WO2012171436A1 - 一种固体储热装置 - Google Patents

一种固体储热装置 Download PDF

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Publication number
WO2012171436A1
WO2012171436A1 PCT/CN2012/076420 CN2012076420W WO2012171436A1 WO 2012171436 A1 WO2012171436 A1 WO 2012171436A1 CN 2012076420 W CN2012076420 W CN 2012076420W WO 2012171436 A1 WO2012171436 A1 WO 2012171436A1
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WO
WIPO (PCT)
Prior art keywords
heat storage
heat
solid
solid heat
storage device
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Application number
PCT/CN2012/076420
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English (en)
French (fr)
Inventor
刘阳
Original Assignee
北京兆阳能源技术有限公司
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Publication of WO2012171436A1 publication Critical patent/WO2012171436A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
    • C09K5/08—Materials not undergoing a change of physical state when used
    • C09K5/14—Solid materials, e.g. powdery or granular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S60/00—Arrangements for storing heat collected by solar heat collectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F28D20/0039—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material with stratification of the heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0082—Multiple tanks arrangements, e.g. adjacent tanks, tank in tank
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • 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
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage
    • 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
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P20/00—Technologies relating to chemical industry
    • Y02P20/10—Process efficiency

Definitions

  • the invention relates to a solid heat storage device, in particular to a heat storage device in a solar thermal utilization system. Background technique
  • Solar energy is an ideal clean energy source, but there are timeliness problems in use.
  • the energy received during the sunshine period exceeds the demand, but it does not work after sunset. Therefore, how to store the excess energy in the sunshine for use in the continuous operation of the system after sunset, that is, to make up for the shortage, has become a key issue for the continuous operation of the solar thermal utilization device.
  • phase change material formed phase change material
  • a specific material as a matrix for storing heat
  • phase change material occurs during heat storage.
  • Phase change due to volume changes, is prone to leakage.
  • industrial use of ternary aluminum alloys is also used as a phase change storage material. Multiple cycles of use have a negative effect on heat storage properties, such as phase change heat storage temperature, life and other parameters, because the heat storage material itself is in the working process. Repeated solid-liquid phase changes, impurity elements will affect its performance and service life.
  • the existing industrial solar thermal power generators mostly use inorganic salts as heat storage materials, but the inorganic salts have the disadvantages of supercooling and phase separation in the phase transformation process, affecting the heat storage capacity, and the solidification temperature is too high.
  • the heat loss of the external pipeline insulation cycle caused by nighttime to ensure its non-solidification is large. Once the system has a freezing point, it is difficult to dispose of it.
  • Solid heat storage schemes include concrete, cobblestone heat storage, etc., the heat exchange pipeline is poured inside the concrete, the cost is high, and the heat transfer coefficient is very low, etc.; sand and stone heat storage, although cheap, but low thermal conductivity, heat transfer Difficult, unable to shape self-support, affecting the use; and the existing solid heat storage scheme is to arrange the heat exchange pipe inside the solid heat storage material, and complete the heat transfer through the heat conduction between the solid surface of the pipe or the fin surface and the surface of the heat storage material Because the contact between the solids is mostly incomplete contact, and the solid heat storage material itself has poor thermal conductivity, and the heat transfer area between the solids is limited, the overall heat conduction efficiency is low, and it is difficult to meet the input power requirement for storing heat. Further, before the heat of the heat transfer medium is completely released from the solid heat storage system, it has flowed out of the solid heat storage system, and the function of storing heat to the solid heat storage system cannot be satisfactorily completed according to the required power.
  • the object of the present invention is to overcome the above problems existing in the prior art, and to provide a solid heat storage using the interface of the solid heat storage medium itself as a heat exchange interface, and directly adopting the heat transfer medium to directly contact the surface of the heat storage medium to complete the interface heat exchange.
  • the method has the advantages of large heat transfer interface area and high heat exchange efficiency; solid heat storage medium is arranged at intervals, and the length direction is reduced (or axis)
  • the heat transfer speed on the) forms an oblique temperature layer layout structure to obtain high-grade temperature output.
  • the overall cost is low, the heat exchange is fast, the heat capacity is large, and the heat storage performance is good.
  • the solid heat storage device can be applied to multi-domain heat storage. .
  • Embodiments of the present invention provide a solid heat storage device comprising at least one heat storage unit connected in series and/or in parallel; the heat storage unit includes a casing, a solid heat storage medium disposed inside the casing, and The outer insulating layer; the outer surface of the solid heat storage medium is a heat exchange interface, and the heat exchange is directly contacted with the heat transfer medium: the heat storage medium inside the heat storage unit is arranged as an oblique temperature layer layout structure along the axial direction of the length .
  • the heat storage units are arranged horizontally, horizontally or at an oblique angle.
  • the heat storage unit comprises a plurality of heat storage zones connected in series, and the whole has a large aspect ratio or an aspect ratio (for example, 10:1 or more to 500:1), and the solid heat storage medium is in the longitudinal direction.
  • the upper (ie axially) heat transfer rate is small, forming a stable natural oblique layer structure.
  • the heat storage unit includes a plurality of heat insulation layers disposed between the heat storage regions connected in series, further reducing heat exchange between different heat storage regions to form a more excellent oblique temperature layer structure.
  • the heat insulation of the heat storage unit is designed as a gap between the heat storage mediums of adjacent heat storage areas.
  • the heat insulation of the heat storage unit is designed as a heat insulating material disposed adjacent to the heat storage interval.
  • the heat insulating material simultaneously has the effect of guiding the heat transfer medium.
  • the material constituting the solid heat storage medium is one or a mixture of at least two of refractory brick, rock, ceramic, glass, graphite, coal, earthy graphite, metal, ore, slag and concrete.
  • the material of the solid heat storage medium is a refractory material of carbon brick and composite carbon brick, which has good heat conduction, large specific heat capacity, low porosity, high density, stable property, wide source of materials, low cost, and special Suitable as a heat storage medium, such as a magnesia carbon brick, an aluminum carbon brick, or the like.
  • the structure of the solid heat storage medium is a solid heat storage block having different sizes and shapes, such as a rectangular block, a cylindrical tube block, and a sector column.
  • the solid heat storage block is formed by casting a solid heat storage medium material or a mixture thereof with molten metal and cold solidifying into a whole.
  • the outer surface of the solid heat storage block has a sealing layer to reduce the penetration of the heat transfer medium into the interior of the solid heat storage block.
  • the filler constituting the solid heat storage block is internally provided with a heat conductive reinforcing material such as a wire, a metal sheet, a graphite, a metal slag or the like to improve the heat conductivity inside the material.
  • the surface of the solid heat storage block has a flow guiding groove and/or a fin as a heat exchange interface to obtain a large heat exchange area.
  • the plurality of solid heat storage block surfaces have mutually intersecting heat exchange channels and/or fins, and each other There is a certain angle between them, so that the heat exchange medium forms a cross-mixing point on the flow path to enhance the heat exchange effect.
  • the solid heat storage medium structure is a solid heat storage block, which is dense in material, has a void ratio of less than 10%, and has less absorption to the heat transfer medium.
  • the solid heat storage block comprises a closed outer casing and a solid heat storage medium material filled inside the closed outer casing, and has a fixed shape and a self-supporting capacity as a whole.
  • the closed casing is a glass or ceramic material such as a glass tube, a ceramic tube, a glass, a ceramic hollow sphere or the like.
  • the closed casing is a metal material such as a metal pipe, a metal hollow ball, a metal shell or the like.
  • the metal-enclosed outer casing material is made of stainless steel.
  • the inside of the closed casing is completely or partially filled with a phase change heat storage phase change material within a certain temperature range.
  • the heat storage unit is arranged in an upright arrangement or in a horizontal arrangement, the high temperature region is located at a high end position of the heat storage unit, and the low temperature region is located at a low end position of the heat storage unit to avoid a uniform temperature trend caused by convection; the heat storage unit is at a length axis Forming a slanting layer upward; and the heat storage unit performs heat storage input or heat exchange output grading control in a specific heat storage area to obtain a maximum heat input and a highest grade heat output.
  • the heat storage unit performs multi-layer hierarchical control of different temperature levels to utilize the input or output heat most efficiently.
  • the heat transfer medium is gas, liquid, vapor or phase change medium; such as air, nitrogen, inert gas, heat transfer oil, molten salt, steam, and vapor-liquid phase change medium.
  • the heat insulating layer is disposed outside the outer casing, and is selected to be a material having a low thermal conductivity, such as an insulating rock wool or the like. Further, the outer casing is insulated by vacuum insulation technology.
  • the outer casing of the heat storage unit is a relatively thin-walled metal pipe (the thickness of the material is selected to be 30% or more thinner than the standard design thickness required for the corresponding use pressure), and the outer reinforcing flange is used to enhance the resistance.
  • the pressure capability is to reduce the good thermal conductivity existing in the axial direction due to the thicker outer casing, and to avoid the temperature gradient effect of the structure of the oblique layer due to the heat transfer of the outer casing.
  • the heat insulating layer disposed in close contact between the reinforcing flange and the outer wall of the outer casing further increases the thermal resistance in the outer casing structure.
  • the solid heat storage device of the embodiment of the invention can be applied to a solar thermal utilization system.
  • the solid heat storage medium of the embodiment of the invention has no fluidity, the heat storage uses the solid state to store heat, and the operation is safe; the solid heat storage medium is piled up according to a certain rule, and some or all of the surface directly contacts the heat transfer medium for heat exchange, and does not need to be increased.
  • the pipeline transition avoids the heat transfer defects of the solid-contact interface, has a large heat exchange interface area and good heat exchange between solid-liquid or solid-vapor contact, and can easily complete the input or output of heat at a high speed, and greatly enhance the heat storage of the solid.
  • Heat transfer between the medium and the heat transfer medium The speed (ie heat transfer power) makes the heat storage device have good overall heat transfer performance.
  • the solid heat storage block has a dense material or surface closure layer design or a closed layer outer casing design that allows less absorption of the heat transfer medium, lower cost, and longer material life.
  • the heat storage medium inside the heat storage unit has high thermal conductivity, fast heat transfer in the radial or width direction, high power absorption and heat release, and can store and extract heat as close as possible to the original temperature grade; In the direction of the length or length, due to the large size or the heat insulation design, the heat transfer rate is slow, and a certain temperature gradient can be maintained for a long time, which is beneficial to avoid avoiding the high grade (temperature) heat source due to the uniform temperature trend in the high and low temperature regions ( The temperature is lowered to ensure the heat output quality; at the same time, the diversion design guides the regular flow path of the heat transfer medium inside the heat storage unit, which is more conducive to the good heat transfer effect of the heat transfer medium;
  • the heat storage input grading control and heat exchange output grading control are implemented, and the heat storage input and heat exchange output control of different temperature levels can also be implemented, which can greatly improve the higher quality of the stored and exchanged heat.
  • the unit combination structure can be flexibly configured according to needs, which is convenient, reliable and low in cost.
  • the solid heat storage device has low overall cost, good heat conduction and large heat capacity, and can be applied to various heat storage applications, especially a solar thermal utilization system.
  • FIG. 1 is a schematic view showing the overall structure of an embodiment of a solid heat storage device of the present invention
  • Figure 2 is a hierarchical control unit of the heat storage unit
  • Figure 3 is a heat transfer control and heat exchange control unit of different temperature levels of the heat storage unit
  • FIG. 4 is a schematic structural view of a first heat storage unit
  • Figure 5 is a schematic view showing the structure of a solid heat storage block
  • FIG. 6 is a schematic structural view of a second heat storage unit
  • Figure 7 is a schematic structural view of a heat storage tube
  • FIG. 8 is a schematic view showing the overall structure of a third heat storage unit embodiment
  • FIG. 9 is a schematic structural view of a solid heat storage block inside the heat storage unit of FIG. 8;
  • Figure 10 is a schematic structural view of another embodiment of a solid heat storage block
  • FIG. 11 is a schematic structural view of an embodiment of a casing of a heat storage unit; detailed description
  • the solid heat storage device is composed of an array of a plurality of heat storage units, such as a heat storage unit 101 and a heat storage unit 103; each heat storage unit of the array stands vertically Ground arrangement; each heat storage unit comprises a casing 12, a solid heat storage medium 13 disposed inside the casing 12, and an insulation layer 10 disposed outside the casing 12.
  • the outer surface of the solid heat storage medium 13 is a heat exchange interface of the heat transfer medium, and the solid heat storage medium 13 is a dense material, and the void ratio is less than 10%: optimally, the surface of the solid heat storage medium 13 has a closed layer to further reduce heat transfer. Infiltration of the medium.
  • the outer casing 12 of the solid heat storage device is preferably a steel material having a certain thickness, and has the ability to withstand a pressure of, for example, 2 Mpa required for the heat transfer medium; the outer heat insulating layer 10 is selected from materials such as rock wool having a low thermal conductivity, and is coated. It can be insulated using vacuum technology to minimize the loss of heat from the solid heat unit.
  • a circulating pipe interface is arranged outside the solid heat storage device, and a plurality of heat storage units are arranged in a series-parallel array, and the circulating pipes are connected in series, in parallel, and finally concentrated in the total circulating pipe.
  • the heat transfer medium After the heat transfer medium receives heat from the heat source 18, such as a solar mirror field, a portion flows directly through the heat exchange device or the work device 19 in the flow direction A, such as a heat exchanger or a steam turbine, and the excess heat transfer medium portion flows along the direction B.
  • the heat exchange device or the work device 19 such as a heat exchanger or a steam turbine
  • the heat medium stores heat in the B direction
  • the heat storage medium in the tank body has a high temperature at a high end position upstream of the heat exchange medium, and a low temperature downstream.
  • the end position is a low temperature; further, when the structure is heated, the low temperature heat exchange medium takes heat in the opposite direction of the B direction (ie, takes heat in the direction of D), thus maintaining and storing the heat during the heat extraction process.
  • the uniform temperature distribution in the middle phase presents a high temperature at the high end position, a low temperature at the low end position, and a temperature gradient in the middle position that gradually changes along the high and low temperatures (when the solid heat storage device is not strictly vertical, the high temperature is also obtained.
  • the inlet end is high temperature, and the low temperature outlet end is a low temperature gradient distribution); thus, the heat storage medium inside the heat storage unit can be arranged along the length axial direction to form an oblique temperature layer layout structure.
  • the heat transfer medium can be a gas, liquid, vapor or other phase change medium.
  • the solid heat storage device can be used in any field of heat utilization, and is particularly suitable for a large-scale high-grade solar heat utilization heat storage system.
  • the heat storage unit can be controlled in layers. 2 is a layered control unit of the heat storage unit; as shown in FIG. 2, the heat storage unit is composed of a plurality of different heat storage area arrays, and the specific heat storage area performs different layered control, such as a heat storage input circulation system.
  • the layered heat transfer control unit comprising the heat storage areas 201, 202 and 203: the heat exchange output circulation system comprises heat storage areas 207, 208 and 209 forming a layered heat exchange output control unit, and the heat storage area in each control unit Equipped with a control width, for example, the control area corresponding to the heat storage area 201 is broadly A, and the control area corresponding to the heat storage area 209 is 1.
  • the heat transfer medium transfers heat to the heat storage medium from the top of the heat storage device, that is, the heat storage space 209, and the temperature gradually decreases, and finally flows out of the heat storage device to be reheated. Since the heat storage medium has good heat conduction, the heat storage medium of the heat storage area 209 quickly reaches a temperature close to the heat transfer medium; in the subsequent heat exchange process, the heat transfer medium flows through the heat storage area 209, basically There is no exothermic cooling, the original high temperature is kept flowing to the heat storage zone 208 part, and the heat storage zone 208 is partially cooled and then cooled down, and continues to descend.
  • the heat storage medium transfers heat to the heat storage medium from the top of the heat storage device, that is, the heat storage space 209, and the temperature gradually decreases, and finally flows out of the heat storage device to be reheated. Since the heat storage medium has good heat conduction, the heat storage medium of the heat storage area 209 quickly reaches a temperature close to the heat transfer medium; in the subsequent heat exchange process, the heat
  • the heat storage input is layered and controlled: First, the control valve C is opened in the stratified heat storage input control unit, and the control valve is opened.
  • the heat exchange medium heats up from the bottom of the solid heat storage unit, that is, the heat storage area 201, and the heat is outputted to the heat storage device, and the temperature gradually rises, and finally flows out of the heat storage device to enter
  • the external system is cooled and recirculated. Since the heat storage medium has good heat conduction, the heat storage medium of the heat exchange medium passing through the heat storage area 201 quickly reaches a slightly lower temperature of the heat storage medium; in the subsequent heat exchange process, the heat transfer medium flows through the heat storage area 201.
  • the heat exchange medium After the heat exchange medium passes through the heat exchange, the temperature of the heat storage device is high.
  • the heat storage input is layered and controlled: the heat exchange medium starts to heat exchange after passing through the stratified heat transfer output control unit.
  • Layer control at this time, the stratified heat transfer output control unit controls the pottery G to open, the control valves H and I are closed, and the heat output of the heat exchange is passed through an external work device such as a heat exchanger or a steam turbine, and after cooling, the cooling is returned.
  • the heat storage unit 3 is a heat transfer control and heat exchange control unit of different temperature levels of the heat storage unit; the heat storage input system and the heat exchange output system of the heat storage unit of the embodiment respectively implement heat storage input control and heat exchange output of different temperature levels. control.
  • the heat storage input control or heat exchange output control design separate inlets or outlets or share an inlet and outlet at the same or close position.
  • the heat storage unit is composed of a plurality of temperature-class heat storage areas, specifically composed of a high-temperature heat storage zone I, a medium-temperature heat storage zone II, and a low-temperature heat storage zone III, and a plurality of heat storage zones with different temperature gradients.
  • the heat storage unit is integrally formed in series; in order to describe the heat storage input and the heat exchange output operation mode control in the heat storage device, the following description mainly describes the high temperature heat storage zone I and the medium temperature heat storage zone II, and the corresponding heat transfer medium Or the heat exchange medium is at a high temperature level I and a medium temperature level II, respectively, and the heat storage input control and the heat exchange output control have the same control width, and the same control valve is an input control valve or an output control valve at different times.
  • the heat transfer medium of high temperature class I (for example, temperature 550 ° C) is selected from the inlet of the heat transfer input line at the position of the slightly lower temperature heat storage zone closest to the I temperature level, for example, from the control width a input, preferentially store the heat carried by it as high temperature as possible, then continue to store the lower temperature of the lower heat storage space layer, and so on, until the lowest temperature point is reached, from the nearest
  • the heat storage unit carries in another heat transfer medium of temperature class II (for example, temperature 35CTC), and the heat transfer medium selects heat transfer from the position of the slightly lower temperature heat storage zone closest to the II temperature class.
  • the heat transfer medium of the high temperature class I is selected to flow out from the heat exchanger line outlet of the slightly higher temperature heat storage zone closest to the I temperature level, for example, from the control valve b, (high temperature At 435 ° C, applied to steam turbine power generation, it is preferred to use the heat energy of the lowest possible temperature state for preheating.
  • the temperature of the heat storage zone cannot meet the output temperature condition, continue to extract higher temperature from the upper heat storage zone.
  • the heat for example, flows out from the control valve a, and so on, until the desired temperature is reached; at the same time, the heat storage unit performs the heat exchange of the intermediate temperature class II of the other path, and the heat transfer heat transfer medium is also selected from the closest
  • the outlet of the heat exchange line at the location of the slightly high temperature heat storage zone of the medium temperature class flows out from the control wide e (temperature is about 200 ° C, applied to industrial steam), and the heat energy of the lowest possible temperature state is preferentially used.
  • the heat exchanger I, II medium temperature grades passing The heat exchange tubes may be partially coincident or independent. This method can enable the heat storage device to simultaneously provide heat output of various grades in an optimal manner, has a wider application range, and is more economical and practical.
  • FIG. 4 is a schematic structural view of a first heat storage unit; the solid heat storage area inside the heat storage unit 1 is cylindrical, and a plurality of heat storage areas, for example, 41 or 43 are connected in series to form a heat storage unit of the heat storage unit, and each storage
  • a heat insulating layer 45 is disposed between the inside of the hot zone and the heat storage zone, and the heat insulating layer is a heat insulating layer having a low thermal conductivity.
  • the heat storage zone comprises an array of solid heat storage blocks 46 and a number of solid heat storage blocks 46 spaced apart from each other; the solid heat storage blocks 46 are regularly arranged, arranged in an annular array as shown, each solid heat storage block 46 The gap between them is the flow passage of the heat transfer medium, and the heat insulation layer 45 separates the heat storage regions to form a significant temperature gradient on different regions of the solid heat storage unit 1, which satisfactorily ensures the storage inside the heat storage unit and
  • the output heat is of high grade
  • the heat insulation layer 45 has the function of the heat transfer medium drainage layer, and the heat transfer medium passes through the gap between the solid heat storage blocks 46 arranged in the array, under the guidance of the heat insulation layer 45, regularly Complete heat transfer, for example, the heat insulation layer 45 first drains the heat transfer medium from the middle of the heat storage zone to the edge of the heat storage zone of the next layer, and then to the middle of the lower heat storage zone, so that The heat medium transfers heat with the largest contact surface and the solid heat storage medium.
  • the heat insulating layer 45 has a pressure bearing capability to further increase the structural strength of the heat storage unit 1.
  • the solid heat storage medium is made of a high density, high specific heat capacity material, such as a mixture of refractory brick, rock, ceramic, glass, graphite, metal, concrete or magnesia carbon brick, or a mixture of at least two; solid heat storage medium structure
  • the fan-shaped solid heat storage block 46 of the array, and the solid heat storage block is dense overall, having a small porosity, for example, the porosity is less than 10% of the volume; preferably, the surface of the solid heat storage block 46 is provided with a sealing layer, further The immersion absorption and destruction of the solid heat storage block 46 by the long-term operation of the heat transfer medium is reduced.
  • the sealing layer is a ceramic glaze, a glass glaze, a metal layer, a graphite layer or the like; the exterior of the solid heat storage unit has an insulating material, or is insulated with a vacuum technique.
  • Figure 5 is a schematic view showing the structure of a solid heat storage block.
  • the solid heat storage block 56 has self-supporting strength, and casts a small-sized solid heat storage medium material or a mixture thereof by molten metal, and condenses and solidifies into a whole: the solid heat storage block 56 includes various shapes. Or the material of the size, the metal layer 520 is optimally arranged between the materials, and the heat storage blocks of the plurality of materials are bonded together by the molten metal, and the solid heat storage block 56 is formed by condensation and solidification, and the desired size can be obtained by using the method.
  • the filler material constituting the solid heat storage medium is mixed with a heat conductive reinforcing material such as a wire, a metal sheet, a graphite, a metal slag or the like to improve the heat conductivity inside the material.
  • a heat conductive reinforcing material such as a wire, a metal sheet, a graphite, a metal slag or the like to improve the heat conductivity inside the material.
  • the heat storage medium itself is characterized by compactness, stability, high thermal conductivity, large specific heat capacity, and high strength. It can be directly used to form heat storage blocks, such as some metals, graphite, and refractory bricks (such as carbon bricks). , magnesia carbon bricks, aluminum magnesia carbon bricks, etc.), glass, ceramics, etc.
  • FIG. 6 is a schematic view showing the structure of a second heat storage unit. As shown in FIG.
  • the heat storage unit 1 includes a plurality of heat storage regions connected in series, such as a heat storage region 61 and a heat storage region 63, and a heat insulation layer is disposed between each heat storage region;
  • the heat storage region 61 includes a plurality of a regularly arranged solid heat storage block
  • the solid heat storage block is a cylindrical pipe block
  • the outer part is a sealed outer casing
  • a granular solid heat storage medium material is arranged inside to form a solid heat storage block having a fixed shape and a self-supporting capability
  • the sealed outer casing is made of a metal material, such as a metal box, a metal tube, a metal hollow ball or a metal shell
  • the 6 is a heat storage tube 68, and the heat storage tube 68 is sealed at both ends; the heat storage tube 68 is a straight tube.
  • the height is consistent with the axial length of the heat storage area 61.
  • the plurality of heat storage tubes 68 are closely arranged in the heat storage area 61, and the heat storage tubes are closely arranged, and the gap between them is a passage of the heat transfer medium.
  • the heat storage tube 78 includes a sealed outer casing 79 and a solid heat storage medium material filled in the sealed outer casing 79; the solid heat storage medium material is densely packed inside the sealed outer casing 79; Further improving the thermal conductivity of the solid heat storage medium material in the radial direction inside the sealed outer casing 79, it is preferable to arrange the metal fins at intervals in the sealed outer casing 79.
  • the support tube in the heat storage tube 78 may be a metal tube, a glass tube or a bellows; the material of the solid heat storage medium material is calcined magnesia, yellow sand, coal or graphite, preferably coal, and the bulk density of coal is 2400 kg/m3, specific heat capacity.
  • the heat storage unit 1 has a certain inclination angle, and the whole is linear, and is inclined at a small angle to the ground (the small angle can also be zero, That is, it is arranged to be completely horizontally arranged), the heat storage unit comprises a casing, a solid heat storage medium disposed inside the casing, and an insulation layer outside the casing; the heat storage unit is internally composed of a plurality of interconnected heat storage zones such as a heat storage zone 81 and a storage
  • the hot zone 83 is composed of heat insulation design structures arranged between the heat storage zones, the heat insulation design structure is a gap 85 between adjacent heat storage zones, and in another case, the heat insulation design can also be adjacent heat storage.
  • the solid heat storage medium comprises a stack of solid heat storage blocks 86 (for example, refractory magnesia carbon bricks) of a dense structure, and the outer surface of the solid heat storage block 86 is a heat exchange interface of the heat transfer medium, each solid
  • the surface of the heat storage block 86 has a certain shape of the groove, and the blocks are closely packed with each other to form a flow guiding groove; each solid heat storage medium has good compactness, and has a small void ratio, preferably less than 10%.
  • the surface of each solid heat storage medium further optimized has a sealing layer to further reduce the penetration phenomenon of the heat transfer medium due to the void ratio.
  • the heat storage unit is generally slender, for example, 600 m, and has a large dimension in the axial direction. At the same time, due to the axial heat insulation design, the axial heat transfer speed is low, and a good oblique layer structure layout can be easily obtained.
  • the storage, input and output of the grade heat source; the high end of the position is the heat storage input end of the high temperature heat transfer medium and the heat exchange output end, and the low end of the position is the output end of the low temperature heat transfer medium to complete the heat storage and the heat exchange input port.
  • a plurality of such heat storage unit arrays are arranged in an overall horizontal arrangement to form a solid arrangement of the solid heat storage device as a whole.
  • FIG. 9 is a schematic structural view of a solid heat storage block inside the heat storage unit of FIG. 8.
  • the surface of the single solid heat storage block 96 is provided with a flow guiding groove for guiding the heat transfer medium, and the heat conducting groove is formed on the back of the solid heat storage block 96 which is closely arranged adjacent thereto.
  • the solid heat storage block 96 of the tightly structured flow guiding channel dense structure is closely arranged; the heat conducting channel has obvious advantages over the conventional metal heat conducting pipe, and the surface of the solid heat storage block 96 can be arranged with a plurality of heat conducting channels, which can be obtained small.
  • the cross-sectional area and large heat exchange surface area, and reduce the manufacturing cost of the metal heat-conducting pipeline, and the heat-exchange medium can directly contact the solid heat storage medium, has high heat exchange efficiency, and has a good heat transfer coefficient as a whole.
  • the large heat exchange surface has a large heat exchange power;
  • the solid heat storage block 96 is preferably a magnesia carbon brick, has a bulk density of 3000 kg/m3, a specific heat capacity of about UKJ/kgK, and has good thermal conductivity, and has a low void ratio. Stable, is an excellent solid heat storage material.
  • the heat storage unit of the above-mentioned solid heat storage block 96 with a flow guiding trough is closely packed.
  • the heat storage unit has an axial length of 200 m and a diameter of 1.5 m, and is horizontally arranged on the ground, and is integrally formed into a horizontal solid heat storage device, and the outer casing is The outer diameter is 1560 mm and the wall thickness is 30 mm.
  • the solid heat storage block 96 is a carbon brick or a magnesia carbon brick.
  • the entire heat storage device is provided with 500 through holes.
  • the adjacent flow guiding grooves are arranged to form a closed cross section.
  • the cross-sectional area is 51.6mm2 and the circumference is 34.2mm .
  • the heat storage device uses its sensible heat.
  • the temperature difference is 150°C, which can store about 40MWh of dynamic heat. It is assumed that the heat transfer medium in each hole is Heat transfer oil, and the intermediate state of the heat transfer oil is 1.5MPa, 29 °C, the input and output temperature difference is 200 °C (from 395 °C to 195 °C), the flow velocity inside the single hole is 0.8m/s, and the input power is greater than 8MWt. After calculation, the heat transfer coefficient in the tube can reach 555W/ m 2 k ; the temperature difference between the fluid in the tube and the tube wall is assumed to be 5K, and the total heat exchange power is about 9.7MWt, which can meet the requirements; Heat and heat transfer performance.
  • the heat transfer medium in each hole is Heat transfer oil
  • the intermediate state of the heat transfer oil is 1.5MPa, 29 °C
  • the input and output temperature difference is 200 °C (from 395 °C to 195 °C)
  • the flow velocity inside the single hole is 0.8m/s
  • the input power is greater than
  • FIG. 10 is a schematic structural view of another embodiment of a solid heat storage block.
  • the surface of the solid heat storage block 106 has oblique parallel grooves, and two solid heat storage blocks 106 arranged to overlap each other are interlaced with flow guiding grooves on the surface.
  • the non-conductive groove portion of the solid heat storage block 106 in contact with the guide groove forms a closed-flow guide groove, and the solid heat storage block 106 in contact with each other contacts the guide grooves to complete the heat transfer medium.
  • the internal turbulent contact again improves the heat transfer coefficient of the heat transfer medium, and the overall heat exchange power is excellent.
  • FIG 11 is a schematic view showing the structure of the outer casing of the heat storage unit; the heat storage unit casing described above needs to be pressurized, for example, 2.5 MPa, and the temperature is for example 400 ° C (the internal heat transfer medium is 2.5 MPa, 395 ° C)
  • the outer casing is designed as a unified conventional pipe, for example, having a diameter of 820 mm and a thickness of 15 mm; and the outer casing 114 is made of a steel material having a good thermal conductivity, and the outer casing 114 receives heat of the fluid, which is thicker due to its own thickness and has a lower thickness.
  • the thermal resistance and good heat transfer performance can quickly transfer the heat received by the inlet to the outlet end of the outer casing 114 along the wall of the casing, and heat the heat transfer medium at the outlet end, thereby increasing the temperature of the low temperature zone of the heat storage unit and destroying the storage.
  • the inclined layer structure of the thermal device design therefore, it is required to reduce the wall thickness of the metal outer casing 114 and reduce the heat storage medium transferred to the low temperature region through the heat storage outer casing 114.
  • the metal outer casing 114 adopts a thin outer casing 114.
  • the thickness is 8 ⁇
  • the outer wall of the metal casing is disposed with an outer reinforcing flange 112 at a certain interval.
  • the reinforcing flange 112 has an inverted " ⁇ "shape; and each reinforcing flange 112 and the metal casing 114
  • the connection arrangement has a low thermal conductivity material of the insulating layer 113, such as an annular pressure calcium silicate board; by a metal housing 114 is disposed to reduce the wall thickness of the insulating layer 113 and The thermal resistance of the heat diffusion to the low temperature region is increased, the stability of the oblique temperature layer is further ensured, and the processing cost of the metal casing 114 is lowered.
  • the solid heat storage medium of the embodiment of the invention has no fluidity, the heat storage uses the solid state to store heat, and the operation is safe; the solid heat storage medium is piled up according to a certain rule, and some or all of the surface directly contacts the heat transfer medium for heat exchange, and does not need to be increased.
  • the pipeline transition has a huge heat exchange interface area and good contact, which can conveniently complete the heat input or output at high speed, and greatly enhance the heat transfer speed between the solid heat storage medium and the heat transfer medium (ie heat transfer power).
  • the heat storage device has good overall heat exchange performance; at the same time, due to the large cross-sectional area of the flow passage, the flow resistance of the heat transfer medium is small, and the pressure drop loss is small, which can reduce the energy consumption of the system operation.
  • the solid heat storage block has a dense material or surface seal layer design or a closed layer shell design that allows less heat transfer to the heat transfer medium, lower cost, and longer material life.
  • the heat storage medium inside the heat storage unit has high thermal conductivity, fast heat transfer in the radial or width direction, high power absorption and heat release, and can store and extract heat as close as possible to the original temperature grade; In the direction of the length or length, due to the large size or the heat insulation design, the heat transfer rate is slow, and a certain temperature gradient can be maintained for a long time, which is beneficial to avoid avoiding the high grade (temperature) heat source due to the uniform temperature trend in the high and low temperature regions ( The temperature is lowered to ensure the heat output quality; at the same time, the diversion design guides the regular flow path of the heat transfer medium inside the heat storage unit, which is more conducive to the good heat transfer effect of the heat transfer medium;
  • the heat storage input grading control and heat exchange output grading control are implemented, and the heat storage input and heat exchange output control of different temperature

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Abstract

一种固体储热装置，由至少一个储热单元（101、103）串联和/或并联组合而成。储热单元（101、103）包括外壳（12）、外壳（12）内部布置的固体储热介质（13）和外壳（12）外部的保温层（10）。固体储热介质（13）的外表面为换热界面。储热单元（101、103）内部规律布置隔热层（45），且沿轴向上具有斜温层。储热单元（101、103）具有分层控制系统，保证热量的高品位储存和输出。阵列的储热单元（101、103）可以垂直、水平或相对水平具有一定倾斜角度地布置。该固体储热装置，利用固体显热性能储热，运行安全，换热效率以及储热性能良好，可应用于太阳能光热利用系统等各种储热场合。

Description

种固体储热装置 技术领域
本发明涉及一种固体储热装置， 特别涉及一种太阳能光热利用系统中的储热装置。 背景技术
太阳能是比较理想的清洁能源， 但利用上却存在时效性问题， 日照期间所接受的能量超 过所需， 日落之后却无法发挥作用。 因而如何把日照时多余的能量储存起来， 以用于日落后 系统的持续运行， 即取有余以补不足， 成为实现太阳能热利用装置连续运行的关键问题。
现有的太阳能储存技术中， 有报道或使用过多种储热介质。 近年有报道在实验室中获得 以特定材料作基体支撑的复合相变材料（定形相变材料）， 用以储存热量， 但其存在导热系数 低的缺点， 而且相变材料在储热过程中发生相变， 由于体积的变化， 容易发生漏露的隐患。 另外， 工业上也有使用三元铝合金用以作为相变储存材料， 多次循环使用对于储热性 能， 例如相变储热的温度、 寿命等参数有负面作用， 因为储热材料本身在工作过程中进行反 复的固液相变， 杂质元素将会影响其使用性能和使用寿命。 目前现有的已经工业化的太阳能 热发电机组多利用无机盐做储热材料， 但无机盐在相变过程中存在过冷和相分离的缺点， 影 响了储热能力， 并且其凝固温度过高， 造成夜间为保证其不凝固而进行的外部管路保温循环 热损失较大， 一旦系统出现凝固点后处置困难， 存在安全隐患： 熔盐系统管路中使用的泵、 陶价格昂贵且使用寿命也比较短， 而且无机盐具有一定毒性， 且容易泄漏发生火灾， 泄漏会 对环境造成的污染。 固体储热方案有混凝土、 鹅卵石储热等， 在混凝土内部浇灌换热管路， 成本较高， 并且换热系数很低等等； 砂石储热， 虽然价格便宜， 但导热率低， 换热困难， 不 能定型自支撑， 影响使用； 且已有固体储热方案是将换热管道布置于固体储热材料内部， 通 过管道或翅片表面和储热材料表面的固体与固体间热传导完成热量传递， 由于固体之间的接 触多为不完全接触， 且固体储热材料本身导热性能不良， 再者固体之间的传热面积有限， 导 致总体导热效率低下， 从而很难满足储存热量的输入功率要求， 更多情况为传热介质的热量 未完全释放于固体储热系统之前， 就已经从固体储热系统流出， 无法按所需功率圆满地完成 向固体储热系统储热的功能。
发明内容
本发明的目的在于克服现有技术中存在的上述问题， 提供一种利用固体储热介质本身的 界面作为换热界面， 采用传热介质与储热介质表面直接接触完成界面换热的固体储热方法， 具有传热界面面积大， 换热效率高的显著优点； 固体储热介质间隔布置， 降低长度方向 (或轴 向)上的热量传递速度， 形成斜温层布局结构， 获得高品位温度输出； 整体成本低廉、 换热快， 热容大， 储热性能好， 可应用于多领域储热的固体储热装置。
本发明实施例提供了一种固体储热装置，所述固体储热装置由至少一个储热单元串联和 /或并联组合而成； 该储热单元包括外壳、 外壳内部布置的固体储热介质及外部的保温层； 以 固体储热介质的外表面为换热界面， 与传热介质直接接触发生换热： 所述储热单元内部储热 介质沿长度轴向方向上设置为斜温层布局结构。
进一步地， 所述储热单元垂直、 水平或具有一定倾斜角度地相对水平布置。
进一步地， 所述储热单元包括多个串联的储热区， 整体具有较大的长径比或长宽比 （如 10:1以上至 500:1 )， 固体储热介质之间在长度方向上 （即轴向上） 热量传递速度较小， 构成 稳定的天然斜温层结构。
进一步地， 所述储热单元包括多个串联的储热区之间设置的隔热层， 进一步减少不同储 热区之间的热交换， 形成更加优良的斜温层结构。
进一步地， 所述储热单元的隔热设计为相邻储热区储热介质之间的空隙。
进一步地， 所述储热单元的隔热设计为相邻储热区间布置的隔热材料。
进一步地， 所述隔热材料同时兼有对传热介质导流布置的作用。
进一步地， 构成所述固体储热介质的材质为耐火砖、 岩石、 陶瓷、 玻璃、 石墨、 煤炭、 土状石墨、 金属、 矿石、 矿渣和混凝土中的一种或至少两种的混合物。
优选地， 所述固体储热介质的材质为炭砖、 复合炭砖类的耐火材料， 由于导热好、 比 热容较大、 孔隙率低、 密度高、 性质稳定、 材料来源广泛、 成本较低， 特别适合优选作为储 热介质， 例如镁炭砖、 铝炭砖等。
进一步地， 所述固体储热介质的结构为具有不同尺寸和形状的固体储热块， 例如长方形 块体、 圆柱管块体、 扇形柱状体。
进一步地， 所述固体储热块采用熔融金属将固体储热介质材料或其混合物浇铸， 冷凝固 化成整体而成。
优选地，所述固体储热块的外表面具有封闭层，减少传热介质向固体储热块内部的渗透。 优选地， 构成所述固体储热块的填充材料内混合布置有导热增强材料， 如金属丝、 金属 片、 石墨、 金属矿渣等， 以提高材料内部的导热能力。
进一步地，所述固体储热块表面具有作为换热界面的导流槽和 /或翅片， 以获得较大的热 交换面积。
进一步地，所述多个固体储热块表面之间具有相互交叉的换热导流槽和 /或翅片，彼此之 间存在一定的角度， 从而使换热介质在流动路径上形成交叉混合点， 以增强换热效果。
进一步地， 所述固体储热介质结构为固体储热块， 其材质致密， 具有小于 10%空隙率， 对传热介质吸收少。
进一步地， 所述固体储热块包括封闭外壳及填充于封闭外壳内部的固体储热介质材料， 整体具有固定形状及自支撑能力。
优选地， 所述封闭外壳为玻璃、 陶瓷材料， 如玻璃管， 陶瓷管， 玻璃、 陶瓷空心球等。 优选地， 所述封闭外壳为金属材料， 如金属管、 金属空心球、 金属壳等。
优选地， 所述金属封闭外壳材料为不锈钢材质。
进一步地， 所述封闭外壳内部全部或部分填充一定温度范围内有相变的储热相变材料。 进一步地，所述储热单元为直立布置或相对水平布置，高温区域位于储热单元高端位置、 低温区域位于储热单元低端位置， 以避免对流造成的均温趋势； 储热单元在长度轴向上形成 斜温层； 且所述储热单元在特定储热区进行储热输入或换热输出分级控制， 以获得最大热量 的输入和最高品位的热量输出。
进一步地， 所述储热单元实施不同温度等级的多层分级控制， 以最高效地利用输入或输 出热量。
进一步地， 所述传热介质为气、 液、 蒸汽或相变介质； 如空气、 氮气、 惰性气体、 导热 油、 熔融盐、 蒸汽以及汽液相变介质等。
进一步地，所述保温层布置于外壳的外部，选择为低导热率的材质，例如保温岩棉等等。 进一步地， 所述外壳采用真空绝热技术进行保温。
进一步地， 所述储热单元的外壳为相对薄壁金属管 （材料的选用厚度相对于对应使用压 力所需的标准设计厚度来说， 减薄 30%以上）， 且通过外部加强法兰增强耐压能力， 以减少由 于较厚外壳在轴向上存在的良好导热性， 避免因外壳传热较多破坏构成斜温层布局结构的温 度梯度效果。
进一步地， 所述加强法兰与外壳外壁间布置紧密接触的隔热层， 进一步增大外壳结构中 的热阻。
本发明实施例的固体储热装置可应用于太阳能光热利用系统。
本发明实施例的固体储热介质不具有流动性， 储热利用固体状态储热， 运行安全； 固体 储热介质按一定规律堆砌， 部分或全部表面直接与传热介质接触换热， 不需要增加管路过渡 从而避免了固固接触界面的传热缺陷， 具有巨大的换热界面面积并且固液或固汽接触换热良 好， 可方便高速的完成热量的输入或输出， 大量增强了固体储热介质与传热介质之间的传热 速度 （即传热功率）， 使储热装置具有良好的整体换热性能;同时， 由于流通截面积大， 传热 介质流动阻力小， 压降损失小， 可降低系统运行能耗。 固体储热块具有的致密材质或表面封 闭层设计或封闭层外壳设计使其对热传介质吸收较少， 成本低， 并且材料寿命更长。 储热单 元内部的储热介质导热率较高， 在径向或宽度方向传热较快， 可高功率吸热和放热， 能尽量 以最接近原温度品位的方式储存和提取热量； 在轴向或长度方向上， 由于尺寸大或存在隔热 设计， 传热速度较慢， 可长期保持一定的温度梯度， 有利于尽量避免高品位 （温度） 热源由 于高低温区域的均温趋势造成品位 （温度） 下降， 保证热量输出品质； 同时导流设计引导传 热介质在储热单元内部的规律流径， 更有利于传热介质的良好换热效果； 储热单元的一定储 热区之间分别实施储热输入分级控制和换热输出分级控制， 且还可以实施不同温度等级的储 热输入和换热输出控制， 可以大大提高储入和换出热量的更加高品位。
单元组合式结构可根据需要灵活配置， 方便可靠成本低。 该固体储热装置总体成本低、 导热好、 热容大， 可应用于各种储热应用， 特别是太阳能光热利用系统。
附图说明
下面参照附图对本发明的具体实施方案进行详细的说明， 附图中：
图 1是本发明固体储热装置实施例整体结构示意图；
图 2是储热单元的分层控制单元；
图 3是储热单元的不同温度等级的传热控制和换热控制单元；
图 4是第一种储热单元结构示意图；
图 5是固体储热块结构示意图；
图 6是第二种储热单元结构示意图；
图 7是储热管结构示意图；
图 8是第三种储热单元实施例整体结构示意图；
图 9是图 8储热单元内部的固体储热块结构示意图；
图 10是固体储热块的另一实施例结构示意图；
图 11是储热单元的外壳实施例结构示意图；。 具体实施方式
下面结合实施例对本发明进行进一步的详细说明。
图 1是本发明固体储热装置实施例整体结构示意图。 如图 1所示， 该固体储热装置由多 个储热单元， 例如储热单元 101和储热单元 103的阵列组成； 阵列的每个储热单元垂直立于 地面布置； 每个储热单元包括外壳 12、 外壳 12内部布置的固体储热介质 13及外壳 12外部 布置的保温层 10。
该固体储热介质 13外表面为传热介质的换热界面， 固体储热介质 13为致密材料， 空隙 率小于 10%: 最优地， 固体储热介质 13表面具有密闭层， 进一步减少传热介质的渗入。该固 体储热装置的外壳 12优选为一定厚度钢材， 具有抗传热介质所需的例如 2 Mpa压力的能力； 外部的保温层 10选择具有低导热率的岩棉等材料，进行包覆， 也可以使用真空技术对其进行 保温， 最大限度地降低固体热装置的热量的损失。
固体储热装置外部还布置循环管道接口， 多个储热单元串并联阵列布置， 循环管道相互 串、 并联， 最后会聚于总循环管道。
传热介质从热源 18， 例如太阳能镜场接收热量后， 一部分沿流经方向 A直接流经换热装 置或做功装置 19， 例如换热器、 汽轮机， 多余传热介质部分沿流经方向 B方向流入多个储热 单元例如 101和 103内部的固体储热介质 13的表面， 将热量传导至固体储热介质 3， 完成热 量的输送后， 从另一接口输送至总循环管道， 沿流经方向 C完成总体热量的输送； 当热源 18 不能持续直接提供热量时， 开始启用储热管内部的已储存的热量， 传热介质沿 E方向进入储 热单元例如 101， 从储热单元中吸收热量后沿流经方向 D， 再经过 A方向进入外部的做功装 置 19， 持续地提供热量的输入； 每个储热单元都严格按照特定的方向流经换热介质， 对固体 储热装置存热时高温换热介质沿 B方向进行存热， 罐体中储热介质在换热介质的上游的高端 位置为高温度， 下游的低端位置为低温度； 再者， 对结构取热时低温的换热介质沿 B方向的 反方向进行取热 （即沿 D的方向取热）， 如此在取热的过程中保持与存热过程中相一致的温 度分布布置， 呈现高端位置高温， 低端位置低温， 且中间位置的温度呈现沿高低温度逐步变 化的温度梯度分布 （当固体储热装置不是严格垂直布置时， 也同样获得高温高温入口端为高 温，低温出口端为低温的温度梯度分布）； 如此可以实现储热单元内部储热介质沿长度轴向方 向上设置形成斜温层布局结构。 该传热介质可以为气、 液、 蒸汽或其它相变介质。
该固体储热装置可以使用于任何热利用的领域， 特别适于大规模高品位太阳能热利用的 储热系统。
储热单元可以采用分层控制。 图 2是储热单元的分层控制单元； 如图 2所示， 储热单元 由多个不同的储热区阵列组成， 特定的储热区实施不同的分层控制， 例如储热输入循环系统 包括储热区 201， 202和 203组成的分层传热控制单元： 换热输出循环系统包括储热区 207， 208和 209组成分层换热输出控制单元， 每个控制单元中的储热区配备一个控制阔， 例如储 热区 201对应的控制阔为 A， 储热区 209对应的控制阔为 I。 传热循环系统中， 传热介质从储热装置的顶部， 即储热空间的 209开始向下流动的过程 中对储热介质输送热量， 温度逐渐降低， 最后流出储热装置， 重新受热循环。 由于储热介质 导热较好， 储热区 209部分的储热介质很快达到与传热介质相近的温度； 在此后的换热过程 中， 传热介质在流经储热区 209部分时， 基本没有放热降温， 保持原有高温流到储热区 208 部分， 对储热区 208部分换热后降温， 继续下行。 以此类推， 自储热区 209开始， 随着换热 进程继续， 自高温段 209开始， 逐渐有更多的储热介质部分被存入高温热能。
传热介质经过换热后， 流出储热装置的温度已经降低， 为更好的利用热能品位， 对储热 输入进行分层控制： 首先分层储热输入控制单元中控制阀 C开启， 控制阀 B和 A闭合； 当控 制 W C对应的储热区 203到达饱和临界传入工作状态时 （即当储热区 203出口温度达到或略 高于允许传热介质流出最高温度限度时， 闭合控制阔 C， 开启控制阀 B， 控制阀 A仍保持闭 合； 当控制阀 B对应的储热区 202到达饱和临界传入工作状态时 （即当储热区 202出口温度 达到或略高于允许传热介质流出最高温度限度时）， 闭合控制阀 B， 开启控制阀 A， 而控制陶 C保持闭合， 直到整个储热区都完成储热 （即最后的储热区出口温度达到或略高于允许传热 介质流出最高温度限度时）， 分层储热输入控制结束， 此时认为热能储满。
换热输出循环系统中， 换热介质从固体储热单元的底部， 即储热区 201开始向上流动的 过程中对储热装置换热输出热量， 温度逐渐升高， 最后流出储热装置， 进入外部系统冷却， 重新循环。 由于储热介质导热较好， 换热介质经过储热区 201部分的储热介质很快达到储热 介质稍低的温度； 在此后的换热过程中， 传热介质在流经储热区 201部分时， 基本没有吸热 升温， 保持原有温度流到储热区 202部分， 吸收储热区 202部分换热后升温， 继续上行。 以 此类推， 自储热区 201开始， 随着换热进程继续， 逐渐有更多的换热介质部分被加热至高温 状态。
换热介质经过换热后， 流出储热装置的温度很高， 为更好的利用热能品位， 对储热输入 进行分层控制： 换热介质经过分层换热输出控制单元时开始换热分层控制， 此时的分层换热 输出控制单元中控制陶 G开启， 控制阀 H和 I闭合， 换热输出的热量经过对外做功装置， 例 如热交换器或汽轮机，冷却循环后，冷却回到储热单元的底部；当控制阔 G对应的储热区 207 到达临界换出工作状态时 （即储热区 207输出口储热体的温度与所需传热介质最低输出温度 限度相近时）， 闭合控制阀 G， 开启控制阀 H， 控制阀 I保持闭合； 当控制阀 H对应的储热区 208到达临界换出工作状态时 （即储热区 208输出口的储热体温度与所需传热介质最低输出 温度限度相近时）， 闭合控制阀 H， 开启控制睛 I， 控制阔 G保持闭合， 直到整个储热单元内 的热量完成热量输出 （即最高温度储热区出口的储热体温度与所需传热介质最低输出温度限 度相近时）， 分层储热输入控制结束， 此时认为热能取空。如此使用分层储热输入控制系统和 换热储出控制系统， 以获得高品位的存储和释放热量， 提高热量的高效利用。
图 3是储热单元的不同温度等级的传热控制和换热控制单元；本实施例的储热单元储热 输入系统和换热输出系统分别实施不同温度等级的储热输入控制和换热输出控制。 储热输入 控制或换热输出控制在相同或接近的位置设计各自独立的出入口或共用一个出入口。 如图 3 所示， 储热单元由多个温度等级的储热区组成， 具体由高温储热区 I、 中温储热区 II和低温 储热区 III组成， 多个不同温度梯度的储热区串联形成储热单元整体； 为了描述储热装置内的 储热输入、 换热输出运行模式的控制， 下文主要以高温储热区 I和中温储热区 II进行举例描 述， 其对应的传热介质或换热介质分别处于高温度等级 I和中温度等级 II， 该储热输入控制 和换热输出控制具有相同的控制阔， 相同的控制阀在不同的时刻分别为输入控制阀或输出控 制阀。
在储热输入运行模式下， 高温度等级 I 的传热介质 （例如温度 550°C )选择从最接近 I 温度等级的稍低温储热区位置的传热输入管路入口进入， 例如从控制阔 a输入， 优先将其携 带的热量储存为尽可能高温度状态， 然后继续向下一层储热空间层存入低一些温度的热量， 依此类推， 直到到达允许的最低温度点后从最近处出口流出； 与此同时， 储热单元进行另一 路中温度等级 II的传热介质 （例如温度 35CTC )传入， 其传热介质选择从最接近 II温度等级 的稍低温储热区位置的传热输入管路入口进入， 例如从控制阔 d输入， 优先将其携带的热量 储存为尽可能高温度状态， 然后继续向下一层储热区存入低一些温度的热量， 依此类推， 直 到到达允许的最低温度点后从最近处出口流出； I、 II两种温度等级的热传介质经过的传热输 入管路可以部分重合或各自独立。 此方式可以使本储存装置能够以最优方式同时接收储存各 种来源各种品位的热量， 具有更加广泛的适用范围， 更加经济实用。
在换热输出运行模式下， 高温度等级 I的热量传输换热介质选择从最接近 I温度等级的 稍高温储热区位置的换热管路出口流出， 例如从控制阀 b流出， （温度高于 435°C， 应用于汽 轮机发电），优先使用尽可能低温度状态的热能进行预热，待此储热区温度无法满足输出温度 条件时， 再继续向上一层储热区提取高一些温度的热量， 例如从控制阀 a流出， 依此类推， 直到到达所需温度； 与此同时， 储热单元进行另一路的中温度等级 II的热量换出， 其换热热 量传输介质也选择从最接近中温度等级 Π的稍高温储热区位置的换热管路出口流出， 例如从 控制阔 e流出 （温度大约 200°C， 应用于工业蒸汽）， 优先使用尽可能低温度状态的热能， 待 此储热区温度无法满足输出温度条件时，再继续向上一储热空间单元提取高一些温度的热量， 例如从控制阀 d流出， 依此类推， 直到到达所需温度； I、 II两种温度等级的换热介质经过的 换热管路可以部分重合或各自独立。 此方式可以使本储热装置能够以最优方式同时提供各种 品位的热量输出， 具有更加广泛的适用范围， 更加经济实用。
图 4是第一种储热单元结构示意图； 该储热单元 1内部的固体储热区为圆柱状， 多个储 热区， 例如 41或 43串联组成储热单元的储热体， 且各储热区内部和储热区之间布置隔热层 45， 该隔热层为具有低导热率的绝热层。该储热区包括阵列布置的固体储热块 46和一定数量 固体储热块 46间隔布置隔热层 45 ; 固体储热块 46规律布置， 如图所示环形阵列布置， 各固 体储热块 46之间的间隙为传热介质的流通通道， 而隔热层 45将储热区分开， 以形成固体储 热单元 1的不同区域上的显著温度梯度， 良好地保证了储热单元内部的储存和输出的热量高 品位， 同时隔热层 45 具有传热介质导流层的功能， 将传热介质经过阵列布置的固体储热块 46之间间隙， 在隔热层 45的引导下， 有规律地完成热量的传输， 例如隔热层 45将传热介质 先从储热区的中间位置引流至下一层的储热区的边缘， 再至更下一层储热区的中间位置， 如 此将传热介质以最大接触面与固体储热介质进行热量的传送。优选地， 该隔热层 45具有承压 能力， 进一步提高储热单元 1的结构强度。 固体储热介质的材质为高密度、 高比热容材质， 例如为耐火砖、 岩石、 陶瓷、 玻璃、 石墨、 金属、 混凝土或镁炭砖等其中一种或至少两种的 混合物； 固体储热介质结构为阵列的扇形固体储热块 46， 且该固体储热块整体致密， 具有较 小的孔隙率， 例如孔隙率小于体积的 10%; 优选地， 固体储热块 46表面设置有封闭层， 进一 步降低传热介质长期运行对固体储热块 46的浸入吸收及破坏。优选地，所述封闭层为陶瓷釉、 玻璃釉、 金属层、 石墨层等； 该固体储热单元的外部具有保温材料， 或同真空技术对其进行 保温处理。
图 5是固体储热块结构示意图。 如图 5所示， 固体储热块 56具有自支撑强度， 采用熔 融金属将小尺寸的固体储热介质材料或其混合物浇铸， 冷凝固化成整体而成： 该固体储热块 56包括多种形状或尺寸的材质， 各材质之间最优布置金属层 520， 经过熔融金属将多种材质 的储热块粘结一起，冷凝固化后形成固体储热块 56整体，使用该方法可以获得所需尺寸较大 和特定形状的固体储热块， 优选地， 构成固体储热介质的填充材料内混合布置有导热增强材 料， 如金属丝、 金属片、 石墨、 金属矿渣等， 以提高材料内部的导热能力。 有些情况下， 储 热介质材料本身就同时具备致密、 稳定、 导热率高、 比热容大、 强度高等特点， 可直接使用 此种材料构成储热块， 例如一些金属、 石墨、耐火砖（如碳砖、镁碳砖、铝镁碳砖等）、玻璃、 陶瓷等。
为了提高固体储热介质与传热介质的热交换表面积， 在固体储热块 56形成过程中设置 翅片或沟槽。 另外， 固体储热块 56表面设置有封闭层 57， 降低固体储热块 56受传热介质的 浸湿渗透， 引起的结构破坏。 该封闭层 57优选为陶瓷釉、 玻璃釉、 金属层、 石墨层等。 图 6是第二种储热单元结构示意图。 如图 6所示， 该储热单元 1包括多个串联的储热区 例如储热区 61和储热区 63， 且各储热区之间布置隔热层； 例如该储热区 61包括多个规律布 置的固体储热块， 该固体储热块为圆柱管块体， 外部为密封外壳， 内部布置有颗粒状固体储 热介质材料， 形成具有固定形状及自支撑能力的固体储热块； 该密封外壳为金属材料， 如金 属盒、 金属管、 金属空心球或金属壳； 图 6示意的该固体储热块为储热管 68， 该储热管 68 两端密封； 该储热管 68为直管， 高度与该储热区 61的轴向长度相一致， 多个储热管 68紧密 规律布置于储热区 61内， 各储热管紧密布置， 之间的空隙为传热介质的通道。
图 7是储热管结构示意图； 如图 7所示， 该储热管 78包括密封外壳 79和密封外壳 79 内填充的固体储热介质材料； 该固体储热介质材料密实堆积于密封外壳 79内部； 为进一步提 高固体储热介质材料在密封外壳 79内部的径向上的导热能力， 优选在密封外壳 79间隔布置 金属翅片。储热管 78中支撑管可为金属管、玻璃管或波纹管； 固体储热介质材料的材质为重 烧镁砂、 黄砂、 煤炭或石墨等， 优选为煤炭， 煤炭的堆积密度 2400kg/m3， 比热容大约
Figure imgf000011_0001
图 8是第三种储热单元实施例整体结构示意图； 如图 8所示储热单元 1具有一定的倾斜 角，整体成线性，与地面成一定小角度倾斜（该小角度亦可以为零， 即设置成完全水平布置）， 储热单元包括外壳、 外壳内部布置的固体储热介质， 外壳外部的保温层； 该储热单元内部由 多个相互连接的储热区例如储热区 81和储热区 83组成， 储热区之间布置隔热设计结构， 该 隔热设计结构为相邻储热区之间的空隙 85， 在另一种情况下， 隔热设计也可以为相邻储热区 间布置的层状隔热材料。 该固体储热介质包括由多块密实结构的固体储热块 86 (例如耐火材 料镁碳砖）堆砌布置而成， 固体储热块 86的外表面为传热介质的换热界面， 每块固体储热块 86表面具有一定形状的凹槽， 各块相互彼此紧密堆砌， 构成可以流通的导流槽； 各固体储热 介质具有良好的致密性， 具有很小的空隙率， 最优小于 10%; 进一步优化的各固体储热介质 表面具有密封层， 进一步减少自身因空隙率带来的传热介质的渗透现象。 该储热单元整体细 长， 例如 600m， 在轴向方向上尺寸很大， 同时由于轴向上的隔热设计， 轴向传热速度低， 具 有良好的斜温层结构布局， 可以轻松获得高品位热源的存储、 输入和输出； 位置高端为高温 传热介质储热输入端和换热输出端， 位置低端为低温传热介质完成储热的输出端和进行换热 输入端口。多个该种储热单元阵列布置， 整体水平布置， 构成水平布置的固体储热装置整体。
图 9是图 8储热单元内部的固体储热块结构示意图。 如图 9所示， 单个固体储热块 96 表面设置有传热介质导流用的导流槽，该导热槽与之相邻紧密布置的固体储热块 96背部形成 横截面密闭的导流通道密实结构的固体储热块 96紧贴布置而成；该导热通道较传统的金属导 热管道具有明显优势， 固体储热块 96表面可以布置多个导热通道，可以获得小的横截面积和 大的换热表面积， 且减少金属导热管道的制作成本， 且换热介质能直接与固体储热介质直接 接触， 具有高效换热效率， 整体具有很好的换热系数、 较大的换热表面， 具有巨大的换热功 率； 固体储热块 96优选为镁炭砖， 堆积密度 3000kg/m3， 比热容大约 UKJ/kgK， 且具有良 好的导热率， 并且空隙率很低， 性质稳定， 是优良的固体储热材料。
上述具有导流槽的固体储热块 96紧密堆砌的储热单元实施例：该储热单元轴向长 200m， 直径 1.5m，水平布置于地面上，整体成卧式固体储热装置，外壳的外径 1560mm，壁厚 30mm， 固体储热块 96为炭砖或镁炭砖，整个储热装置内部布置 500个贯通的孔；相邻紧压对齐布置 的导流槽形成密闭的横截面， 该横截面面积 51.6mm2， 周长为 34.2mm; 该储热装置储热利用 其显热， 使用温度差为 150°C， 大约可以储热 40MWh的动态热量， 假定每个孔内的传热介质 为导热油，且导热油中间状态为 1.5MPa， 29 °C ,输入输出温度差 200°C (由 395°C至 195°C )， 单孔内部的流速 0.8m/s，则输入功率大于为 8MWt;经计算，管内的换热系数大约可达到 555W/ m2 k; 管内流体与管壁温差假定平均温差为 5K， 则总的换热功率约为为 9.7MWt， 可满足要 求； 具有良好的储热和换热性能。
图 10是固体储热块的另一实施例结构示意图， 如图 10所示， 固体储热块 106表面具有 斜平行槽， 两个相互重叠布置的固体储热块 106其表面的导流槽交错叠合布置， 导流槽与之 相接触的固体储热块 106非导槽部分形成截面密闭的导流槽，与之相互接触的固体储热块 106 导流槽相互接触， 完成传热介质的再次内部紊流接触， 利于传热介质的换热系数的提高， 整 体换热功率优良。
图 11 是储热单元的外壳实施例结构示意图； 上文描述的储热单元外壳需承压例如 2.5MPa, 耐温例如 400°C (内部流经的传热介质为 2.5MPa， 395°C )， 外壳都设计成统一的传 统管道， 例如直径 820mm， 厚度为 15mm; 且该外壳 114为钢质材料， 具有良好的导热系数， 该外壳 114接收流体的热量， 因本身厚度较厚， 具有较低的热阻和良好的传热性能， 能将入 口接收的热量， 沿壳壁快速地传至外壳 114的出口端， 加热出口端传热介质， 从而使储热单 元低温区的温度上升，破坏储热装置设计的斜温层结构； 因此需要降低金属外壳 114的壁厚， 减少通过储热外壳 114传递至低温区的储热介质， 如图 11所示， 金属外壳 114采用较薄的外 壳 114， 例如厚度为 8ηπη， 金属外壳的外壁一定间隔位置布置有外部加强法兰 112， 该加强 法兰 112截面为倒 "Τ"型； 且每个加强法兰 112与金属外壳 114的连接处布置具有低导热率 材质的隔热层 113，例如环形耐压硅酸钙板；金属外壳 114壁厚的降低和隔热层 113的布置增 大了向低温区扩散热量的热阻， 进一步保证的斜温层的稳定性， 且降低金属外壳 114的加工 成本。
本发明实施例的固体储热介质不具有流动性， 储热利用固体状态储热， 运行安全； 固体 储热介质按一定规律堆砌，部分或全部表面直接与传热介质接触换热， 不需要增加管路过渡， 具有巨大的换热界面面积、 并接触良好， 可方便高速的完成热量的输入或输出， 大量增强了 固体储热介质与传热介质之间的传热速度（即传热功率），使储热装置具有良好的整体换热性 能;同时， 由于流道截面积大， 传热介质流动阻力小， 压降损失小， 可降低系统运行能耗。 固 体储热块具有的致密材质或表面封闭层设计或封闭层外壳设计使其对热传介质吸收较少， 成 本低， 并且材料寿命更长。 储热单元内部的储热介质导热率较高， 在径向或宽度方向传热较 快， 可高功率吸热和放热， 能尽量以最接近原温度品位的方式储存和提取热量； 在轴向或长 度方向上， 由于尺寸大或存在隔热设计， 传热速度较慢， 可长期保持一定的温度梯度， 有利 于尽量避免高品位 (温度) 热源由于高低温区域的均温趋势造成品位 （温度） 下降， 保证热 量输出品质； 同时导流设计引导传热介质在储热单元内部的规律流径， 更有利于传热介质的 良好换热效果；储热单元的一定储热区之间分别实施储热输入分级控制和换热输出分级控制， 且还可以实施不同温度等级的储热输入和换热输出控制， 可以大大提高储入和换出热量的更 加高品位。 单元组合式结构可根据需要灵活配置， 方便可靠成本低。 该固体储热装置总体成 本低、 导热好、 热容大， 可应用于各种储热应用， 特别是太阳能光热利用系统。
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显而易见的改变， 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仅由所述的权利要求书进行限定。

Claims

权 利 要 求 书 权利要求书
1、 一种固体储热装置， 其特征在于， 所述固体储热装置由至少一个储热单元串联和 /或并联 组合而成； 该储热单元包括外壳、 外壳内部布置的固体储热介质及外部的保温层； 以固体储 热介质的外表面为换热界面， 与传热介质直接接触发生换热； 所述储热单元内部储热介质沿 长度轴向方向上设置为斜温层布局结构。
2、根据权利要求 1所述的固体储热装置， 其特征在于， 所述储热单元包括在多个串联的储热 区之间设置的隔热层。
3、 根据权利要求 1所述的固体储热装置， 其特征在于， 所述固体储热介质的材质为耐火砖、 岩石、 陶瓷、 玻璃、 石墨、 煤炭、 土状石墨、 金属、 矿石、 矿渣和混凝土中的一种或至少两 种的混合物。
4、根据权利要求 1所述的固体储热装置，其特征在于，所述固体储热介质结构为固体储热块， 其材质致密， 具有小于 10%空隙率。
5、 根据权利要求 4所述的固体储热装置， 其特征在于， 所述固体储热块为炭砖或镁炭砖。
6、根据权利要求 4所述的固体储热装置， 其特征在于， 所述固体储热块表面具有作为换热界 面的导流槽和 /或翅片。
7、根据权利要求 6所述的固体储热装置， 其特征在于， 所述多个固体储热块表面之间具有相 互交叉的换热导流槽和 /或翅片。
8、根据权利要求 4所述的固体储热装置， 其特征在于， 所述固体储热块采用熔融金属将固体 储热介质材料或其混合物浇铸， 冷凝固化成整体而成。
9、根据权利要求 4所述的固体储热装置， 其特征在于， 所述固体储热块包括封闭外壳及填充 于封闭外壳内部的固体储热介质材料， 整体具有固定形状及自支撑能力。
10、 根据权利要求 9所述的固体储热装置， 其特征在于， 所述封闭外壳为金属材料。
11、 根据权利要求 1所述的固体储热装置， 其特征在于， 所述储热单元在特定储热区进行储 热输入或换热输出分级控制。
12、 根据权利要求 1或 11所述的固体储热装置， 其特征在于， 所述储热单元实施不同温度等 级的多层分级控制。
13、 根据权利要求 1所述的固体储热装置， 其特征在于， 所述储热单元的外壳为相对薄壁金 属管， 且通过外部加强法兰增强耐压能力。
14、根据权利要求 13所述的固体储热装置， 其特征在于， 所述加强法兰与外壳外壁间布置紧 密接触的隔热层。
15、 根据权利要求 1所述的固体储热装置， 其特征在于， 所述储热单元垂直、 水平或具有一 定倾斜角度地相对水平布置。
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