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WO1998028493A1 - Unite de chauffage d'agregats froids comportant un bruleur de sechoir thermique a conversion de vapeur - Google Patents

Unite de chauffage d'agregats froids comportant un bruleur de sechoir thermique a conversion de vapeur Download PDF

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Publication number
WO1998028493A1
WO1998028493A1 PCT/KR1997/000198 KR9700198W WO9828493A1 WO 1998028493 A1 WO1998028493 A1 WO 1998028493A1 KR 9700198 W KR9700198 W KR 9700198W WO 9828493 A1 WO9828493 A1 WO 9828493A1
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WO
WIPO (PCT)
Prior art keywords
dryer
steam
aggregate
ignition
fuel
Prior art date
Application number
PCT/KR1997/000198
Other languages
English (en)
Inventor
Ei Hoe Ku
Original Assignee
Ei Hoe Ku
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ei Hoe Ku filed Critical Ei Hoe Ku
Priority to AU47939/97A priority Critical patent/AU4793997A/en
Publication of WO1998028493A1 publication Critical patent/WO1998028493A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B20/00—Combinations of machines or apparatus covered by two or more of groups F26B9/00 - F26B19/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details, e.g. burner cooling means, noise reduction means
    • F23D11/38—Nozzles; Cleaning devices therefor
    • F23D11/383—Nozzles; Cleaning devices therefor with swirl means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F23D11/402—Mixing chambers downstream of the nozzle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B11/00—Machines or apparatus for drying solid materials or objects with movement which is non-progressive
    • F26B11/02—Machines or apparatus for drying solid materials or objects with movement which is non-progressive in moving drums or other mainly-closed receptacles
    • F26B11/028—Arrangements for the supply or exhaust of gaseous drying medium for direct heat transfer, e.g. perforated tubes, annular passages, burner arrangements, dust separation, combined direct and indirect heating

Definitions

  • the present invention relates , in general, to heaters for cold aggregate used as a material necessary for the production of Ascon and, more particularly, to a cold aggregate heater with a steam conversion heat dryer burner capable of completely burning mixed fuel and introducing complete combustion intensive heat into a dryer, thus vaporizing moisture of cold aggregate into steam suitable for uniformly increasing the inner temperature of the dryer and effectively heating the fine and crude aggregate and reducing the amount of AP3 liquid, and improving the quality of resulting Ascon.
  • a single or double- layered binder is applied onto the street prior to laying Ascon on the binder.
  • fine aggregate, sands and crude aggregate with the crude aggregate having a size of not larger than 19 mm, are mixed with each other into a mixture prior to heating the mixture in a dryer burner at an appropriate temperature. Thereafter, the heated mixture is weighted at a predetermined mixing ratio prior to adding AP3 liquid into the weighted mixture and mixing the AP3 liquid with the mixture in a mixer, thus producing such Ascon.
  • the fine and crude aggregate are differently heated during the heating step for mixed aggregate in an Ascon producing process, thus causing a serious problem in resulting Ascon.
  • the volume of fine aggregate having a size of 3 mm with a volume formula of 4/3 ⁇ r J is 14 mm
  • the volume of crude aggregate having a size of 19 mm is 3,589 mm . Therefore, the ratio of volume between the fine aggregate and the crude aggregate is 1 : 256.
  • the volume of crude aggregate having a size of 28 mm is 11,488 mm and so the ratio of volume between the fine aggregate (14 mm 3 ) and the crude aggregate (11,488 mm 3 ) is 1 : 825.
  • the fine aggregate is overheated and exceedingly burnt during such a heating step, thus reducing the viscosity of the AP3 liquid and reducing the oxidation adhesive power of the AP3 liquid and deteriorating the quality of resulting asphalt.
  • the temperature of the heating step is too low to completely heat the crude aggregate, thus preventing a roller from uniformly applying its full pressure onto the layer of Ascon during a paving work and allowing wheels of cars to wear grooves and bumps into the street. Therefore, such Ascon shortens the expected life span of a paved street and may cause traffic accidents due to such a bumpy surface.
  • a typical cold aggregate heater with a dryer burner deteriorates the heating conditions and causes an incomplete combustion of mixed fuel, thus reducing the quality of resulting Ascon and asphalt.
  • the construction of such a typical aggregate heater 1 is shown in Figs. 1 to 4.
  • Fig. 1 shows the construction of a typical cold aggregate heater.
  • the heater 1 has a dryer burner 10, which mixes primary combustion air with bunker-C oil into mixed fuel prior to discharging the mixed fuel from a nozzle at a high speed.
  • the primary combustion air is introduced into the dryer burner 10 from a damper 11a.
  • the heater 1 also includes a second combustion channel 30, which is hollowed and is provided with a thermal insulating layer 31 on its inner surface.
  • the second channel 30 is positioned around the outlet end of the primary channel 20 with an interval being formed between the primary and second channels 20 and 30.
  • a dryer 40 is provided at the outlet end of the second channel 30, thus communicating with the channel 30.
  • the dryer 40 is provided with a plurality of radial dryer wings 42, which are regularly and axially arranged on the inner surface of the dryer 40. The dryer wings 42 move the inlet aggregate from the top to the bottom in the dryer 40, thus allowing the aggregate to be effectively heated and dried in the dryer 40.
  • a feeding means 50 is provided at the junction between the second channel 30 and the dryer 40.
  • Fig. 2 is a sectional view showing the construction of the typical dryer burner 10.
  • Fig. 3 is a sectional view of the dryer burner 10 taken along the section line A-A of Fig. 2.
  • the dryer burner 10 is comprised of a burner body 11, which is provided with the damper 11a at its bottom portion for controlling the amount of inlet air and has an opening at one end thereof.
  • a fuel injection Venturi nozzle 13 is installed in the burner body 11, with a plurality of supports 12 being regularly interposed between the burner body 11 and the nozzle 13, thus holding the nozzle 13 in the burner body 11 while forming an interval between the nozzle 13 and the burner body 11.
  • a plurality of air inlet holes 13a are radially and inclinedly formed on the fuel injection Venturi nozzle 13.
  • the air inlet holes 13a are concentrated to the axis of the nozzle 13 and individually spiral at an angle of about 30°.
  • a pipe fitting hole 13c is formed at the center of the nozzle 13, with the air inlet holes 13a surrounding the pipe fitting hole 13c.
  • the pipe fitting hole 13c is closed at one end thereof.
  • a plurality of fuel injection holes 13d are axially formed at the closed end of the hole 13c, thus allowing the pipe fitting hole 13c to communicate with the mixing chamber 13b of the Venturi nozzle 13.
  • a fuel injection pipe 14 is fitted into the pipe fitting hole 13c of the nozzle 13.
  • Fig. 4 is a sectional view showing the construction of the dryer included in the typical cold aggregate heater 1.
  • the dryer 40 is provided with a plurality of brackets 41 and a plurality of dryer wings 42.
  • the brackets 41 are mounted on the inlet end of the inner surface of the dryer 40, while the dryer wings 42 are attached to the inner surface of the dryer 40 using set screws at positions in back of the brackets 41.
  • Each of the dryer wings 42 is bent at its bottom, thus forming a bucket suitable for bucketing an appropriate amount of cold aggregate so as to effectively lift and drop the aggregate in the dryer 40.
  • a plurality of radial flanges are mounted to the heat inlet end of the dryer 40, thus feeding the heated and dried aggregate into the inlet port (not shown) of the feeding means 50.
  • heavy oil such as bunker-C oil
  • the dryer burner 10 the vaporized heavy oil is injected from the fuel injection holes 13d into the mixing chamber 13b of the nozzle 13 at a high injection speed.
  • atmospheric air or primary combustion air from the damper 11a of the burner body 11 is introduced into the nozzle 13 through the air inlet holes 13a, thus being mixed with the heavy oil into mixed fuel.
  • the mixed fuel from the fuel injection Venturi nozzle 13 is injected into the primary and second channels 20 and 30 at a high speed, thus being ignited and burnt in the channels 20 and 30.
  • the combustion flame of the two channels 20 and 30 is introduced into the dryer 40, thus heating cold aggregate in the dryer 40.
  • the above heater 1 is problematic in that the fuel or the heavy oil from the linear fuel injection holes 13d of the nozzle 13 does not flow in whirls but flows only linearly. Therefore, when an exceeding amount of primary combustion air is fed into the mixing chamber 13b of the nozzle 13, the fuel from the fuel injection holes 13d fails to be completely burnt, thus being introduced into the dryer 40 with unburnt fuel.
  • the amount of inlet air has to be controlled and reduced to a level allowing the fuel from the fuel injection holes 13d to be completely burnt.
  • such a reduced amount of inlet air causes the cold aggregate in the dryer 40 to be heated under incomplete combustion conditions.
  • the dryer 40 is rotated at a constant speed with the cold aggregate being continuously lifted and dropped in the dryer 40 by the dryer wings 42.
  • the heated and dried aggregate is fed to the screen unit by the feeding means and is mixed with AP3 liquid into Ascon, which will be applied on a street as a top layer.
  • the above cold aggregate heater 1 has the following problems. That is, a plurality of fuel injection holes, having an appropriate size, are axially and linearly formed on the center of the fuel injection nozzle, thus only allowing the fuel to be linearly discharged into the mixing chamber of the Venturi nozzle. Therefore, the fuel injection holes unstably inject fuel and are unexpectedly blocked and cause incomplete combustion due to the shortage of inlet air.
  • the fuel when the amount of inlet air is less than an appropriate level, the fuel may be stuck onto the interior surfaces of the first and second channels, thus being burnt on the interior surfaces. Meanwhile, when the amount of inlet air is more than an appropriate level, the fuel may be stuck onto the aggregate while being not burnt due to the shortage of ignition means.
  • a plurality of fuel injection holes are formed on a cast cylindrical body, thus being unexpectedly blocked by dust and failing to smoothly inject the fuel and causing an incomplete combustion of mixed fuel.
  • the cold aggregate in the dryer may be directly and rapidly heated by intensive combustion flame in a short time.
  • the dryer burner is arranged in front of the dryer without positioning the primary or second combustion channel or the ignition unit in the heater, thus causing a direct combustion of mixed fuel in the dryer.
  • the dryer wings may be arranged at low positions or may be free from lifting or dropping the aggregate.
  • such a heater is problematic in that it overheats and exceedingly burns the outside surface of crude aggregate and fails to effectively heat the interior of the crude aggregate.
  • Such crude aggregate, with both the overheated outside surface and the incompletely heated interior causes a plastic deformation of resulting Ascon.
  • the typical cold aggregate heater also causes a problem when it heats mixed aggregate comprised of fine and crude aggregate. That is, in the event of a top layer of asphalt, the volume of fine aggregate having a size of 3 mm with a volume formula of 4/3 ⁇ r J is 14 mm , while the volume of crude aggregate having a size of 19 mm is 3,589 mm . Therefore, the ratio of volume between the fine aggregate and the crude aggregate is 1 : 256. Therefore, when such mixed aggregate is heated in the dryer, the fine aggregate is overheated and exceedingly burnt during such a heating step, thus reducing the viscosity of the AP3 liquid and reducing the oxidation adhesive power of the AP3 liquid and deteriorating the quality of resulting asphalt.
  • Such overheated fine aggregate causes the AP3 liquid to be exceedingly added to the aggregate by about 30 %, thus resulting in the addition of 6.3 % of AP3 liquid.
  • Such an addition of AP3 liquid allows the asphalt to lose color in a short time and shortens the expected life span of the asphalt.
  • the crude aggregate is heated in a short time, thus being incompletely heated.
  • the incompletely heated crude aggregate is coated with a thick AP3 liquid layer, thus causing waste of the AP3 liquid.
  • Such crude aggregate also prevents a roller from uniformly applying its full pressure onto the layer of Ascon during a paving work, thus forming cavities between the fine aggregate in the asphalt.
  • the asphalt street with such cavities is unevenly compressed by wheels of cars, thus becoming bumpy on its surface in a short time.
  • the AP3 liquid in such an asphalt is unexpectedly exposed on the surface of the asphalt in hot weather.
  • Such a bumpy street with exposed AP3 liquid causes traffic accidents.
  • an object of the present invention is to provide a cold aggregate heater, which is provided with a steam conversion heat dryer burner capable of completely igniting and burning mixed fuel and feeding the complete combustion heat into a dryer, thus vaporizing moisture of cold aggregate into steam and uniformly increasing the inner temperature of the dryer using the steam conversion heat, and which appropriately heats the mixed aggregate with both fine aggregate being not overheated and crude aggregate being completely heated at its interior, thus saving AP3 liquid and improving the quality of resulting Ascon free from any plastic deformation.
  • the present invention provides a cold aggregate heater comprising: a steam conversion heat dryer burner mixing fuel with primary combustion air and primary steam, thus forming mixed fuel prior to injecting the mixed fuel at a high speed; a hollow ignition unit having a thermal insulating layer on its inner surface and positioned around the outlet end of the dryer burner, the ignition unit including: an ignition promoting panel provided at the inlet end of the ignition unit and adapted for promoting ignition of the mixed fuel; and a steam boiler provided at the outlet end of the ignition unit and adapted for feeding secondary steam to aggregate; a hollow combustion unit having a thermal insulating layer on its inner surface and positioned around the outlet end of the ignition unit with an interval being formed between the ignition unit and the combustion unit; and a dryer arranged at the outlet end of the combustion unit and adapted for uniformly heating the aggregate with both the complete combustion heat from the dryer burner and the steam from the steam boiler.
  • Fig. 1 is a view showing the construction of a typical cold aggregate heater with a dryer burner
  • Fig. 2 is an enlarged sectional view showing the construction of the typical dryer burner
  • Fig. 3 is a sectional view of the heater taken along the line A-A of Fig. 1;
  • Fig. 4 is a sectional view of a dryer of the typical heater
  • Fig. 5 is a view showing the construction of a cold aggregate heater with a steam conversion heat dryer burner in accordance with the preferred embodiment of the present invention
  • Fig. 6 is a sectional view of the steam conversion heat dryer burner of this invention.
  • Fig. 7 is a side view of a fuel injection nozzle included in the dryer burner of Fig. 6, with a fuel injection tip being removed from the nozzle;
  • Fig. 8 is a front view of an air inlet fan included in the dryer burner of Fig. 6;
  • Fig. 9 is a sectional view showing the construction of an ignition promoting means included in the heater of this invention.
  • Fig. 10 is a sectional view of the ignition promoting means taken along the line B-B of Fig. 9;
  • Fig. 11 is a view showing a steam boiler included in the heater of this invention.
  • Fig. 12 is a sectional view of the first steam nozzle of the steam boiler of Fig. 11;
  • Fig. 13 is a sectional view of the second steam nozzle of the steam boiler of Fig. 11;
  • Fig. 14 is a sectional view of a dryer included in the heater of this invention.
  • Fig. 15 is a perspective view of a dryer wing included in the dryer of this invention.
  • Fig. 5 is a view showing the construction of a cold aggregate heater with a steam conversion heat dryer burner in accordance with the preferred embodiment of this invention.
  • the cold aggregate heater is designated by the reference character A.
  • the steam conversion heat dryer burner 100 of this invention has a cylindrical configuration and mixes fuel, which is fed from a fuel tank, such as a bunker-C oil tank 90 or another oil tank 91, with both primary combustion air and primary steam, thus forming mixed fuel prior to injecting the mixed fuel at a high speed.
  • An ignition unit 200 which is hollowed and is provided with a thermal insulating layer 201 on its inner surface, is positioned around the outlet end of the dryer burner 100.
  • the ignition unit 200 includes an ignition promoting panel 210 and a steam boiler 220.
  • the ignition promoting panel 210 promotes ignition of mixed fuel from the dryer burner 100, while the steam boiler 220 feeds secondary steam to aggregate in a dryer 400.
  • the heater A also includes a combustion unit 300, which is hollowed and is provided with a thermal insulating layer 301 on its inner surface.
  • the combustion unit 300 is positioned around the outlet end of the ignition unit 200 with an interval being formed between the outlet end of the ignition unit 200 and the inlet end of the combustion unit 300.
  • the dryer 400 is provided at the outlet end of the combustion unit 300 and communicates with the unit 300. The dryer 400 uniformly heats the cold aggregate with both the complete combustion heat from the dryer burner 100 and the steam from the steam boiler 220.
  • an elevator-type feeding means 500 is provided at the junction between the combustion unit 300 and the dryer 400.
  • Fig. 6 is an enlarged sectional view of the dryer burner
  • Fig. 7 is a side view of a fuel injection nozzle of dryer burner 100, with a fuel injection tip being removed from the nozzle.
  • Fig. 8 is a front view of an air inlet fan of the dryer burner 100.
  • the dryer burner 100 is positioned approximate to the ignition unit 200 so as to directly communicate with the unit 200.
  • the dryer burner 100 is comprised of a cylindrical burner body ill, which is provided with a damper Ilia at its bottom portion for introducing pressurized air or primary combustion air into the burner body ill and has an opening at its outlet end.
  • the dryer burner 100 thus communicates with the ignition unit 200 at the opening.
  • the opposite end of the burner body ill is closed.
  • a fuel injection Venturi tube 113 is installed in the burner body 111, with a plurality of supports 112 being regularly interposed between the burner body 111 and the Venturi tube 113, thus holding the tube 113 in the burner body 111 with an interval being formed between the burner body 111 and the tube 113.
  • a diverged ignition part 113a is formed at the outlet end of the Venturi tube 113, while an air inlet fan 114 is fitted into the opposite end of the Venturi tube 113.
  • the air inlet fan 114 is provided with a plurality of radial blades 114a and is preferably made of stainless steel through a casting process.
  • a fuel injection nozzle 115 is fitted into the center of the air inlet fan 114, while a fuel supply pipe 117 connects the fuel tank to the nozzle 115.
  • the fuel injection nozzle 115 is provided with a fuel inlet hole 115a at its inlet end, thus allowing the fuel supply pipe 117 to be fitted into the nozzle 115.
  • the nozzle 115 has a conical end at its outlet end.
  • a plurality of spiral holes 115a are formed in the conical end of the nozzle 115 and commonly communicate with the fuel inlet hole 115a, thus allowing fuel to be discharged in whirls from the nozzle 115.
  • a nozzle tip 116 having a conical opening with a fuel injection hole 116a, is screwed to and fitted over the conical end of the nozzle 115.
  • a steam injector 118 is mounted to the burner body 111 using a bracket, thus being fixedly positioned at a side of the air inlet fan 114.
  • the steam injector 118 discharges pressurized steam or primary steam into the Venturi tube 113, thus allowing the steam to be mixed with both the primary combustion air and the fuel in the Venturi tube 113.
  • Fig. 9 is a sectional view showing the construction of an ignition promoting means provided at the junction between the dryer burner 100 and the ignition unit 200.
  • Fig. 10 is a sectional view of the ignition promoting means taken along the line B-B of Fig. 9.
  • the ignition promoting means comprises an ignition promoting panel 210, which has an annular configuration with an inner diameter of the panel 210 being slightly larger than that of the opening of the burner body 111.
  • the ignition promoting panel 210 is mounted to the inlet end of the ignition unit 200 through a welding process.
  • a plurality of radial air inlet holes 211 are formed on the ignition promoting panel 210, thus feeding air into the ignition unit 200 so as to promote ignition of the mixed fuel.
  • the ignition promoting panel 210 also forms an annular ignition chamber 212 which communicates with the radial air inlet holes 211.
  • a plurality of bent resist members As shown in Fig. 9, a plurality of bent resist members
  • the above bent members 404 also cause a resistance in the air circulation from the ignition promoting panel, thus allowing the mixed fuel to be stuck thereto.
  • Fig. 11 is a view showing the steam boiler 220 of this invention.
  • Figs. 12 and 13 are sectional views of the first and second steam nozzles of the steam boiler 220, respectively.
  • the steam boiler 220 is comprised of a hollow body 221 having an arcuate cross-section and is exteriorly mounted to the ignition unit 200 with the arcuate inside wall of the body 221 being brought into surface contact with the outside wall of the cylindrical ignition unit 200.
  • the steam boiler 220 has a water pipe 222 at its center and has first and second steam nozzles 223, 223' and 224, 224' at opposite sides.
  • first steam nozzles 223 and 223' are axially formed on the lower portion of one end of the arcuate hollow body 221, while two or more second steam nozzles 224 and 224' are axially formed on the same end of the arcuate hollow body 221 at positions higher than those of the first nozzles 223 and 223'.
  • the second nozzles 224 and 224' directly discharge steam from the body 221.
  • each of the first nozzles 223 and 223' is connected to an associated second nozzle 224, 224' through a branch pipe 225, 225', thus receiving steam from an associated second nozzle 224, 224' through the branch pipe 225, 225' prior to discharging the steam from the body 221.
  • Fig. 14 is a sectional view of the dryer 400 of this invention.
  • Fig. 15 is a perspective view of a dryer wing included in the dryer 400.
  • the dryer 400 has a cylindrical body, of which one end approximate to the combustion unit 300 is provided with an aggregate inlet 401.
  • a plurality of dryer wings 402 are radially arranged on the inner surface of the dryer 400.
  • each dryer wing 402 is bent, thus forming a bucket which has a spreading angle of about 15° suitable for spreading the aggregate at that angle while dropping the aggregate in the dryer 400. Due to such a specific configuration of the bent bottom 402a, the dryer wings 402 smoothly lift and drop crude aggregate and allow hot air to be effectively applied to the aggregate when the aggregate is dropped in the dryer 400.
  • the above bent bottom 402a is tapered from one end to the other end at an angle of inclination.
  • the dryer wings 402 are preferably attached to the inner surface of the dryer 400, for example, using set screws.
  • a plurality of supports 112 are radially and regularly mounted to the inner surface of the burner body 111 of the dryer burner 100, for example, through a welding process prior to fitting the fuel injection Venturi tube 113 into the burner body 111 with the supports 112 concentrically holding the Venturi tube 113 in the burner body 111. Thereafter, the Venturi tube 113 is preferably bolted to the supports 112.
  • the air inlet fan 114 which has an annular configuration and is made of stainless steel through a casting process, is fitted into one end of the Venturi tube 113 prior to fitting the fuel injection nozzle 115 into the center of the fan 114.
  • the steam injector 118 which extends from a steam generator (not shown), is arranged in the burner body 111 at a position around the air inlet fan 114. After the dryer burner 100 is completely assembled, the burner 100 is installed at a predetermined position relative to the ignition unit 200, with the outlet end of the burner 100 being positioned approximate to and spaced apart from the inlet end of the ignition unit 200 at a predetermined interval.
  • the radial air inlet holes 211 and ignition chamber 212 of the ignition promoting panel 210, the bent resist members 404 and the diverged ignition part 113a of the Venturi tube 113 are arranged so as to effectively reduce the instantaneous flow speed of the mixed fuel and allow a part of the mixed fuel to be stuck thereto, and completely ignite the mixed fuel in the ignition unit 200. Due to such a complete ignition of the mixed fuel, the ignition unit 200 generates completely burnt intensive flame regardless of how high the speed injection of the mixed fuel is.
  • the steam boiler 220 is exteriorly mounted to the outlet end of the ignition unit 200 with the arcuate inside surface of the boiler body 221 being brought into surface contact with the outside surface of the ignition unit 200.
  • the first and second steam nozzles of the boiler 220 are positioned so as to effectively discharge steam to the combustion flame.
  • the combustion unit 300 is arranged around the outlet end of the ignition unit 200, while the dryer 400 is connected to the outlet end of the combustion unit 300.
  • each of the dryer wings 402 is attached to the inner surface of the dryer 400, for example, using set screws.
  • the bottom 402a of each dryer wing 402 is bent at an appropriate spreading angle suitable for uniformly spreading the aggregate in the dryer 400, thus allowing the aggregate to be uniformly heated while being lifted and dropped in the dryer 400.
  • cold aggregate being comprised of fine aggregate having a size of not larger than 6 mm and crude aggregate having a size of about 19 mm.
  • cold aggregate which is comprised of fine aggregate of 3 mm or 6 mm in size, crude aggregate of about 19 mm in size and powdered rock, is poured into the dryer 400 through the aggregate inlet 401 prior to starting the dryer burner 100 using a control unit (not shown).
  • fuel is fed from the bunker-C oil tank 90 or another tank 91 into the fuel injection nozzle 115 of the burner 100 through the fuel supply pipe 117.
  • the fuel injection nozzle 115 the fuel passes through the fuel inlet hole 115a and the spiral holes 115b, thus being discharged in whirls and finely sprayed from the spiral holes 115b.
  • the fuel is, thereafter, uniformly discharged from the fuel injection hole 116a of the nozzle tip 116 into the Venturi tube 113.
  • the primary combustion air under pressure passes through the damper Ilia and is discharged in whirls from the air inlet fan 114 into the Venturi tube 113 at a high speed, thus being finely sprayed in the Venturi tube 113.
  • the fuel from the fuel injection hole 116a is effectively mixed with the combustion air from the air inlet fan 114, thus forming mixed fuel.
  • the steam injector 118 adds an appropriate amount of steam to the mixed fuel in the Venturi tube 113.
  • the mixed fuel, with the steam passes through the neck of the Venturi tube 113, thus being introduced into the diverged ignition part 113a with a rapidly enlarged diameter.
  • a part of the mixed fuel is stuck to the diverged ignition part 113a.
  • the bent resist members 404 which hold the Venturi tube 113 in the burner body 111 with an interval being formed between the tube 113 and body 111, also cause a resistance in the air circulation from the ignition promoting panel 210, thus allowing the mixed fuel to be stuck thereto.
  • Both the air inlet holes 211 and the ignition chamber 212 of the ignition promoting panel 210 allow a part of the mixed fuel to flow in whirls, thus allowing the mixed fuel to be effectively ignited by an ignition plug (not shown). Therefore, the mixed fuel in the ignition unit 200 is completely ignited and forms a completely ignited flame with the maximum amount of pressurized air being introduced into the ignition unit 200. 28493
  • the completely ignited flame of the ignition unit 200 is, thereafter, introduced into the combustion unit 300.
  • the flame is shrunken.
  • the shrunken flame remains in the combustion unit 300, while complete combustion heat is introduced from the combustion unit 300 into the dryer 400.
  • the complete combustion heat heats the cold aggregate, thus vaporizing moisture of the aggregate into hot steam.
  • the hot steam uniformly increases the inner temperature of the dryer 400 regardless of positions of aggregate in the dryer 400. Due to such a uniformly increased temperature, the fine aggregate in the dryer 400 is not burnt but is appropriately heated. Meanwhile, the crude aggregate is highly heated with the interior of the crude aggregate being effectively heated.
  • the conversion heat of the steam effectively removes impurities from the outside surface of the crude aggregate, thus making the crude aggregate clean and allowing the crude aggregate to be easily coated with a thin AP3 liquid layer. Therefore, the heater of this invention conserves the AP3 liquid to be coated on the crude aggregate.
  • the dryer 400 In the operation of the heater A, the dryer 400 is rotated at a constant speed.
  • the dryer wings 402 repeatedly lift and drop the aggregate in the dryer 400, thus allowing dust and smoke to be effectively discharged from the dryer 400 through an exhaust fan.
  • the dryer wings 402 also allow the fine aggregate to be quickly discharged from the dryer 400, thus preventing the fine aggregate from being overheated in the dryer 400.
  • the crude aggregate With a large volume, is effectively lifted and dropped in the dryer 400 by the dryer wings 402 and so the interior of the crude aggregate is effectively heated to a high temperature.
  • the heater of this invention provides appropriately-heated fine and crude aggregate suitable for forming high quality Ascon.
  • the cold aggregate is heated by steam heat. That is, when moisture of the aggregate is vaporized, thus effectively drying the surface of the fine aggregate, the steam boiler 220 receives heat from the ignition unit 200, thus vaporizing water in the boiler body 221 into steam. The steam of the boiler 220 is discharged from the boiler body 221 into the dryer 400 through the first and second steam nozzles 223, 223', 224 and 224' when necessary.
  • the appropriately heated and dried aggregate of the dryer 400 is, thereafter, fed to a screen unit through the elevator- type feeding means 500.
  • the aggregate is classified into fine and crude aggregate according to size prior to being mixed with AP3 liquid into Ascon.
  • the present invention provides a cold aggregate heater with a steam conversion heat dryer burner.
  • fuel which is fed into a fuel injection nozzle under a pressure of about 2.5 - 3 kg, passes through a plurality of vortex holes at a high speed, thus being discharged in whirls from the nozzle into the dryer burner while being finely sprayed.
  • the primary combustion air passes through an air inlet fan prior to being introduced into the dryer burner, thus being finely sprayed in the dryer burner. Therefore, the fuel in the dryer burner is effectively mixed with the combustion air into mixed fuel.
  • the heater has a means for promoting ignition of the mixed fuel.
  • the ignition promoting means is comprised of an ignition promoting panel with radial holes and ignition chamber, a diverged ignition part of a fuel injection Venturi tube and a plurality of bent resist members arranged at the junction between the burner body and the Venturi tube.
  • the ignition promoting means effectively reduces the instantaneous flow speed of the mixed fuel, thus allowing a part of the mixed fuel to be spread in every direction and be effectively ignited. Therefore, the mixed fuel is completely burnt and generates complete combustion heat, thus vaporizing the moisture of cold aggregate into steam and uniformly increasing the inner temperature of the dryer regardless of internal positions of the dryer. Therefore, the fine aggregate is not overheated, thus conserving AP3 liquid to be coated on the fine aggregate.
  • the crude aggregate is continuously and repeatedly lifted and dropped in the longitudinal dryer at a high temperature. Therefore, the interior of the crude aggregate is effectively heated to an appropriate temperature, thus allowing resulting Ascon to maintain a high temperature for a lengthy period of time.
  • the steam conversion heat removes impurities from the outside surface of the crude aggregate, thus making the crude aggregate clean and allowing the crude aggregate to be easily coated with AP3 liquid.
  • the heater of this invention generates steam conversion heat suitable for effectively heating the interior of the crude aggregate to a high temperature with the fine aggregate being not overheated. Therefore, when about 20 % of crude aggregate, having a size of 19 mm, is included in Ascon used as a top layer of asphalt, it is possible to reduce the amount (6.3 %) of AP3 liquid by about 30 %. Such an appropriately heated aggregate also uniformly improves the quality of Ascon, thus almost completely preventing the resulting Ascon from any plastic deformation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Drying Of Solid Materials (AREA)
  • Road Paving Machines (AREA)

Abstract

Cette invention concerne une unité de chauffage d'agrégats froids comportant un brûleur de séchoir thermique à conversion de vapeur. Ce brûleur de séchoir va mélanger efficacement le combustible finement vaporisé avec un flux primaire d'air de combustion et un flux primaire de vapeur. L'unité de chauffage comprend également un panneau d'aide à l'allumage situé à l'extrémité d'entrée de l'unité d'allumage, ainsi qu'une chaudière à vapeur située à l'extrémité de sortie de ladite unité d'allumage. Le panneau va faciliter l'allumage du combustible mélangé, tandis que la chaudière à vapeur va envoyer un flux de vapeur secondaire vers l'agrégat dans le séchoir. L'unité de chauffage va allumer complètement et brûler le combustible mélangé, puis envoyer toute la chaleur de la combustion dans le séchoir de manière à vaporiser l'humidité de l'agrégat froid en vapeur. L'unité de chauffage va accroître uniformément la température interne du séchoir à l'aide de la chaleur de conversion de la vapeur. Ce système permet de chauffer de manière appropriée l'agrégat mélangé tant avec l'agrégat fin qui n'est pas surchauffé qu'avec l'agrégat brut qui est complètement chauffé à l'intérieur.
PCT/KR1997/000198 1996-12-24 1997-10-22 Unite de chauffage d'agregats froids comportant un bruleur de sechoir thermique a conversion de vapeur WO1998028493A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU47939/97A AU4793997A (en) 1996-12-24 1997-10-22 Cold aggregate heater with steam conversion heat dryer burner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1019960071515A KR100211676B1 (ko) 1996-12-24 1996-12-24 스팀 전환가열식 완전연소 드라이어버너를 채용한 냉골재 가열장치
KR1996/71515 1996-12-24

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KR (1) KR100211676B1 (fr)
AU (1) AU4793997A (fr)
WO (1) WO1998028493A1 (fr)

Cited By (7)

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WO2001071251A1 (fr) * 2000-03-24 2001-09-27 Webasto Thermosysteme International Gmbh Bruleur binaire avec atomisation de combustible par tube de venturi, et tube de venturi pour atomisation de combustible liquide
WO2002012792A1 (fr) * 2000-08-06 2002-02-14 Webasto Thermosysteme International Gmbh Bruleur a pulverisation
WO2003022423A1 (fr) * 2001-09-05 2003-03-20 Webasto Thermosysteme International Gmbh Systeme de conversion de carburant et d'air en reformat, et procede de montage d'un systeme de ce type
CN102563642A (zh) * 2012-02-14 2012-07-11 中国人民解放军国防科学技术大学 一种自吸式气泡雾化燃油喷嘴
CN103015295A (zh) * 2012-12-28 2013-04-03 湖南湘路机械科技有限公司 一种用于加热再生沥青混凝土的搅拌设备
CN103952964A (zh) * 2014-05-09 2014-07-30 李涛 沥青拌和站砂石料加热用的煤气发生和燃烧装置
RU184631U1 (ru) * 2018-01-10 2018-11-01 Андрей Михайлович Черников Сушильная установка для свекловичного жома

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KR100309798B1 (ko) * 1998-12-28 2001-12-17 엄동섭 아스팔트재생장치
KR100440890B1 (ko) * 2001-05-09 2004-07-19 주식회사 자동기 폐모래 재생 시스템 및 그 시스템을 이용한 재생방법
KR101723818B1 (ko) 2016-11-11 2017-04-06 (주) 동일우드 완전연소 시스템 및 완전연소 시스템의 운용 방법
CN109631031A (zh) * 2018-12-07 2019-04-16 云南公投建设集团第五工程有限公司 沥青拌合机用燃烧系统
CN110779013B (zh) * 2019-11-22 2021-07-06 乔永 一种沥青搅拌站超低氮燃烧器

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US4255058A (en) * 1979-06-20 1981-03-10 Wibau Industrie Und Verwaltung Gmbh Apparatus for preparing bituminous mixtures, especially road construction mixtures
DE3628106A1 (de) * 1986-08-19 1988-02-25 Bagela Baumaschinen Gmbh & Co Umlauffaehige mischtrommel fuer asphaltaufbereiter

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DE2446579A1 (de) * 1974-09-30 1976-04-01 Walter Schoelkopf Verfahren und vorrichtung zur wiederverwendung bituminoeser massen
US4255058A (en) * 1979-06-20 1981-03-10 Wibau Industrie Und Verwaltung Gmbh Apparatus for preparing bituminous mixtures, especially road construction mixtures
DE3628106A1 (de) * 1986-08-19 1988-02-25 Bagela Baumaschinen Gmbh & Co Umlauffaehige mischtrommel fuer asphaltaufbereiter

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6793487B2 (en) * 2000-03-24 2004-09-21 Webasto Thermosysteme International Gmbh Binary burner with Venturi tube fuel atomization and Venturi jets for the atomization of liquid fuel
WO2001071251A1 (fr) * 2000-03-24 2001-09-27 Webasto Thermosysteme International Gmbh Bruleur binaire avec atomisation de combustible par tube de venturi, et tube de venturi pour atomisation de combustible liquide
WO2002012792A1 (fr) * 2000-08-06 2002-02-14 Webasto Thermosysteme International Gmbh Bruleur a pulverisation
KR100771965B1 (ko) 2000-08-06 2007-11-01 베바스토 써모시스테메 인터내셔널 게엠베하 분무 버너
US7357820B2 (en) 2001-09-05 2008-04-15 Webasto Ag System for converting fuel and air into reformate
WO2003022422A1 (fr) * 2001-09-05 2003-03-20 Webasto Thermosysteme International Gmbh Systeme de conversion d'air et de carburant en reformat et son procede de montage
WO2003022423A1 (fr) * 2001-09-05 2003-03-20 Webasto Thermosysteme International Gmbh Systeme de conversion de carburant et d'air en reformat, et procede de montage d'un systeme de ce type
US7357821B2 (en) 2001-09-05 2008-04-15 Webasto Ag System for converting fuel and air into reformate
CN102563642A (zh) * 2012-02-14 2012-07-11 中国人民解放军国防科学技术大学 一种自吸式气泡雾化燃油喷嘴
CN103015295A (zh) * 2012-12-28 2013-04-03 湖南湘路机械科技有限公司 一种用于加热再生沥青混凝土的搅拌设备
CN103015295B (zh) * 2012-12-28 2015-01-07 湖南湘路机械科技有限公司 一种用于加热再生沥青混凝土的搅拌设备
CN103952964A (zh) * 2014-05-09 2014-07-30 李涛 沥青拌和站砂石料加热用的煤气发生和燃烧装置
CN103952964B (zh) * 2014-05-09 2016-02-03 李双美 沥青拌和站砂石料加热用的煤气发生和燃烧装置
RU184631U1 (ru) * 2018-01-10 2018-11-01 Андрей Михайлович Черников Сушильная установка для свекловичного жома

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AU4793997A (en) 1998-07-17
KR100211676B1 (ko) 1999-08-02
KR19980052508A (ko) 1998-09-25

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