WO2013121965A1 - In-bed heat transfer tube for fluidized bed boiler - Google Patents
In-bed heat transfer tube for fluidized bed boiler Download PDFInfo
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- 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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- WIPO (PCT)
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- heat transfer
- bed
- fluidized bed
- protector
- transfer tube
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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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
Abstract
Description
また、伝熱管をスタッドと耐火物で覆うことにより伝熱管の減肉を低減するようにした伝熱管の耐摩耗構造が特開平5-187789号公報(特許文献1)に開示されている。しかしながら、特許文献1に開示された構造は、伝熱管を耐火物で覆うことにより、熱伝達率が下がり、伝熱面積が多く必要になる。また、伝熱管と耐火物により径が太くなり伝熱管を配置しづらいという欠点がある。
一方、特開平7-217801号公報(特許文献2)では、伝熱管の摩耗による減肉を防止する方法として、プロテクタを取り付ける方法や肉盛りや溶射する方法が提案されているが、プロテクタを取り付けると伝熱が大幅に阻害されるという問題があり、また肉盛りや溶射はコストが高いという問題があった(段落〔0004〕参照)と記載して従来の減肉対策の問題点を指摘し、伝熱管自体を耐摩耗性に優れた高クロム鋼又はステンレス鋼とすることを提案している。しかしながら、特許文献2に記載された方法では、摩耗による減肉は防止できるが、摩耗と同時に溶融塩腐食を直接受ける環境においては、耐久性に劣るという問題点がある。 In the past, measures to reduce the thickness of the heat transfer tube installed in the fluidized bed were carried out by thermal spraying of a self-fluxing alloy (Ni-based) or overlaying a stainless steel material, but sufficient effects can be obtained. It was not done.
Japanese Patent Application Laid-Open No. 5-187789 (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
On the other hand, in JP-A-7-217801 (Patent Document 2), 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. And the problem that heat transfer is significantly impeded, and that there was a problem that build-up and thermal spraying were expensive (see paragraph [0004]), and pointed out the problems with conventional thinning measures. It has been proposed that the heat transfer tube itself be made of high chromium steel or stainless steel excellent in wear resistance. However, although the method described in
本発明によれば、流動媒体の熱は、プロテクタおよび充填層を介して水管に伝達され、水管内の流体が加熱される。水管とプロテクタとの間に介在する充填層を低い熱伝導率とすることにより、プロテクタと水管の間の熱伝達率を下げることができる。したがって、プロテクタ表面と水管表面の間の温度差を大きくすることができる。これにより、伝熱管の溶融塩腐食を抑えて減肉量が少なく、耐久性に優れた層内伝熱管とすることができる。 In order to achieve the above object, 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.
According to the invention, 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.
本発明によれば、充填層の空隙は低い熱伝導率を有した空気からなるため、プロテクタと水管の間の熱伝達率を下げることができる。この場合、熱伝達率を下げすぎると非効率になるので、プロテクタの表面温度が450~650℃、好ましくは、480~620℃になるように、充填層の充填材の材質、形状および厚さを適宜選定する。 According to a preferred embodiment of the present invention, the packed bed is formed by packing a solid particle filler.
According to the present invention, since 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. In this case, 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.
本発明によれば、上記範囲の充填率を採用することにより、プロテクタが熱膨張した際、充填材の重力沈降によって充填層の表面(上面)とプロテクタの内面との間に形成される隙間、すなわち空気層の厚みを小さくし、水管への熱伝達を確保することができる。 According to a preferred aspect of the present invention, 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. Here, 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.
According to the present invention, when the protector is thermally expanded, a gap formed between the surface (upper surface) of the packed bed and the inner surface of the protector by gravity settling of the filler by adopting the filling rate in the above range. That is, the thickness of the air layer can be reduced to ensure heat transfer to the water pipe.
本発明によれば、充填層の熱伝導率が0.4~1.4W/mKであるため、プロテクタと水管の間の熱伝達率を下げることができる。したがって、プロテクタ表面と水管表面の間の温度差を大きくすることができ、プロテクタの表面温度を450~650℃の高温に保つことができる。
本発明の好ましい態様によれば、前記充填層の厚みは、2~4mmであることを特徴とする。 According to a preferred embodiment of the present invention, the packed bed has a thermal conductivity of 0.4 to 1.4 W / mK.
According to the present invention, since 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.
According to a preferred embodiment of the present invention, the thickness of the filler layer is 2 to 4 mm.
本発明の好ましい態様によれば、前記ステンレス鋼は、SUS304またはSUS316またはSUS310Sであることを特徴とする。
本発明によれば、プロテクタをSUS304,SUS316,SUS310S等のステンレス鋼で構成することにより、溶融塩腐食による減肉を抑制することができる。 According to a preferred aspect of the present invention, the protector is made of stainless steel.
According to a preferred embodiment of the present invention, 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.
本発明によれば、プロテクタの外面に熱交換効率が優れたフィンを設けたため、流動媒体からプロテクタへの熱伝達率を高めることができる。したがって、経済的な熱伝達量を確保することができる。
本発明の好ましい態様によれば、前記フィンは螺旋状のフィンであることを特徴とする。
本発明の好ましい態様によれば、前記フィンはピン形状のフィンであることを特徴とする。 According to a preferred aspect of the present invention, the protector is provided with fins on the outer surface.
According to the present invention, since 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.
According to a preferred aspect of the present invention, the fin is a spiral fin.
According to a preferred aspect of the present invention, the fin is a pin-shaped fin.
本発明によれば、燃料のカロリー等に応じて、流動層に供給する流動化空気の空気量を調節することにより、流動層の温度を700~900℃に制御する。そして、700~900℃に維持された流動層の熱をプロテクタおよび充填層を介して水管に伝達し、水管内の飽和水を加熱する。水管とプロテクタとの間に介在する充填層により、プロテクタと水管の間の熱伝達率を下げることができる。したがって、プロテクタ表面と水管表面の間の温度差を大きくすることができ、プロテクタの表面温度を450~650℃の高温に保つことができる。 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
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.
本発明によれば、層内伝熱管が配置される流動層(移動層)の流動化条件をu0/umf=2.0~4.0にすることにより、流動層(移動層)の流動化を活発にして流動媒体からプロテクタへの熱伝達率を高くすることができる。これにより、プロテクタと水管との間に充填層が介在した層内伝熱管であっても、総括熱伝達率および総熱通過量を肉盛の層内伝熱管と同程度に保つことができる。したがって、経済的な熱伝達量を確保することができる。 According to a preferred aspect of the present invention, the air amount of the fluidizing air of the portion provided with the in-bed heat transfer pipe of the fluidized bed is u 0 / u mf = 2.0 to 4.0.
According to the present invention, by setting the fluidization condition of the fluidized bed (moving bed) in which the in-bed heat transfer pipe is arranged to u 0 / u mf = 2.0 to 4.0, Fluidization can be activated to increase the heat transfer coefficient from the fluid medium to the protector. As a result, even in the case of an in-layer heat transfer tube in which the packed bed is interposed between the protector and the water tube, the overall heat transfer coefficient and the total heat passing amount can be maintained to be similar to the in-layer heat transfer tube. Therefore, economical heat transfer can be secured.
本発明によれば、燃料を燃焼する燃焼室と、熱回収をする熱回収室とが分離されているため、燃料中の不燃物が層内伝熱管に絡まる等のトラブルが生ずることがない。また、熱回収室における流動化空気の空気量を制御することにより、層内伝熱管の熱回収量を制御することができる。 According to a preferred aspect of the present invention, 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 internal circulation fluidized bed boiler is characterized in that the air amount of the liquefaction air is set to u 0 / u mf = 2.0 to 4.0 and the fluidizing medium circulates between the combustion chamber and the heat recovery chamber.
According to the present invention, since 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. In addition, by controlling 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.
(1)層内伝熱管を水管と充填材とプロテクタで構成し、水管とプロテクタとの間に介在する充填層を設置することにより、プロテクタと水管の間の熱伝達率を下げることができる。したがって、プロテクタ表面と水管表面の間の温度差を大きくすることができ、プロテクタの表面温度を450~650℃の高温に保つことができる。これにより、伝熱管の溶融塩腐食を抑えて減肉量が少なく、耐久性に優れた層内伝熱管を提供できる。
(2)プロテクタをSUS304,SUS316,SUS310S等のステンレス鋼で構成することにより、溶融塩腐食による減肉を抑制することができる。
(3)層内伝熱管が配置される流動層(移動層)の流動化条件をu0/umf=2.0~4.0にすることにより、流動層(移動層)の流動化を活発にして流動媒体からプロテクタへの熱伝達率を高くしている。これにより、プロテクタと水管との間に充填層が介在した層内伝熱管であっても、総括熱伝達率および総熱通過量を肉盛の層内伝熱管と同程度に保つことができる。したがって、経済的な熱伝達量を確保することができる。
(4)プロテクタの外面に熱交換効率が優れたフィンを設けたため、流動媒体からプロテクタへの熱伝達率を高めることができる。したがって、経済的な熱伝達量を確保することができる。 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.
(2) 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.
(3) Fluidization of the fluidized bed (moving bed) is achieved by setting the fluidization conditions of the fluidized bed (moving bed) in which the heat transfer pipes in the bed are arranged to u 0 / u mf = 2.0 to 4.0. Actively increases the heat transfer coefficient from the fluid medium to the protector. As a result, even in the case of an in-layer heat transfer tube in which the packed bed is interposed between the protector and the water tube, the overall heat transfer coefficient and the total heat passing amount can be maintained to be similar to the in-layer heat transfer tube. Therefore, economical heat transfer can be secured.
(4) Since the fin which was excellent in heat exchange efficiency was provided in the outer surface of a protector, the heat transfer coefficient from a fluid medium to a protector can be raised. Therefore, economical heat transfer can be secured.
図1は、本発明に係る層内伝熱管を備えた流動層ボイラの一実施形態を示す模式的断面図である。図1に示すように、流動層ボイラ1は、略円筒形状又は略四角筒形状の炉本体2と、廃棄物やRDF等の燃料を燃焼させる流動層3と、流動層3を支える炉床底板4とを備え、流動層3内には層内伝熱管5が設置されている。流動層3内には、層内伝熱管5を埋めるように珪砂等の流動砂である流動媒体が充填されている。炉床底板4には、流動化ガスとしての流動化空気を炉内に噴出するための多数の散気ノズルが形成されている。 Hereinafter, an embodiment of the in-bed heat transfer tube of the fluidized bed boiler according to the present invention will be described with reference to FIGS. 1 to 8. In FIG. 1 to FIG. 8, the same or corresponding components are given the same reference numerals, and duplicate explanations are omitted.
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. As shown in FIG. 1, the
図3は、層内伝熱管5の模式的断面図である。図3に示すように、層内伝熱管5は、内部に流体(缶水)が流れる水管6と、水管6の外周側に設けられ水管6を保護するプロテクタ8と、水管6とプロテクタ8との間に設けられる充填層7とから構成されている。水管6は、厚さ4~8mmのボイラ・熱交換器用鋼管、例えばSTB410Sから構成されており、水管6内を流れる流体(缶水)は2MPa~12MPaの飽和水である。充填層7は、砂、ステンレス粉、酸化マグネシウム、鉄、アルミナ等の固体粒子の充填材を充填させたものであり、厚さ2~4mmの円筒状に形成されている。充填層の熱伝導率は、例えば「粉体の反応、日刊工業新聞社、p.54-57」に示される計算により算出され、0.4~1.4W/mKとなるようにしている。充填層の熱伝導率がこの範囲内で充填して使用できるものであれば、上記で列挙した以外の種類・材質の充填材を用いることができる。
充填材は、粉粒状が好ましい。また、充填材の充填率は0.5以上0.9以下が好ましく、より好ましくは0.6以上0.8以下である。ここで、水管6とプロテクタ8の間の空隙に充填材を充填する際の充填率とは、次式による。
充填率[-]=充填物が占める体積[m3]/水管外面とプロテクタ内面の空隙の体積[m3]
上記範囲の充填材の充填率を採用することによって、プロテクタが熱膨張した際、充填材の重力沈降によって充填層の表面(上面)とプロテクタの内面との間に形成される隙間、すなわち空気層の厚みを小さくし、水管への熱伝達を確保することができる。 Next, the in-bed
FIG. 3 is a schematic cross-sectional view of the in-layer
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. Here, the filling factor at the time of filling the filler in the space between the
Packing ratio [-] = volume occupied by filling [m 3 ] / volume of void in water tube outer surface and protector inner surface [m 3 ]
A gap formed between the surface (upper surface) of the packed bed and the inner surface of the protector by gravity settling of the filler when the protector is thermally expanded by employing the filling factor of the filler in the above range, that is, the air layer Can be reduced in thickness to ensure heat transfer to the water pipe.
本発明は、(1)~(3)の構成を採用することにより、プロテクタ8の表面温度が450~650℃、好ましくは480~620℃の高温に保たれる。 In the present invention, (1) the material of the
In the present invention, the surface temperature of the
従来の層内伝熱管は、水管の表面改質にステンレス材による3mmの肉盛を採用したものを用いている。図4Aに示すように、流動層の温度を800℃および缶水の温度を300℃とし、流動層に供給する流動化空気の空気量をu0/umf=1.5とした場合、流動媒体(砂)から肉盛への熱伝達率は210W/m2K、肉盛の表面温度は320℃、肉盛内面基準(水管外表面基準)で総括熱伝達率は222W/m2K、総熱通過量は111118W/m2である。なお、肉盛の表面温度と水管の表面温度との温度差は20℃である。 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. and the temperature of the can water is 300 ° C., and the amount of air in the fluidizing air supplied to the fluidized bed is u 0 / u mf = 1.5, the flow heat transfer rate from the medium (sand) into the cladding is 210W / m 2 K, the surface temperature of the deposition is 320 ° C., overall heat transfer coefficient in the cladding inner surface reference (water pipe outer surface reference) is 222W / m 2 K, The total heat passing rate is 111118 W / m 2 . The temperature difference between the surface temperature of the overlay and the surface temperature of the water pipe is 20 ° C.
ちなみに水管外表面基準では総括熱伝達率は263W/m2K、総熱通過量は131586W/m2である。 On the other hand, 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. and the temperature of the can water is 300 ° C., and the amount of air of fluidizing air supplied to the fluidized bed is u 0 / u mf = 2.5, the flow 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 (
Incidentally, 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.
図5は、層内伝熱管5の正面図である。図5においては、2本の層内伝熱管5が並列して配置された伝熱管群が示されている。層内伝熱管5は直管部と曲がり管部とを有し、直管部には多数のフィン9が設置されている。
図6は、層内伝熱管5の縦断面図である。図6に示す層内伝熱管5は、図3に示す層内伝熱管5と同様に、水管6、充填層7、プロテクタ8から構成されることに加えて、プロテクタ8の外周にフィン9を備えている。フィン9は、SUS304,SUS316,SUS310S等のステンレス鋼板からなり、プロテクタ8の外周面の上下に固定されている。 Next, an example of the detailed structure of the in-bed heat transfer pipe used in the fluidized bed boiler shown in FIGS. 1 and 2 will be described with reference to FIGS. 5 and 6.
FIG. 5 is a front view of the in-layer
FIG. 6 is a longitudinal sectional view of the in-layer
2 炉本体
3 流動層
4 炉床底板
5 層内伝熱管
6 水管
7 充填層
8 プロテクタ
9,34,35 フィン
11 流動層ボイラ
12 炉本体
13 仕切壁
14 燃焼室
15 熱回収室
17 不燃物排出口
18 開口部
20 流動床
21 移動層
22 流動層
23 流動床
30 炉床底板
31 炉床底板
32,32,33,33 空気箱
Claims (14)
- 流動層ボイラの流動層内に配置される層内伝熱管において、
前記層内伝熱管は、内部を流体が流れる水管と、前記水管の外周側に設けられ前記水管を保護するためのプロテクタと、前記水管と前記プロテクタの間に設けられる充填層とから構成されることを特徴とする流動層ボイラの層内伝熱管。 In the in-bed heat transfer pipe disposed in the fluidized bed of the fluidized bed boiler,
The in-layer heat transfer pipe is composed of a water pipe through which the fluid flows, 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. An in-bed heat transfer tube of a fluidized bed boiler characterized in that - 前記プロテクタの表面温度が450~650℃に保たれることを特徴とする請求項1記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to claim 1, wherein the surface temperature of the protector is maintained at 450 to 650 属 C.
- 前記充填層は、固体粒子の充填材を充填して形成されることを特徴とする請求項1記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to claim 1, wherein the packed bed is formed by packing a solid particle filler.
- 前記充填層は、固体粒子の充填材の充填率が0.5以上0.9以下であることを特徴とする請求項3記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer pipe of a fluidized bed boiler according to claim 3, wherein the filling rate of the solid particle filling material is 0.5 or more and 0.9 or less.
- 前記充填層は、熱伝導率が0.4~1.4W/mKであることを特徴とする請求項1記載の流動層ボイラの層内伝熱管。 The in-layer heat transfer tube according to claim 1, wherein the packed bed has a thermal conductivity of 0.4 to 1.4 W / mK.
- 前記充填層の厚みは、2~4mmであることを特徴とする請求項5記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to claim 5, wherein the thickness of the packed bed is 2 to 4 mm.
- 前記プロテクタは、ステンレス鋼からなることを特徴とする請求項1記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to claim 1, wherein the protector is made of stainless steel.
- 前記ステンレス鋼は、SUS304またはSUS316またはSUS310Sであることを特徴とする請求項7記載の流動層ボイラの層内伝熱管。 The in-layer heat transfer tube according to claim 7, wherein the stainless steel is SUS304 or SUS316 or SUS310S.
- 前記プロテクタは、外面にフィンを備えることを特徴とする請求項1乃至8のいずれか1項に記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to any one of claims 1 to 8, wherein the protector comprises fins on an outer surface.
- 前記フィンは螺旋状のフィンであることを特徴とする請求項9記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to claim 9, wherein the fin is a spiral fin.
- 前記フィンはピン形状のフィンであることを特徴とする請求項9記載の流動層ボイラの層内伝熱管。 The in-bed heat transfer tube according to claim 9, wherein the fins are pin-shaped fins.
- 燃料を流動層内で燃焼させ、燃焼熱を層内伝熱管で回収する流動層ボイラにおいて、
前記層内伝熱管は、請求項1乃至11のいずれか1項に記載の層内伝熱管であり、
前記流動層の温度を700~900℃に制御することを特徴とする流動層ボイラ。 In a fluidized bed boiler in which fuel is burned in a fluidized bed and heat of combustion is recovered by a heat transfer pipe in the bed,
The in-layer heat transfer pipe is the in-layer heat transfer pipe according to any one of claims 1 to 11,
A fluidized bed boiler characterized in that the temperature of the fluidized bed is controlled to 700 to 900 ° C. - 前記流動層の層内伝熱管が設けられる部分の流動化空気の空気量をu0/umf=2.0~4.0にしたことを特徴とする請求項12記載の流動層ボイラ。 The fluidized bed boiler according to claim 12, wherein an amount of air of fluidizing air in a portion provided with an in-bed heat transfer pipe of the fluidized bed is set to u 0 / u mf = 2.0 to 4.0.
- 前記流動層ボイラは、燃料を燃焼させるための燃焼室と、前記層内伝熱管が配置され燃焼熱を回収する熱回収室とを備え、熱回収室の流動化空気の空気量をu0/umf=2.0~4.0にして流動媒体が前記燃焼室と前記熱回収室とを循環する内部循環流動層ボイラであることを特徴とする請求項12記載の流動層ボイラ。 The fluidized bed boiler includes a combustion chamber for burning fuel and a heat recovery chamber in which the heat transfer pipe in the layer is disposed to recover combustion heat, and the air amount of the fluidizing air of the heat recovery chamber is u 0 / The fluidized bed boiler according to claim 12, characterized in that it is an internal circulating fluidized bed boiler in which the flow medium circulates between the combustion chamber and the heat recovery chamber with u mf = 2.0 to 4.0.
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JP2013558659A JP6085570B2 (en) | 2012-02-13 | 2013-02-07 | Heat transfer tube in a fluidized bed boiler |
CN201380009114.6A CN104136842B (en) | 2012-02-13 | 2013-02-07 | Heat-transfer pipe in the layer of fluidized bed boiler |
KR1020147024890A KR101998448B1 (en) | 2012-02-13 | 2013-02-07 | Immersed heat transfer tube for fluidized-bed boiler |
EP13749873.9A EP2821697B1 (en) | 2012-02-13 | 2013-02-07 | In-bed heat transfer tube for fluidized bed boiler |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20180079724A (en) * | 2017-01-02 | 2018-07-11 | 현대건설주식회사 | Circulating fluidized bed boiler system |
CN112166286A (en) * | 2018-05-21 | 2021-01-01 | 维美德技术有限公司 | Coaxial heat transfer tube suitable for fluidized bed boiler and manufacturing method thereof |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3124862B1 (en) * | 2015-07-28 | 2019-01-02 | Ebara Environmental Plant Co., Ltd. | Heat transfer tube for fluidized-bed boiler |
JP6691834B2 (en) * | 2015-07-28 | 2020-05-13 | 荏原環境プラント株式会社 | Heat transfer tube of fluidized bed boiler |
CN110017473B (en) * | 2019-03-20 | 2020-04-14 | 江苏能建机电实业集团有限公司 | Anti-abrasion device for membrane water wall of circulating fluidized bed boiler |
CN110017472B (en) * | 2019-03-20 | 2020-04-14 | 江苏能建机电实业集团有限公司 | Anti-wear device for boiler |
CN110425919B (en) * | 2019-07-12 | 2020-12-04 | 泰兴市梅兰化工有限公司 | Liquid chlorine vaporizer |
CN111964479A (en) * | 2020-08-20 | 2020-11-20 | 广东博盈特焊技术股份有限公司 | High-temperature corrosion-resistant and erosion-resistant coiled pipe, coiled pipe group and manufacturing method thereof |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6196106U (en) * | 1984-11-27 | 1986-06-20 | ||
JPS61115804U (en) * | 1985-01-07 | 1986-07-22 | ||
JPS61121306U (en) * | 1985-01-11 | 1986-07-31 | ||
JPH05187789A (en) | 1992-01-14 | 1993-07-27 | Mitsubishi Heavy Ind Ltd | Wear resistant structure for heat transfer tube |
JPH07217801A (en) | 1994-02-08 | 1995-08-18 | Babcock Hitachi Kk | Heat transfer tube for fluidized-bed boiler |
JP2000266314A (en) * | 1999-03-15 | 2000-09-29 | Babcock Hitachi Kk | Fluidized-bed boiler |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ATE61651T1 (en) * | 1986-06-16 | 1991-03-15 | Lorraine Carbone | THERMAL COMPOUND WITH STRONG TRANSFER COEFFICIENT AND USES TO COOL DOWN AN ARRANGEMENT SUBJECT TO INTENSE THERMAL FLOW. |
DE68925033T2 (en) * | 1988-08-31 | 1996-05-15 | Ebara Corp | FLUID BED FABRIC WITH A COMPOSITE CIRCUIT. |
CA2116745C (en) * | 1993-03-03 | 2007-05-15 | Shuichi Nagato | Pressurized internal circulating fluidized-bed boiler |
TW270970B (en) * | 1995-04-26 | 1996-02-21 | Ehara Seisakusho Kk | Fluidized bed combustion device |
FI122481B (en) * | 2004-12-29 | 2012-02-15 | Metso Power Oy | Superheater design |
-
2013
- 2013-02-07 KR KR1020147024890A patent/KR101998448B1/en active IP Right Grant
- 2013-02-07 JP JP2013558659A patent/JP6085570B2/en active Active
- 2013-02-07 CN CN201380009114.6A patent/CN104136842B/en active Active
- 2013-02-07 WO PCT/JP2013/052843 patent/WO2013121965A1/en active Application Filing
- 2013-02-07 EP EP13749873.9A patent/EP2821697B1/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6196106U (en) * | 1984-11-27 | 1986-06-20 | ||
JPS61115804U (en) * | 1985-01-07 | 1986-07-22 | ||
JPS61121306U (en) * | 1985-01-11 | 1986-07-31 | ||
JPH05187789A (en) | 1992-01-14 | 1993-07-27 | Mitsubishi Heavy Ind Ltd | Wear resistant structure for heat transfer tube |
JPH07217801A (en) | 1994-02-08 | 1995-08-18 | Babcock Hitachi Kk | Heat transfer tube for fluidized-bed boiler |
JP2000266314A (en) * | 1999-03-15 | 2000-09-29 | Babcock Hitachi Kk | Fluidized-bed boiler |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20180079724A (en) * | 2017-01-02 | 2018-07-11 | 현대건설주식회사 | Circulating fluidized bed boiler system |
KR101895382B1 (en) | 2017-01-02 | 2018-09-05 | 현대건설 주식회사 | Circulating fluidized bed boiler system |
CN112166286A (en) * | 2018-05-21 | 2021-01-01 | 维美德技术有限公司 | Coaxial heat transfer tube suitable for fluidized bed boiler and manufacturing method thereof |
CN112166286B (en) * | 2018-05-21 | 2022-10-11 | 维美德技术有限公司 | Coaxial heat transfer tube suitable for fluidized bed boiler and manufacturing method thereof |
US11859911B2 (en) | 2018-05-21 | 2024-01-02 | Valmet Technologies Oy | Coaxial heat transfer tube suitable for a fluidized bed boiler and a method for manufacturing same |
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CN104136842B (en) | 2016-05-11 |
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