KR860000565B1 - The high efficiency burner of the heavy oil - Google Patents

Abstract

This invention provides high efficiency combustion device for small or middle size boilers using heavy oils, especially bunker-C oil. This includes fuel intake part which flows back and then supplies exhaust gas partly; burner part which mixes the fuel pulverized in two steps with the preheated injection air and then injects the mixed gas as the state of an elementary particle by making nozzle injection angles different.

Description

High efficiency combustion device of heavy oil boiler

1 is an overall configuration diagram of the present invention.

) 사시도.2 is a boiler crater of the present invention (

) Perspective view.

3 is a perspective view of the burner of the present invention.

4 is an exploded perspective view of the burner of FIG.

5 is an enlarged perspective view of the burner of FIG.

6 is a cross-sectional view of the cradle of FIG.

7 is a partially enlarged view of the burner of FIG.

FIG. 8 is a configuration diagram of the secondary mixer nozzle spray surface in FIGS. 4, 5, and 7; FIG.

9 is a schematic view of the primary mixer nozzle spray surface.

* Explanation of symbols for main parts of the drawings

1: boiler 2: heat exchanger

3: Injector Air Compressor 4: Deflector Plate

5: oil supply pipe 6: compressed hot air supply pipe

7: compressed air exhaust pipe 8: ventilation control valve

9: fan 10: exhaust gas return duct (DUCT)

11: opening 12: year

13: insulation 20: burner

21: supply pipe 22: nozzle holder

23: Impeller 24: Inner tube

25 spring 26 primary mixer nozzle

27: ring 28: secondary mixer nozzle

29: nozzle cap 30: crater

31: Myth 32: Myth

33: partition plate 34: opening

35: front sealing plate 36: burner support for attaching the bolt

37: bolts for mounting the reflux duct support

38: A fireproof wall deposited on the surface of the Geumgangsa by the uneven shape

The present invention relates to a small and medium boiler high efficiency combustion apparatus which is particularly suitable for heavy oil, especially bunker C.

Specifically, a crater is installed on the crater surface of the boiler combustion chamber so that a part of the exhaust gas can be reflux-supplied, and the crater is extruded by vortical decomposition of the oil fuel in the first and second stages. By attaching a burner capable of atomizing and diffusing while colliding with air to form a mixture of air and fuel, ignition of high-viscosity fuel can be performed quickly and easily, as well as soot and soot. In particular, the present invention relates to a combustion apparatus of a boiler that enables high combustion efficiency with little death of nitrogen oxide (NO _x ) generation.

Originally, heavy oil is a dark viscous oil obtained at 300 ° C or higher after classifying gasoline, kerosene and light oil from petroleum oil. It is known that it is widely used as fuel for ships, ships, etc., but since heavy oil, especially bunker C oil, has high solidification properties, it is necessary to pay close attention to its use in ordinary homes and small factories. However, there is a serious flaw with pollution.

In other words, heavy oil as a fuel is usually preheated for the purpose of having a degree of atomization, and the viscosity thereof is lowered. However, the viscosity is limited because of transportability and atomization, and is contained therein. Due to the high formation of 0.01-0.5%, burner nozzles were clogged, or due to the solidification phenomena that occurred during relatively long periods of storage such as summer, etc. _X ), CO, and soot caused by dust, unburned, and air pollution were inevitable.

In view of this, even if the combustion efficiency is increased under different conditions, the generation rate of nitrogen oxides is relatively increased, so that a separate scrubbing facility and subsequent pollution treatment using malzone in water + oil to remove it There is a drawback that this scrubbing facility must have the necessary secondary secondary and neutralization facilities to control water pollution.

In addition, they need additional facilities to prevent freezing during the cold season, which requires the best heat. In case of using a subsequent facility such as water and oil, the efficiency is relatively high, but the thermal efficiency decreases according to the amount of evaporation of water. On the other hand, if the exhaust temperature is lowered to obtain efficiency, the sulfate life due to the combination of sulfur oxides (SO _x ) in the combustion gas, and the corrosion of the boiler, shortens the life of the boiler. There have been many problems with eliminating pollution factors, such as the release of fumes (such as soot) that are tangled together.

式 : 50-400kg/㎠) 회전식(回轉式 : 주속-1cm/s) 등이 알려진 바 있으며 액체 연료 버어너의 경우에는 유압 분무식 버어너, 회전식 버어너, 저압 분무식 버어너, 고압 분무식 버어너, 내부 혼합식 버어너 등의 기술이 알려져 있다.In general, the fuel-free atomization includes a low pressure air spray type (0.01-1.5 kg / cm 2) and a high pressure air (or water vapor) spray type (2-10 kg / cm 2) in the case of air (or water vapor) injection type. In the case of the spray type, the vortex spray type (3-40kg / cm 2), the collision sorting type (衝突 噴 流 式: 1-7kg / ㎠), the high pressure intermittent type (高壓 間

式: 50-400kg / ㎠) Rotary type (circumference: 1cm / s) is known. For liquid fuel burners, hydraulic spray burners, rotary burners, low pressure spray burners, high pressure spray types Techniques such as burners and internally mixed burners are known.

Although the pump power is the minimum in the type of hydraulic spray burner, the operation range in which spray operation is stable around optimum conditions because of hydraulic pressure is narrow. That is, when the flow rate changes freely and stops, clogging of the nozzle is likely to occur due to radiant heat in the furnace.

The rotary burner is a method in which oil is dropped into a rotating cup of about 3,500-10,000 rpm per minute and fined by its centrifugal force, and primary air is sucked by a coaxial fan. In this burner, the pressure is about 0.3 kg / cm 2 and the flow rate can be controlled to be quite wide, but is not suitable for the viscous oil heavy oil fuel as in the present invention.

Low pressure spray burners usually use 50-150 cmAq of low pressure air as a dispensing medium, and oil pressurizes 0.3-0.5kg / cm2, which is suitable for small and medium boilers. There are many shortcomings of pollution factors.

In the high pressure spray burner, oil is atomized by a high speed flow of air or steam of about 2-10 kg / cm 2, and the amount of air or steam required for spraying is determined by the theoretical amount of air (Stoichiomatric: 理 論 空氣 量). It can make a combustion flame evenly close to 2-10%, but it is heavy, and due to its structural complexity, it can not be applied to small and medium boilers, and it consumes 0.2kg of steam for 1kg of oil burning (boiler structure, There are drawbacks, such as inefficiency, followed by capacity), and slow flame imbalance and ignition at constant steam pressures.

In the case of the internally mixed burner, the oil entering the inlet is mixed in the mixing chamber with the fluid for spray entering the air port, and then atomized in the injection hole. There are many advantages such as high viscosity, atomization, small spray angle, and flow control range of 1: 10 and quite wide. The defects such as the occurrence of vibrations and gusts of unbalanced combustion caused by them are of course difficult to manufacture and use.

) 현상 등의 여러 가지 문제점이 있으며, 특히 질소 산화률(NO_x)의 발생억제 수단이 결여되어 있다.The known techniques, although suitable for their intended purpose, include, in addition to the drawbacks listed above, heat loss (communication suction force) due to vapor binding phenomenon or draft rising heat dissipation of the inlet. Overload during ignition

There are various problems such as) phenomenon, in particular, there is a lack of means for suppressing the generation of nitrogen oxidation rate (NO _x ).

In other words, these well-known techniques are used in the combustion chamber even if the burner is used in a different form depending on the shape of the boiler combustion chamber, the connection, the water pipe type, the hot water, the steam boiler, or the required steam pressure. Combustion flames are diffuse diffusion flames of opaque fluoride due to molecular diffusion or vortex dispersion of fuel, so that fumes, nitrogen oxides, etc., caused by suspended carbon particles formed in the flame during combustion It was not possible to rule out pollution tolerance.

This is usually possible in the combustion of liquid fuel, only in the gas phase, ignited in a natural mixer layer near the liquid surface, and diffusion of vapor and air by heat in the flame. Combustion is continued by two related processes of its combustion, creating a mixer by mixing, while reactants (fuel and oxidant) are initially separated in the case of diffuse flames produced by the release of fuel gas. When the fuel is burned and then ignited, there is no theory that quantitatively elucidates the mechanisms of combustion chemical reactions, and the "geldobitchi" nitrogen oxides (NO) have been proposed. _x ) Formation theory and equations generally indicate that NO _x formation is characterized by a higher combustion temperature, a higher air concentration in the combustion zone, and a residence time of the combustion gas in the hot zone. It is thought that this may be due to the above two facts which indicate that the generation of NO _x increases greatly with the long time.

The present invention, unlike the known techniques at all, so-called pre-mixed flame (豫 混合 火炎) properties to obtain a combustion flame that can not only increase the thermal efficiency, but also to reduce the generation of smoke and the like, to minimize the flame temperature NO _{x The} main objective is to obtain a combustion apparatus for medium and small boilers, which is optimal for heavy oil, especially bunker C oil, which can suppress production.

Another object of the present invention is that the atomization of the fuel, which is similar to the collision classification method by compromising the types of the low pressure spray type, the high pressure spray type and the internal mixed burner among the burners listed in the above known technologies. Heavy oil burner (1kg / ㎠-10kg / ㎠) to obtain.

As a specific element of the present invention, a crater frame capable of refluxing and supplying a part of the exhaust gas to the crater surface of the boiler combustion chamber, and extruded while decomposing the oil into the vortex in the first and second phases, preheating injection air and one In the second stage, the burner can be formed into a nearly free mixer, which is then sprayed by the nozzle jetting angle difference, and the mixer can be sprayed into ultra-fine particles. The installation maximizes the ignition and combustion efficiency of highly viscous fuels and enables synergistic fuel savings with little soot, soot and NO _x emissions.

This will be described in detail with reference to the accompanying drawings.

1 is an overall configuration diagram showing an embodiment of the present invention, the reference numeral 1 denotes a boiler.

The flue gas outlet 1a is perforated above the boiler 1 in the direction of the crater, and a known flue 12 is installed, and a reflux duct 10 of some flue gas is provided at the lower end of the flue 12 to be described later. It is installed in communication with the opening 34 above the mold 30, and the switch 11 which opens and adjusts by the annual 11a of a handle (not shown) is installed in the appropriate position in the middle of this duct 10.

In the flue surface immediately above the exhaust gas inlet port 10a of the duct 10, a known heat exchanger 2 is connected to communicate with the compressed air exhaust pipe 7 of the injection air compressor 3, and the compressed air supplied therefrom. While preheating the flue-gas waste heat of the flue, the compressed hot air supply pipe 6 is delivered to be fed to the supply pipe 21 of the burner 30 described later. In the drawings, reference numeral 4 denotes a deflector plate, 5 an oil supply pipe, 8 a draft damper 9 a fan, 9a a pulley, and 13 a burner 20.

FIG. 2 is a perspective view of the crater frame 30 fixed to the crater surface of the boiler 1 in FIG. 1, wherein the body of the crater frame 30 is composed of a circular inner frame 31 and an outer frame 32. The bottom sealing plate 35 and the partition plate 33 are protruded between them, and the partition plate 33 is provided with a plurality of through holes 33a.

A ring-shaped diaphragm 30b is integrally provided so that a fuel injection hole 30a is formed at the front side of the inner frame 31, and a plurality of through holes communicating with the hollow portions of the inner and outer frames are provided at the front side of the diaphragm 30b. 31a), a fireproof wall 38 formed by depositing gold-coated steel on the surface on the rear side in an uneven shape is formed as a front narrow back light, and the upper surface of the outer frame 32 of the exhaust gas return duct 10 described above. The opening part 34 which is connected to the outlet 10b is provided, and is closely attached to the end part of the outlet 10b and the bolt 37. FIG.

In the figure, reference numeral 36 denotes a bolt tightly attached to the burner 20 protective support frame (unsigned).

3 is a perspective view of the burner 20 installed in the crater 30 fuel injection port 30a of FIG. 1, in which 21 is a supply pipe, 22 is a nozzle holder, 28 is a secondary mixer nozzle, and 29 is a nozzle cap. to be.

FIG. 4 is an exploded perspective view of FIG. 3, in the center of the supply pipe 21, an oil line 21a communicating with the oil supply pipe 5 is passed through, and at the outer periphery of the oil line 21a, the aforementioned compressed hot air supply pipe ( 21a) is a plurality of hot air supply hole (21b) that is separated and supplied in multiple galle is drilled.

The nozzle holder 22 screwed forward of the supply pipe 21 is provided with through-holes 22b communicating with the hot air supply hole 21b, and a flow passage 22a communicating with the oil pipeline 21a. A vacancy is formed behind the 22a, and a well-known impeller 23 is built in here, and the inner tube 24 is protruded relatively long in front of the flow path 22a.

The inner tube 24 is melt-molded with a tip end face in an arc shape, and a primary mixer nozzle 26 having a radial spraying material surface 26f and a projection surface 26e is provided with an outer diameter surface of the inner tube 24. It is almost intimately formed and elastically formed by the spring 25 to be described later, and on the body surface of the nozzle 26, an arc-shaped split surface 26g is formed on the inner tip side, and the inner tube A pore 26d is drilled at a position substantially coincident with the tip surface of (24) so that the oil fuel is ejected.

On the outside of the body of the nozzle 26 through which the pores 26d are perforated, a collision column 26c is projected between the pores 26d, and on the back side thereof, the reverse of the fuel particles ejected from the pores 26d is prevented. The ring 27 for maintaining pressure equilibrium is rotated.

At the rear of the ring 27, a plurality of ridges 26b are raised to the same height as the collision ridges 26c so as to form a crossroad 26a. Snow. The spring 25 is smoke and pores compressed in the through-hole 22b by arranging the tip projection surface 26e of the primary mixer nozzle 26 in close contact with the inner surface of the tip of the secondary mixer nozzle 28 which will be described later. While the precision is injected to the mixer injection with the fuel ejected at 26d, the primary mixer nozzle 26 is pushed backward during the overload, and the momentary pore 26d is pushed back while elasticizing the spring 25. ) Overpressure is regulated by closing action by tip end surface.

Again, the nozzle 26 is attached to the tip of the nozzle holder 22 while the secondary mixer nozzle 28 is covered outside the body of the nozzle 26.

The secondary mixer nozzle 28 punctures the injection hole 28b whose inner diameter is in communication with the through hole 22b of the primary mixer nozzle holder 22 by a fine hole having a smaller diameter than the through hole 22b of the nozzle holder. In front of the injection hole 28b, a nozzle portion is formed so as to form a circular demand 28e, and in this nozzle portion, a plurality of projections 28d radially protrude radially on the peripheral end surface of the mesopores 28a. It is comprised so that the preheating air which blows out from the yarn holes 28b may be injected into the sensory tract 28c between the protrusions 28d.

Subsequently, the nozzle cap 29 attached to the secondary mixer nozzle 28 punctures the diffuser hole 29a having a larger diameter than the central through hole 28a of the nozzle 28 in the middle of the secondary mixer nozzle. 28, that is, the edge of the central through hole 28a is slightly projected outwardly, and the tip inner surface of the nozzle cap 29 is almost in contact with the projections 28d of the secondary mixer nozzle 28. It is configured to be attached.

5 and 6 are cross-sectional views of the burner 20 and the crater 30 described above, and FIG. 7 is a first vortex-decomposed oil fuel by the impeller 23 in the burner 20. Oil collides with the preheating air which is collided at the splitting surface 26g of the inner end of the mixer nozzle 26 and sputtered again and spouted into the pores 26d and extruded into the airway 26a. And a preheated extruded air and ash ejected from the tip triangular path 28c of the secondary mixer nozzle 28 at the moment of forming a mixer with the preheated compressed air and then ejecting it to the spray path surface 26f at the tip. It is an expanded sectional view for showing the state which forms a secondary mixer, while joining.

Reference numeral A denotes the injection direction of the fuel injected from the triangular path 28c of the secondary mixer nozzle 28 and B is the injection of fuel injected from the injection path surface 26f of the primary mixer nozzle 26. The direction is shown.

8 and 9 are plan views showing the spray path surface states of the above-described secondary mixer nozzles 28 and primary mixer nozzles 26.

의 두갈래로 송기되고, 기로(26a)→세공(26d)에서 분출되는 기름연료와 격돌하면서 1차 혼합기를 조성하여 상기와 같이 분사되는 한편, 분사공(28b)→환요구(28e)에서 와류 순환→2차 혼합기 노즐(28)의 선단 삼각요로(28c)로 분출하여 1차 혼합기와 격돌하면서 2차 혼합기를 조성하게된다. 이와같이 분사되는 연료(2차 혼합기)는 노즐 선단의 분사각(화살표 A,B)방향으로 확산되면서 화구틀(30) 내면의 금강사를 피착한 내화벽(38)에 다시 부딪혀 연료는 초미쇄의 소립자로 분해되고, 따라서 점화초기에 있어서도 화염대(연료와 산화제와의 경계화염역)가 거의없이 신속 용이하게 착화되면서 균일한 연소 화염을 행하게 되므로 과부하(過負荷)현상은 거의 일어나지 않음을 알 수 있었다.The present invention configured in this way, first, in the burner 20, the oil fuel passes through the oil supply pipe 5 and starts to flow into the oil pipe passage 21a at the center of the supply pipe 21 at the rear of the burner body, It is injected into the central through hole 28a at the tip of the body 20, and the path thereof is the first vortex decomposition → flow path 22a by the oil supply line 5a → the oil supply line 21a of the supply line 21 → the pelleter 23. ) → inner tube (24) → fractionation surface (26 g) → vortex decomposition again → pore (26d) → primary mixer composition → injection furnace surface (26f) → secondary mixer nozzle while colliding with the extruded air of furnace (26a) A secondary mixer is formed while re-colliding with the preheated extruded air ejected from the tip triangular path 28c of (28). In parallel, the flow of preheated compressed air supplied from the air compressor 3 for injection is controlled by the air compressor 3 for injection → valve 7a → air pipe 7 → heat exchanger 2 → air supply 6 → operation of valve (6a) → air supply hole (21b) formed in supply pipe (21) of burner (20) → through hole (22b) of nozzle holder (22) → increase of air pressure in the space portion of spring 25

It is blown in two ways, and the primary mixer is formed by injecting as described above while colliding with the oil fuel ejected from the airway 26a → the pore 26d, and the vortex in the injection hole 28b → the ring demand 28e. The secondary mixture is blown into the tip triangular path 28c of the circulation-secondary mixer nozzle 28 to collide with the primary mixer. The fuel (secondary mixer) injected in this way is diffused toward the injection angles (arrows A and B) at the tip of the nozzle and again hits the fire wall 38 on which the gold steel on the inner surface of the crater 30 is deposited. Therefore, it was found that almost no overload phenomenon occurred because evenly in the initial stage of ignition, flame zone (border flame zone between fuel and oxidant) was ignited quickly and easily and uniformly combusted. .

That is, the combustion of the heavy oil (bunker C oil) fuel according to the present invention is a combustible mixer layer because the mixer due to the vortex and collision over the water and air is atomized at a rate of velocity. 연소) does not exist separately, and combustion occurs as soon as it is close to the premixed flame. In the actual experiments, the combustion oil of the heavy oil fuel stream according to the present invention, which was visually confirmed, produced almost transparent non-fluorinated salts. From the fact that it is almost the same as, the fuel particles according to the present invention are assumed to be flames of a nature close to the premixed flame which appears when the particle diameter is sufficiently small.

In addition, the uniform continuous flame of non-fluorine was obtained because the air supply by the fan 9 at the rear of the burner 20 is supplied to the combustion chamber through the deflector plate 4, so that the air concentration is relatively limited. Meanwhile, the crater 30 has a part of the exhaust gas circulated through the reflux duct 10, so that the residence time of the combustion gas is generally short, and the reflux duct supplied to the through hole 31a at the tip of the crater 30 ( Some high temperature flue gases in 10) form a high temperature zone in addition to the fuel mixer atomized from the burner 20, and at the same time maintain the flame temperature by always promoting crushing and combustibility when it strikes the gold steel coating layer of the hardened wall. It is thought to be due in points that hyeongseo to normal flame of less than 1,100-1,200 ℃ critical temperature of the NO _x generation.

Therefore, in the present invention, the combustion efficiency is excellent and the pollution factor can be minimized under the injection conditions of the mixer which becomes the air + fuel by the burner 20 and the crushing conditions of some flue gas and gold steel yarn supplied to the crater 30, Although the high viscosity heavy oil can improve the ignition and combustibility to such an extent that it is almost inferior to the liquid having good vaporization, it is possible to achieve a relatively excellent effect even under the conditions alone of the burner 20.

Also in the actual experiment, the compressed air heated at 100 ° C. or higher of 1 kg / cm 2 -10 kg / cm 2 and bunker C oil (JIS K 2205-1958: No. 6) were supplied to the burner 20 of the present invention. As a result of spraying on the steel coating layer in the combustion chamber at the spray angle of 15-45 °, it was possible to obtain a uniform continuous flame of transparent non-fluorine in the initial ignition as described above, and the flame temperature at this time was approximately 1,000-1,100 ° C. It was found that the flames were continuously burned at 1,100-1,200 ° C. after being maintained for a minute, which means that some of the exhaust gases in the reflux duct 10 were burned from the burner 20 and atomized was added to the fuel heater and the hot zone. It is thought to be due to the formation of.

As described above, the boiler combustion apparatus according to the present invention is not only excellent in ignition and combustion efficiency but also in reducing soot, soot and NOx generation in heavy oil, especially bunker C-oil fuel. Since it is most suitable for medium boilers, it can be used for small factories as well as general households, and it is particularly economically effective.

Claims (3)

On the crater surface of the boiler combustion chamber (1), a crater frame (30) capable of refluxing and supplying a part of the exhaust gas is installed, and the pre-heater and the secondary mixer are mixed with the preheated air and the heavy oil fuel stream in that order. It is characterized in that the burner 20 is installed, and the compressed air of the injection air compressor 3 is a preliminary air source supplied to the burner 20 through the heat exchanger 2 installed in the flue 12. High efficiency combustor of heavy oil boiler. In the crater frame 30 according to claim 1, the inner frame 31 and the outer frame 32, the partition plate 33, the upper surface opening 34 and the through hole 33a is perforated, and the hollow portion between the inner frame and the outer frame. Heavy oil, characterized in that the through-holes (31a) are formed in contact with each other, and the inner surface of the inner frame (31) is formed into a typical halo shape from the fuel injection port (30a), and a fireproof wall (38) is formed on the surface of which is deposited uneven steel. High efficiency combustion device of the boiler. In the burner (20) of claim 1, a hot air supply hole (21b) is formed at the periphery of the high-quality pipe (21) in which the oil pipe (21a) is formed, and the nozzle holder (22) is screwed and fixed thereto. The flow path 22a and the through-hole 22b are formed, the well-known impeller 23 is installed in the back surface of the flow path 22a, and the main mixer nozzle | bulb which is closely installed in this front end has the air flow 26a and the projection 26b. , A collision projection 26c, a pore 26d, a projection surface 26e, an injection path surface 26f, and a fractionation surface 26g are formed, and a central through hole 28a, an injection hole 28b, and a triangular path ( 28c), a high-efficiency combustion apparatus for a steam boiler, characterized by covering a secondary mixer nozzle (28) formed by forming a ring demand (28e) and a protrusion (28d).

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