅炉汽包， 3是汽轮 发电机组， 3a是汽轮机冷凝器， 3b和 3c为开关阀； 3d为蒸汽流量调节阀； 4是除氧器， 5是给水泵， 5a、 5b是开关阀， 5c是给水调节阀， 6是软化水储罐 （软化水来自化水处 理厂）。
上述图 6的系统工作流程如下：
白天阳光充足时， 5a、 5b、 If开关阀均处于开状态， 并启动回水泵 ld， 来自除氧器 的水在给水泵 5的驱动下绝大部分输往太阳能光场的 la段，经会聚的太阳光预热为 90°C 左右， 进入 lb两相流蒸发段继续被加热， 产生水与蒸汽的两相混合流， 混合流被隔离板 强制， 螺旋状地翻滚流动到汽水分离器 lc中， 分离出的饱合蒸汽与来自锅炉汽包 2b的 饱合蒸汽汇合， 再进入锅炉 2的过热器 2a中， 成为过热蒸汽进入汽轮机 3中发电。分离 器 lc中分离出的水经回水泵 Id驱动， 回流到汽水两相流蒸发段 lb中再蒸发。
由于在 lb两相流蒸发段，太阳能自动均热聚热管的 lb3內腔中设置有螺旋状的隔离 板 lb4， 两相混合流体在给水泵 5的驱动下， 必然在吸收管 lb3中螺旋式上下翻滚前进， 由于水的热传导性能很好， 尽管太阳能自动均热聚热管始终是吸收管 lb3下半部受热， 但水的上下翻滚流动， 会很快将热量传导到吸收管 lb3的上半部， 从而使太阳能吸收管 lb3 的上下部分很快达到热均衡状态， 根除了太阳能真空集热管直接通水发生爆管的蔽 病。
白天有云层太阳光减少时， 调解给水泵 5出口设置的调节阀 5c的开度， 使 5c开度 减小， 则输往太阳聚热场的水流量减少， 而流过 5b开关阀， 输往常规锅炉 2的水流量增 大， 锅炉负荷增大， 多产蒸汽保证汽轮发电机输出功率不变。
夜晚来临时， 关闭开关阀 5a及 lf， 并停运回水泵 ld， 来自除氧器 4的水在给水泵 5 的驱动下输往常规锅炉 2， 经锅炉 2产生过热蒸汽， 进入汽轮机发电。 而太阳能光场夜 间停止工作， 介质停止流动， 处于保温状态。
上述图 7的系统工作流程如下：
白天阳光充足时， 5a、 5b、 If开关阀均处于开状态， 并启动回水泵 ld， 来自除氧器 的水在给水泵 5的驱动下绝大部分输往太阳能光场的 la段，被会聚的太阳光预热为 90°C 左右， 再进入 lb两相流蒸发段继续被加热， 并产生水与蒸汽的两相混合流， 混合流被隔 离板强制， 螺旋状地翻滚流动到汽水分离器 lc中， 分离器中分离出的水经回水泵 Id驱 动， 回流到汽水两相流蒸发段 lb中再蒸发。
分离器 lc中分离出的饱合蒸汽继续前进，到达槽式太阳能光场的强制均热式槽式组 件串连构成的过热段 le， 饱合蒸汽在过热段 le继续被加热成为过热蒸汽， 过热蒸汽与 来自常规锅炉过热器 2a的过热蒸汽汇合， 再进入汽轮机 3中发电。
在上述 lb两相流蒸发段，太阳能自动均热聚热管吸收管的內腔中设置有螺旋状的隔 离板， 两相混合流体在给水泵 5的驱动下， 必然在管中螺旋式上下翻滚前进， 由于水的 热传导性能很好， 尽管真空集热管始终是吸收管下半部受热， 但水的上下翻滚流动， 会 很快将热量传导到吸收管的上半部， 从而使太阳能吸收管 lb3的上下部分很快达到热均 衡状态， 根除了太阳能真空集热管的吸收管 lb3直接通水发生爆管的蔽病。
在上述过热段 le中，由于太阳能自动均热聚热管的吸收管 lb3内设置有隔离板 lb4， 过热蒸汽在吸收管 lb3内同样螺旋状地翻滚流动， 这种单一流体的螺旋状翻滚流动方式 起到了极强的上下搅拌的作用， 尽管热蒸汽的导热性很差， 但激烈地搅拌作用， 会使得 各处的蒸汽很快均匀， 从而使得吸收管 lb3温度比较均衡， 无较大的内应力， 避免了爆 管事故。
白天有云层太阳光减少时， 调节给水泵 5出口设置的调节阀 5c的开度， 使 5c开度 减小， 则输往太阳聚热场的水流量减少， 而流过 5b开关阀， 输往锅炉 2的水流量增大， 锅炉负荷随之增大， 多产蒸汽从而保证汽轮发电机输出功率不变。
夜晚来临时， 关闭开关阀 5a及 lf， 同时停运回水泵 ld， 来自除氧器的水在给水泵 5 的驱动下输往常规锅炉 2， 经锅炉产生过热蒸汽、 再进入汽轮机发电。 而太阳能聚热光 场夜间停止工作， 介质停止流动处于保温状态。
本发明的优点： 由于本发明的槽式太阳能聚热光场是由太阳能聚热单元组件构成的 预热段及汽水两相流蒸发段组成的 （或者是由预热段、 汽水两相流蒸发段及过热段组成 的），而在汽水两相流蒸发段及过热段均采用了本发明特有的太阳能自动均热聚热管、强 制均热式槽式组件， 并在在汽水两相流蒸发段至少设置一个汽水分离器， 解决了太阳能 直接通水产生蒸汽与常规锅炉产生蒸汽的互补汇合问题， 很好的解决了太阳能受天气影 响， 不稳定， 电站不能夜晚发电的问题。 特别是本发明关于太阳能自动均热聚热管、 强 制均热式槽式组件的发明， 为直接通水的抛物面槽式太阳能光热发电， 开创了全新的工 艺技术路径。

Claims

权利要求书
1、 一种太阳能自动均热聚热管， 包括玻璃管和套置于其中且涂有吸热层的吸收管， 玻璃管和吸收管间为真空； 其特征在于： 吸收管内腔中设置有能够使吸收管中流体上下 交替翻滚流动的隔离板， 隔离板呈螺旋状， 并固定在吸收管内。
2、根据权利要求 1所述的太阳能自动均热聚热管， 其特征在于： 隔离板呈螺旋状旋 转并连续分布于整段吸收管内， 沿轴向螺距相同； 或者隔离板呈螺旋状旋转并以多段间 隔的方式分布于整段吸收管内， 且沿轴向不同段螺距均相同； 沿吸收管轴向， 隔离板的 一端固定在吸收管内腔管壁上， 另一端为自由端；
或者隔离板是在一根轴杆上固定若干螺旋状叶片， 并通过轴杆一端的螺旋状叶片固 定在吸收管内腔中构成， 另一端轴杆上螺旋状叶片为自由端， 螺旋状叶片的螺距相等且 各螺旋状叶片均布。
3、一种强制均热式槽式组件， 其特征在于： 采用了上述权利要求 1或 2所述的太阳 能自动均热聚热管， 其中， 太阳能自动均热聚热管位于抛物面槽式反射镜焦点上。
4、一种热发电系统，为光热互补发电的热发电系统，主要包括太阳能聚光供热模块、 锅炉供热模块、 汽轮发电机组； 其特征在于： 太阳能聚光供热模块由预热段和汽水两相 流蒸发段顺次串联而成， 预热段由太阳能真空集热管组件组成， 而两相流蒸发段是由权 利要求 3所述的强制均热式槽式组件构成； 在两相流蒸发段， 至少在其末端的输出管路 中串联一个汽水分离器， 汽水分离器的蒸汽输出端与锅炉汽包输出端汇聚， 汇聚后并经 锅炉供热模块中的过热器与汽轮发电机组连通； 汽水分离器的分离水输出端与两相流蒸 发段中的任一个强制均热式槽式组件的太阳能自动均热聚热管回流连通； 汽轮发电机组 的汽轮机冷凝器输出端与供水模块连通;供水模块还设置一路进水管线和两路出水管线， 一路出水管线与预热段第一个太阳能真空集热管组件连通， 另一路出水管线与锅炉给水 管路连通。
5、根据权利要求 4所述的热发电系统， 其特征在于： 最后一级汽水分离器的蒸汽输 出端经蒸汽开关阀后与锅炉汽包输出端汇聚为一路。
6、根据权利要求 4或 5所述的热发电系统， 其特征在于： 供水模块主要包括顺次连 接的除氧器和给水泵； 软化水储罐经过所述的一路进水管线与除氧器连通； 汽轮发电机 组的汽轮机冷凝器输出端与除氧器连通； 给水泵出口分别连接两路出水管线， 各出水管 线上分别设置开关阀， 所述一路出水管线上还设置给水调节阀。
7、采用上述权利要求 4-6之一所述热发电系统的光热互补热发电工艺，其特征在于: 根据天气状况， 在锅炉供热发电模式、 以及光热互补发电模式下切换进行持续发电； 光 热互补发电模式下， 给水管线的供水送往太阳能聚光供热模块， 首先在预热段的太阳能 真空集热管中经太阳能预热， 然后进入两相流蒸发段的太阳能自动均热聚热管中继续被 加热升温， 并在吸收管中产生水与蒸汽的两相混合流， 混合流被吸收管中的隔离板强制 螺旋状地翻滚， 使得吸收管温度快速均衡， 然后两相混合流流动到汽水分离器中进行汽 水分离； 分离器中分离出的水回流到汽水两相流蒸发段中再蒸发， 分离出的饱合蒸汽与 来自锅炉汽包的饱合蒸汽汇合， 再进入锅炉加热模块的过热器中升温， 成为过热蒸汽进 入汽轮发电机组中进行光热互补发电；
夜晚或无太阳光时， 处于锅炉供热发电模式； 锅炉供热发电模式下， 供水模块的供 水仅供给锅炉加热模块， 经锅炉产生过热蒸汽， 经过热器后进入汽轮发电机组发电； 而 太阳能供热模块在锅炉供热发电模式下停止工作， 太阳能自动均热聚热管中的水停止流 动， 处于保温状态。
8、一种热发电系统，为光热互补发电的热发电系统，主要包括太阳能聚光供热模块、 锅炉供热模块、 汽轮发电机组； 其特征在于： 太阳能聚光供热模块由预热段、 两相流蒸 发段和过热段顺次串联而成， 预热段由太阳能真空集热管组件组成， 而两相流蒸发段、 过热段均由权利要求 3所述强制均热式槽式组件构成； 在两相流蒸发段， 至少在其末端 的输出管路中串联一个汽水分离器， 汽水分离器的蒸汽输出端与过热段的第一个强制均 热式槽式组件的太阳能自动均热聚热管连通， 过热段末端的最后一个太阳能自动均热聚 热管与汽轮机蒸汽入口连通； 汽水分离器的分离水输出端与两相流蒸发段中的任一个太 阳能自动均热聚热管回流连通； 锅炉供热模块中， 锅炉汽包输出端经过热器后与汽轮机 蒸汽入口连通， 汽轮机冷凝器输出端与供水模块连通； 供水模块还设置一路进水管线和 两路出水管线， 一路出水管线与预热段第一个太阳能真空集热管组件的太阳能真空集热 管连通， 另一路出水管线与锅炉给水系统连通。
9、根据权利要求 8所述的热发电系统， 其特征在于： 过热段最后一级太阳能自动均 热聚热管输出端经蒸汽开关阀后与锅炉中的过热器输出端汇聚， 汇聚管线与汽轮机蒸汽 入口连通；汇聚点前，锅炉中的过热器输出端管路上设置蒸汽开关阀和蒸汽流量调节阀。
10、 根据权利要求 8或 9所述的热发电系统， 其特征在于： 供水模块主要包括顺次 连接的除氧器和给水泵； 软化水储罐经过所述的一路进水管线与除氧器连通； 汽轮发电 机组的汽轮机冷凝器输出端与除氧器连通； 给水泵出口分别连接两路出水管线， 各出水 管线上分别设置开关阀， 所述一路出水管线上还设置给水调节阀。
11、 采用权利要求 8-10之一所述热发电系统的光热互补热发电工艺， 其特征在于： 根据天气状况， 在锅炉供热发电模式、 太阳能发电模式以及光热互补发电模式下切换进 行持续发电； 光热互补发电模式下， 供水管线的供水送往太阳能供热模块， 首先在预热 段的太阳能真空集热管中经太阳能预热， 然后进入两相流蒸发段的太阳能自动均热聚热 管中继续被加热升温， 并在吸收管中产生水与蒸汽的两相混合流， 混合流被吸收管中的 隔离板强制螺旋状地翻滚， 使得吸收管温度快速均衡， 然后混合流流动到汽水分离器中 进行汽水分离； 分离器中分离出的水回流到汽水两相流蒸发段中再蒸发； 分离器中分离 出的饱合蒸汽继续前进， 到达过热段的太阳能自动均热聚热管中， 继续被加热升温成为 过热蒸汽， 过热蒸汽在该段的吸收管内螺旋状翻滚流动， 使得吸收管温度快速均衡； 过 热蒸汽输出后与来自锅炉过热器的过热蒸汽汇合， 再进入汽轮发电机组中发电；
夜晚或无太阳光时， 处于锅炉供热发电模式； 锅炉供热发电模式下， 供水模块的供 水仅供给锅炉加热模块， 经锅炉产生过热蒸汽， 经过热器后进入汽轮发电机组发电， 而 太阳能供热模块在锅炉供热发电模式下停止工作， 太阳能真空集热管和太阳能自动均热 聚热管中的供水停止流动， 处于保温状态；
阳光足够强时处于太阳能发电模式下， 此模式下， 供水在太阳能加热模块经预热段 和两相流蒸发段后产生水与蒸汽的两相混合流， 混合流经分离器分离出的饱合蒸汽经过 热段太阳能继续加热后产生过热蒸汽， 过热蒸汽直接输往汽轮发电机组中发电； 由于夜 晚来临时锅炉尚需启动工作， 为縮短锅炉启动时间， 此模式下仅少量供水给锅炉加热模 块， 维持锅炉的低负荷运行。
12、根据权利要求 7或 11所述的光热互补热发电工艺， 其特征在于： 系统给水在预 热段的太阳能真空集热管中经太阳能预热到 90°C左右。
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JP2016505129A (ja) 2016-02-18
ZA201506506B (en) 2017-11-29
US20150337811A1 (en) 2015-11-26
CN103115445A (zh) 2013-05-22
EP2955460A1 (en) 2015-12-16
KR20150110676A (ko) 2015-10-02
EP2955460A4 (en) 2016-11-02
DK2955460T3 (en) 2018-03-26
US9897077B2 (en) 2018-02-20
CN103115445B (zh) 2014-09-24
KR101788730B1 (ko) 2017-11-15
CA2899966A1 (en) 2014-08-14
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BR112015018759A2 (pt) 2017-07-18
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