JP2001235113A - Burner for burning waste oil, or the like - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a burner structure for burning waste oil, etc., which can exhibit high combustion performance against waste oil, etc. SOLUTION: This burner is provided with an atomizing nozzle 10 composed of a flow passage 1 which is installed along the center axis of the nozzle 10 to supply waste oil, etc., another flow passage 2 which is installed around the passage 1 to supply a gas for atomizing the waste oil, etc., and oil and gas mixing chamber 5 in which the waste oil, etc., and atomizing gas which are respectively introduced into the chamber 5 from the flow passages 1 and 2 through a hole 3 for supplying waste oil, etc., and another hole 4 for supplying atomizing gas are mixed with each other, and a spray nozzle 6 which sprays the mixed fluid produced in the mixing chamber 5 into the air in an atomized state. The atomizing gas supplying hole 4 through which the atomizing gas from the flow passage 2 is supplied into the mixing chamber 5 is constituted in such a way that the mixed fluid produced in the chamber 5 can be revolved by the atomizing gas when the gas is supplied.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a burner for burning waste oil and the like.

[0002]

2. Description of the Related Art Waste oil such as residue oil and oil waste oil discharged from internal combustion engines and other various driving engines are accumulated every day because there is no appropriate use or an optimal treatment method, and such waste oil is used as fuel. There is a demand for the development of a combustion treatment apparatus capable of performing appropriate combustion treatment.

FIG. 17 and FIG. 18 show an example of a waste oil combustion treatment apparatus conventionally provided from such a viewpoint (for example, see Japanese Patent Application Laid-Open No. 6-50524: First Conventional Example). The configuration of this waste oil combustion treatment device includes a combustion furnace A formed by surrounding a combustion chamber 32 with a refractory structure wall 31;
Two left and right flame guide cylinders C, C provided with the front side refractory structure wall 31 of the combustion furnace A penetrating inward and outward.
And a blower 3 on one side of the outer end via an open / close damper 35a.
6a are provided in series, the cylinder wall of the portion located in the combustion chamber 32 is provided with air supply holes 34, 34,... Into the combustion chamber 32, and the cooling water passage 41 is provided in the cylinder wall. 1
And an opening / closing damper 35 on one of the outer ends.
b, a cooling water passage 41 is provided inside the cylinder wall, the inner end of which is opposed to the inner end side opening of the flame guide path C 'in the flame guide cylinder C, while the blower 36b is connected to the blower 36b.
And an external hopper B provided separately from the combustion furnace body A through an openable and closable shutoff cover plate 53 at its outer end side waste oil receiving portion. A waste oil supply mechanism 42 having a screw conveyor structure with a side waste oil delivery unit facing the inside of the combustion chamber 32, and a waste oil supply mechanism 42 connected to the bottom of the combustion chamber 32 for storing and burning waste oil from the waste oil supply mechanism 42. It comprises a combustion oil residue discharge chamber 46 in which a trolley 47 is movably mounted between the trolley 47 and the bottom of the combustion chamber 32. In the trolley 47, ceramic balls 21 for generating far-infrared rays are housed.

In the configuration of the combustion processing apparatus according to the present invention, an appropriate amount of waste oil is stored in the upper part of the trolley 47 via the waste oil supply mechanism 42, and then is ignited directly, and the first and second air blowers are provided. By burning a large amount of air supplied through the pipes 37 and 38 and the high temperature by the flame guide cylinders C and C, waste oil containing impurities or waste oil solidified in a sludge state. Can also be effectively burned.

Further, by housing the ceramic balls 21, 21... On the trolley 47 as described above, the burning of waste oil is accelerated by the far infrared rays generated from the ceramic balls 21, 21. By accumulating heat of the balls 21, 21, ..., combustion can be promoted.

However, in such a furnace-type combustion processing apparatus, if a large amount of waste oil is to be burned at a time,
Since the size of the apparatus is inevitably increased, it is necessary to take measures to increase the number of apparatuses and to process a large amount. In addition, because of poor combustion start performance, incomplete combustion products are inevitably discharged at the time of initial waste oil supply. Therefore, in a situation in which a small amount of waste oil is generated intermittently, a waste oil storage facility is separately installed and incomplete combustion products are frequently discharged unless the waste oil is collected and treated to some extent.

[0007] In order to solve such a problem, a burner structure is adopted, and the burner portion is provided with an atomizing nozzle capable of atomizing waste oil, which is originally difficult to atomize, as small as possible. It is necessary to reduce the emission of incomplete combustion products as early as possible from the beginning of combustion, and to make it possible to efficiently burn by continuously burning waste oil every time waste oil is discharged. Required.

[0008] Next, from such a viewpoint, an example of the structure of an atomizing nozzle which is considered to be most suitable for combustion of waste oil among nozzles (atomizers) for atomizing liquid fuel or the like which have been conventionally proposed. As shown in FIG.
No. 683: Second conventional example).

As shown in FIG. 19, the atomizing nozzle 50 has a fuel supply passage 51 for supplying a fuel CWM containing solid particles, and a spray medium supply passage for supplying a spray medium mixed with the fuel CWM. 52, an upstream mixing pre-chamber 56 communicating with the fuel supply passage 51 and the spray medium supply passage 52, and a fuel CWM communicating with the mixing pre-chamber 56.
Downstream spray hole 5 for spraying a mixed fluid of spray and spray medium
In the atomizer for liquid fuel provided with the mixing chamber 55 having 7, 57..., The pre-mixing chamber 56 has an annular cross section formed by the large-diameter inner peripheral wall 58 and the small-diameter inner peripheral wall 59, In addition, one of the fuel supply passage 51 and the spray medium supply passage 52 communicates with the mixing pre-chamber 56 having the annular cross section formed by the large-diameter inner peripheral wall 58 and the small-diameter inner peripheral wall 59. On the other hand, the supply path on the other side is configured to communicate with the premixing chamber 56 having an annular cross section through a communication hole 60 opened in the peripheral wall in a direction intersecting therewith.

[0010] The atomizing nozzle 50 is provided with a CWM (Coal Water Mixtu), which is a liquid fuel in a broad sense.
re) A nozzle developed for combustion. CWM is a slurry that contains 60-70% of coal particles in water.
No matter how much the atomization proceeds, the atomization cannot be made smaller than the size of the coal particles, and the coal is supplied in a solid-liquid two-phase state. Therefore, a structure that prevents abrasion of the nozzle material is desired. Therefore, as described above, the pre-mixing chamber 56 before entering the mixing chamber 55
Is to form an annular flow path, and a fluid film is formed in the annular flow path. For this reason, a part of the fluid film is remixed in the downstream mixing chamber 55 that is continuous with the annular flow path, and the atomization efficiency is reduced.

Further, in the atomization nozzle 50, a part of the fuel CWM enters the mixing chamber 55 in a state of a fluid film formed in the pre-mixing chamber 56, and scatters from the spray holes 57, while the remaining fuel CWM is removed. A part is scattered as it is as a mixed phase flow in the mixing chamber 55. Therefore, the spray holes 57, 57
... The spray angle per nozzle is limited to more than ten degrees. To increase the spray angle of the nozzle as a whole, the spray holes 57 and 5 are required.
.. Must be increased to increase the spray volume per nozzle.

[0012] These situations are the same in the case of waste oil containing various sludges, and similar problems occur.

[0013]

As described above, in the conventional apparatus for treating waste oil and the like according to the first conventional example, when the waste oil containing a large amount of impurities is subjected to the combustion treatment, the second conventional example is disclosed in Japanese Patent Application Laid-Open No. HEI 9-163873. In the case where the fuel atomization nozzle is not provided as in JP-A-6-50524, incomplete combustion products are likely to be generated at the beginning of the combustion. Therefore, the second
It is desirable to add a atomizing nozzle as shown in the conventional example of Example 1 to atomize waste oil and then burn it.

However, as described above, atomization of a fluid such as waste oil having high viscosity and containing impurities is not always easy by the atomization nozzle as in the second conventional example.
Therefore, development of a combustion burner having a high-performance atomization nozzle structure capable of efficiently atomizing even the high-viscosity waste oil described above has been desired.

The present invention has been made to solve such a problem, and has a nozzle structure capable of efficiently atomizing high-viscosity waste oil as described above. It is an object of the present invention to provide a burner for combustion of waste oil or the like, which makes it possible to reduce the emission of incompletely combusted substances even in the early stage of the start of combustion as in the prior art and to enable efficient combustion treatment.

[0016]

In order to achieve the above objects, the present invention is provided with the following means for solving the problems.

(1) A waste oil etc. combustion burner according to the present invention is a waste oil etc. supply flow path 1 for supplying waste oil etc. installed along a central axis of a nozzle portion.
A gas supply channel 2 for atomizing gas for atomizing waste oil and the like, which is provided to surround the supply channel 1 for waste oil and the like, and a gas supply channel 2 for atomizing the waste oil and the like. The waste oil and the atomizing gas from the atomizing gas supply flow path 2 are supplied to the waste oil supply hole 3 and the atomizing gas supply hole 4, respectively.
And an atomizing nozzle 10 composed of an oil-gas mixing chamber 5 to be introduced through the oil-gas mixing chamber 5 and a spray port 6 for atomizing the mixed fluid in the oil-gas mixing chamber 5 and injecting it into the atmosphere. The atomizing gas supply hole 4 for supplying the atomizing gas from the atomizing gas supply flow path 1 into the oil-gas mixing chamber 5 is provided with the atomizing gas supplied when the atomizing gas is supplied. Thus, the mixed fluid in the oil-air mixing chamber 5 is swirled.

(2) The burner for burning waste oil or the like according to the second aspect of the present invention is the same as the first aspect of the invention, except that the tubular body 20b having a porous wall provided so as to surround the atomizing nozzle 10 is provided. And a flame stabilizer 20 comprising a divergent diffuser portion 20a provided at the tip of the cylindrical body 20b.

(3) The burner for burning waste oil or the like according to the third aspect of the present invention is the burner for burning waste oil etc. according to the second aspect of the present invention, wherein the diameter φ ₇ of the cylindrical body 20b of the porous wall of the flame stabilizer 20 is fine. Ratio φ ₇ / φ ₁ with the diameter φ ₁ of the forming nozzle 10
Therefore, the configuration is such that φ ₇ / φ ₁ is 1.8 or less.

(4) The invention according to claim 4 The burner for burning waste oil etc. according to the present invention, in the configuration according to the invention according to claim 2, is characterized in that the length L ₁ of the cylindrical body 20 b of the porous wall of the flame stabilizer 20 is Ratio L ₁ / φ ₇ of diameter φ ₇ of cylindrical body 20 b
Therefore, the configuration is such that L ₁ / φ ₇ is 1.2 or more.

(5) The burner for burning waste oil etc. of the present invention according to the fifth aspect of the present invention, the diameter of the diffuser portion 20a of the flame stabilizer 20 is reduced by the diameter φ ₈ of the atomizing nozzle 10 Ratio to diameter φ ₁ φ ₈ / φ ₁
Thus, the configuration is such that φ ₈ / φ ₁ is 6.0 or less.

[0022]

According to the first aspect of the present invention, there is provided a burner for burning waste oil or the like, which is provided along a central axis of a nozzle portion and supplies waste oil or the like.
A gas supply channel 2 for atomizing gas for atomizing waste oil and the like, which is provided to surround the supply channel 1 for waste oil and the like, and a gas supply channel 2 for atomizing the waste oil and the like. The waste oil and the atomizing gas from the atomizing gas supply flow path 2 are supplied to the waste oil supply hole 3 and the atomizing gas supply hole 4, respectively.
And an atomizing nozzle 10 composed of an oil-gas mixing chamber 5 to be introduced through the oil-gas mixing chamber 5 and a spray port 6 for atomizing the mixed fluid in the oil-gas mixing chamber 5 and injecting it into the atmosphere. The atomizing gas supply hole 4 for supplying the atomizing gas from the atomizing gas supply flow path 1 into the oil-gas mixing chamber 5 is provided with the atomizing gas supplied when the atomizing gas is supplied. Thus, the mixed fluid in the oil-air mixing chamber 5 is swirled.

Therefore, in the burner for burning waste oil etc. of the present invention, by using the above nozzle structure,
The mixing performance of the waste oil and the like and the atomizing gas in the oil-gas mixing chamber 5 and the atomization performance of the waste oil and the like are improved, and the droplets of the waste liquid having a smaller particle size than the nozzles conventionally used can be formed. As a result, the ignitability at the beginning of the combustion start can be improved. Further, since the particle diameter of the waste oil or the like becomes small, the burn-out time is shortened, and the unburned matter can be reduced.

Further, in the atomizing nozzle structure, since the mixed fluid in the oil-gas mixing chamber 5 is particularly atomized by applying a swirling force, the fluid is injected from the oil-gas mixing chamber 5 to the atmosphere. The spray angle θdeg of the fuel such as waste oil changes depending on the flow rate of the atomizing gas, and becomes wider than when there is no turning force. In other words, the spraying in the so-called full cone state approaches the preferable spray characteristics in the hollow cone state while maintaining the full cone state.

This spray flow produces an effective entrain flow in the gap between the divergent diffuser portion 20a of the flame stabilizer 20 which will be described later, and the porous wall cylindrical body 20b of the flame stabilizer 20 and the atomizing nozzle. Since it works so that air is efficiently drawn in from the flow path between the fuel cell 10 and the fuel cell 10, it also serves as a driving force for supplying air for combustion. That is, by matching the spray angle θdeg of the atomization nozzle 10 with the spread angle R of the diffuser portion 20 a of the flame stabilizer 20, a further suction force of the combustion air is generated. Further, in front of the spray flow, when the swirling force is strong, a so-called recirculation region is formed in which air is drawn into the spray flow side.

(2) According to the second aspect of the present invention, in the configuration of the burner for combustion of waste oil or the like according to the present invention, in the configuration of the first aspect of the present invention, the cylindrical wall of the porous wall provided so as to surround the atomizing nozzle 10. Body 20b and cylindrical body 20
The diffuser portion 2 having a divergent shape provided at the tip of b.
0a is provided. And
The flame stabilizer 20 is provided so that the porous wall cylindrical body 20b surrounds the atomization nozzle 10, and combustion air is provided on the porous wall cylindrical body 20b of the flame stabilizer 20. It flows from many holes and mixes with the spray droplets at the nozzle tip side spray port 6 while forming a gentle flow in the same nozzle axial direction of the atomizing nozzle 10 to ignite and effectively use as combustion air. Will be done. The driving force for this flow is created by the spray flow as described above.

In front of the atomization nozzle 10 as described above, the divergent diffuser portion 20a
As a result, the flow velocity in the axial direction is suddenly reduced or a backflow occurs, so that the flow of the spray droplets does not exceed the flame propagation speed and forms a stable flame.

(3) The burner for burning waste oil etc. of the present invention according to the third aspect of the present invention, in the structure of the second aspect of the present invention, comprises a tubular body 20 having a perforated wall of the flame stabilizer 20.
b is the ratio φ ₇ of the diameter φ ₁ of the atomizing nozzle 10 to the diameter φ ₇ of the atomization nozzle 10.
In _{/ φ 1, φ 7 / φ} 1 is set to be 1.8 or less.

The diameter φ ₇ of the cylindrical body 20b of the flame stabilizer 20
Is important because it governs the air flow to the flow path formed by the spray flow and the divergent diffuser portion 20a.

That is, the flow path formed between the cylindrical body 20b and the atomizing nozzle 10 is provided in the diffuser section 20.
Since it is a run-up flow path to the a-side divergent flow path, it must form a uniform flow without deviation. Therefore, the ratio φ ₇ / φ ₁ between the diameter φ ₇ of the cylindrical body 20 b and the diameter φ _{1 of the} portion of the atomization nozzle 10 is theoretically small (ie,
Equivalent I / d is large: where I is the length of the flow path and d is the equivalent diameter of the flow path), but if it is too small, an eccentric flow path is actually formed and a uniform flow cannot be formed. So there are limits. This limit is governed by the processing accuracy and construction accuracy of the equipment components.

From such various conditions, φ ₇ / φ ₁ is 1.
It is preferably 8 or less.

(4) The burner for burning waste oil or the like according to the present invention according to the fourth aspect of the present invention, in the structure according to the second aspect of the present invention, wherein the tubular body 20 having a porous wall of the flame stabilizer 20 is provided.
b length L ₁ and the ratio L ₁ of the diameter φ ₇ of the cylindrical body 20 b to L _1.
/ Φ ₇ , L ₁ / φ ₇ is set to 1.2 or more.

As described above, the cylindrical body 20b of the flame stabilizer 20
Diameter phi ₇ and the length L ₁ of is important because it governs the air flow to the spray stream and a divergent shape diffuser portion 20a and the flow path formed by the.

That is, the flow path formed between the cylindrical body 20b and the atomizing nozzle 10 is provided in the diffuser section 20.
Since it is a run-up flow path to the a-side divergent flow path, it must form a uniform flow without deviation. Therefore, the ratio L ₁ / L of the length L ₁ and the diameter φ ₇ of the cylindrical body 20b is determined.
If φ ₇ is too small, an eccentric flow path is formed and a uniform flow cannot be formed, so L ₁ / φ ₇ is preferably 1.2 or more.

(5) The burner for burning waste oil etc. of the present invention according to the fifth aspect of the present invention, in the structure of the second aspect of the present invention, wherein the diffuser portion 20 of the flame stabilizer 20 is provided.
The ratio φ ₈ of the diameter φ _{8 of a} to the diameter φ ₁ of the atomizing nozzle 10
/ Φ ₁ , φ ₈ / φ ₁ is set to 6.0 or less.

The diameter φ ₈ of the diffuser portion 20 a of the flame stabilizer 20 and the diameter φ ₁ of the atomizing nozzle 10 are important because they govern the air flow to the divergent flow path of the spray flow.

That is, in front of the atomizing nozzle 10 in the divergent flow path from the atomizing nozzle 10 portion to the diffuser portion 20a, the axial flow velocity is suddenly reduced or a reverse flow is generated, so that the spray liquid is formed. This is important in that a stable flame can be formed without the flow of the droplet exceeding the flame propagation speed.

In this sense, φ ₈ / φ ₁ is preferably 6.0 or less.

[0039]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The construction and operation of a burner for burning waste oil and the like according to an embodiment of the present invention and various experimental examples will be described below in detail with reference to FIGS.

First, FIGS. 1 to 3 show a nozzle 10 for atomizing a waste oil or the like of a burner for burning a waste oil or the like according to an embodiment of the present invention.
The structure of the whole part and the main part is shown. In FIG.
Reference numeral 1 denotes a supply passage (diameter φ ₃ ) provided at the central axis of the cylindrical nozzle tip 10 a of the atomization nozzle (diameter φ ₁ ) 10, and reference numeral 2 denotes a flow path located on the outer peripheral side in the radial direction. A gas supply channel for atomization (diameter φ ₂ ) provided so as to surround the supply channel 1 for waste oil and the like. The waste oil and the atomizing gas (air) are provided in the circumferential direction on the central portion of the disk plate-shaped partition wall (diameter φ ₂ , thickness D ₁ ) 7 from the downstream ends of the respective supply flow paths 1 and ₂ . Through a plurality of waste oil supply holes 3, 3... And a plurality of atomization gas supply holes 4, 4, 4 (nozzle tip 10b
Side) into the oil-air mixing chamber (diameter φ ₄ , depth D ₂ ) 5 so as to be uniformly mixed.

A plurality (six in the figure) of waste oil supply holes 3, 3... Are provided in parallel along the center axis OO 'of the nozzle tip, and are supplied from outside through the waste oil supply passage 1. The waste oil is introduced straight through the plurality of waste oil supply holes 3, 3. On the other hand, the plurality (three in the figure) of the atomizing gas supply holes 4, 4, 4 are, for example, arranged with respect to the center axis OO 'direction of the nozzle tip 10a, for example, as shown in detail in FIG. 4
A gas supply flow path for atomization, which is provided at a 120 ° interval in the circumferential direction with an inclination angle θa of 5 degrees and at a predetermined angle θb from the tangential direction of the circumference toward the center side. The gas for atomization supplied from the outside through the pipe 2 has the flow velocity component of the swirling method thereby, and the oil-gas mixture chamber 5
It is configured to flow toward the waste oil supply area at the inner central part.

As a result, the waste oil supplied through the waste oil supply holes 3, 3... And the atomizing gas supply holes 4, 4, 4
The atomizing gas supplied through the oil-mixing chamber 5
Sprays are mutually swirled in the inside, and while forming a liquid film of the waste oil on the inner wall surface of the oil-gas mixing chamber 5, the spray at the center of the tip 10 b of the nozzle tip which communicates with the atmosphere side from the central part downstream of the oil-gas mixing chamber 5 It reaches the mouth (diameter φ ₅ , depth D ₃ ). Then, when atomized through the spray port 6 and discharged into the atmosphere, the liquid film of the waste oil is severely torn off, and the liquid film is particularly effectively atomized.

FIG. 4 shows measurement characteristics of the spray angle θdeg of the atomized waste oil at this time, for example.

In this case, the kinematic viscosity of the waste oil used for measuring the spray angle θdeg was 400 × 10 ⁻⁶ m ² / s, and the waste oil flow rate was kept constant at 2.5 g / s and 5.0 g / s.
The air flow rate for the atomization medium was changed from 0.5 to 4.0 g / s. Then, the spray state of the waste oil from the nozzle tip side spray port 6 at that time was photographed, and the spray angle θdeg was measured from the image. The spray angle θdeg increases as the air flow rate for the atomization medium increases, and when the air flow rate for the atomization medium is 1.6 to 4.0 g / s, θdeg = about 6
It is asymptotic to 0 °. This angle of about 60 ° is close to the spread angle R = 60 ° of the front end of the diffuser section 20a of the flame stabilizer 20 to be described later combined with the atomizing nozzle 10, and the spray flow and the diffuser section 20a of the flame stabilizer 20 are It is easy to form an entrained flow in the gap flow path between. In order to form the entrained flow in a preferable state, a gap between the spray flow and a diffuser portion 20a of the flame stabilizer 20 described later is preferably set to about 2 to 5 mm.

That is, when the waste oil droplets injected from the atomizing nozzle 10 having the structure of the present embodiment are burned, in order to enhance the flame holding at the tip thereof, for example, as shown in FIG. Numerous holes in the peripheral wall (for example, φ ₉ = 12 mm)
A tubular body (straight pipe portion) 20b having a porous wall through which air is easily formed and formed integrally with the tip of the tubular body 20b to expand the spray flow in the radial direction. A diffuser part having a divergent shape (spread angle R = 60
°, diameter φ ₈ ) A flame stabilizer 20 made of 20a is adopted, and this can be installed at a predetermined interval around the tip (nozzle tip) of the atomizing nozzle 10 as shown in FIG. preferable. In the case of this measurement, the atomizing nozzle 10
Phi ₁ is 4.5 mm (outer diameter of the nozzle tip 10a) of a diameter
On the other hand, the cylindrical body (straight pipe portion) 2 of the flame stabilizer 20
0b diameter (outer diameter) phi _7, for example 80 mm, 100 m
m, and 120 mm were used in combination. Further, the cylindrical body (straight pipe) 20b of the length L ₁ of the flame stabilizer 20, 130 mm ones (Figure 9) and 260mm ones use those two different lengths (Figure 10) Was.

Next, FIG. 6 shows the outline of the configuration of an experimental apparatus used for an experiment for measuring the combustion characteristics of the burner for burning waste oil or the like.

In FIG. 6, reference numeral 10 denotes the above-mentioned atomizing nozzle, and the waste liquid in the waste liquid storage tank 11 is filled with a nitrogen cylinder 12.
By supplying a constant pressure, the waste liquid was supplied such that the flow rate of the waste oil flowing in the waste liquid supply pipe 13 was kept constant at 2.5 g / s, while the needle valve 15 and the flow meter 16 were provided from the air compressor 14. The air for the atomization medium was supplied at a varied flow rate through the air supply pipe 18.
The kinematic viscosity of the waste liquid was 400 × 10 ⁻⁶ m ² / s. The flame holder 20 has a cylindrical body 20b that is formed by the atomizing nozzle 1 described above.
It is installed at a predetermined interval so as to surround the outer periphery of the zero. In addition, a camera 23 is provided in front of the spray port 6 of the atomizing nozzle 10 so that the state of the flame in the flame holder 20 can be accurately photographed. Reference numeral 17 denotes a pressure gauge for monitoring the pressure of the fluid in each of the supply lines 13 and 18.

First, in the same experiment, it was considered that the diameter φ ₇ of the cylindrical body 20 b of the flame stabilizer 20 greatly affected the stability of the flame in the recirculation region. The flame was observed by changing the diameter φ ₇ of the 20 cylindrical bodies 20b as follows.

(Preliminary Experiment 1) Tubular Body 20b of Flame Holder 20
Experiment in the case of diameter φ ₇ = 80 mm. As a result of visual observation,
Even if the mass flow rate of the atomized air is small, the flame has a large area of bright flame, generates less soot, and burns stably.

(Preliminary Experiment 2) Cylindrical Body 20b of Flame Holder 20
Experiment in the case of φ ₇ = 120 mm. In this case,
Compared with the case of the above-mentioned preliminary experiment 1, the area of the bright flame is reduced, and even if the mass flow rate of the atomized air is increased, the flame is red-orange, and many large fuel oil droplets fly out from the end of the flame while burning. And a lot of unburned fuel is produced.
In addition, the amount of white smoke and soot emitted is extremely large, and the flame is burning while pulsating, resulting in unstable combustion.

From this result, it is found that the cylindrical body 20b of the flame stabilizer 20
When the diameter phi ₇ the optimum size, the area of the luminous flame is large, it was found that soot is possible to perform almost not generated stable combustion.

(Experimental Example 1) Further, on the premise of the above, visual observation of the flame was carried out by changing the mass flow rate of the fuel and the mass flow rate of the atomized air widely. The graph now FIGS. 7 and 8 show the effect on the combustion characteristics of the diameter phi ₇ of the cylindrical body 20b portion of the flame holder 20 based on the observations. First, FIG. 7 is the diameter phi ₇ of the cylindrical body 20b of the flame holder 20 is in the case of a 120mm result, FIG. 8 shows the results of when the diameter phi ₇ of the cylindrical body 20b of the flame stabilizer 20 is 80 mm. 7 and 8, (1) a red-orange flame,
An area where a large amount of soot is generated is “Red”, (2) a yellow flame, and an area where a little soot is generated is “Yellow”.
(3) The region where little soot is generated by the bright flame is referred to as "Lu".
(4) A region where a large number of unburned fuel oil droplets are generated is classified as “Drop”, and a region where the flame blows out is classified as “Blow-Off”. The atomization nozzle 10 uses the one shown in FIGS. 1 to 3 (type-D) according to the embodiment of the present invention, and the flame stabilizer 20 has the structure shown in FIG. 5 and the diameter of the cylindrical body 20b. phi ₇ indicates the case of the two ones 80mm and 120 mm.

From the data shown in FIGS. 7 and 8, the flame stabilizer 20
When the diameter phi ₇ of the cylindrical body 20b is 120 mm, the fuel mass flow rate is small area (1.3 g / s), when gradually increasing the flow rate of atomizing air, but disappears blow quickly, coercive The diameter φ ₇ of the cylindrical body 20 b of the flame device 20 is 80 mm
In the case of (1), even if the flow rate of the atomized air is increased, the blow-out hardly occurs. On the other hand, in a region where the mass flow rate of the fuel is large (5.9 g / s), the use of the flame stabilizer 20 having a diameter φ ₇ of the cylindrical body 20b of 120 mm of the flame stabilizer 20 increases the flow rate of the atomized air. without words, less soot yellow, or is not obtained luminous flame, the diameter phi ₇ of the cylindrical body 20b of the flame stabilizer 20 is used flameholder 20 of 80 mm, an air flow rate for a relatively small atomization Preferred yellow,
Or a bright flame is obtained.

(Experimental example 2) Next, the cylindrical body 20 of the flame stabilizer 20
The effect on the combustion characteristics when the diameter φ ₇ of b was made constant (φ ₇ = 80 mm) and the length L ₁ was changed was observed. For example two types of flame holder shown in FIG. 9 and FIG. 10 is a first case of FIG. 9 is a length L ₁ of the cylindrical body 20b is short shopping (type -S1, L ₁ = 130 mm), the following Figure 1
If 0 is become a length L ₁ of the cylindrical body 20b is long (type -L1, L ₁ = 260mm). And as a result of measuring these combustion characteristics and comparing them with each other,
For example, when using the cylindrical body 20b of the short flame holder 20 of length L ₁ as shown in FIG. 9, as shown in FIG. 11, the region of luminous flame is narrow, easily blow-off, the unstable combustion. However, as shown in FIG. 12, the length L of the cylindrical body 20b shown in FIG.
With ₁ long flame holder 20, preferably luminous flame is obtained with less atomizing air was found to stable combustion in a wide fuel flow range.

(Experimental Example 3) Further, as shown in comparison with FIGS. 13 and 14, each of the case where the above-mentioned diffuser portion 20a is not provided at the tip of the above-mentioned cylindrical body 20b of the flame stabilizer 20 and the case where it is present FIG. 15 shows the differences between the combustion characteristics.
And FIG. When there is no diffuser section 20a in FIG. 15, there is almost no bright flame burning area, and the combustion is unstable with unburned droplets and soot discharge is large.
In the case where there is the diffuser portion 20a of 6, a good bright flame can be obtained in a wide range of the fuel mass flow rate. Therefore, it can be seen that the presence of the diffuser unit 20a is effective.

From the above experimental results, the length L ₁ of the tubular body 20 b of the flame stabilizer 20 is long, and the diameter φ ₇ is φ ₇ = 80.
mm flame stabilizer 20 is used regardless of the fuel flow rate range.
With a small amount of air for atomization, little soot is generated and a bright flame is obtained. It was also found that blow-off hardly occurred, and a stable combustion state was obtained in a wide range of air flow rates for atomization.

As described above, the burner for burning waste oil and the like according to the present invention comprises a waste oil supply passage 1 for supplying waste oil and the like disposed along the central axis of the nozzle portion, and a waste oil supply passage 1 for the waste oil and the like. A gas supply channel 2 for atomization for supplying atomizing gas for atomizing waste oil and the like installed so as to surround, a waste oil from the supply channel 1 for waste oil and the gas supply flow for atomization The gas for atomization from the passage 2 is introduced through the supply hole 3 for waste oil etc. and the gas supply hole 4 for atomization, respectively, and is mixed with the oil / gas mixing chamber 5 and the oil / gas mixing chamber 5. An atomizing nozzle 10 comprising a spray port 6 for atomizing a fluid and injecting the atomized air into the atmosphere, and supplying the atomizing gas from the atomizing gas supply flow path 1 into the oil-gas mixing chamber 5. The atomizing gas supply hole 4 is used to supply the atomized gas supplied when the atomizing gas is supplied. Are constructed as fluid mixture of the oily mixing chamber 5 is made to pivot by.

Therefore, in the burner for burning waste oil etc. of the present invention, by using the above nozzle structure,
The mixing performance of the waste oil and the like and the atomizing gas in the oil-gas mixing chamber 5 and the atomization performance of the waste oil and the like are improved, and the droplets of the waste liquid having a smaller particle size than the nozzles conventionally used can be formed. As a result, the ignitability at the beginning of the combustion start can be improved. Further, since the particle diameter of the waste oil or the like becomes small, the burn-out time is shortened, and the unburned matter can be reduced.

Further, in the atomizing nozzle structure, the mixed fluid in the oil-gas mixing chamber 5 is atomized by applying a swirling force, so that the fluid is injected from the oil-gas mixing chamber 5 to the atmosphere. The spray angle θdeg of the fuel such as waste oil changes depending on the flow rate of the atomizing gas, and becomes wider than when there is no turning force. In other words, the spraying in the so-called full cone state approaches the preferable spray characteristics in the hollow cone state while maintaining the full cone state.

This spray flow produces an effective entrain flow in the gap between the divergent diffuser portion 20a of the flame stabilizer 20 which will be described later, and the porous wall cylindrical body 20b of the flame stabilizer 20 and the atomizing nozzle. Since it works so that air is efficiently drawn in from the flow path between the fuel cell 10 and the fuel cell 10, it also serves as a driving force for supplying air for combustion. That is, by matching the spray angle θdeg of the atomization nozzle 10 with the spread angle R of the diffuser portion 20 a of the flame stabilizer 20, a further suction force of the combustion air is generated. Further, in front of the spray flow, when the swirling force is strong, a so-called recirculation region is formed in which air is drawn into the spray flow side.

Further, in the structure of the burner for burning waste oil etc. of the present invention, the atomizing nozzle 10
Is provided in combination with a flame stabilizing device 20 including a cylindrical body 20b having a porous wall provided so as to surround the cylindrical body 20 and a diffuser portion 20a having a divergent shape provided at the tip of the cylindrical body 20b. I have. The flame holder 20 is provided such that the porous wall cylindrical body 20b surrounds the atomizing nozzle 10, and combustion air is provided on the porous wall cylindrical body 20b of the flame stabilizer 20. It flows in through a number of holes and mixes with the spray droplets at the nozzle tip side spray port 6 while forming a gentle flow in the same nozzle axis direction of the atomizing nozzle 10, ignites, and is effective as combustion air. Will be used for. The driving force for this flow is created by the spray flow as described above.

In front of the atomization nozzle 10 as described above, the divergent diffuser portion 20a
As a result, the flow velocity in the axial direction is suddenly reduced or a backflow occurs, so that the flow of the spray droplets does not exceed the flame propagation speed and forms a stable flame.

Further, in the burner for burning waste oil etc. of the present invention, the diameter φ ₇ of the cylindrical body 20 b of the porous wall of the flame stabilizer 20 in the above configuration is set to the ratio φ of the diameter φ ₁ of the atomizing nozzle 10 to φ _{1. 7} / φ ₁ , so that φ ₇ / φ ₁ is 1.8 or less.

The diameter φ ₇ of the cylindrical body 20b of the flame stabilizer 20
Is important because it governs the air flow to the flow path formed by the spray flow and the divergent diffuser portion 20a.

That is, the flow path formed between the cylindrical body 20 b and the atomizing nozzle 10 is
Since it is a run-up flow path to the a-side divergent flow path, it must form a uniform flow without deviation. Therefore, the ratio φ ₇ / φ ₁ between the diameter φ ₇ of the cylindrical body 20 b and the diameter φ _{1 of the} portion of the atomization nozzle 10 is theoretically small (ie,
Equivalent I / d is large: where I is the length of the flow path and d is the equivalent diameter of the flow path), but if it is too small, an eccentric flow path is actually formed and a uniform flow cannot be formed. So there are limits. This limit is governed by the processing accuracy and construction accuracy of the equipment components.

From such various conditions, φ ₇ / φ ₁ is 1.
It is preferably 8 or less.

Further, in the burner for burning waste oil or the like according to the present invention, in the above-described configuration, the length L ₁ of the cylindrical body 20 b of the porous wall of the flame stabilizer 20 is made equal to the diameter φ ₇ of the cylindrical body 20 b. It is configured such that L ₁ / φ ₇ is 1.2 or more at a ratio L ₁ / φ ₇ .

As described above, the cylindrical body 20b of the flame stabilizer 20
Diameter phi ₇ and the length L ₁ of is important because it governs the air flow to the spray stream and a divergent shape diffuser portion 20a and the flow path formed by the.

That is, the flow path formed between the cylindrical body 20 b and the atomizing nozzle 10 is
Since it is a run-up flow path to the a-side divergent flow path, it must form a uniform flow without deviation. Therefore, the ratio L ₁ / L of the length L ₁ and the diameter φ ₇ of the cylindrical body 20b is determined.
If φ ₇ is too small, an eccentric flow path is formed and a uniform flow cannot be formed, so L ₁ / φ ₇ is preferably 1.2 or more.

Further, in the burner for burning waste oil or the like according to the present invention, in the above configuration, the ratio of the diameter φ ₈ of the diffuser portion 20 a of the flame stabilizer 20 to the diameter φ ₁ of the atomizing nozzle 10 is φ ₈ / in φ _1, φ ₈ / φ ₁ is set to be 6.0 or less.

The diameter φ ₈ of the diffuser portion 20 a of the flame stabilizer 20 and the diameter φ ₁ of the atomization nozzle 10 are important because they govern the air flow to the divergent flow path of the spray flow.

That is, in front of the atomizing nozzle 10 in the divergent flow path extending from the atomizing nozzle 10 to the diffuser portion 20a, the axial flow velocity is suddenly reduced or a backflow is caused to occur. This is important in that a stable flame can be formed without the flow of the droplet exceeding the flame propagation speed.

In this sense, φ ₈ / φ ₁ is preferably 6.0 or less.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view (AA in FIG. 2) showing a structure of a burner for burning waste oil or the like according to an embodiment of the present invention.

FIG. 2 is a front end side view of the burner.

FIG. 3 is a cross-sectional view of the burner taken along the line BB in FIG. 2;

FIG. 4 is a diagram showing spray angle characteristics of a nozzle portion of the burner.

FIG. 5 is a side view showing the structure of a flame stabilizer used in combination with the burner.

FIG. 6 is a diagram showing a schematic configuration of a combustion experimental device for confirming waste oil combustion performance of the burner.

FIG. 7 is a view showing combustion characteristics when a length φ ₁ of a flame stabilizer cylindrical portion is made constant and a diameter φ ₇ is made 120 mm in a combustion experiment of the same burner.

8 is a diagram showing the combustion characteristics when the diameter phi ₇ by a constant length L ₁ of the flame holder the cylindrical body in the combustion experiment of the same burner was 80 mm.

FIG. 9 shows that the diameter L ₇ of the cylindrical body of the flame stabilizer in the combustion test of the burner was fixed (φ ₇ = 80 mm) and the length L ₁ was 13
It is a figure which shows the structure of a flame stabilizer when it is set to 0 mm.

FIG. 10 is a graph showing the relationship between the diameter L ₇ of the cylindrical body of the flame stabilizer and the length L ₁ of 2 in the combustion test of the burner, where the diameter φ ₇ is constant (φ ₇ = 80 mm).
It is a figure which shows the structure of the flame stabilizer when lengthening to 60 mm.

FIG. 11 is a view showing a condition where the diameter φ ₇ of the cylindrical body of the flame stabilizer in the combustion test of the burner is fixed (φ ₇ = 80 mm) and the length L ₁ is 1
FIG. 10 is a diagram showing the combustion characteristics of the flame stabilizer in the case of the configuration of FIG.

FIG. 12 is a diagram showing a condition in which the diameter φ ₇ of the cylindrical body of the flame stabilizer in the combustion test of the burner is fixed (φ ₇ = 80 mm) and the length L ₁ is 2;
It is a figure which shows the combustion characteristic of the flame stabilizer in the case of the said FIG. 10 lengthened to 60 mm.

FIG. 13 is a view showing a structure in a case where a diffuser portion is not provided at the tip of a flame stabilizer in a combustion experiment of the burner.

FIG. 14 is a view showing a structure in a case where a diffuser portion is provided at the tip of a flame stabilizer in a combustion experiment of the burner.

FIG. 15 is a diagram showing combustion characteristics in the case of the configuration of FIG. 13 in which the diffuser is not provided at the tip of the flame stabilizer in a combustion experiment of the burner.

FIG. 16 is a view showing combustion characteristics in the case of the configuration of FIG. 14 in which a diffuser portion is provided at the tip of a flame stabilizer in a combustion experiment of the same burner.

FIG. 17 is a front view showing a configuration of a waste oil combustion treatment device of a first conventional example.

FIG. 18C shows the configuration of the waste oil combustion treatment device in FIG.
It is -C sectional drawing.

FIG. 19 is a cross-sectional view showing a structure of an atomizing nozzle of a second conventional example.

[Explanation of symbols]

1 is a waste oil supply passage, 2 is an atomization gas supply passage, 3 is a waste oil supply hole, 4 is an atomization gas supply hole, 5 is an oil-gas mixing chamber, 6 is a spray port, and 20 is a flame stabilizer. , 20a is a diffuser part, 20b is a cylindrical body, 21 is a hole.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Masanori Shimizu 305-269 Kurita-machi, Kurose-cho, Kamo-gun, Hiroshima Prefecture (72) Inventor Nobuge Tamaki 1-1-21 Hiroko Shinkai, Kure City, Hiroshima Prefecture F term (reference) 3K052 GA01 GA05 GB01 GB03 GC01 GE04 3K056 AA03 AA05 AA08 AB01 AB06 AC01 AD02 CA01 CA11 CB06

Claims (5)

[Claims] 1. A waste oil supply passage (1) for supplying waste oil and the like provided along a central axis of a nozzle portion, and a waste oil and the like installed around the waste oil supply passage (1). A gas supply channel (2) for supplying atomizing gas for atomizing water, a waste oil from the supply channel (1) and a gas supply channel (2) for atomization. And a gas-mixing chamber (5) which are introduced through a waste oil or the like supply hole (3) and a gas-mixing gas supply hole (4), respectively, and mixed with each other. 5) a atomizing nozzle (10) comprising a spray port (6) for atomizing the mixed fluid in the air and spraying the atomized air into the atmosphere, and the oil-gas mixing chamber ( 5) The atomizing gas supply hole (4) for supplying the atomizing gas into the inside is supplied when the atomizing gas is supplied. A burner for burning waste oil or the like, characterized in that the mixed fluid in the oil-air mixing chamber (5) is swirled by the atomizing gas. 2. A tubular body (20b) having a porous wall provided so as to surround the atomization nozzle (10) and the tubular body (20).
2. A burner for burning waste oil or the like according to claim 1, wherein a flame stabilizer (20) comprising a divergent diffuser portion (20a) provided at the tip of b) is combined. 3. A tubular body (20) having a porous wall of a flame stabilizer (20).
b) the diameter (φ _7), the ratio between the diameter of the atomizing nozzle _{(10) (φ 1) (} φ 7 / φ 1), is (φ ₇ / φ ₁₎ 1.8
3. The burner for combustion of waste oil or the like according to claim 2, wherein: 4. A tubular body (20) having a porous wall of a flame stabilizer (20).
b) In the ratio (L ₁ / φ ₇ ) of the length (L ₁ ) to the diameter (φ ₇ ) of the cylindrical body (20b), (L ₁ / φ ₇ ) is 1.2.
3. The burner for burning waste oil or the like according to claim 2, wherein: 5. The diffuser section (20) of a flame stabilizer (20).
The diameter of a) (φ _8), the ratio between the diameter of the atomizing nozzle _{(10) (φ 1) (} φ 8 / φ 1), is (φ ₈ / φ ₁₎ 6.0
3. The burner for combustion of waste oil or the like according to claim 2, wherein: