WO2013071848A1 - 一种太阳能集热器 - Google Patents

一种太阳能集热器 Download PDF

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Publication number
WO2013071848A1
WO2013071848A1 PCT/CN2012/084464 CN2012084464W WO2013071848A1 WO 2013071848 A1 WO2013071848 A1 WO 2013071848A1 CN 2012084464 W CN2012084464 W CN 2012084464W WO 2013071848 A1 WO2013071848 A1 WO 2013071848A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
metal
heat
tube
heat exchange
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PCT/CN2012/084464
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English (en)
French (fr)
Inventor
刘阳
Original Assignee
北京兆阳光热技术有限公司
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Publication of WO2013071848A1 publication Critical patent/WO2013071848A1/zh

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Classifications

    • 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
    • F24S10/20—Solar heat collectors using working fluids having circuits for two or more working fluids
    • 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

Definitions

  • the invention relates to a solar collector in the field of solar thermal utilization. Background technique
  • the heat exchange medium of solar energy collection technology mainly uses heat transfer oil as the heat transfer medium. After heat exchange of heat transfer oil, the conventional steam turbine is driven to drive the generator set to generate electricity.
  • the operating temperature of the heat transfer oil must be controlled within 400 ° C. Exceeding this temperature will cause problems such as cracking of the heat transfer oil, increase in viscosity, and reduction in heat transfer efficiency, thus limiting the operating temperature of the solar thermal power generation.
  • the cost of heat transfer oil is too high, so there is an urgent need for new heat transfer fluids to replace the heat transfer oil to increase the operating temperature and reduce the cost of equipment and operating costs.
  • the substitutes for the heat exchange medium of the international solar collector technology are molten salt materials, but the crystallization points are relatively high, mostly around 230 to 260 ° C, so there are still many difficulties in direct replacement.
  • the current molten salt is mainly used for heat. Energy storage.
  • the direct steam generation (DSG) technology which directly uses water as a heat exchange medium, has been tested for many years.
  • This technology is similar to the operation principle of a steam boiler heated pipe. With water as the working medium, the low temperature water is injected from one end of the heat absorption pipe, and the water is along the pipe. During the axial travel of the road, the heat absorption gradually increases, and after reaching the boiling point, it becomes saturated steam, and then the heat absorption continues to become superheated steam.
  • the embodiment of the invention provides a novel solar collector, comprising a heat transfer zone, a heat transfer medium and a heat exchange zone, and a heat exchange medium, wherein the heat transfer zone is located at a position where the sun light converges, and the heat exchange zone is The heat transfer zone is surrounded by a flowing heat transfer medium; a heat exchange medium flowing through the heat exchange zone is arranged; a boiling point of the heat transfer medium in the heat transfer zone is higher than an output temperature of the heat exchange medium; The sunlight energy transfers heat through the heat transfer medium and the internal heat transfer medium to the heat exchange medium flowing through the heat exchange zone; after the heat exchange medium absorbs heat, the heat sink flows out to complete heat exchange.
  • the heat exchange medium generates phase change heat in the heat exchange region.
  • the external portion of the solar collector is locally heated, and the heat transfer medium flows inside the heat transfer region to obtain high heat transfer performance, overcome the deformation warpage caused by external local heat unevenness, and effectively
  • the received heat is conducted to the heat exchange zone; a portion or all of the heat transfer medium undergoes a permeable flow in the heat transfer zone, preferably in a heat transfer zone.
  • the solar collector comprises a metal outer tube and a metal middle tube; a space formed between the metal outer tube and the metal middle tube is a heat transfer area; and all or part of a space inside the metal tube is a heat exchange area
  • the heat exchange medium flows through the inside of the metal tube to allow heat to flow out of the system.
  • the metal outer tube further includes a metal inner tube; after the heat transfer medium passes through the heat transfer region in the outer metal tube, the circulating flow path of the heat transfer medium passes through the metal inner tube, and the heat transfer medium is in the metal The circulating flow is completed in the loop formed by the tube to realize the overall circulation of the heat transfer medium inside the metal outer tube.
  • the heat exchange zone is comprised of all or a portion of the interior space of one or more metal intermediate tubes, and a plurality of heat exchange zones are implemented to simultaneously phase change heat.
  • the metal inner tube and the inner tube of the metal tube are arranged in parallel inside and outside the metal outer tube, and a space formed between the inner wall of the metal tube and the outer wall of the metal inner tube is a heat exchange area, and the other space in the outer metal tube is Heat transfer zone.
  • a part of the metal inner tube and/or the metal middle tube is provided with a medium passage, and the heat transfer medium and the heat exchange medium are the same medium, and part or all after the heat transfer flow is completed in the heat transfer area. Enter the heat exchange zone to complete the heat exchange.
  • the metal inner tube or the metal middle tube is a spiral corrugated tube or a spiral corrugated tube, which increases the eddy current of the heat exchange medium and the heat transfer medium, generates a higher heat transfer coefficient, and improves efficiency.
  • the solar collector further includes a superheating zone, and receives a gas phase of the heat exchange space output Or the heat exchange medium of the vapor-liquid mixed phase is superheated to obtain better steam parameters.
  • the superheating zone or the heat transfer zone is arranged with a spiral flow guiding device.
  • the spiral advances to reduce the temperature difference of the circumferential wall surface. Reduce the warpage of the pipe.
  • the superheating zone is a space of the fourth metal pipe extending along the longitudinal direction of the outer pipe axis, receiving heat in the axial direction, and changing the gas phase heat exchange medium into high-parameter superheated steam.
  • the superheating zone is an inner space of the independent metal fourth pipe arranged in parallel with the outer pipe, and the manner is more conveniently utilized in the linear concentrating system, and the fourth tube and the outer pipe of the metal can be realized by a reasonable optical design. A certain proportion receives the concentrated light energy, and the fourth tube receives a small amount of heat to turn the saturated steam or the wet steam into the outside of the superheated steam delivery system.
  • the heat exchange medium inlet is provided with a one-way valve to control the amount of continuous feed water and pressure.
  • the heat transfer zone has an exhaust device that mainly collects a gas phase generated by a sudden intense heating of the heat transfer medium in the heat transfer zone, and passes through an exhaust valve discharge system disposed at a high end position. External, avoid affecting heat transfer.
  • the heat transfer zone is arranged obliquely, and its high end position is an exhaust device.
  • the heat transfer zone is provided with a voltage stabilizing device to continuously maintain the pressure inside the heat transfer zone within a certain stable range to ensure that the heat transfer medium does not undergo a phase change.
  • the heat transfer medium is pressurized water, a heat transfer oil, a thermal conductive or molten salt, and has a higher boiling point than the heat exchange medium.
  • the heat exchange medium is a substance having a gas-liquid two-phase change in a temperature range lower than a boiling point of a heat transfer medium in a heat transfer zone, such as water, a ketone, an ether, an alcohol, and a liquid phase or a low boiling point.
  • a heat transfer medium such as water, a ketone, an ether, an alcohol, and a liquid phase or a low boiling point.
  • Metal heat pipe medium is a substance having a gas-liquid two-phase change in a temperature range lower than a boiling point of a heat transfer medium in a heat transfer zone, such as water, a ketone, an ether, an alcohol, and a liquid phase or a low boiling point.
  • Metal heat pipe medium such as water, a ketone, an ether, an alcohol, and a liquid phase or a low boiling point.
  • the heat exchange medium is water
  • phase change heat is performed in the heat exchange zone to complete the DSG process.
  • the phase change solar collector provided by the invention can be applied to the field of solar thermal utilization such as trough photothermal, Fresnel array photothermal or tower photothermal collector.
  • phase change solar collector of the embodiment of the present invention even if the outside of the metal outer tube is unevenly heated, the circulation of the heat transfer medium flowing inside the closed loop in the system reduces the temperature of the circumferential interface caused by the uneven heating of the pipe. Uniformity to avoid tube warpage.
  • a plurality of heat exchange tubes are arranged in parallel inside the metal outer tube, the heat exchange tubes are small in size, and are uniformly heated under the action of heat transfer medium heat transfer, overcoming the axis of the two-phase flow conversion and vaporization pressure occurring in the axial direction Water hammer, vibration phenomena and pipeline fatigue damage caused by non-uniform distribution, as well as problems such as excessive tube temperature burnout and pipeline bending.
  • the cation collector further includes a superheating zone, and the saturated steam or soda-water mixture output from the heat exchange tube is again heated to become high-parameter steam.
  • the overall heat absorption efficiency of the device of the embodiment of the invention is higher than that of the conventional single-ended input mode.
  • Figure 1 is a schematic view showing a first embodiment of a solar thermal collector of the present invention.
  • Figure 2-1 is a schematic cross-sectional view showing a second embodiment of the solar thermal collector of the present invention.
  • FIG. 2-2 is a schematic cross-sectional view showing a second embodiment of the solar heat collector of the present invention.
  • Fig. 3 is a schematic view showing a third embodiment of the solar heat collector of the present invention.
  • Fig. 4 is a view showing the fourth embodiment of the overall structure of the solar collector of the present invention applied to the field of solar Fresnel array.
  • Figure 5-1 is a schematic view showing a fifth embodiment of the overall structure of the solar collector of the present invention applied to the field of solar Fresnel array.
  • Fig. 5-2 is a schematic structural view of a solar heat collector of a fifth embodiment.
  • Fig. 5-3 is a schematic view showing the heating of the solar collector of the fifth embodiment.
  • 5-4 is a schematic view showing the structure of a fourth tube of the solar collector of the fifth embodiment. detailed description
  • FIG. 1 is a schematic view showing a first embodiment of a solar thermal collector of the present invention.
  • the solar collector 1 comprises a metal inner tube 2, a metal outer tube 3, a metal intermediate tube 4, a heat transfer medium 7 and a heat exchange medium 6.
  • the metal inner tube 2 and the metal middle tube 4 are arranged in parallel inside the metal outer tube 3.
  • the heat transfer zone of this embodiment comprises two parts, a space formed by the inside of the metal outer tube 3, the outer part of the metal inner tube 2 and the outer part of the metal middle tube 4, and the space inside the metal inner tube 2; the heat transfer medium 7 Part or all of the circulating flow path passes through the inner metal tube 2 and circulates inside the heat transfer zone; the inner space of the metal tube 4 is a heat exchange zone, and a heat exchange medium flows inside, and the heat exchange zone is surrounded by the heat transfer zone;
  • the phase change heat is completed inside the heat exchange zone;
  • the heat transfer medium 7 has a higher boiling point than the heat exchange medium 6, such as pressurized water, heat transfer oil, thermal grease or molten salt, completes the heat exchange medium 6 in the liquid circulation The phase change heat of the heat exchange medium 6 during the flow.
  • At least one metal intermediate tube 4 may be arranged in an array in a space formed by the outer metal tube 3 and the inner metal tube 2, and the heat exchange medium 6 inside the plurality of metal tubes 4 is partially or completely obtained with sufficient heat. Phase change provides sufficient phase change heat.
  • the outer wall of the metal outer tube 3 of the solar collector partially receives external heat and passes through the metal.
  • the outer wall of the tube 3 is transferred to the heat transfer medium 7 inside the heat transfer zone, and the heat transfer medium 7 flows in the heat transfer zone, for example, through a fluid flow or a circulating flow, has a strong heat exchange capability, and has excellent heat transfer heat of reception.
  • it also has a good uniform temperature capability, which overcomes the problem of warping of the metal outer tube 3 caused by excessive temperature difference caused by local heat unevenness of the conventional solar collector; the heat transfer medium 7 is heated and flowed inside the heat transfer area.
  • the heat is also transferred to the inside of the phase change hot zone of the metal tube 4; during the flow of the heat exchange medium 6 in the phase change hot zone, the heat transferred by the heat transfer medium 7 is received, and after being gradually heated, The vaporization occurs, and the gaseous heat exchange medium 6 flows out of the system to complete the heat exchange stably and efficiently.
  • the upper portion of the heat transfer zone may be provided with an exhaust device such as an exhaust valve 14 to prevent the heat transfer zone from being locally heated. , causing a decrease in heat transfer performance inside the heat transfer zone.
  • the sunlight energy transfers heat to the heat exchange medium 6 flowing through the heat exchange zone through the heat transfer zone and the internal heat transfer medium 7; the outer wall corresponding to the outer metal pipe 3 is located at the sun light convergence position to receive the sunlight energy;
  • the liquid convection and forced circulation of the medium 7 are substantially uniform in temperature, which can avoid the serious warpage caused by the large wall temperature difference caused by the uneven heat external to the metal outer tube 3.
  • the temperature of the heat transfer medium 7 in the heat transfer zone is higher than the temperature of the saturated steam corresponding to the pressure of the vaporization zone formed by the heat exchange medium 6 inside the metal tube 4, so as to continuously supply the heat exchange medium in the metal middle tube 4. 6 vaporization required heat, complete the phase change heat process of the heat exchange medium 6; specific heat exchange process ⁇ mouth:
  • a check valve may be arranged at the inlet of the metal tube 4 to control the continuous supply of the heat exchange medium 6 and maintain the internal pressure of the heat exchange tube; the heat exchange medium 6 flows through the inside of the metal heat exchange tube in the form of a liquid phase, and receives the outer wall of the metal outer tube 3
  • the heat transferred, the internal liquid phase heat transfer medium 7 temperature is higher than the saturation temperature of the heat exchange medium 6 under specific parameters 20-50 ° C, for example, the heat exchange medium 6 water parameter is 6MPa corresponding to the saturation temperature is 275 ° C, the heat transfer medium 7 ⁇ uses 1 OMPa high-pressure water, the temperature can reach 300 ° C and remain liquid; the heat transfer medium 7 continues to heat the medium 6 to maintain a temperature difference of more than 25 ° C; heat transfer medium 7 After being heated, it circulates in the heat transfer zone to transfer heat to the heat exchange medium 6 flowing inside the metal tube 4.
  • the heat exchange medium 6 is gradually heated during the process of flowing through the inside of the metal tube 4, and finally completes vaporization and overheating.
  • the temperature difference in the whole process of superheat boiling is maintained at about 25 °C, and the tube in the metal tube is heated uniformly; and the phase change heat generated inside is basically uniform boiling heat exchange, thereby avoiding a large amount of liquid deposition bottom. Local boiling occurs suddenly and so unstable state.
  • the outer wall of the outer metal pipe 3 When the outer wall of the outer metal pipe 3 continues to receive an increase in external heat, the outer wall conducts heat to the inner wall of the outer metal pipe 3 and the heat of the liquid phase heat transfer medium 7 inside the heat transfer zone increases, so that the temperature of the liquid phase heat transfer medium 7 increases, and the heat exchange The medium 6 receives more heat and can obtain saturated steam in a shorter phase change heat zone.
  • the output end of the metal tube 4 outputs superheated steam.
  • the increase of the amount of the heat exchange medium 6 at the beginning of the solar collector is adjusted, so that the heat exchange medium 6 can always maintain a fairly stable heat exchange medium.
  • the output of the parameter At the end of the solar collector 1, according to the change of the temperature and pressure of the heat exchange medium 6, the increase of the amount of the heat exchange medium 6 at the beginning of the solar collector is adjusted, so that the heat exchange medium 6 can always maintain a fairly stable heat exchange medium. The output of the parameter.
  • the parameter of the heat exchange medium 6 at the outlet of the heat exchange tube becomes low, and according to the change of the temperature and pressure of the heat exchange medium 6, the amount of the heat exchange medium 6 is adjusted to be reduced, and the automatic is achieved.
  • the purpose of controlling the stability requirements of the heat exchange medium parameters of the heat exchange medium 6 of the heat exchange zone is controlled.
  • the solar collector 1 can intelligently control the flow inside the metal tube 4 according to the external heating condition, continuously ensure the relative stability of the inner wall temperature of the metal inner tube 2, and provide a good heat exchange environment for the heat exchange medium 6; more importantly, Because the liquid-phase heat transfer medium 7 formed inside the annular liquid phase region formed by the metal outer tube 3 and the metal inner tube 2 can well ensure the temperature stability of the metal outer tube 3, and the circumferential direction of the metal outer tube 3 in contact with it is unevenly heated.
  • the temperature of the pipe wall is substantially uniform; and the problem of uneven temperature of the ring wall caused by the vaporization phase change process inside the metal inner pipe 2 is solved, and if the heat exchange medium 6 is water, it can be well Solve the problems caused by the uneven temperature of the ring wall caused by the uneven temperature of the ring wall in the traditional DSG system and the stability of the system.
  • the solar collector can also be simplified to include only the metal outer tube 3 and the metal middle tube 4, and the metal medium tube 4 can also be arranged inside the metal outer tube 3 in a plurality of middle tubes and parallel to each other; the metal outer tube 3
  • the space formed inside the inner tube and the plurality of metal tubes 4 is a heat transfer area, and the inside of the plurality of metal tubes 4 is a concomitant heat exchange area.
  • the heat exchange medium 6 of the solar collector may be a gas-liquid two-phase change in a temperature range lower than the boiling point of the heat transfer medium in the heat transfer zone.
  • the heat exchange medium 6 is water, ketones, ethers, alcohols, and liquid or low boiling metal heat pipe media.
  • the heat transfer medium 7 inside the heat transfer zone is a substance which can keep the liquid from boiling at a certain pressure and temperature, and is preferably water, heat transfer oil, heat conduction or molten salt.
  • the heat exchange medium 6 can also not undergo phase change heat inside the heat exchange zone, and the heat of the heat of the heat exchange medium 6 is utilized, for example, the saturated steam of low temperature becomes high temperature after stable and uniform heat exchange. superheated steam.
  • FIG. 2-1 is a schematic cross-sectional view showing a second embodiment of the solar thermal collector of the present invention.
  • the solar collector 1 includes a metal outer tube 3, a metal intermediate tube 4, and a metal inner tube 2; wherein the metal middle tube 4 and the metal inner tube 2 are arranged inside each other in the metal outer tube 3.
  • the annular space formed by the metal outer tube 3 and the metal intermediate tube 4 and the inner space of the metal inner tube 2 constitute a heat transfer region.
  • a flowing heat transfer medium 7 is arranged inside the heat transfer zone.
  • the annular space formed by the metal intermediate tube 4 and the metal inner tube 2 constitutes a heat exchange zone, and the heat exchange medium 6 flows through the annular section, and the heat exchange medium 6 is heated in the heat exchange zone, and the phase change vaporizes and flows out of the system. .
  • the heat transfer medium 7 in the heat transfer zone has a higher temperature than the heat exchange medium 6 in the phase change hot zone, and the heat exchange medium 6 circulates in the closed circulation space of the heat transfer zone, and the heat received by the metal outer pipe 3 is quickly transmitted to Heat exchange zone;
  • the heat exchange medium 6 flows out of the system after a stable phase change inside the heat exchange zone.
  • the solar collector is arranged at the output end of the heat exchange medium 6 with a closed loop control circuit 13 for adjusting the flow rate and flow rate of the heat transfer medium 7 by the change of the parameters of the output heat exchange medium 6.
  • the metal inner tube 2 or the metal intermediate tube 4 can be optimized as a spiral bellows or a spiral corrugated tube (not shown), where the heat transfer medium 7 or the heat exchange medium 6 is located.
  • the movement of eddy currents and turbulence is formed inside the heat transfer zone or the heat exchange zone to enhance the heat transfer coefficient.
  • a flow guiding device is arranged in the heat transfer zone, for example, the flow guiding device enables the heat transfer medium 7 to obtain a swirling flow effect inside the heat transfer zone to enhance heat transfer performance.
  • a voltage stabilizing device and a safety valve or a pressure relief valve are arranged in the heat transfer zone, and the voltage stabilizing device can stabilize the pressure inside the heat transfer zone and prevent local leakage.
  • the pressure drop caused by the stability causes boiling after entering the saturation zone; a safety valve or a pressure relief valve arranged in series at a certain position in the heat transfer zone to prevent the danger caused by excessive pressure.
  • FIG. 2-1 The flow path of the heat transfer medium 7 in the heat transfer zone inside the solar collector is as shown in FIG. 2-1.
  • the heat transfer medium may also flow from the metal inner tube 2 to the metal outer tube. 3
  • the flow in the annular space formed by the metal tube 4 completes the flow inside the heat transfer region.
  • Fig. 2-2 is a schematic cross-sectional view showing a second embodiment of the solar energy collector of the present invention.
  • Fig. 3 is a schematic view showing a third embodiment of the solar heat collector of the present invention.
  • the solar collector includes a metal outer tube 3, a metal intermediate tube 4, and a metal inner tube 2.
  • the inner metal tube 2 and the metal inner tube 4 are arranged concentrically inside the metal outer tube 3 in parallel.
  • the outer metal tube 3 and the metal intermediate tube 4 form an annular space and the inner metal tube 2 constitutes a heat transfer area, and a heat transfer medium 7 is disposed inside the heat transfer portion.
  • the annular space formed by the metal intermediate tube 4 and the metal inner tube 2 constitutes a heat exchange zone, and the heat exchange medium 6 flows through the inside of the annular section.
  • a portion of the metal inner tube 2 and/or the metal intermediate tube 4 of the solar collector is provided with a medium passage.
  • the heat transfer medium 7 and the heat exchange medium 6 may be the same medium.
  • the heat transfer medium 7 and the heat exchange medium 6 are both water. After the heat transfer flow is completed in the heat transfer zone, some or all of them enter the heat exchange zone to complete the heat exchange.
  • the heat transfer medium 7 has a high pressure and high temperature parameter inside the heat transfer zone to complete the liquid flow, After entering the heat exchange zone through the medium passage of the heat transfer zone and the heat exchange zone having the pressure reduction function, the heat is transferred from the high pressure heat transfer medium 7 to the relatively low pressure heat exchange medium 6, and the heat exchange medium 6 is partially flashed, but large Part of the heat exchange medium 6 is outside the temperature difference of the heat transfer medium 7 (the external temperature has a temperature difference higher than the pressure of the internal heat exchange medium 6 corresponding to the saturation temperature, for example, 25 ° C), and the heat exchange medium 6 is in the heat exchange region. Continue to be heated, phase change vaporized and then flow out of the system.
  • the medium passages of the heat transfer zone and the heat exchange zone may be a certain size orifice arranged on the pipe wall of the metal pipe 4 or the inner pipe of the metal pipe. The pressure through the orifice orifice completes the pressure drop and the specific flow into the heat exchange zone.
  • the flow path of the heat transfer medium 7 inside the solar collector is as shown in FIG.
  • the heat transfer medium 7 may flow from the inner metal tube 2 to the annular space formed by the outer metal tube 3 and the metal intermediate tube 4, and finally flow through the metal inner tube 2 and the metal inner tube.
  • the heat exchange process is completed inside the 4 heat exchange zones.
  • a closed loop control circuit 13 is arranged at the output end of the heat exchange medium 6, and the flow rate and flow rate of the heat transfer medium 7 are adjusted by the change of the parameters of the output heat exchange medium 6.
  • Fig. 4 is a view showing the fourth embodiment of the overall structure of the solar collector of the present invention applied to the field of solar Fresnel array.
  • the fourth embodiment differs from the first embodiment in that a metal fourth tube 5 is provided which is arranged along the extension axis of the first embodiment.
  • the heat exchange medium receives the solar Fresnel array of solar mirror fields 10 reflected light, completing the output of steam from the heat transfer tubes. Then, the steam heat exchange medium enters the superheating zone in the fourth metal pipe 5.
  • the wet steam heat exchange medium obtains the higher parameters required to be heated inside the superheated zone of the fourth metal tube 5, and flows out from the end; the steam is substantially single phase inside the superheated zone, and no liquid phase heat exchange medium phase change brings A series of problems such as water hammer, vibration and severe warpage.
  • Fig. 5-1 is a schematic view showing a fifth embodiment of the overall structure of the solar collector of the present invention applied to the field of solar Fresnel array. Since the steam output is completed after the first embodiment (the heat exchange medium is water), the obtained steam parameters are not easily controlled, and even in accordance with the second embodiment of the present invention, the metal is arranged in the extension line of the first embodiment. Tube 5, there may also be cases where the heat received by the liquid phase is not uniform (for example, the solar collector is applied to the solar thermal fresnel array field or the solar thermal trough field), the internal temperature difference of the fourth metal tube 5 It is still possible to be high and uneven, and warpage still occurs. According to a fifth embodiment of the present invention, as shown in FIG. 5-1, the solar collector receives the light reflected by the solar mirror field 10 of the solar Fresnel array, The solar collector is incident on the re-concentration of the compound parabolic concentrator (CPC) 9.
  • CPC compound parabolic concentrator
  • Fig. 5-2 is a schematic structural view of a solar heat collector of a fifth embodiment. See Figure 5-2, Metal No.
  • the superheating zones of the four tubes 5 are arranged in parallel on the upper part of the axis of the metal outer tube 3, which are arranged below the compound parabolic concentrator (CPC) 9; the metal inner tube 2 and the metal outer tube 3 are arranged concentrically inside and outside.
  • the annular cross-sectional space between the inner metal tube 2 and the outer metal tube 3 and the space formed inside the inner metal tube 2 constitute a heat transfer region, and the heat transfer medium 7 is disposed inside; the inner portion of the metal tube 4 is a heat exchange medium 6 and receives heat.
  • Fig. 5-3 is a schematic view showing the heating of the solar collector of the fifth embodiment.
  • the metal fourth tube 5 and the metal outer tube 3 are assisted by a specific shape of the auxiliary concentrator 9 (the inner metal tube 3 is internally arranged with a metal inner tube 2 and a metal inner tube 4 arranged concentrically inside and outside)
  • the ratio of the heat receiving the solar mirror field is related to the different diameters of the tubes and the different solar rays at different times.
  • the solar collector, the metal fourth tube 5 tube diameter is smaller than the metal outer tube 3, and the heat ratio of the metal fourth tube 5 and the metal outer tube 3 receiving the solar mirror field at different times is about 1: 2 ⁇ 5;
  • the lower metal outer tube 3 receives 75% of the total heat, and the upper metal fourth tube 5 receives 25% of the total heat, which is equivalent to the ratio of the heat of vaporization of the water heat exchange medium to the heat of the superheated steam, ie, the lower metal
  • the heat received by the tube 3 substantially satisfies the conversion of the internal liquid phase heat exchange medium into a saturated steam heat exchange medium, and then enters the metal fourth tube 5; the metal fourth tube 5 receives another part of the total heat, so that the saturated steam heat exchange The medium is further overheated and the system is removed after the required parameters are reached to complete the heat transfer.
  • the metal fourth tube 5 of the structure of the embodiment is arranged on the upper part of the metal outer tube 3, and the received heat density is small, and the tube diameter is small, and the internal heat exchange is more easily completed, and the tube wall temperature has a more uniform temperature difference, further Decreasing the tube wall warping temperature; and in the third embodiment, even if there is a partial heat unevenness or no heat in a certain length region in the axial direction of the solar collector (for example, clouds obscuring sunlight entering the mirror field) Case), because the metal outer tube 3 and the metal fourth tube 5 are arranged in parallel, the ratio of the received external solar light of the metal outer tube 3 to the metal fourth tube 5 is still comparable, and the saturated heat exchange medium and the superheated heat exchange are still well treated.
  • the quality proportional relationship of the medium avoids the unfavorable condition of the conventional system due to a certain partial heat unevenness, which makes the phase change process of the heat exchange medium difficult to control, and causes unstable operation of the system.
  • the metal fourth tube 5 and the metal outer tube 3 can be fixed to each other by welding or the like, and the structure and the dimensional stability of the system are not damaged even if the tube is warped. Sex.
  • FIG. 5-4 is a schematic structural view of a fourth tube of the solar collector according to the fifth embodiment; as shown in FIG. 5-4, in order to obtain a wall temperature difference of a more uniform wall of the tube, the inside of the fourth tube 5 of the metal is disposed.
  • a spiral flow guiding device such as a spiral rotating fin 12; such a gas phase heat exchange medium in the process of flowing through the hot zone, under the action of the spiral rotating fin 12, spiral advances, reducing the temperature difference of the circumferential wall surface of the superheating zone, further reducing the tube The degree of warpage of the road.
  • the liquid phase heat transfer medium in the heat transfer zone may be partially aggravated by the sudden increase of heat, etc., so that the upper part of the heat transfer zone has a venting zone for storage.
  • the exhaust device is located at the high end, is inclined by the whole, for example, at 2° with the horizontal plane; further, the exhaust device is disposed at a specific position of the exhaust region, such as an exhaust valve, The heat medium is discharged by a gas phase heat transfer medium which is unstable by heat.
  • the solar collector can also be applied to a tower system in the field of solar thermal field.
  • the solar collector array is arranged on the tower type photothermal central receiving tower, and receives the sunlight concentrated by the mirror field.
  • the superheated vapor after the vaporization phase change inside the heat medium will leave the sunlight tropical away from the heat collecting system.

Abstract

一种太阳能集热器（1），包括传热区和换热区，传热区位于太阳光线会聚位置，换热区被传热区包围；传热区内部布置有流动的传热介质（7），换热区内部布置有流动通过的换热介质（6）；传热区内的传热介质（7）的沸点高于换热介质（6）的输出温度，太阳光能量通过传热区以及内部的传热介质（7）对流动通过换热区的换热介质（6）传递热量；换热介质（6）吸收能量后，流出太阳能集热器（1）完成换热。该太阳能集热器（1）运行安全可靠，具有良好的适用范围。

Description

技术领域
本发明涉及一种太阳能热利用领域的太阳能集热器。 背景技术
随着太阳能等可再生能源利用在全世界蓬勃发展， 太阳能聚热发电
( CSP )逐步为人们所认识。 在 CSP体系中， 吸热传热部分具有非常重要的 地位。 太阳能的集热技术的换热介质， 目前主要釆用导热油为传热工质， 经 导热油换热后驱动常规蒸汽轮机带动发电机组发电。导热油工作温度必须控 制在 400°C以内， 超出这一温度将会导致导热油裂解、 粘度提高以及传热效 率降低等问题， 因此限制了太阳能聚热发电的工作温度。 同时， 导热油使用 成本 [艮高， 因此迫切需要有新的传热工质取代导热油， 以提高工作温度， 并 降低装置造价和运行成本。 目前国际太阳能集热技术的换热介质的替代品有 熔融盐类材料， 但其结晶点较高， 大多在 230至 260°C左右， 因此直接替换 仍有诸多困难， 当前熔融盐主要用于热储能。
用水直接作为换热介质的直接蒸汽发生 （DSG )技术已经试验多年， 该 技术与蒸汽锅炉受热管道运行原理相似， 以水为工质， 将低温水自吸热管路 一端注入， 水在沿管路轴向行进过程中吸热逐渐升温， 达到沸点后变为饱和 蒸汽，再继续吸热变为过热蒸汽。由于水在受热管内发生沸腾时状态不稳定， 存在两相流传输和汽化压力在集热管内不均匀等问题，发生例如水锤、振动、 管路材料疲劳破坏现象； 另外在饱和蒸汽变为过热蒸汽段， 由于蒸汽导热能 力差，热吸收能力较弱，容易发生管路过温损毁； 并且当管路受热不均匀时， 管壁温差较大， 会发生严重弯曲， 带来其他损失（如真空密封破坏）； 再者 现有技术仍然没有解决 DSG管道在局部无受热（例如镜场因云朵遮挡引起的 局部出现阴影）所带来的一系列问题， 例如水输入及汽输出流量控制， 参数 变化的影响。因此该技术仍停留在试验阶段，但只要这些问题能够得以解决， DSG技术就成为成本最低、 效率最高的环保安全型太阳能热发电关键技术。 发明内容 多领域的新型太阳能集热器。
本发明实施例提供了一种新型太阳能集热器， 包括传热区、 传热介质和 换热区、 换热介质， 其特征在于， 所述传热区位于太阳光线会聚位置， 换热 区被传热区包围； 传热区内部布置有流动的传热介质； 换热区内部布置有流 动通过的换热介质；所述传热区内的传热介质沸点高于换热介质的输出温度; 太阳光能量通过所述传热区及内部的传热介质对流动通过换热区内的换热 介质传递热量； 所述换热介质吸收热量后， 流出太阳能集热器完成换热。
进一步地， 所述换热介质在换热区内发生相变换热。
进一步地， 所述太阳能集热器的外部局部受热， 传热介质在传热区的内 部流动，获得较高的传热性能，克服外部局部受热不均引起的变形翘曲问题， 同时有效地将接收的热量传导至换热区； 所述传热介质的一部分或全部在传 热区内进行通过性流动， 优选为在传热区内进行循环流动。
进一步地， 所述太阳能集热器包括金属外管、 金属中管； 所述金属外管 与金属中管之间所形成的空间为传热区； 金属中管内部全部或部分空间为换 热区； 换热介质贯穿流动于金属中管内部， 实现换热后流出系统外部。
进一步地， 所述金属外管内部还包括金属内管； 所述传热介质经过金属 外管内的传热区后， 所述传热介质的循环流动路径通过金属内管， 传热介质 在金属内管所形成的回路中完成循环流动， 实现金属外管内部的传热介质的 总体循环。
进一步的实施例中，所述换热区由一根或多根的金属中管的全部或部分 内部空间组成， 实施多个换热区同时相变换热。
进一步地， 所述金属内管、 金属中管内外平行布置于金属外管内部， 所 述金属中管内壁与金属内管外壁之间所形成的空间为换热区，金属外管内的 其它空间为传热区。
进一步地， 所述金属内管和 /或金属中管的某个部分设置有介质通道， 所述传热介质与换热介质为同一种介质， 在传热区完成传热流动后， 部分或 全部进入换热区完成换热。
优化地， 所述金属内管或金属中管为螺旋波纹管或螺旋波纹节管， 增加 换热介质和传热介质在内部的涡流， 产生更高的换热系数， 提高效率。
进一步地， 所述太阳能集热器还包括过热区， 接收换热空间输出的气相 或汽液混合相的换热介质进行过热加热， 以获得更好的蒸汽参数。
优选地， 所述过热区或传热区内布置有螺旋导流装置， 换热介质或传热 介质在流经的过程中， 在导流装置的作用下， 螺旋前进， 降低圓周壁面温度 差， 降低管路的翘曲程度。
进一步地， 所述过热区为沿外管轴线长度方向上延伸布置的金属第四管 管内空间， 接收轴向上的热量， 将气相换热介质变成高参数的过热蒸汽。
进一步地， 所述过热区为与外管并列布置的独立金属第四管内部空间， 方式更加便利地利用于线形聚光系统， 通过合理的光学设计， 可实现该金属 第四管与外管按一定比例接收会聚光能量， 第四管接收小量的热量将饱和蒸 汽或湿蒸汽变成过热蒸汽输送系统外部。
进一步地， 所述换热介质入口布置单向阀， 控制持续补给水量及压力。 进一步地， 所述传热区具有排气装置， 该排气装置主要将传热区的传热 介质内部因突然剧烈受热等原因产生的气相收集， 并通过位于高端位置布置 的排气阀排出系统外部， 避免影响传热效果。
进一步地， 所述传热区倾斜布置， 其高端位置为排气装置。
进一步地， 所述传热区布置有稳压装置， 将传热区内部的压力持续维持 一定的稳定范围内， 保证传热介质不会发生相变。
优选地， 所述传热介质为加压水、 导热油、 导热姆或熔盐， 具有比换热 介质更高的沸点。
进一步地， 所述换热介质为在低于传热区内的传热介质沸点的温度范围 内具有气液两相变化的物质， 如水、 酮类、 醚类、 醇类及液相或低沸点金属 热管介质。
优选地，所述换热介质为水，在换热区内实施相变换热， 完成 DSG过程。 本发明提供的相变太阳能集热器可以应用于槽式光热、 菲涅尔阵列光热 或塔式光热集热器等太阳能热利用领域。
本发明实施例的相变太阳能集热器的金属外管外部即使不均匀受热， 内 部密闭循环流动的传热介质在系统中的循环， 降低了管道因受热不均引起的 圓周界面上的温度不均匀性， 避免管路翘曲。 多个换热管平行布置于金属外 管内部， 换热管的尺寸较小， 且在传热介质流动传热的作用下均匀受热， 克 服轴向上发生的两相流变换和汽化压力的轴向非均匀分布带来的水锤、振动 现象和管路疲劳损坏， 以及局部管温过高烧坏、 管路弯曲等问题。 且相变太 阳能集热器还包括过热区，将换热管输出的饱和蒸汽或汽水混合物再次受热 变成高参数蒸汽。本发明实施例装置整体热吸收效率较传统单端输入方式更 高。 附图说明
图 1是本发明的太阳能集热器第一实施例示意图。
图 2-1是本发明的太阳能集热器第二实施例剖面示意图。
图 2-2是本发明的太阳能集热器第二实施例截面示意图。
图 3是本发明的太阳能集热器第三实施例示意图。
图 4是本发明的太阳能集热器应用于太阳能菲涅尔阵列领域的整体结构 第四实施例示意图。
图 5-1为本发明的太阳能集热器应用于太阳能菲涅尔阵列领域的整体结 构第五实施例示意图。
图 5-2是第五实施例的太阳能集热器的结构示意图。
图 5-3是第五实施例的太阳能集热器受热示意图。
图 5-4是第五实施例的太阳能集热器第四管结构示意图。 具体实施方式
下面参照附图对本发明的具体实施方案进行详细的说明。
图 1是本发明的太阳能集热器第一实施例示意图。从图 1的局部剖视部 分可见， 太阳能集热器 1包括金属内管 2、 金属外管 3、 金属中管 4、 传热介 质 7和换热介质 6。 金属内管 2、 金属中管 4平行布置于金属外管 3内部。 该实施方式的传热区包括两部分， 分别为金属外管 3内部、 金属内管 2外部 和金属中管 4外部三者所形成的空间， 及金属内管 2内部的空间； 传热介质 7的一部分或全部循环流动路径通过金属内管 2 ,且在传热区内部循环流动； 金属中管 4的内部空间为换热区， 内部流动着换热介质， 换热区被传热区包 围； 优选为在换热区内部完成相变换热； 传热介质 7具有较换热介质 6更高 的沸点， 例如加压水、 导热油、 导热姆或熔盐， 完成换热介质 6在液体循环 流动的过程中对换热介质 6的相变换热。 图 1中， 金属外管 3与金属内管 2 所形成的空间内可以阵列布置至少一根金属中管 4 , 多根金属中管 4内部的 换热介质 6部分或全部获得足够热量后完成的相变，提供足够的相变换热量。
该太阳能集热器的金属外管 3的外壁局部接收外部的热量， 穿过金属外 管 3的外壁传递至传热区内部的传热介质 7 , 传热介质 7在传热区内流动， 例如通过性流动或循环流动， 具有较强的换热能力， 具有优良的接收传热热 能的同时， 也具有良好的均温能力， 克服了传统太阳能集热器因局部受热不 均造成温差过大引起的金属外管 3的翘曲问题；传热介质 7在传热区内部受 热、 流动的同时， 也将热量传递至金属中管 4的相变换热区内部； 换热介质 6在相变换热区内流动的过程中，接收传热介质 7译放的热量，逐步受热后， 发生汽化， 变成气态换热介质 6流出系统的外部， 稳定高效地完成换热； 传 热区的上部可以布置排气装置，例如排气阀 14 , 以防止传热区因局部受热产 生的气体， 造成传热区内部的换热性能的下降。
太阳光能量通过传热区及内部的传热介质 7对流动通过换热区内的换热 介质 6传递热量； 对应于金属外管 3的外壁位于太阳光线会聚位置接收太阳 光能量； 由于传热介质 7的液态对流及强制循环， 圓周温度基本均温， 可避 免因为金属外管 3 外部受热不均匀引起的管壁温差较大造成的严重翘曲问 题。 该传热区的传热介质 7的温度， 比金属中管 4内部的换热介质 6所形成 的汽化区的压力所对应的饱和蒸汽温度要高， 以便持续提供金属中管 4内换 热介质 6汽化所需热量， 完成换热介质 6的相变换热过程； 具体的换热过程 ^口下：
可以在金属中管 4的入口布置单向阀，控制持续补给换热介质 6并保持 换热管内部压力； 换热介质 6以液相形式流经金属换热管内部， 接收金属外 管 3外壁传导来的热量， 内部的液相传热介质 7温度高于特定参数下的换热 介质 6的饱和温度 20-50°C ,例如换热介质 6水的参数为 6MPa对应的饱和温 度为 275 °C , 传热介质 7釆用 l OMPa高压的水， 温度可以达到 300°C且保持 为液态；传热介质 7持续对换热介质 6保持 25 °C以上温度差均匀给热；传热 介质 7受热后在传热区循环流动，将热量传递至金属中管 4内部流动的换热 介质 6 , 换热介质 6在金属中管 4的内部贯通流动的过程中， 逐步受热， 最 终完成汽化和过热，整个过热沸腾过程中温度差都保持 25 °C左右，金属中管 4道受热均匀； 且内部发生的相变换热基本为均匀的沸腾换热， 从而避免大 量液相沉积底部， 发生局部突然沸腾等不稳定状态。
当金属外管 3外壁持续接收外部热量增多时， 外壁传导至金属外管 3的 内壁和传热区内部液相传热介质 7的热量增多，使液相传热介质 7的温度增 加， 换热介质 6接收热量增多， 能在更短的相变换热区内获得饱和蒸汽， 在 金属中管 4的输出端输出过热蒸汽。在太阳能集热器 1的末端根据换热介质 6的温度和压力的变化，调整增加太阳能集热器始端的换热介质 6的进入量， 使换热介质 6能始终保持相当稳定的换热介质参数的输出。
当金属外管 3外壁持续接收外部热量不足时， 换热管出口的换热介质 6 参数变低， 根据换热介质 6的温度和压力的变化， 调整减少换热介质 6的进 入量， 达到自动根据系统接收的热流量， 控制换热区的换热介质 6输出口换 热介质参数的稳定性要求的目的。
该太阳能集热器 1能根据外部受热情况， 智能控制金属中管 4内部的流 量， 持续保证金属内管 2内壁温度的相对稳定， 提供良好的换热介质 6换热 环境； 更为重要的是， 因为金属外管 3和金属内管 2所形成环形液相区内部 的液相传热介质 7能良好地保证自身温度稳定，使与之接触的金属外管 3管 壁周向上虽然受热不均， 但在液相水作用下， 管壁温度基本均匀； 而且金属 内管 2内部的水汽化相变过程引起的环壁温度不均问题得到解决，如果换热 介质 6为水， 即可以良好地解决传统 DSG系统出现的因环壁温度的不均匀造 成管道严重翘曲及破坏系统稳定性等问题。
该太阳能集热器还可以简化为只包括金属外管 3和金属中管 4 , 金属中 管 4也可以按多个中管且彼此平行的方式布置于金属外管 3的内部； 金属外 管 3内部与多个金属中管 4外部所形成的空间为传热区， 多个金属中管 4内 部为相伴换热区。
太阳能集热器的换热介质 6可以是在低于传热区内的传热介质沸点的温 度范围内具有气液两相变化的物质。优选地，换热介质 6为水、 酮类、 醚类、 醇类及液相或低沸点金属热管介质。传热区内部传热介质 7为在一定压力和 温度下能保持液态不沸腾的物质， 优选为水、 导热油、 导热姆或熔盐。
实际的操作过程中， 换热介质 6也可以在换热区内部不发生相变换热， 利用换热介质 6的显热受热热量， 例如低温的饱和蒸汽经过稳定均匀的换热 后变成高温过热蒸汽。
图 2-1是本发明的太阳能集热器第二实施例剖面示意图。如图 2-1所示， 太阳能集热器 1包括金属外管 3、金属中管 4、金属内管 2 ;其中金属中管 4、 金属内管 2互套布置于金属外管 3内部。
金属外管 3与金属中管 4所形成环形空间及金属内管 2管内空间构成传 热区。 传热区的内部布置有流动的传热介质 7。 金属中管 4与金属内管 2所形成的环形空间构成换热区， 该环形区间内 部贯穿流动着换热介质 6 , 换热介质 6在换热区内受热， 相变汽化后流出系 统的外部。
传热区的传热介质 7温度高于相变换热区的换热介质 6 , 该换热介质 6 在传热区形成密闭循环空间中循环流动，将金属外管 3接收的热量快速传递 至换热区； 换热介质 6在换热区内部稳定相变后， 流出系统的外部。
太阳能集热器在换热介质 6输出端布置有闭环控制回路 13 ,通过输出的 换热介质 6的参数的变化， 调整传热介质 7的流速和流量。
为了获得更加优化的传导热量的效果，金属内管 2或金属中管 4可以优 化为螺旋波纹管或螺旋波纹节管（图中没有示出），传热介质 7或换热介质 6 在所在的传热区或换热区内部形成涡流、 湍流的运动， 增强传热系数。 为了 进一步在传热区形成湍流， 在传热区实施布置导流装置， 例如导流装置使传 热介质 7在传热区内部获得旋转导流效果， 以增强换热性能。
为了稳定传热区内部的压力以防止传热介质 7沸腾，在传热区布置稳压 装置及安全阀或泄压阀， 该稳压装置能实现传热区内部的压力的稳定， 防止 局部不稳定引起的压力下降， 导致进入饱和区后的沸腾情况； 串联布置于传 热区某位置的安全阀或泄压阀， 防止压力过高带来的危险。
该太阳能集热器内部的传热区的传热介质 7的流经路线如图 2-1所示， 在实际的操作中也可以为传热介质从金属内管 2流经再向金属外管 3与金属 中管 4所形成的环形空间流动完成传热区内部的流动。 图 2-2是本发明的太 阳能集热器第二实施例截面示意图。
图 3是本发明的太阳能集热器的第三实施例示意图。 如图 3所示， 太阳 能集热器包括金属外管 3、 金属中管 4和金属内管 2。 其中， 金属内管 2、 金 属中管 4内外同心平行布置于金属外管 3内部。金属外管 3与金属中管 4所 形成环形空间及金属内管 2管内空间构成传热区，传热区的内部布置有流动 的传热介质 7。 金属中管 4与金属内管 2所形成的环形空间构成换热区， 该 环形区间内部贯穿流动着换热介质 6。
该太阳能集热器的金属内管 2和 /或金属中管 4的某个部分设置有介质 通道。 传热介质 7与换热介质 6可以为同一种介质， 比如传热介质 7与换热 介质 6都为水。在传热区完成传热流动后，部分或全部进入换热区完成换热。 传热介质 7在传热区内部具有高的压力高温度参数，完成液态的通过性流动， 经过传热区与换热区的具有降压功能的介质通道， 进入换热区后， 热量从高 压传热介质 7转换到相对低压的换热介质 6 , 换热介质 6部分闪蒸， 但大部 分换热介质 6在传热介质 7的外部温度差下（外部温度具有高于内部换热介 质 6的压力对应饱和温度的温度差， 例如 25 °C ), 换热介质 6在换热区内继 续受热、 相变汽化后流出系统的外部。
在实际的实施过程中， 传热区与换热区的介质通道， 可以为布置于金属 中管 4或者金属内管 2管壁上的一定尺寸喷孔。通过喷孔的介质完成压力的 下降和进入换热区的特定流量流入。
该太阳能集热器内部的传热介质 7的流经路线如图 3所示。在实际的操 作中也可以为传热介质 7从金属内管 2流经再向金属外管 3与金属中管 4所 形成的环形空间流动， 最后在流经至金属内管 2与金属中管 4所形成换热区 内部完成换热过程。且换热介质 6输出端布置有闭环控制回路 13 ,通过输出 的换热介质 6的参数的变化， 调整传热介质 7的流速和流量。
图 4是本发明的太阳能集热器应用于太阳能菲涅尔阵列领域的整体结构 第四实施例示意图。 如图 4所示， 第四实施例不同于第一实施例的地方在于 增设了金属第四管 5 , 该金属第四管 5沿第一实施例的延长轴线布置。 换热 介质接收太阳能菲涅尔阵列的太阳能镜场 10反射来的光， 完成蒸汽从换热 管的输出。 然后， 蒸汽换热介质进入到金属第四管 5内的过热区。 湿蒸汽换 热介质在金属第四管 5的过热区内部完成受热后获得所需更高参数，从端头 流出； 蒸汽在过热区内部基本为单相， 没有液相换热介质相变带来的水锤、 振动和严重翘曲等一系列问题。
图 5 - 1为本发明的太阳能集热器应用于太阳能菲涅尔阵列领域的整体结 构第五实施例示意图。 由于第一实施例（换热介质为水）完成蒸汽的输出后， 获得的蒸汽参数并不容易控制， 且即使按照本发明的第二实施例， 在第一实 施例的延长线布置金属第四管 5 , 也可能出现液相区接收的热量不均匀的情 况（例如该太阳能集热器应用于太阳能光热菲涅尔阵列领域或太阳能光热槽 式领域）， 金属第四管 5 内部温度差仍然有可能偏高且不均匀， 仍然会出现 翘曲； 本发明的第五实施例， 如图 5-1所示， 太阳能集热器接收太阳能菲涅 尔阵列的太阳能镜场 10反射的光， 在复合抛物聚光器（CPC ) 9的再次聚光 下入射太阳能集热器。
图 5-2是第五实施例的太阳能集热器的结构示意图。 见图 5-2 , 金属第 四管 5的过热区平行布置于金属外管 3轴线的上部，二者布置于复合抛物聚 光器（CPC ) 9之下； 金属内管 2与金属外管 3 同心内外布置。 金属内管 2 和金属外管 3之间的环形截面空间及金属内管 2内部所形成的空间构成传热 区， 内部布置传热介质 7; 金属中管 4 内部为换热介质 6 , 接收热量变成饱 和的蒸汽， 金属第四管 5内部为过热区， 接收换热管内部流经来的饱和气相 换热介质； 金属第四管 5与金属外管 3平行布置， 在复合抛物聚光器（CPC ) 9的作用下， 金属第四管 5、 金属外管 3二者获得的太阳能镜场 10反射光的 比例保持在一定范围内例如。此方式可以在经常及管路长度方向上的局部位 置被云朵遮挡形成阴影时， 保持蒸发与过热两过程的吸收能量比例不变， 易 于稳定控制输出蒸汽品质。
图 5-3是第五实施例的太阳能集热器受热示意图。 如图 5-3 , 金属第四 管 5与金属外管 3在特定形状的辅助聚光器 9的辅助下（金属外管 3内部布 置有内外同心布置的金属内管 2 和金属中管 4 ), 接收太阳能镜场的热量的 比， 与不同的管径和不同时刻太阳光线不完全一致有关。 本太阳能集热器， 设计金属第四管 5管径小于金属外管 3 , 且满足不同时刻的金属第四管 5与 金属外管 3接收太阳能镜场的热量比大约 1 : 2〜5； 例如下部的金属外管 3 接收总热量的 75%, 上部的金属第四管 5接收总热量的 25%, 该比例与水换 热介质的汽化热与过热蒸汽热的比值相当， 即下部的金属外管 3接收的热量 基本满足将内部的液相换热介质转化成饱和蒸汽换热介质， 然后进入金属第 四管 5; 金属第四管 5内部接收总热量的另外一部分热量， 使饱和蒸汽换热 介质进一步过热， 达到所需参数后离开系统， 完成换热。
该实施例结构的金属第四管 5布置于金属外管 3上部， 接收的热量密度 较小， 且管径较小， 更加容易完成内部的换热， 其管壁温度具有更加一致的 温差， 进一步降低管壁翘曲温度； 而且该第三实施例中， 即使出现太阳能集 热器轴向上的一定长度区域内的某个局部受热不均或者无受热情况（例如云 朵遮蔽太阳光入射镜场的情况）， 因金属外管 3与金属第四管 5并行布置， 金属外管 3与金属第四管 5对应的接收太阳光线的比值仍然相当，依然能良 好地处理饱和换热介质和过热换热介质的质量比例关系，避免常规系统因某 个局部受热不均， 造成换热介质相变过程难以控制， 引发系统运行不稳定等 不良情况。 进一步优选地， 金属第四管 5和金属外管 3可以通过焊接等方式 相互上下固定， 即使管道有翘曲也不会破坏系统的结构及外形尺寸的稳定 性。
图 5-4是第五实施例的太阳能集热器第四管结构示意图；如图 5-4所示， 为了获得管壁更均勾的管壁温度差，在金属第四管 5的内部设置螺旋导流装 置， 例如螺旋旋转翅片 12 ; 如此气相换热介质在流经过热区的过程中， 在螺 旋旋转翅片 12 的作用下， 螺旋前进， 降低过热区圓周壁面温度差， 进一步 降低管路的翘曲程度。
实际的运行过程中，传热区的液相传热介质可能会出现因受热突然加剧 等情况， 造成传热介质内部产生部分的蒸汽， 因此， 优选地， 传热区上部具 有排气区， 存放和排除传热介质产生的气体； 优选地， 排气装置位于高端， 通过整体倾斜， 例如与水平面成 2° 布置； 进一步地， 排气区特定位置布置 排气装置， 例如排气阀， 将传热介质受热不稳定产生的气相传热介质排出。
毋庸置疑地， 该太阳能集热器同样可以应用于太阳能光热领域的塔式系 统当中， 该太阳能集热器阵列布置于塔式光热中央接收塔上， 接收镜场会聚 的太阳光，通过换热介质内部的汽化相变后的过热蒸汽将太阳光热带离集热 系统。
显而易见， 在不偏离本发明的真实精神和范围的前提下， 在此描述的本 发明可以有许多变化。因此，所有对于本领域技术人员来说可以预见的改变， 都应包括在本权利要求书所涵盖的范围之内。本发明所要求保护的范围由所 述的权利要求书进行限定。

Claims

权 利 要 求 书
1、 一种太阳能集热器， 包括传热区和换热区， 其特征在于， 所述传热 区位于太阳光线会聚位置， 换热区被传热区包围； 传热区内部布置有流动的 传热介质 ( 7 ); 换热区内部布置有流动通过的换热介质 (6)；所述传热区内 的传热介质 (7) 沸点高于换热介质 (6) 的输出温度；太阳光能量通过所述 传热区及内部的传热介质 ( 7 )对流动通过换热区内的换热介质 ( 6 )传递热 量； 所述换热介质 （6)吸收热量后， 流出太阳能集热器完成换热。
2、 根据权利要求 1 所述的一种太阳能集热器， 其特征在于， 所述换热 介质 (6)在换热区内发生相变换热。
3、 根据权利要求 1 所述的一种太阳能集热器， 其特征在于， 所述传热 介质 （7) 的一部分或全部在传热区内进行通过性流动。
4、 根据权利要求 1 所述的一种太阳能集热器， 其特征在于， 所述传热 介质 ( 7 )在传热区内进行循环流动。
5、 根据权利要求 1 所述的一种太阳能集热器， 其特征在于， 所述太阳 能集热器包括金属外管 （3)、 金属中管 （4); 所述金属外管 （3) 与金属中 管（4)之间所形成的空间为传热区； 金属中管（4) 内部全部或部分空间为 换热区。
6、 根据权利要求 5所述的一种太阳能集热器， 其特征在于， 所述金属 外管（3) 内部还包括金属内管（2); 所述传热介质 (7)的流动路径通过金 属内管 （2)。
7、 根据权利要求 5或 6所述的一种太阳能集热器， 其特征在于， 所述 换热区由一根或多根的金属中管 （4) 的全部或部分内部空间组成。
8、 根据权利要求 6所述的一种太阳能集热器， 其特征在于， 所述金属 内管 （2)、 金属中管 （4)平行布置于金属外管 （3) 内部。
9、 根据权利要求 6所述的一种太阳能集热器， 其特征在于， 所述金属 中管 （4)、 金属内管 （2)互套布置于金属外管 （3) 内部。
10、 根据权利要求 8所述的一种太阳能集热器， 其特征在于， 所述金属 中管（4) 内壁与金属内管（2)外壁之间所形成的空间为换热区， 金属外管
(3) 内的其它空间为传热区。
11、 根据权利要求 8所述的一种太阳能集热器， 其特征在于， 所述金属 内管 （2)和 /或金属中管 （4) 的某个部分设置有介质通道； 所述传热介质
(7)与换热介质 (6)为同一种介质， 在传热区完成传热流动后， 部分或全 部进入换热区完成换热。
12、 根据权利要求 5或 6所述的一种太阳能集热器， 其特征在于， 所述 金属内管 （2 )或金属中管 （4 )为螺旋波纹管或螺旋波纹节管。
1 3、 根据权利要求 1所述的一种太阳能集热器， 其特征在于， 所述传热 区布置有稳压装置。
14、 根据权利要求 1或 2所述的一种太阳能集热器， 其特征在于， 所述 太阳能集热器还包括过热区，接收换热区输出的气相或汽液混合相的换热介 质 （6 )。
15、 根据权利要求 1或 14所述的一种太阳能集热器， 其特征在于， 所 述过热区或传热区内布置螺旋导流装置。
16、 根据权利要求 14所述的一种太阳能集热器， 其特征在于， 所述过 热区为沿金属外管（3 )轴线长度方向上延伸布置的金属第四管（5 )管内空 间。
17、 根据权利要求 14所述的一种太阳能集热器， 其特征在于， 所述过 热区为与外管并列布置的独立金属第四管 （5 ) 内部空间。
18、 根据权利要求 1所述的一种太阳能集热器， 其特征在于， 所述换热 介质入口布置单向阀。
19、 根据权利要求 1所述的一种太阳能集热器， 其特征在于， 所述传热 区具有排气装置。
20、 根据权利要求 1所述的一种太阳能集热器， 其特征在于， 所述传热 区倾斜布置， 传热区的高端位置布置排气装置。
21、 根据权利要求 1所述的一种太阳能集热器， 其特征在于， 所述传热 介质 （7 )为加压水、 导热油、 导热姆或熔盐。
22、 根据权利要求 1所述的一种太阳能集热器， 其特征在于， 所述换热 介质 ( 6 )为在低于传热区内的传热介质 ( 7 )沸点的温度范围内具有气液两 相变化的物质。
23、 根据权利要求 22所述的一种太阳能集热器， 其特征在于， 所述换 热介质 ( 6 )为水、 酮类、 醚类、 醇类及液相或低沸点金属热管介质。
PCT/CN2012/084464 2011-11-14 2012-11-12 一种太阳能集热器 WO2013071848A1 (zh)

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CN106839465B (zh) * 2017-01-23 2019-03-19 东南大学 纳米流体直接吸收式太阳能蒸汽发生装置及方法
CN109029032A (zh) * 2018-08-07 2018-12-18 黎琼珍 一种安全高效平行热交换器及其应用

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