WO2013121965A1 - 流動層ボイラの層内伝熱管 - Google Patents

流動層ボイラの層内伝熱管 Download PDF

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Publication number
WO2013121965A1
WO2013121965A1 PCT/JP2013/052843 JP2013052843W WO2013121965A1 WO 2013121965 A1 WO2013121965 A1 WO 2013121965A1 JP 2013052843 W JP2013052843 W JP 2013052843W WO 2013121965 A1 WO2013121965 A1 WO 2013121965A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
bed
fluidized bed
protector
transfer tube
Prior art date
Application number
PCT/JP2013/052843
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
吉田　裕
阪本　英之
恭久 本田
Original Assignee
荏原環境プラント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 荏原環境プラント株式会社 filed Critical 荏原環境プラント株式会社
Priority to EP13749873.9A priority Critical patent/EP2821697B1/en
Priority to CN201380009114.6A priority patent/CN104136842B/zh
Priority to JP2013558659A priority patent/JP6085570B2/ja
Priority to KR1020147024890A priority patent/KR101998448B1/ko
Publication of WO2013121965A1 publication Critical patent/WO2013121965A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F22B21/22—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes of form other than straight or substantially straight
    • F22B21/24—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes of form other than straight or substantially straight bent in serpentine or sinuous form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • F22B31/0007—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed
    • F22B31/0015—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed for boilers of the water tube type
    • F22B31/0023—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus with combustion in a fluidized bed for boilers of the water tube type with tubes in the bed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/107—Protection of water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C10/00—Fluidised bed combustion apparatus
    • F23C10/18—Details; Accessories
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/30—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having a fluidised bed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G7/00—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals
    • F23G7/10—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of field or garden waste or biomasses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G7/00—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals
    • F23G7/12—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of plastics, e.g. rubber
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D13/00—Heat-exchange apparatus using a fluidised bed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/003—Multiple wall conduits, e.g. for leak detection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/124—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and being formed of pins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
    • F28F19/06—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings of metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2206/00—Fluidised bed combustion
    • F23C2206/10—Circulating fluidised bed
    • F23C2206/103—Cooling recirculating particles
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0024—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for combustion apparatus, e.g. for boilers

Definitions

  • the present invention relates to an in-bed heat transfer pipe installed in a fluidized bed of a fluidized bed boiler that burns fuel such as biomass and plastic, high calorific value RDF (waste solidified fuel) and waste, and recovers combustion heat. .
  • fuel such as biomass and plastic
  • RDF waste solidified fuel
  • Patent Document 1 discloses a wear resistant structure of a heat transfer tube in which the thickness reduction of the heat transfer tube is reduced by covering the heat transfer tube with a stud and a refractory. However, in the structure disclosed in Patent Document 1, covering the heat transfer tube with a refractory lowers the heat transfer coefficient and requires a large heat transfer area.
  • Patent Document 2 JP-A-7-217801
  • Patent Document 2 JP-A-7-217801
  • a method of attaching a protector and a method of overlaying or thermal spraying are proposed as a method of preventing thickness reduction due to wear of a heat transfer tube.
  • the heat transfer tube itself be made of high chromium steel or stainless steel excellent in wear resistance.
  • the method described in Patent Document 2 can prevent thickness reduction due to wear, there is a problem that the durability is inferior in an environment directly subjected to molten salt corrosion simultaneously with wear.
  • the present inventors obtained the following knowledge in the process of performing continuous operation over a long period of time using various in-bed heat transfer tubes in a fluidized bed boiler. That is, when chlorine is contained in the fuel like biomass-based RDF and wastes, when part of the chlorine is transferred to the fluid medium (fluid sand) after the fuel is burned, the chlorine in the fluid medium becomes the fluid bed. When operated at a temperature of 700.degree. C. to 850.degree. C., it produces eutectic salts with alkali metals (Na, K etc.) contained in the fuel. The condensation temperature at which this eutectic salt condenses in the molten state is, for example, 650 to 700.degree.
  • the surface temperature of the in-layer heat transfer pipe is higher than the condensation temperature, condensation of the eutectic salt on the surface of the in-layer heat transfer pipe can be suppressed, and the reduction in thickness due to molten salt corrosion can be reduced.
  • the in-layer heat transfer tube whose durability has been enhanced by providing a protector made of a stainless steel such as SUS310S on the outer peripheral side of the water tube, the present inventors have found that the surface temperature of the in-layer heat transfer tube It has been discovered that corrosion loss due to corrosion wear can be reduced at lower temperatures and above a predetermined temperature (e.g., 450 ⁇ 0> C).
  • the inventors of the present invention based on the above findings, in order to adjust the surface temperature of the protector to a temperature range where molten salt corrosion is suppressed and thickness reduction is difficult, (1) heat transfer between the fluidized bed and the protector It was conceived that it was effective to increase the rate and (2) to lower the heat transfer coefficient between the protector and the water pipe, and the invention was achieved.
  • the heat transfer pipe is reduced in the amount of thickness reduction by suppressing the molten salt corrosion of the heat transfer pipe while securing the economical heat transfer amount It is an object of the present invention to provide an in-bed heat transfer pipe of a fluidized bed boiler excellent in durability.
  • the in-bed heat transfer pipe of the fluidized bed boiler of the present invention is an in-bed heat transfer pipe disposed in the fluidized bed of the fluidized bed boiler, wherein the in-bed heat transfer pipe A water pipe, a protector provided on the outer peripheral side of the water pipe for protecting the water pipe, and a packed bed provided between the water pipe and the protector are characterized.
  • the heat of the flowing medium is transferred to the water pipe via the protector and the packed bed, and the fluid in the water pipe is heated.
  • the heat transfer coefficient between the protector and the water pipe can be lowered by setting the filler layer interposed between the water pipe and the protector to a low thermal conductivity. Therefore, the temperature difference between the protector surface and the water tube surface can be increased. Thereby, the molten salt corrosion of the heat transfer pipe can be suppressed, the amount of thickness reduction can be small, and the in-layer heat transfer pipe excellent in durability can be obtained.
  • the surface temperature of the protector is maintained at 450 to 650.degree.
  • the packed bed is formed by packing a solid particle filler.
  • the air gap of the packed bed is made of air having a low thermal conductivity, it is possible to lower the heat transfer coefficient between the protector and the water tube.
  • the material, shape, and thickness of the filler of the filling layer are set such that the surface temperature of the protector becomes 450 to 650 ° C., preferably 480 to 620 ° C., because the heat transfer coefficient becomes inefficient if lowered too much. Select as appropriate.
  • the packed bed is characterized in that the packing ratio of the solid particle filler is 0.5 or more and 0.9 or less.
  • the filling rate is a value obtained by dividing the volume [m 3 ] occupied by the filling by the volume [m 3 ] of the space between the outer surface of the water pipe and the inner surface of the protector.
  • the packed bed has a thermal conductivity of 0.4 to 1.4 W / mK.
  • the thermal conductivity of the packed bed is 0.4 to 1.4 W / mK, the heat transfer coefficient between the protector and the water pipe can be lowered. Therefore, the temperature difference between the surface of the protector and the surface of the water tube can be increased, and the surface temperature of the protector can be maintained at a high temperature of 450 to 650.degree.
  • the thickness of the filler layer is 2 to 4 mm.
  • the protector is made of stainless steel.
  • the stainless steel is SUS304 or SUS316 or SUS310S. According to the present invention, by forming the protector from stainless steel such as SUS304, SUS316, or SUS310S, it is possible to suppress thickness reduction due to molten salt corrosion.
  • the protector is provided with fins on the outer surface.
  • the fins with excellent heat exchange efficiency are provided on the outer surface of the protector, the heat transfer coefficient from the fluid medium to the protector can be enhanced. Therefore, economical heat transfer can be secured.
  • the fin is a spiral fin.
  • the fin is a pin-shaped fin.
  • the fluidized bed boiler according to the present invention is a fluidized bed boiler in which fuel is burned in a fluidized bed and combustion heat is recovered by an in-bed heat transfer pipe, wherein the in-bed heat transfer pipe is any one of claims 1 to 11.
  • the in-bed heat transfer tube according to the present invention is characterized in that the temperature of the fluidized bed is controlled to 700 to 900 ° C. According to the present invention, the temperature of the fluidized bed is controlled to 700 to 900 ° C. by adjusting the amount of air of the fluidizing air supplied to the fluidized bed according to the fuel calories and the like. Then, the heat of the fluidized bed maintained at 700 to 900 ° C. is transferred to the water pipe through the protector and the packed bed, and the saturated water in the water pipe is heated.
  • the heat transfer coefficient between the protector and the water pipe can be reduced by the packed bed interposed between the water pipe and the protector. Therefore, the temperature difference between the surface of the protector and the surface of the water tube can be increased, and the surface temperature of the protector can be maintained at a high temperature of 450 to 650.degree.
  • Fluidization can be activated to increase the heat transfer coefficient from the fluid medium to the protector.
  • the fluidized bed boiler includes a combustion chamber for burning a fuel, and a heat recovery chamber in which the heat transfer pipe in the bed is disposed to recover combustion heat, and the flow of the heat recovery chamber
  • the combustion chamber which burns the fuel and the heat recovery chamber which recovers heat are separated, troubles such as incombustibles in the fuel entwining in the in-layer heat transfer pipe do not occur.
  • the air amount of the fluidizing air in the heat recovery chamber it is possible to control the heat recovery amount of the in-layer heat transfer pipe.
  • the present invention has the following effects.
  • (1) The heat transfer coefficient between the protector and the water pipe can be lowered by forming the in-layer heat transfer pipe with the water pipe, the filler and the protector, and installing the filling layer interposed between the water pipe and the protector. Therefore, the temperature difference between the surface of the protector and the surface of the water tube can be increased, and the surface temperature of the protector can be maintained at a high temperature of 450 to 650.degree. As a result, it is possible to provide an in-layer heat transfer pipe with reduced durability and reduced amount of thickness reduction while suppressing molten salt corrosion of the heat transfer pipe.
  • FIG. 1 is a schematic cross-sectional view showing an embodiment of a fluidized bed boiler provided with an in-bed heat transfer tube according to the present invention.
  • FIG. 2 is a schematic sectional view showing another embodiment of the fluidized bed boiler provided with the in-bed heat transfer tube according to the present invention.
  • FIG. 3 is a schematic cross-sectional view of the in-layer heat transfer tube.
  • FIG. 4A is a diagram showing experimental results of a conventional in-layer heat transfer pipe in which a stainless steel is built on a water pipe.
  • FIG. 4B is a diagram showing experimental results of the in-layer heat transfer tube of the present invention.
  • FIG. 5 is a front view of the in-layer heat transfer tube.
  • FIG. 6 is a longitudinal sectional view of the in-layer heat transfer tube.
  • FIG. 7A is a view showing another form of the in-layer heat transfer tube, and FIG. 7A is a front view of the in-layer heat transfer tube.
  • FIG. 7B is a view showing another form of the in-layer heat transfer tube, and FIG. 7B is a longitudinal sectional view of the in-layer heat transfer tube.
  • FIG. 8A is a view showing still another form of the in-layer heat transfer tube, and FIG. 8A is a front view of the in-layer heat transfer tube.
  • FIG. 8B is a view showing still another form of the in-layer heat transfer tube, and FIG. 8B is a longitudinal sectional view of the in-layer heat transfer tube.
  • FIG. 1 is a schematic cross-sectional view showing an embodiment of a fluidized bed boiler provided with an in-bed heat transfer tube according to the present invention.
  • the fluidized bed boiler 1 comprises a furnace main body 2 having a substantially cylindrical shape or a substantially square cylinder shape, a fluidized bed 3 for burning waste or fuel such as RDF, and a hearth bottom plate supporting the fluidized bed 3
  • an in-bed heat transfer pipe 5 is installed in the fluidized bed 3.
  • the fluidized bed 3 is filled with a fluidized medium, which is a fluidized sand such as silica sand, so as to fill the intra-bed heat transfer pipe 5.
  • a fluidized medium which is a fluidized sand such as silica sand, so as to fill the intra-bed heat transfer pipe 5.
  • the hearth bottom plate 4 is formed with a large number of aeration nozzles for injecting fluidizing air as fluidizing gas into the furnace.
  • fuel is supplied to the fluidized bed 3 from an inlet (not shown).
  • fluidizing air having a uniform amount of air is ejected from the aeration nozzle of the hearth bottom plate 4 over the whole of the fluid bed 3, and in the fluid bed 3, the fluid medium is up and down. It becomes a so-called bubbling fluidized bed that flows actively.
  • the fuel supplied into the furnace is thermally decomposed and burned in the fluidized bed 3, and the heat of combustion heats the fluidized medium to a high temperature, and the temperature of the fluidized bed 3 is maintained at 700 to 900.degree.
  • the temperature of the fluidized bed 3 is controlled by adjusting the amount of fluidization air.
  • the fluid medium that has become high temperature comes into contact with the in-bed heat transfer tube 5, and the fluid (can water) in the in-bed heat transfer tube 5 exchanges heat with the fluid medium to recover heat from the fluid medium.
  • FIG. 2 is a schematic sectional view showing another embodiment of the fluidized bed boiler provided with the in-bed heat transfer tube according to the present invention.
  • the fluidized bed boiler 11 is provided with a furnace main body 12 having a substantially square cylindrical shape, and the inside of the furnace main body 12 has one combustion chamber 14 in the center by a pair of left and right partition walls 13 and 13. And two heat recovery chambers 15, 15 at both sides.
  • a fluidized bed 20 for thermally reacting waste and fuel such as RDF is formed, and the fluidized bed 20 is supported by the hearth bottom plate 30.
  • the hearth bottom plate 30 installed in the furnace body 12 has a mountain shape which is high at the center and gradually lowered toward the side edges.
  • the hearth bottom plate 30 is provided with a number of aeration nozzles for injecting fluidizing air as fluidizing gas into the furnace.
  • a fluidized bed 23 is formed in each heat recovery chamber 15, and the fluidized bed 23 is supported by the hearth bottom plate 31.
  • the hearth bottom plate 31 is provided with an aeration nozzle for injecting fluidizing air as fluidizing gas into the furnace.
  • air boxes 32, 32, 33, 33 are formed below the mountain-shaped heart floor bottom plate 30, and these air boxes 32, 32, 33, 33 are formed from the outside of the furnace. Fluidized air is provided. Aeration nozzles above the two central air boxes 32, 32 by adjusting the opening of a control valve (not shown) to adjust the air flow rate supplied to the air boxes 32, 32, 33, 33 From there, the fluidizing air is jetted so as to give a substantially small fluidization velocity, and from the aeration nozzles above the two air boxes 33, 33 on both sides, to give a substantially high fluidization velocity Erupt the fluidizing air.
  • a moving bed 21 is formed above the central portion of the hearth floor plate 30 to move the flowing medium downward at a relatively slow speed from above, and the flowing medium flows from above below both sides of the hearth floor plate 30.
  • a fluidized bed 22 moving upward is formed. Therefore, the moving medium moves from the moving bed 21 to the fluidized bed 22 in the lower part of the fluidized bed 20 and the moving medium from the fluidized bed 22 to the moving bed 21 in the upper part of the fluidized bed 20.
  • a circulating flow is formed on the left and right through which the fluid medium circulates.
  • the inclined portion of each partition wall 13 functions as a deflector which makes it easy for the rising fluid medium to be inverted to the inside of the furnace body 12.
  • the air amount of the fluidizing air supplied to the moving bed 21 is 2 to 3 u 0 / u mf
  • the air amount of the fluidizing air supplied to the fluid bed 22 is 4 to 6 u 0 / u mf .
  • u 0 is the sky velocity
  • u mf is the lowest fluidization sky velocity.
  • the fuel supplied to the moving bed 21 is swallowed by the fluid medium and moves downward with the fluid medium. At this time, thermal decomposition of the fuel is performed by the heat of the fluid medium, and combustible gas is generated from the combustibles in the fuel to become brittle thermal decomposition residue.
  • the pyrolysis residue typically contains incombustible matter and unburned matter (char) which has become brittle due to the pyrolysis.
  • the pyrolysis residue generated in the moving bed 21 travels to the fluidized bed 22 along the inclined bottom floor plate 30 when it reaches the bottom floor plate 30 together with the fluid medium.
  • the thermal decomposition residue that has reached the fluidized bed 22 comes in contact with the strongly flowing fluid medium, and the unburned matter is exfoliated from the incombustible matter, and the incombustible matter remaining after the unburned matter is exfoliated together with some fluid medium It is discharged from the discharge port 17.
  • the unburned material separated from the incombustible material moves upward with the flowing fluid medium as the fluidizing air is supplied.
  • the unburned matter is combusted by the supplied fluidizing air, generates combustion gas while heating the fluid medium, and becomes fine unburned matter and ash particles which are carried to the gas.
  • a part of the high temperature fluid medium reaching the upper part of the fluid bed 22 flows into the moving bed 21.
  • the fluidized medium is raised in the fluidized bed 22 to a temperature at which the fuel can be properly pyrolyzed when it flows to the moving bed 21.
  • the fluid medium having flowed into the moving bed 21 receives the supplied fuel again, and repeats the thermal reaction in the moving bed 21 and the fluid bed 22 described above.
  • the temperature of the moving bed 21 is maintained at 700 to 900 ° C.
  • the temperature of the fluidized bed 22 is maintained at 700 to 900 ° C.
  • a part of the high temperature fluid medium in the upper part of the fluidized bed 22 passes the upper part of the partition wall 13 and enters the heat recovery chamber 15.
  • the fluid medium that has entered the heat recovery chamber 15 forms a fluid bed 23 moving downward from above.
  • the hearth bottom plate 31 of the heat recovery chamber 15 is inclined downward from the inner wall side of the furnace body 12 toward the combustion chamber, and an opening 18 is provided in the lower portion of the heat recovery chamber 15.
  • the inflowing fluid medium settles to form the fluid bed 23, and circulates from the opening 18 to the combustion chamber 14.
  • the temperature of the fluidizing medium entering the heat recovery chamber 15 is 700 to 900 ° C., but the in-bed heat transfer pipe 5 is disposed in the fluidizing bed 23 of the heat recovery chamber 15.
  • the amount of heat recovery of the heat transfer tube 5 can be controlled by controlling the amount of air of fluidizing air ejected from the aeration nozzle of the heart floor bottom plate 31 of the fluidized bed 23 to 2 to 4 u 0 / u mf. .
  • the fluid medium circulated to the combustion chamber 14 joins the fluid bed 22 and ascends with the fluid medium of the fluid bed 22, and a part of the fluid medium enters the heat recovery chamber 15 again. Repeat heat exchange with the fluid.
  • FIG. 3 is a schematic cross-sectional view of the in-layer heat transfer tube 5.
  • the in-layer heat transfer pipe 5 includes a water pipe 6 through which a fluid (canned water) flows, a protector 8 provided on the outer peripheral side of the water pipe 6 to protect the water pipe 6, a water pipe 6 and a protector 8 And a filler layer 7 provided between the two.
  • the water pipe 6 is composed of a steel pipe for a boiler or heat exchanger having a thickness of 4 to 8 mm, for example, STB 410S, and a fluid (water can flow) flowing in the water pipe 6 is saturated water of 2 MPa to 12 MPa.
  • the filler layer 7 is filled with a filler of solid particles such as sand, stainless steel powder, magnesium oxide, iron, alumina and the like, and is formed in a cylindrical shape having a thickness of 2 to 4 mm.
  • the thermal conductivity of the packed bed is, for example, 0.4 to 1.4 W / mK as calculated by the calculation shown in “Reaction of powder, Nikkan Kogyo Shimbun, p. 54-57”.
  • the filler is preferably particulate.
  • the filling rate of the filler is preferably 0.5 or more and 0.9 or less, and more preferably 0.6 or more and 0.8 or less.
  • the filling factor at the time of filling the filler in the space between the water pipe 6 and the protector 8 is according to the following equation.
  • Packing ratio [-] volume occupied by filling [m 3 ] / volume of void in water tube outer surface and protector inner surface [m 3 ]
  • the protector 8 is made of stainless steel such as SUS304, SUS316, or SUS310S, which is excellent in wear resistance and corrosion resistance, and is formed in a cylindrical shape having a thickness of 3 to 6 mm.
  • the protector 8 may be formed by cylindrically forming a stainless steel plate, or a stainless steel pipe may be used.
  • the material of the protector 8 is stainless steel such as SUS304, SUS316, SUS310S, and (2) a thermal conductivity of 0.4 to 1.4 W / mK between the water pipe 6 and the protector 8
  • the formed packed bed 7 is formed to a predetermined thickness, that is, a thickness of 2 to 4 mm, and (3) the fluidized bed 3 (see FIG. 1) in which the in-layer heat transfer tube 5 is installed It is configured to maintain the temperature of 700.degree.-900.degree. C.).
  • the surface temperature of the protector 8 is maintained at a high temperature of 450 to 650 ° C., preferably 480 to 620 ° C., by adopting the configurations of (1) to (3).
  • FIGS. 4A and 4B are diagrams showing a comparison result of a conventional in-layer heat transfer pipe in which a stainless steel is accumulated on a water pipe, and the in-layer heat transfer pipe of the present invention having the configurations of (1) to (4) above. is there.
  • the conventional heat transfer pipe in the layer uses a 3 mm buildup made of stainless steel for surface modification of the water pipe. As shown in FIG. 4A, assuming that the temperature of the fluidized bed is 800 ° C.
  • the temperature difference between the surface temperature of the overlay and the surface temperature of the water pipe is 20 ° C.
  • the in-layer heat transfer tube of the present invention uses a 2 mm thick filler layer filled with magnesium oxide particles and a 3 mm thick protector made of SUS310S on the outer periphery of the water tube. There is. As shown in FIG. 4B, assuming that the temperature of the fluidized bed is 800 ° C.
  • the heat conductivity from the medium (sand) to the protector is 390 W / m 2 K
  • the thermal conductivity of the protector is 16.2 W / m K
  • the thermal conductivity of the packed bed filled with magnesium oxide (thickness 2 mm) is 1.3 W / mK
  • surface temperature of the protector 513 ° C. the surface temperature of the packed bed 491 ° C.
  • overall heat transfer coefficient (protector inner surface reference) is 246W / m 2 K
  • total heat transfer amount is 122957W / m 2.
  • the temperature difference between the surface temperature of the protector and the surface temperature of the packed bed is 22 ° C.
  • the temperature difference between the surface temperature of the packed bed and the surface temperature of the water pipe is 191 ° C.
  • the overall heat transfer coefficient is 263 W / m 2 K and the total heat passing amount is 131,586 W / m 2 on the basis of the outer surface of the water pipe.
  • (1) Increase the heat transfer coefficient between the fluid medium (sand) and the protector by activating the fluidization of the fluid bed (moving bed) and appropriately selecting the thickness and thermal conductivity of the packed bed, )
  • the heat transfer rate between the protector and the water tube can be reduced.
  • the protector surface temperature can be set to 450 ° C. or higher while maintaining the overall heat transfer coefficient and the total heat passing amount to the same level as the in-layer heat transfer pipe of the buildup.
  • the conventional in-bed heat transfer tube is designed to quickly transfer the heat of the fluid medium in the fluidized bed to the fluid (water can) in the heat transfer tube.
  • the in-layer heat transfer tube 5 of the present invention by providing the filling layer 7 between the water tube 6 and the protector 8, the surface temperature of the protector 8 is raised by gentle heat transfer. Thereby, it is possible to suppress the molten salt corrosion of the heat transfer tube, reduce the thickness reduction of the heat transfer tube, and extend the heat transfer tube life.
  • FIG. 5 is a front view of the in-layer heat transfer tube 5.
  • FIG. 5 shows a heat transfer tube group in which two in-layer heat transfer tubes 5 are arranged in parallel.
  • the in-layer heat transfer pipe 5 has a straight pipe portion and a bent pipe portion, and a large number of fins 9 are installed in the straight pipe portion.
  • FIG. 6 is a longitudinal sectional view of the in-layer heat transfer tube 5. Similar to the in-layer heat transfer tube 5 shown in FIG. 3, the in-layer heat transfer tube 5 shown in FIG.
  • the 6 includes fins 9 on the outer periphery of the protector 8 in addition to the water tube 6, the filling layer 7 and the protector 8.
  • the fins 9 are made of stainless steel plates such as SUS304, SUS316, and SUS310S, and are fixed to the upper and lower sides of the outer peripheral surface of the protector 8.
  • FIGS. 7A and 7B are views showing another form of the in-layer heat transfer tube 5, FIG. 7A is a front view of the in-layer heat transfer tube 5, and FIG. 7B is a longitudinal sectional view of the in-layer heat transfer tube 5.
  • spiral fins 34 are attached to the entire outer periphery of the protector 8 by welding. The spiral shape facilitates the attachment of the fins and significantly reduces the construction period.
  • FIGS. 8A and 8B show still another embodiment of the in-layer heat transfer tube 5, FIG. 8A is a front view of the in-layer heat transfer tube 5, and FIG. 8B is a longitudinal cross-sectional view of the in-layer heat transfer tube 5.
  • the in-layer heat transfer pipe 5 shown in FIGS. 8A and 8B is attached to the outer periphery of the protector 8 as a pin-shaped fin 35 instead of a plate (blade). A large number of pin-shaped fins 35 are welded to the outer peripheral surface of the protector 8.
  • the heat transfer coefficient per inner surface of the protector can be increased by the protector 8 including the fins 9, 34 or 35. . Therefore, the heat transfer coefficient between the fluid medium (sand) and the protector can be increased, and the surface temperature of the protector 8 can be increased to 450 ° C. or higher.
  • the water pipe 6, the packed bed 7 and the protector 8 in the in-layer heat transfer pipe 5 shown in FIGS. 5, 7A, 7B and 8A, 8B have the same configuration as the in-layer heat transfer pipe shown in FIG.
  • the present invention relates to an in-bed heat transfer pipe installed in a fluidized bed of a fluidized bed boiler that burns fuel such as biomass and plastic, high calorific value RDF (waste solidified fuel) and waste, and recovers combustion heat. It is available.
  • fuel such as biomass and plastic
  • RDF powder solidified fuel

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Geometry (AREA)
  • Combustion & Propulsion (AREA)
  • Environmental & Geological Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2013/052843 2012-02-13 2013-02-07 流動層ボイラの層内伝熱管 WO2013121965A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13749873.9A EP2821697B1 (en) 2012-02-13 2013-02-07 In-bed heat transfer tube for fluidized bed boiler
CN201380009114.6A CN104136842B (zh) 2012-02-13 2013-02-07 流动层锅炉的层内传热管
JP2013558659A JP6085570B2 (ja) 2012-02-13 2013-02-07 流動層ボイラの層内伝熱管
KR1020147024890A KR101998448B1 (ko) 2012-02-13 2013-02-07 유동층 보일러의 층 내 전열관

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JP2012028225 2012-02-13

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KR20180079724A (ko) * 2017-01-02 2018-07-11 현대건설주식회사 순환유동층 보일러 시스템
CN112166286A (zh) * 2018-05-21 2021-01-01 维美德技术有限公司 适用于流化床锅炉的同轴传热管及其制造方法

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EP3124862B1 (en) * 2015-07-28 2019-01-02 Ebara Environmental Plant Co., Ltd. Heat transfer tube for fluidized-bed boiler
JP6691834B2 (ja) * 2015-07-28 2020-05-13 荏原環境プラント株式会社 流動層ボイラの伝熱管
CN110017472B (zh) * 2019-03-20 2020-04-14 江苏能建机电实业集团有限公司 锅炉用防磨损装置
CN110017473B (zh) * 2019-03-20 2020-04-14 江苏能建机电实业集团有限公司 循环流化床锅炉膜式水冷壁防磨损装置
CN110425919B (zh) * 2019-07-12 2020-12-04 泰兴市梅兰化工有限公司 一种液氯汽化器
CN111964479A (zh) * 2020-08-20 2020-11-20 广东博盈特焊技术股份有限公司 耐高温腐蚀及耐冲蚀的蛇形管、蛇形管组及其制造方法

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CN112166286A (zh) * 2018-05-21 2021-01-01 维美德技术有限公司 适用于流化床锅炉的同轴传热管及其制造方法
CN112166286B (zh) * 2018-05-21 2022-10-11 维美德技术有限公司 适用于流化床锅炉的同轴传热管及其制造方法
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EP2821697A4 (en) 2016-03-09
JPWO2013121965A1 (ja) 2015-05-11
CN104136842B (zh) 2016-05-11
KR20140127861A (ko) 2014-11-04
EP2821697B1 (en) 2018-12-19
CN104136842A (zh) 2014-11-05
JP6085570B2 (ja) 2017-02-22
KR101998448B1 (ko) 2019-07-09
EP2821697A1 (en) 2015-01-07

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