EP2821697B1 - In-bed heat transfer tube for fluidized bed boiler - Google Patents

In-bed heat transfer tube for fluidized bed boiler Download PDF

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Publication number
EP2821697B1
EP2821697B1 EP13749873.9A EP13749873A EP2821697B1 EP 2821697 B1 EP2821697 B1 EP 2821697B1 EP 13749873 A EP13749873 A EP 13749873A EP 2821697 B1 EP2821697 B1 EP 2821697B1
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EP
European Patent Office
Prior art keywords
heat transfer
fluidized
bed
transfer tube
protector
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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EP13749873.9A
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German (de)
English (en)
French (fr)
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EP2821697A4 (en
EP2821697A1 (en
Inventor
Hiroshi Yoshida
Hideyuki Sakamoto
Yasuhisa Honda
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Ebara Environmental Plant Co Ltd
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Ebara Environmental Plant Co Ltd
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Publication of EP2821697A4 publication Critical patent/EP2821697A4/en
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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 immersed heat transfer tubes installed in a fluidized bed in a fluidized-bed boiler for recovering combustion heat generated when a fuel such as RDF (refuse derived fuel) with high calorific value containing biomass and plastics, or wastes, etc. is combusted.
  • a fuel such as RDF (refuse derived fuel) with high calorific value containing biomass and plastics, or wastes, etc.
  • Patent document 1 JP 5-187789 A discloses a wear-resistant structure of heat transfer tubes in which heat transfer tubes are covered with studs and a refractory material to control tube thickness reduction.
  • Patent document 1 results in a reduced heat transfer rate and requires an increased heat transfer area because the heat transfer tubes are covered with the refractory material.
  • Another drawback is that the heat transfer tubes covered with the refractory material increase the diameter of heat transfer tubes, making it difficult to lay out the heat transfer tubes.
  • Patent document 2 proposes a method for attaching protectors or a method for weld overlay or thermal spray, as a method for preventing heat transfer tubes from causing tube thickness reduction due to wear, and points out the problems of the conventional measures against tube thickness reduction by stating that attachment of the protectors greatly reduces heat transfer and the cost of weld overlay and thermal spray are high (see paragraph [0004]).
  • Patent document 2 proposes that heat transfer tubes be made of wear-resistant high-chromium steel or stainless steel.
  • the method disclosed in Patent document 2 is effective to prevent the tube thickness reduction due to wear, the heat transfer tubes have poor durability in an environment where they are directly subject to wear and corrosive attack by molten salt at the same time.
  • WO 2006 070 075 A2 relates to a structure of a superheater.
  • the superheater comprises a superheater piping, which comprises a steam pipe, where the steam to be superheated is directed to.
  • the steam pipe is separated by a protective shell, whose surface settling in the flue gas space has a temperature that rises above an upper critical temperature, above which temperature in the flue gas space the compounds from the fuel are substantially in a gaseous form.
  • a superhater for a circulating fluidized bed boiler is also disclosed.
  • JP S61 121 306 U discloses a protector arrangement for a heat exchanger tube which is filled up with ceramic powder or metal powder which is plated with a nickel boron alloy in the gap between a heat exchanger tube and a protector in the heat exchanger tube.
  • the present inventors have gotten the following knowledge from the continuous operation of the fluidized-bed boiler over a long period of time by using various immersed heat transfer tubes. Specifically, in the case where chloride is contained in a fuel such as biomass-based RDF or wastes, part of the chloride moves to the fluidizing particles (fluidizing sand) after combustion, and then the chloride in the fluidizing particles forms an eutectic salt with alkali metals (Na, K, etc.) contained in the fuel while the fluidized bed is operated at a temperature ranging from 700 to 850°C. The eutectic salt in its molten state is condensed at a temperature of 650 to 700°C, for example.
  • a fuel such as biomass-based RDF or wastes
  • the eutectic salt is prevented from being condensed on the surface of the immersed heat transfer tubes, so that tube thickness reduction due to corrosive attack by molten salt can be reduced.
  • the present inventors have found that the tube thickness reduction due to corrosive attack by molten salt can be reduced when the surface temperature of the immersed heat transfer tubes whose durability is increased by providing protectors made of stainless steel such as SUS310S and disposed around the outer circumferential surfaces of water tubes is lower than the above-described condensing temperature and exceeds a predetermined temperature (e.g., 450°C).
  • the present inventors have conceived that (1) increasing the heat transfer rate between the fluidized bed and the protectors and (2) lowering the heat transfer rate between the protectors and the water tubes are effective in order to adjust the surface temperature of the protectors to a temperature range for suppressing the corrosive attack by molten salt and controlling the tube thickness reduction.
  • an object of the present invention to provide an immersed heat transfer tubes for a fluidized-bed boiler which suppresses corrosive attack by molten salt, controls tube thickness reduction, and has a good durability by lowering heat transfer rate between protectors and water tubes while ensuring an economically sufficient heat transfer amount by all the immersed heat transfer tubes.
  • an immersible heat transfer tube for a fluidized-bed boiler as set forth in claim 1. Further embodiments are inter alia disclosed in the dependent claims.
  • the heat transfer tube is suitable for being installed in a fluidized bed, and inter alia comprises: a water tube through which a fluid may flow; a protector provided at an outer circumferential side of the water tube and configured to protect the water tube; and a packed bed provided between the water tube and the protector.
  • the heat of the fluidizing particles is transferred to the water tube through the protector and the packed bed, thus heating the fluid in the water tube. Since the packed bed interposed between the water tube and the protector has a low heat conductivity, the heat transfer rate between the protector and the water tube can be lowered. Therefore, the temperature difference between the surface of the protector and the surface of the water tube can be increased. Thus, the corrosive attack by molten salt can be suppressed to decrease the tube thickness reduction, and durability of the immersed heat transfer tube can be increased.
  • a surface temperature of the protector is kept in the range of 450 to 650°C.
  • the packed bed is formed by filling solid particles.
  • a void of the packed bed comprises air having a low heat conductivity
  • the heat transfer rate between the protector and the water tube can be lowered.
  • the material, shape of solid particles, and thickness of the packed bed are suitably selected to keep the surface temperature of the protector in the range of 450 to 650°C, preferably in the range of 480 to 620°C.
  • the packed bed has a packing ratio of solid particles which is in the range of 0.5 to 0.9.
  • the packing ratio is defined as a value obtained by dividing the volume [m 3 ] occupied by the packing material by the volume [m 3 ] of the gap between the outer surface of the water tube and the inner surface of the protector.
  • the packing ratio of the packing material within the above range, when the protector is thermally expanded, the space formed between the surface (upper surface) of the packed bed and the inner surface of the protector by the gravitational sedimentation of the packing material, i.e., a thickness of air layer is reduced, thereby ensuring heat transfer to the water tube.
  • the packed bed has a heat conductivity ranging from 0.4 to 1.4 W/mK.
  • the heat conductivity of the packed bed is in the range of 0.4 to 1.4 W/mK
  • the heat transfer rate between the protector and the water tube can be lowered. Therefore, the temperature difference between the surface of the protector and the surface of the water tube can be increased, and thus the surface temperature of the protector can be kept in the range of 450 to 650°C.
  • a thickness of the packed bed is in the range of 2 to 4 mm.
  • the protector is made of stainless steel.
  • the stainless steel comprises SUS304 or SUS316 or SUS310S.
  • the protector is made of stainless steel comprising SUS304, SUS316, SUS310S, or the like, the tube thickness reduction due to corrosive attack by molten salt can be suppressed.
  • the protector has a fin on an outer surface thereof.
  • the protector since the protector has a fin having excellent heat exchange performance on an outer surface thereof, the heat transfer rate from the fluidizing particles to the protector can be increased. Therefore, a sufficient heat transfer amount can be obtained.
  • the fin comprises a helical fin.
  • the fin comprises a pin fin.
  • a fluidized-bed boiler configured to combust a fuel in a fluidized bed and to recover combustion heat by an immersed heat transfer tube
  • the fluidized-bed boiler comprising: an immersed heat transfer tube according to any one of claims 1 to 11; wherein a fluidized-bed temperature is controlled in the range of 700 to 900°C.
  • the amount of the fluidizing air supplied to the fluidized bed is adjusted depending on the calorific value of the fuel or the like, and thus the temperature of the fluidized bed is controlled in the range of 700 to 900°C.
  • the amount of the heat held by the fluidized bed which is kept in the range of 700 to 900°C is transferred to the water tube through the protector and the packed bed, thus heating saturated water in the water tube.
  • the packed bed that is interposed between the water tube and the protector can reduce the heat transfer rate between the protector and the water tube. 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 kept in the range of 450 to 650°C.
  • an amount of a fluidizing air in an area of the fluidized bed where the immersed heat transfer tube is provided is set so that u o /u mf is in the range of 2.0 to 4.0.
  • the fluidizing condition for the fluidized bed (moving bed) in which the immersed heat transfer tube is installed is set so that u o /u mf is in the range of 2.0 to 4.0, the fluidization of the fluidized bed (moving bed) becomes vigorous to increase the heat transfer rate from the fluidizing particles to the protector.
  • u o /u mf is in the range of 2.0 to 4.0
  • the fluidized-bed boiler comprises an internally circulating fluidized-bed boiler which comprises a combustion chamber configured to combust the fuel therein, and a heat recovery chamber having the immersed heat transfer tube therein and configured to recover the combustion heat; and an amount of a fluidizing air in the heat recovery chamber is set so that u o /u mf is in the range of 2.0 to 4.0 to circulate fluidizing particles between the combustion chamber and the heat recovery chamber.
  • the combustion chamber for combusting the fuel and the heat recovery chamber for recovering the heat are separated from each other, a trouble caused by incombustibles in the fuel which twine around the immersed heat transfer tube does not occur. Further, by regulating the amount of the fluidizing air in the heat recovery chamber, the amount of heat recovered by the immersed heat transfer tube can be controlled.
  • FIGS. 1 through 8B Immersed heat transfer tubes for a fluidized-bed boiler according to embodiments of the present invention will be described below with reference to FIGS. 1 through 8B .
  • identical or corresponding parts are denoted by identical reference numerals, and will not be described in duplication.
  • FIG. 1 is a schematic cross-sectional view showing a fluidized-bed boiler having immersed heat transfer tubes according to an embodiment of the present invention.
  • the fluidized-bed boiler 1 comprises a furnace 2 having a substantially cylindrical shape or substantially square tubular shape, a fluidized bed 3 for combusting a fuel such as wastes or RDF, etc., and a hearth plate (furnace bottom plate) 4 for supporting the fluidized bed 3 thereon.
  • Immersed heat transfer tubes 5 are disposed in the fluidized bed 3.
  • the fluidized bed 3 is filled with fluidizing particles such as silica sand, so that the immersed heat transfer tubes 5 are embedded in the fluidizing particles.
  • the hearth plate 4 has a number of gas diffusion nozzles for ejecting air as a fluidizing gas into the furnace 2.
  • the fuel is supplied from a supply port (not shown) to the fluidized bed 3.
  • the fluidizing air is ejected at a uniform flow rate into the entire fluidized bed 3, and thus the fluidized bed 3 becomes a so-called bubbling-type fluidized bed wherein the fluidizing particles are fluidized vigorously up and down.
  • the fuel supplied into the furnace is pyrolyzed and combusted in the fluidized bed 3, and the fluidizing particles are heated to a high temperature by combustion heat, thus keeping the fluidized bed 3 at a temperature ranging from 700 to 900°C.
  • the temperature of the fluidized bed 3 is controlled by regulating an amount of the fluidizing air.
  • the fluidizing particles that have been heated to the high temperature are brought into contact with the immersed heat transfer tubes 5, and a fluid (boiler water) in the immersed heat transfer tubes 5 recovers heat from the fluidizing particles by heat exchange with the fluidizing particles.
  • FIG. 2 is a schematic cross-sectional view showing a fluidized-bed boiler having immersed heat transfer tubes according to another embodiment of the present invention.
  • the fluidized-bed boiler 11 comprises a furnace 12 having a substantially square tubular shape, and the interior of the furnace 12 is divided by a pair of right and left partition walls 13, 13 into one central combustion chamber 14 and two heat recovery chambers 15, 15 on both sides of the combustion chamber 14.
  • a fluidized bed 20 for reacting thermally a fuel such as wastes or RDF, etc. is formed in the combustion chamber 14.
  • the fluidized bed 20 is supported by a hearth plate 30.
  • the hearth plate 30 installed in the furnace 12 has a chevron shape which is the highest at its center and is gradually lowered toward the opposite side edges.
  • the hearth plate 30 has a number of gas diffusion nozzles for ejecting air as a fluidizing gas into the furnace.
  • Fluidized beds 23 are formed in the respective heat recovery chambers 15 and supported by hearth plates 31.
  • Each of the hearth plates 31 has a number of gas diffusion nozzles for ejecting air as a fluidizing gas into the furnace.
  • air chambers 32, 32, 33, 33 are formed below the chevron-shaped hearth plate 30. These air chambers 32, 32, 33, 33 are supplied with fluidizing air from outside of the furnace 2.
  • the opening degrees of regulating valves (not shown) to control the flow rates of air supplied to the air chambers 32, 32, 33, 33, the fluidizing air is ejected from the air diffusion nozzles above the two central air chambers 32, 32 so as to give a substantially small fluidizing velocity and from the air diffusion nozzles above the two air chambers 33, 33 on both sides so as to give a substantially large fluidizing velocity.
  • a moving bed 21 in which the fluidizing particles move downwardly at a relatively low speed is formed above the central region of the hearth plate 30, and fluidized beds 22 in which the fluidizing particles move upwardly are formed above both side regions of the hearth plate 30. Therefore, the fluidizing particles move from the moving bed 21 to the fluidized beds 22 in a lower portion of the fluidized bed 20, and move from the fluidized beds 22 to the moving bed 21 in an upper portion of the fluidized bed 20, thus forming right and left circulating flows of the fluidizing particles circulating between the moving bed 21 and the fluidized beds 22.
  • the partition walls 13 have respective slanted portions which function as reflector walls for allowing the ascending fluidizing particles to turn into the inner side of the furnace 12.
  • the fuel is supplied from a supply port (not shown) to the moving bed 21.
  • the opening degrees of the regulating valves are adjusted to control an amount of the fluidizing air such that an amount of the fluidizing air supplied to the moving bed 21 is smaller than an amount of the fluidizing air supplied to the fluidized beds 22.
  • the amount of the fluidizing air supplied to the moving bed 21 is set so that u o /u mf is in the range of 2 to 3 and the amount of the fluidizing air supplied to the fluidized beds 22 is set so that u o /u mf is in the range of 4 to 6.
  • u o represents a superficial velocity
  • u mf represents a minimum fluidizing superficial velocity.
  • the fuel supplied to the moving bed 21 sinks into the fluidizing particles and moves downwardly together with the fluidizing particles. At this time, the fuel is decomposed by the heat of the fluidizing particles to generate a combustible gas from a combustible component in the fuel, thus producing a brittle pyrolysis residue.
  • the pyrolysis residue typically includes incombustibles and unburned combustibles (char) which become brittle by pyrolysis.
  • the pyrolysis residue produced in the moving bed 21 moves downwardly and reaches the hearth plate 30 together with the fluidizing particles, and then moves along the inclined hearth plate 30 toward the fluidized beds 22.
  • the pyrolysis residue which has reached the fluidized beds 22 is brought into contact with the fluidizing particles that are vigorously fluidized, and thus the unburned combustibles are separated from the incombustibles.
  • the incombustibles from which the unburned combustibles have been separated are discharged together with part of the fluidizing particles from incombustible discharge ports 17.
  • the unburned combustibles which have been separated from the incombustibles move upwardly together with the fluidizing particles that are fluidized by supply of the fluidizing air.
  • the unburned combustibles are combusted by the supplied fluidizing air to produce a combustion gas while heating the fluidizing particles, and are turned into particles of unburned combustibles and ash that are fine enough to be carried by the gas.
  • the high-temperature fluidizing particles that have reached the upper portions of the fluidized beds 22 partly flow into the moving bed 21. In the fluidized beds 22, the fluidizing particles are heated to a temperature which is high enough to completely pyrolyze the fuel when the fluidizing particles flow into the moving bed 21.
  • the fluidizing particles that have flowed into the moving bed 21 receive the supplied fuel again, and repeat the above thermal reactions in the moving bed 21 and the fluidized beds 22.
  • the moving bed 21 is kept at a temperature ranging from 700 to 900°C
  • the fluidized beds 22 are kept at a temperature ranging from 700 to 900°C.
  • the high-temperature fluidizing particles in the upper portions of the fluidized beds 22 partly flow over the upper ends of the partition walls 13 into the heat recovery chambers 15.
  • the fluidizing particles that have entered the heat recovery chambers 15 form fluidized beds 23 in which the fluidizing particles move downwardly.
  • the hearth plates 31 in the heat recovery chambers 15 are slanted downwardly from the inner wall side of the furnace 12 toward the combustion chamber side. Openings 18 are provided at lower portions of the heat recovery chambers 15.
  • the fluidizing particles that have entered the heat recovery chambers 15 descend while forming the fluidized beds 23, and circulate from the openings 18 into the combustion chamber 14.
  • the temperature of the fluidizing particles that flow into the heat recovery chambers 15 is in the range of 700 to 900°C.
  • the immersed heat transfer tubes 5 are disposed in the fluidized beds 23 in the heat recovery chambers 15.
  • the high-temperature fluidizing particles are brought into contact with the immersed heat transfer tubes 5 while moving downwardly, and thus a fluid (boiler water) in the immersed heat transfer tubes 5 recovers heat from the fluidizing particles by heat exchange with the fluidizing particles.
  • the amount of heat recovered by the immersed heat transfer tubes 5 can be controlled by adjusting an amount of the fluidizing air to be ejected from the gas diffusion nozzles on the hearth plates 31 of the fluidized beds 23 so that u o /u mf is the range of 2 to 4.
  • the fluidizing particles that have circulated into the combustion chamber 14 are supplied to the fluidized beds 22, and ascend together with the fluidizing particles of the fluidized beds 22.
  • the fluidizing particles partly enter the heat recovery chambers 15 again, and repeat heat exchange with the fluid in the immersed heat transfer tubes 5.
  • the immersed heat transfer tubes 5 that are used in the bubbling-type fluidized-bed boiler shown in FIG. 1 and the internally circulating fluidized-bed boiler shown in FIG. 2 will be described below.
  • FIG. 3 is a schematic cross-sectional view of the immersed heat transfer tube 5.
  • the immersed heat transfer tube 5 comprises a water tube 6 through which a fluid (boiler water) flows, a cylindrical protector 8 provided at an outer circumferential side of the water tube 6 and configured to protect the water tube 6, and a packed bed 7 provided between the water tube 6 and the protector 8.
  • the water tube 6 is made of a steel tube for boilers and heat exchangers such as STB410S which has a wall thickness of 4 to 8 mm.
  • the fluid (boiler water) that flows through the water tube 6 is saturated water having a pressure of 2 MPa to 12 MPa.
  • the packed bed 7 is formed by filing solid particles such as sand, stainless steel powder, magnesium oxide, iron, or alumina, and is formed in a hollow cylindrical shape having a wall thickness of 2 to 4 mm.
  • the packed bed 7 has a heat conductivity ranging from 0.4 to 1.4 W/mK calculated according to the calculation formula described in " Powder Reaction", NIKKAN KOGYO SHIMBUN, LTD., p. 54 - 57 .
  • the packed bed 7 may be made of any other packing materials than those enumerated above insofar as the heat conductivity falls within the above range.
  • the packing material should preferably be a powder and granular material. Further, the packing ratio of the packing material should preferably be in the range of 0.5 to 0.9, and more preferably in the range of 0.6 to 0.8.
  • the packing ratio of the packing material which falls within the above range, when the protector is thermally expanded, the space formed between the surface (upper surface) of the packed bed and the inner surface of the protector by the gravitational sedimentation of the packing material, i.e., a thickness of the space is reduced, thereby ensuring heat transfer to the water tube.
  • the protector 8 is made of stainless steel comprising SUS304, SUS316, SUS310S, or the like which has excellent wear resistance and corrosion resistance, and is formed in a hollow cylindrical shape having a wall thickness of 3 to 6 mm.
  • the protector 8 may comprise a stainless steel plate formed in a hollow cylinder or a stainless steel tube.
  • the present invention is configured as follows: (1) the protector 8 is made of stainless steel comprising SUS304, SUS316, SUS310S, or the like, (2) the packed bed 7, between the water tube 6 and the protector 8, which has a heat conductivity ranging from 0.4 to 1.4 W/mK is formed in a predetermined thickness, i.e., a thickness of 2 to 4 mm, and (3) the temperature of the fluidized bed 3 (see FIG. 1 ) in which the immersed heat transfer tubes 5 are disposed and the temperature of the fluidizing particles that enter the heat recovery chambers 15 (see FIG. 2 ) are maintained in the range of 700 to 900°C.
  • the surface temperature of the protector 8 can be kept at a temperature ranging from 450 to 650°C, or preferably from 480 to 620°C.
  • FIGS. 4A and 4B are views showing the results of comparison between a conventional immersed heat transfer tube having a weld overlay of stainless steel on a water tube and an immersed heat transfer tube according to the present invention which provides the above elements (1) to (4).
  • the conventional immersed heat transfer tube has weld overlay of stainless steel having a thickness of 3 mm for surface modification of the water tube.
  • the temperature of the fluidized bed is 800°C
  • the temperature of the boiler water is 300°C
  • the fluidizing air is supplied to the fluidized bed so that u o /u mf is equal to 1.5
  • the heat transfer rate from the fluidizing particles (sand) to the weld overlay is 210 W/m 2 K
  • the surface temperature of the weld overlay is 320°C
  • the overall heat transfer rate at the inner surface basis of the weld overlay (the outer surface basis of the water tube) is 222 W/m 2 K
  • the heat transfer amount is 111118 W/m 2 .
  • the temperature difference between the surface temperature of the weld overlay and the surface temperature of the water tube is 20°C.
  • the immersed heat transfer tube according to the present invention has a packed bed formed by filling magnesium oxide particles and having a thickness of 2 mm, and a protector made of SUS310S and having a thickness of 3 mm, at the outer circumference of the water tube. As shown in FIG.
  • the overall heat transfer rate at the outer surface basis of the water tube is 263 W/m 2 K, and the heat transfer amount is 131586 W/m 2 .
  • the immersed heat transfer tube having the packing material and the protector at the outer circumference of the water tube is used and an amount of the fluidizing air is set so that u o /u mf is equal to 2.5 or higher to intensify the fluidization of the fluidized beds (moving bed), and the thickness and the heat conductivity of the packed bed are appropriately selected, and thus the following can be achieved:
  • the conventional immersed heat transfer tube is designed to transfer the heat of the fluidizing particles in the fluidized bed quickly to the fluid (boiler water) in the heat transfer tube.
  • the immersed heat transfer tube 5 according to the present invention is configured to have the packed bed 7 between the water tube 6 and the protector 8 to achieve gradual heat transfer, thereby increasing the surface temperature of the protector 8.
  • the corrosive attack by molten salt on the heat transfer tube and thereby resulting the tube thickness reduction can be suppressed and the service life of the heat transfer tube can be prolonged.
  • FIGS. 1 and 2 An example of a detailed structure of the immersed heat transfer tubes used in the fluidized-bed boilers shown in FIGS. 1 and 2 will be described below with reference to FIG. 5 and 6 .
  • FIG. 5 is a front elevational view of immersed heat transfer tubes 5.
  • FIG. 5 shows a heat transfer tube bundle in which two immersed heat transfer tubes 5 are disposed in parallel.
  • the immersed heat transfer tube 5 has a straight tube section and a bent tube section, and a number of fins 9 are provided on the straight tube section.
  • FIG. 6 is a vertical cross-sectional view of the immersed heat transfer tube 5.
  • the immersed heat transfer tube 5 shown in FIG. 6 comprises a water tube 6, a packed bed 7, and a protector 8 as with the immersed heat transfer tube 5 shown in FIG. 3 , and additional fins 9 provided on the outer circumferential surface of the protector 8.
  • the fins 9 are composed of stainless steel plates of SUS304, SUS316, SUS310S, or the like, and are fixed to upper and lower portions of the outer circumferential surface of the protector 8.
  • FIGS. 7A and 7B are view showing an immersed heat transfer tube 5 according to another embodiment.
  • FIG. 7A is a front elevational view of the immersed heat transfer tube 5, and
  • FIG. 7B is a vertical cross-sectional view of the immersed heat transfer tube 5.
  • the immersed heat transfer tube 5 shown in FIGS. 7A and 7B includes a helical fin 34 welded to the entire outer circumferential surface of the protector 8. By adopting the helical fin, attachment of the fin is facilitated and the construction period can be greatly shortened.
  • FIGS. 8A and 8B are views showing an immersed heat transfer tube 5 according to still another embodiment.
  • FIG. 8A is a front elevational view of the immersed heat transfer tube 5, and
  • FIG. 8B is a vertical cross-sectional view of the immersed heat transfer tube 5.
  • the immersed heat transfer tube 5 shown in FIGS. 8A and 8B includes fins 35 in the form of pins, rather than plates (vanes), fixed to the outer circumferential surface of the protector 8. A number of pin fins 35 are welded to the outer circumferential surface of the protector 8.
  • the protector 8 since the protector 8 is provided with the fins 9, the fin 34, or the fins 35, the heat transfer rate per inner surface of the protector can be increased. Therefore, the heat transfer rate between the fluidizing particles (sand) and the protector can be increased and the surface temperature of the protector 8 can be kept at a temperature of 450°C or higher.
  • the water tube 6, the packed bed 7, and the protector 8 of the immersed heat transfer tube 5 shown in FIGS. 5 , 7A , 7B , 8A and 8B are the same as those of the immersed heat transfer tube shown in FIG. 3 .
  • the present invention is applicable to immersed heat transfer tubes installed in a fluidized bed in a fluidized-bed boiler for recovering combustion heat generated when a fuel such as RDF (refuse derived fuel) with high calorific value containing biomass and plastics, or wastes is combusted.
  • a fuel such as RDF (refuse derived fuel) with high calorific value containing biomass and plastics, or wastes is combusted.

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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)
EP13749873.9A 2012-02-13 2013-02-07 In-bed heat transfer tube for fluidized bed boiler Active EP2821697B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012028225 2012-02-13
PCT/JP2013/052843 WO2013121965A1 (ja) 2012-02-13 2013-02-07 流動層ボイラの層内伝熱管

Publications (3)

Publication Number Publication Date
EP2821697A1 EP2821697A1 (en) 2015-01-07
EP2821697A4 EP2821697A4 (en) 2016-03-09
EP2821697B1 true EP2821697B1 (en) 2018-12-19

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EP13749873.9A Active EP2821697B1 (en) 2012-02-13 2013-02-07 In-bed heat transfer tube for fluidized bed boiler

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EP (1) EP2821697B1 (zh)
JP (1) JP6085570B2 (zh)
KR (1) KR101998448B1 (zh)
CN (1) CN104136842B (zh)
WO (1) WO2013121965A1 (zh)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN110017473A (zh) * 2019-03-20 2019-07-16 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

Families Citing this family (7)

* Cited by examiner, † Cited by third party
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 (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
KR101895382B1 (ko) * 2017-01-02 2018-09-05 현대건설 주식회사 순환유동층 보일러 시스템
FI130359B (fi) 2018-05-21 2023-07-20 Valmet Technologies Oy Leijupetikattilaksi soveltuva koaksiaalinen lämmönsiirtoputki ja menetelmä sen valmistamiseksi
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
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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JPS61121306U (zh) * 1985-01-11 1986-07-31
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JP3192726B2 (ja) 1992-01-14 2001-07-30 三菱重工業株式会社 伝熱管の耐摩耗構造
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JPH07217801A (ja) 1994-02-08 1995-08-18 Babcock Hitachi Kk 流動層ボイラの伝熱管
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Also Published As

Publication number Publication date
EP2821697A4 (en) 2016-03-09
JPWO2013121965A1 (ja) 2015-05-11
CN104136842B (zh) 2016-05-11
KR20140127861A (ko) 2014-11-04
CN104136842A (zh) 2014-11-05
WO2013121965A1 (ja) 2013-08-22
JP6085570B2 (ja) 2017-02-22
KR101998448B1 (ko) 2019-07-09
EP2821697A1 (en) 2015-01-07

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