KR20170092224A

KR20170092224A - Waste refrigernat burning system

Info

Publication number: KR20170092224A
Application number: KR1020160013289A
Authority: KR
Inventors: 이강우; 문동현; 석민광
Original assignee: 씨이테크주식회사; 이이알앤씨 주식회사
Priority date: 2016-02-03
Filing date: 2016-02-03
Publication date: 2017-08-11

Abstract

Disclosed is a waste refrigerant burning system capable of preventing a decrease in combustion efficiency caused by a decrease in the internal temperature of a combustion furnace due to evaporation heat of a waste refrigerant generated inside the combustion furnace. The waste refrigerant burning system includes: the combustion furnace (11) wherein the waste refrigerant is burned; a supply chamber (12) formed in one side of the combustion furnace (11) and having a heating burner (16) therein; a waste refrigerant supply passage (7a) connected to a waste refrigerant tank (7) and receiving a supply of the waste refrigerant; a recirculation pipe (5a) wherein some of the exhaust gas that penetrated the combustion furnace (11) is supplied to be recirculated; and an evaporation section (30) having one end connected to the waste refrigerant supply passage (7a) and the recirculation pipe (5a) and receiving the waste refrigerant and exhaust gas and the other end connected to the supply chamber (12) and supplying the waste refrigerant of which its temperature is increased by being mixed with the exhaust gas to the supply chamber (12). The waste refrigerant burning system is capable of mixing the waste refrigerant and the exhaust gas in the evaporation section (30), thereby supplying the waste refrigerant of which the temperature is increased to the combustion chamber (12).

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a waste refrigerant combustion system,

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a waste refrigerant combustion system, and more particularly, to a waste refrigerant combustion system that uses exhaust gas to prevent heat loss due to heat of vaporization generated when waste refrigerant is supplied to a combustor.

Currently, the waste refrigerant generated in the process of collecting, recovering or disposing of refrigerant equipment in Korea is representative of CFC, which is an ozone depletion material, and HFC, which is a global warming material. In Korea, there is no facility that stably disposes or destroys waste refrigerant generated from automobiles, households, industrial air conditioners, etc., and related technologies registered in Korea are mainly related to technologies for destroying waste refrigerant by using plasma to be.

The plasma decomposition method of the related art (Korean Patent No. 10-18984, apparatus and method for treating waste using plasma gas) is a technology for completely decomposing a waste refrigerant by using a high-temperature plasma.

However, such a plasma decomposition method is disadvantageous in that a dedicated facility for decomposing the refrigerant must be installed, and the processing cost is high economically. In addition, when the equipment is enlarged, it is difficult to maintain the temperature of the plasma gas, which is disadvantageous in that it is not suitable for large capacity processing.

In the case of LNG-Burning technology, which is another technology to destroy the waste refrigerant, since refractory having a relatively large heat capacity is installed to mislead the outer wall of the combustion chamber from a high temperature, there is a limit to increase the combustion efficiency. Energy is consumed.

The waste refrigerant for thermal destruction is compressed into a liquid state for transportation and is transported to the treatment facility. When the waste liquid refrigerant is supplied to the combustor, incomplete combustion occurs due to the internal temperature of the combustor due to the heat of vaporization of the waste refrigerant There is a problem.

Korean Patent No. 10-189842 (Waste Treatment Apparatus Using Plasma Gas and Method Thereof)

It is another object of the present invention to provide a waste refrigerant combustion system capable of improving the combustion efficiency by reducing the heat of vaporization generated by supplying waste refrigerant to a combustor.

It is another object of the present invention to provide a waste refrigerant combustion system capable of improving combustion efficiency by supplying exhaust gas to a combustor in a state of being mixed with waste refrigerant in advance.

It is another object of the present invention to provide a waste refrigerant combustion system capable of improving combustion efficiency by allowing waste refrigerant and exhaust gas to be smoothly mixed before being supplied to a combustor.

It is another object of the present invention to provide a waste refrigerant combustion system for reducing the nitrogen oxide concentration discharged from a combustor while compensating for the heat of vaporization of waste refrigerant.

According to an aspect of the present invention, there is provided a waste refrigerant combustion system comprising: a waste refrigerant tank for supplying waste refrigerant discharged from an exhaust gas containing hydrogen fluoride through a waste refrigerant supply path during combustion; A combustion chamber provided with a supply chamber provided with a heating burner therein and a combustion chamber for burning waste refrigerant transferred from the waste refrigerant tank at an internal temperature of 900 to 1200 ° C by the heating burner; And a recirculation pipe for recovering a part of the exhaust gas discharged from the combustion furnace to the waste refrigerant supply path, wherein the waste refrigerant is vaporized by an exhaust gas having a temperature of 60 to 120 ° C. passing through the recycling pipe, And supplies it to the combustion furnace.

More preferably, the vaporizing section connected to the combustion chamber after the recycling pipe is combined with the waste-refrigerant supply passage has a distance of 3 m to 10 m.

More preferably, the recirculation rate (%) = k * (60 / recirculated exhaust gas temperature) representing the amount of exhaust gas recovered through the recirculation pipe in the exhaust gas discharged through the combustion furnace, wherein k is And has a value of 18 to 22.

More preferably, the inner circumferential surface of the vaporizing section is provided with a vortex generating projection for promoting the mixing of the waste refrigerant and the exhaust gas.

More preferably, the vortex generating protrusions project toward the center of the vaporizing section and extend along the inner circumferential surface to form a screw shape.

More preferably, the vaporization section is provided with an orifice portion whose inner diameter is reduced at an inlet side connected to the recycling pipe, and the waste refrigerant supply passage is connected to the orifice portion.

More preferably, the inner diameter of the waste refrigerant supply path is formed to be smaller than the inner diameter of the vaporizing section.

More preferably, a first check valve is mounted at a front end of a portion of the recirculation pipe connected to the waste-refrigerant supply path to prevent the waste refrigerant from flowing back to the recycling pipe.

More preferably, a second check valve is installed in the flow path connecting the recirculation pipe connection part to the chimney, to prevent air outside the chimney from flowing back to the recirculation pipe side.

More preferably, a heat exchanger for exchanging heat between the exhaust gas discharged from the combustion furnace and water to cool the combustion gas at a temperature of 80 to 180 DEG C to vaporize water to generate steam, and a heat exchanger And a cleaning tower for removing impurities including hydrogen fluoride contained in the combustion gas, wherein the cleaning tower is made of a resin material so as to be in contact with the exhaust gas so as to prevent corrosion by the impurities,

The steam is supplied to the combustion chamber,

C ₂ H ₂ F ₄ + 4H ₂ O? 4HF + 3H ₂ + 2CO ₂ ?????

Lt; / RTI >

More preferably, the cleaning tower is constructed such that a thermosetting resin is applied to an inner wall which is in contact with an exhaust gas, a glass fiber is adhered to a place where the thermosetting resin is applied, a thermosetting resin is further applied thereon, Thereafter, it is cured to form an F-alpha layer.

In the waste refrigerant combustion system according to the present invention, the waste refrigerant supplied in a liquid state is brought into contact with the exhaust gas in the vaporizing section and the waste refrigerant is introduced into the combustor in a vaporized state, So that the combustion efficiency of the waste refrigerant is improved.

The waste refrigerant combustion system according to the present invention mixes the waste refrigerant supplied in a liquid state through the vaporization section with the exhaust gas and mixes the waste gas with the primary gasified waste refrigerant in the supply chamber 12 , The mixed gas is supplied to the combustion chamber of the combustion furnace together with the flame generated in the heating burner provided in the supply chamber 12 to burn the waste refrigerant so that the heat of vaporization generated upon combustion of the waste refrigerant can be reduced, The internal temperature of the combustion chamber is prevented from being lowered, thereby improving the combustion efficiency.

Further, since the waste refrigerant combustion system according to the present invention does not use a separate heater or heat exchanger for raising the temperature of the waste refrigerant, the manufacturing cost is reduced and corrosion or damage of the heat exchanger due to exhaust gas is prevented .

Further, the waste refrigerant combustion system according to the present invention has the effect of reducing the nitrogen oxide emission and reducing the cost by using the exhaust gas recycled to the combustor.

Further, in the waste refrigerant combustion system according to the present invention, since the combustion air discharged so as to form the swirling flow is discharged in an inclined direction toward the supply chamber, sufficient time is ensured for the combustion gas to be completely combusted in the combustion furnace, It is effective.

FIG. 1 is a state diagram showing a waste refrigerant combustion system according to a first preferred embodiment of the present invention. FIG.
FIG. 2 is a cross-sectional view of the combustor shown in FIG. 1,
3 is a cross-sectional view showing a portion "AA" shown in Fig. 2,
4 is a side view showing a vaporization section connected to a combustor,
5 is a cross-sectional view illustrating a vaporization section of a waste refrigerant combustion system according to a second preferred embodiment of the present invention.
FIG. 6 is a sectional view showing a vaporization section of a waste refrigerant combustion system according to a third preferred embodiment of the present invention, FIG.
7 is a graph showing the temperature distribution of the combustor according to the length of the vaporization section,
Figure 8 is a side view of the heat exchanger shown in Figure 1,
FIG. 9 is a cross-sectional view of the heat exchanger shown in FIG. 1; FIG.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a waste refrigerant combustion system according to a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

Here, the shape, size, ratio, angle, number and the like shown in the accompanying drawings are schematic and may be modified somewhat. 2) Since the drawing is shown by the line of sight of the observer, the direction or position to explain the drawing can be variously changed according to the position of the observer. 3) The same reference numerals can be used for the same parts even if the drawing numbers are different. 4) If 'include', 'have', 'have', etc. are used, other parts can be added unless '~ only' is used. 5) Numerals can also be interpreted as described in the singular. 6) Even if the shape, size comparison, positional relationship, etc. are not described as 'weak or substantial', it is interpreted to include the normal error range. 7) 'after', 'before', 'after', 'after', and 'after' are not used to limit the temporal position. 8) The terms 'first, second, third', etc. are used selectively, interchangeably or repeatedly for convenience of division, and are not construed in a limiting sense. 9) If the positional relationship of the two parts is described as 'on top of', 'on top', 'on bottom', 'on side', 'on side' and so on, This can also be located. 10) When parts are electrically connected to '~ or', parts are interpreted to include not only singles but also combinations, but parts are interpreted solely if they are electrically connected to '~ or'.

FIG. 2 is a cross-sectional view of the combustor shown in FIG. 1, and FIG. 3 is a cross-sectional view taken along the line AA in FIG. 2, And FIG. 4 is a side view showing a vaporization section connected to the combustor.

1 to 4, a waste refrigerant combustion system according to a first preferred embodiment of the present invention includes an air-cooled type combustor 10 in which waste liquid refrigerant is stored, A waste heat exchanger 50 in which the gas combusted in the air-cooled combustor 10 is moved, a cleaning tower 70, an ID fan 4, a chimney 5, Prevention facilities. And a recirculation pipe 5a that branches off from the flow path before passing through the stack 5 and recirculates the exhaust gas to the air-cooled combustor 10.

The air-cooled combustor 10 is composed of a combustion furnace 11 having a predetermined internal accommodation space. The internal space of the combustion furnace 11 is provided with a supply chamber 12 and a combustion chamber 2 in order from the bottom.

A heating burner 16 is provided in the supply chamber 12 formed at the lower end of the combustion furnace 11 and a fuel tank 8 is connected to the heating burner 16. [ It is preferable to use LNG as the auxiliary fuel for the combustion of the waste refrigerant in the fuel tank 8, but other fossil fuels that can be combusted may be used.

The combustion chamber 20 formed in the combustion furnace 11 is formed with an inflow pipe 21 through which combustion air that forced air is forcedly blown by the pump 22 into the combustion chamber 20. The inflow pipe 21 is installed along the tangential direction of the inner surface of the furnace 11 so that the combustion air discharged into the combustion furnace 11 can be pivoted along the inner side. The inflow pipe 21 is preferably installed along the tangential direction, but it may be installed so that its installation angle is at an obtuse angle of 90 degrees with respect to the center point of the combustion furnace 11. It is preferable to be formed to be close to 90 degrees even if an obtuse angle or an acute angle is formed. As shown in FIG. 3, the guide member 40 is extended from the inlet pipe 21 at a predetermined distance from the inner surface. The guide member 40 serves to guide the combustion air discharged from the inflow pipe 21 to swing along the inner surface of the combustion furnace 11. A plurality of combustion chambers 20 are formed in the combustion furnace 11 in layers. The guide member 40 may be configured to extend to the neighborhood of the adjacent inflow pipe 21. [ The furnace 11 has a thickness of 5 to 20 mm. Most preferably, it has a thickness of 10 mm. The combustion furnace 11 is made of a single wall and made of carbon steel. Preferably, STS310S material is used. Further, since the inner surface of the combustion furnace 11 is cooled by the combustion air, the temperature of the outer surface of the combustion furnace 11 is maintained at 80 DEG C or lower.

As shown in FIG. 4, in the combustion furnace 11, a plurality of combustion chambers 20 are formed in layers. The inflow pipe 21 mounted in each combustion chamber 20 is formed in a direction perpendicular to the longitudinal direction of the combustion furnace 11 or inclined with respect to the vertical direction. The inflow pipe 21 mounted on the combustion furnace 11 formed at the farthest position from the supply chamber 12 is mounted so as to be inclined so that the discharged combustion air is obliquely directed toward the supply chamber 12. When the inflow pipe 21 is tilted, the combustion air is circulated toward the supply chamber 12 so that the gas to be burned is sufficiently retained in the combustion furnace 11, thereby achieving complete combustion. As another embodiment, the inclination of the inflow pipe 21 mounted in each combustion chamber 20 can be adjusted. The inflow pipe 21 near the discharge passage 13 is mounted so as to be inclined so that the end thereof faces the direction of the supply chamber 12 and the inflow pipe 21 located at the middle is mounted perpendicularly to the longitudinal direction of the combustion furnace 11 And the inflow pipe 21 close to the supply chamber 12 may be configured to be mounted so as to be inclined toward the discharge flow path 13. [ The inflow pipe 21 is mounted obliquely with respect to the horizontal plane so as to ensure a time when the gas under combustion can be sufficiently burned in the combustion furnace 11. [

The waste refrigerant supply path 7a is connected to the supply chamber 12 and the vaporization section 30 is formed from the point where the waste refrigerant supply path 7a is connected to the waste refrigerant supply path 7a. That is, on the inlet side of the vaporization zone 30, a waste refrigerant supply passage 7a connected to the waste refrigerant tank 7 and a recycle pipe 5a through which the exhaust gas is recirculated are formed. As shown in FIG. 1, one side of the recycle piping 5a branches off from the flow path connected to the chimney 5, and a blower is installed in the middle to introduce a part of the exhaust gas discharged to the outside through the chimney 5 . The other end of the recirculation pipe 5a communicates with the vaporization zone 30. The waste refrigerant supply passage 7a is connected to a portion where the recycling pipe 5a and the vaporizing section 30 are connected. The waste refrigerant supply pipe 7a is drawn into the vaporization zone 30 and its end is bent along the vaporization zone 30. [ The waste refrigerant supply pipe 7a is bent so that the waste refrigerant is discharged along the moving direction of the exhaust gas flowing through the recycle pipe 5a.

A first check valve 5c is mounted on the front end of the portion to which the waste refrigerant supply passage 7a is connected in the recirculation pipe 5a. The first check valve 5c prevents the waste refrigerant supplied to the waste refrigerant supply path 7a from flowing back to the recycling pipe 5a side. In addition, a second check valve 5b is mounted in the flow path connected to the chimney 5 through the connection portion of the recycle pipe 5a. The second check valve 5b prevents the air discharged through the chimney or the air outside the chimney from flowing backward to the recirculation pipe 5a side. The operator can selectively install the first check valve 5c and the second check valve 5b. That is, only one of the first check valve 5c and the second check valve 5b may be installed, or both of them may be installed, or two or more of them may be provided. It is possible to prevent backflow by providing a plurality of check valves to prevent backflow in the recirculation pipe 5a, but the recirculation of the exhaust gas may be impeded by the resistance of the check valve. The inner diameter of the waste refrigerant supply path (7a) is formed smaller than the inner diameter of the vaporization section (30).

As shown in FIGS. 4 and 5, the vaporization zone 30 is connected to the supply chamber 12. The waste refrigerant whose temperature has risen through the vaporization section 30 is supplied into the combustion chamber 20 together with the flame of the heating burner 16. The length L of the vaporization zone 30 is 3m to 10m.

The internal temperature of the combustion furnace 11 is maintained at about 900 to 1200 ° C by using the heating burner 16 and the outlet temperature is preferably maintained at about 850 to 1100 ° C. When the waste liquid refrigerant in the liquid state is directly introduced into the combustion chamber 20, the temperature inside the combustion furnace 11 is lowered by about 100 degrees due to the heat of vaporization of the waste refrigerant, and the combustion efficiency is lowered. In order to prevent this, the waste refrigerant is supplied in a state where the temperature is raised by the exhaust gas (vaporized state) in the vaporization zone 30. 7, when the distance L of the vaporization zone 30 was 2 m, the outlet temperature of the combustor was measured at about 1020 ° C., and the distance L was measured at about 1090 ° C. when the distance L was 3 m. At 5 m, the outlet temperature of the combustor was measured close to 1100 ° C. Also, as the distance (L) was longer than 5 m, the outlet temperature of the combustor was increased. Therefore, it is most preferable that the distance of the vaporization zone 30 is 3 m to 10 m.

In order to smoothly vaporize the waste refrigerant in the vaporization zone 30, a recirculation rate representing the amount of exhaust gas recovered through the recycle line 5a among the exhaust gases discharged through the combustion furnace 11 is important.

'Recirculation rate (%) = k * (60 / recirculated exhaust gas temperature)', where k has a value of 18 to 22. k is preferably 20.

That is, when the temperature of the recirculated exhaust gas is 60 캜, the waste refrigerant is vaporized actively by the exhaust gas when the recirculation rate of the recirculated exhaust gas is 20%, thereby enabling complete combustion of the waste refrigerant, When the temperature of the gas is 120 ° C, even if the recirculation rate of the recirculated exhaust gas is maintained at 10%, the evaporation of the waste refrigerant is vigorous, and complete combustion is possible.

Therefore, a temperature sensor is provided in the recirculation pipe 5a to measure the temperature of the recirculated exhaust gas, and the recirculation rate is controlled by controlling the rotational speed of the blower installed in the recirculation pipe 5a according to the measured temperature do.

Since the supply amount of the waste refrigerant supplied through the waste refrigerant supply pipe 7a is determined according to the processing capacity of the combustor, the recirculation rate of the exhaust gas is controlled to control the complete combustion in the combustor.

A vortex generating protrusion (31) protrudes inside the vaporizing section (30). The vortex generation projections 31 generate a vortex in the vaporization zone 30 to promote vaporization of the waste refrigerant by promoting mixing of the waste refrigerant and the exhaust gas. As shown in FIG. 5, the vortex generating protrusions 31 may protrude at a predetermined height toward a center in a predetermined section and extend along the inner circumferential surface to form a screw shape Or the like. Mixing of the waste refrigerant and the exhaust gas is promoted by the vortex generating protrusions 31 protruding to form a screw shape, and vaporization of the waste refrigerant is actively performed.

When the vortex generating protrusions 31 are provided inside the vaporizing zone 30, the mixture of the waste refrigerant and the exhaust gas is promoted. Therefore, even if the length of the vaporizing zone 30 is shorter than 3 m, the outlet temperature of the combustor can be maintained close to 1100 have. That is, if the vortex generating protrusion 31 is provided inside the vaporization zone 30, the combustion chamber outlet temperature can be maintained close to 1100 ° C even if the length of the vaporization zone 30 is set to 2 m. Therefore, the designer designs the vortex generating protrusion 31 in the vaporization section 30 so that the length of the vaporization section 30 can be reduced in a site where the installation space of the vaporization section 30 is difficult to maintain 3 m .

The heat exchanger 50, the cleaning tower 70, the ID fan 4 and the chimney 5 are connected in turn to the discharge flow passage 13 of the air-cooled combustor 10. A part of the exhaust gas which is moved to the chimney 5 by the ID fan 4 is transferred to the vaporization section 30 of the waste refrigerant supply passage 7a through the recycle pipe 5a and recirculated.

As shown in FIGS. 1, 8 and 9, a heat exchanger 50 to which exhaust gas having been burned in the combustion chamber 20 is supplied, and a cleaning tower (not shown) to which exhaust gas having passed through the heat exchanger 50 flows 70 and a water tank 60 for supplying water to the heat exchanger 50.

The heat exchanger 50 includes a tubular wall 51 having an internal space communicating with the discharge passage 13 through which exhaust gas after combustion is introduced and a plurality of water tubes A first header 53 installed on one side of the wall 51 to communicate with one end of the water pipe 52 and a water tank 60 connected to the first header 53 to supply water, A second header 54 provided on the other side of the wall 51 so as to communicate with the other end of the water tube 52 and a second header 54 connected to the second header 54, And a supply pipe 55 for supplying the inside of the pipe 11 to the inside thereof.

The wall 51 is made of a refractory having a rectangular cross-sectional shape. The wall 51 may have a circular shape or a polygonal shape other than a square shape in consideration of the installation space and the heat exchange performance. The thickness of the wall 51 is preferably 20 to 40 mm.

The water pipe 52 is cut off from contact with the exhaust gas passing through the inside of the wall 51. It is preferable that the water pipe 52 is arranged along the longitudinal direction while being inserted so that a part of the water pipe 52 is exposed to the outside from the outer surface of the wall body 51. The water pipe 52 may be entirely inserted into the wall 51, but it is preferable that the water pipe 52 is partially inserted to the outside as shown in FIG. In addition, the water pipe 52 may be installed to be wound along the outer surface of the wall body 51. Since the hot exhaust gas introduced into the heat exchanger is in direct contact with the wall 51 made of refractory material and does not come into direct contact with the water pipe 52, the water pipe 52 is free from other corrosion in the metal dusting. Therefore, it is possible to use carbon steel with relatively low corrosion resistance but good heat transfer efficiency. Exhaust gas in the state of 850 to 1100 ° C drawn into the heat exchanger 50 is heat-exchanged with water flowing through the water tube 51 and is supplied to the cleaning tower 70 in a state of being cooled to 80 to 180 ° C.

The material of the water pipe 52 is important in corrosion resistance and heat transfer rate by metal dusting. Therefore, the content of the carbon steel used in the water pipe 52 is in the range of 0.1 to 0.2, and the carbon content is preferably 0.18%. The thermal conductivity is preferably 44 to 46 W / m ° C, and the thickness is 2 to 4 mm. Membrane walls are welded between the water tubes to adhere to the wall 51. At this time, a part of the water pipe 52 is exposed to the outside.

The water in the water tank 61 is supplied to the first header 53 mounted on the lower end side of the wall body 51. Water supplied to each water pipe 52 through the first header 53 is subjected to heat exchange with the exhaust gas, and steam is generated due to the heat of the exhaust gas. The generated steam is collected in the second header 54 and the steam filled in the second header 54 is supplied into the combustion furnace 11 through the supply pipe 55 by pressure.

The connecting portion between the water pipe 52 and the first and second headers 53 and 54 is mounted at a predetermined interval so as not to be in contact with the wall body 51. The water pipes 52 and the connecting portions of the respective headers may be vulnerable to corrosion, and therefore, it is preferable that they are spaced apart from each other so as not to be in contact with the wall 51.

The exhaust gas whose temperature is lowered to 80 to 180 ° C through heat exchange is transferred to the cleaning tower 70. The cleaning tower 70 is composed of a main body having an internal space into which exhaust gas flows, and has a shape in which an injection nozzle for spraying water is provided in an internal space of the main body. At the lower end of the cleaning tower 70, The recovered recovery tank is installed. The cleaning tower 70 is a device for removing impurities contained in the exhaust gas by spraying water into the exhaust gas.

On the inner wall of the cleaning tower 70, an FPC layer is formed. The process of forming the FEF layer is as follows. A thermosetting resin is applied to the inner wall of the cleaning tower 70 which is in contact with the exhaust gas. Next, the glass fiber is attached to the upper surface coated with the thermosetting resin, the thermosetting resin is once applied to the attached glass fiber, and then the upper surface is pressed with a roller or the like to remove the air bubbles contained in the thermosetting resin. At this time, the pressing force of the roller is adjusted so that a constant thickness is formed on the inner wall. Finally, the thermosetting resin is cured to form an F-alpha layer. And has properties of being cured by heat due to the characteristics of the thermosetting resin. The unsaturated polyester resin is cured by self heat generation by mixing 1 to 2% of the resin amount with a curing agent, and cures for a certain period of time at an ambient temperature of about 25 ° C and a humidity of about 60%. When the phenol resin is cured, the curing temperature is about 60 ° C, and the mixture is cured while heating for a certain period of time.

When the temperature of the exhaust gas flowing into the cleaning tower 1 is close to 180 degrees, when forming the Folp layer, an Folp layer is formed by lamination of unsaturated polyester resin and glass fiber to a thickness of 10 mm for the first time , And a layer of phenol resin and glass fiber is sequentially laminated on the upper part to a thickness of about 3 mm. The inside of each component is configured to be formed of a phenol resin so that the heat resistance to the unsaturated polyester resin is minimized by the low thermal conductivity of the phenol resin while having a high heat resistance through the phenol resin, So that reinforcement can be achieved.

The hydrogen fluoride (HF), which is highly corrosive when burning the waste refrigerant, is generated at a concentration of about 5 vol% (about 50,000 ppm). According to the domestic Air Quality Preservation Act, the allowable air pollutant emission standard is about 3ppm. Therefore, the concentration of hydrogen fluoride in the exhaust gas must be reduced to 3 ppm through the washing tower 70. Since hydrogen fluoride is highly corrosive, there is a problem that internal parts are easily corroded and damaged when a general cleaning tower 70 is used. In order to solve this problem, in the present invention, the entire inner parts of the cleaning tower 70 are made of a resin material (plastic material such as FRP or PE) resistant to corrosion. The cleaning tower 70 made of such a synthetic resin material is resistant to corrosiveness but has a weak heat characteristic. Therefore, it is very important to cool the temperature of the exhaust gas to 180 DEG C or less by using the heat exchanger (50).

As described above, the exhaust gas is supplied to the cleaning tower 70 while being cooled to 80 to 180 DEG C while passing through the heat exchanger 50, and the cleaning tower 70 is fully operated without being damaged by heat and is included in the exhaust gas It is possible to lower the concentration of hydrogen fluoride to 3 ppm or less.

The steam generated by the heat exchanger (50) is also supplied into the combustion furnace (11) through the supply pipe (55).

The supply pipe 55 is supplied to the combustion chamber 20 via the supply chamber 12.

In the combustion reaction of fluorinated hydrocarbons (composed of C, H and F) such as waste refrigerant, the final products are CO ₂ and HF. However, since most fluorinated hydrocarbons have a higher molar number of fluorine (F) (CF ₄ ).

Therefore, in order to completely burn out fluorinated hydrocarbons, it is necessary to supply additional hydrogen (H). In the present invention, steam generated in the heat exchanger (50) is supplied to the inside of the combustion chamber (20) to effectively remove carbon tetrafluoride.

C ₂ H ₂ F ₄ + 4H ₂ O? 4HF + 3H ₂ + 2CO ₂ ?????

As described above, steam (4H ₂ O) is additionally supplied to the inside of the combustion chamber 20 in which the waste refrigerant is burning, so that generation of carbon tetrafluoride (CF ₄ ) can be suppressed.

When steam is supplied into the combustion chamber 20, intermediate production such as carbon tetrachloride is suppressed at about 1000 ° C., which is the combustion temperature, and converted to carbon dioxide and HF.

In the waste refrigerant combustion system according to the second preferred embodiment of the present invention, the vaporization section 30 is connected to the supply chamber 12 as shown in FIG. The distance L of the vaporization zone 30 is 3m to 10m. As shown in FIG. 7, when the distance L of the vaporization zone 30 is 2 m, the combustor outlet temperature is measured at about 1020 ° C., and the distance L is measured at about 1090 ° C. when the distance L is 3 m. At 5 m, the outlet temperature of the combustor was measured close to 1100 ° C. Also, as the distance (L) was longer than 5 m, the outlet temperature of the combustor was increased. Therefore, it is most preferable that the distance of the vaporization zone 30 is 3 m to 10 m.

The orifice portion 33 whose inner diameter is reduced is provided at the inlet side of the vaporization section 30 connected to the recycling pipe 5a and the waste refrigerant supply passage 7a is provided in the orifice portion 33 constituting the section of which the inner diameter is reduced . The inner diameter d1 of the inner space 32 of the vaporization zone 30 is maintained to be larger than the inner diameter d2 of the orifice portion 33. [ The inner diameter of the waste refrigerant supply path 7a is formed to be smaller than the inner diameter of the vaporization section 30. [

The exhaust gas supplied through the recirculation pipe 5a by the Bernoulli phenomenon is increased in speed as the exhaust gas passes through the orifice portion 33. [ At this time, the liquid refrigerant supplied to the orifice portion 33 is rapidly mixed with the exhaust gas and is vaporized. The vaporization of the liquid refrigerant is promoted by the orifice portion 33. The mixture of the exhaust gas and the waste refrigerant is activated through the orifice portion 33 to raise the temperature of the waste refrigerant and promote vaporization.

Also, although not shown, a shape in which the vortex generating protrusion 31 protrudes may be applied to the inside of the vaporization zone 30. [ Mixing of the waste refrigerant and the exhaust gas is promoted by the projected vortex generating projections 31 and vaporization of the waste refrigerant is actively performed.

Since the mixing of the waste refrigerant and the exhaust gas is promoted by providing the orifice portion 33 at the entrance side of the vaporization zone 30 or by providing the vortex generation projections 31, even if the distance of the vaporization zone 30 is shorter than 3 m, The outlet temperature can be kept close to 1100 degrees. That is, if the orifice portion 33 is provided at the inlet of the vaporization zone 30, the combustion chamber outlet temperature can be kept close to 1100 ° C even if the vaporization zone 30 is set at 2 m. Therefore, the designer can design the vortex generating protrusion 31 or the orifice portion 33 in the vaporization section 30 in a site where the installation space of the vaporization section 30 is difficult to maintain 3 m, thereby reducing the length of the vaporization section 30 It is desirable to design it so that it can be installed.

The internal volume of the air-cooled combustor 10 constructed as the preferred embodiment of the present invention is 0.15 m ³ .

In the fuel tank 8, LNG is supplied as an auxiliary fuel to the combustion furnace 11 at 5.71 kg / hr and 8.99 Nm ³ / hr, at which time the temperature of the auxiliary fuel is normal temperature. The waste refrigerant stored in the waste refrigerant tank 7 is supplied at a rate of 20 kr / hr in a liquid state at room temperature. At this time, the gas is supplied to the combustor 10 in the state of being converted into gas phase while passing through the vaporization zone 30.

Further, the exhaust gas at about 60 to 120 ° C is supplied to the supply chamber 12 at 24.45 kr / hr in a state where heat exchange is performed with the waste refrigerant while passing through the vaporization section 30.

Further, the combustion air supplied to the combustor is supplied to the combustion furnace 11 at 230 kr / hr and 177 Nm 3 / hr. The air forcedly blown by the pump 22 is supplied into the combustion furnace 11 through the inflow pipe 21. The combustion air passing through the inflow pipe 21 formed in the normal direction turns along the inner surface of the outer wall. At this time, the combustion air repeatedly turns sufficiently along the inner surface of the outer wall by the guide member (40). The combustion air circulates along the inner surface of the outer wall to cool the outer wall. Simultaneously, the combustion gas is prevented from contacting the inner surface of the outer wall. Therefore, since the combustion air is burned in a preheated state while being in contact with the outer wall, the combustion efficiency is improved and the inner surface of the combustion furnace 11 is prevented from being corroded by the gas under combustion.

When the internal temperature of the combustion furnace 11 is 900 to 1200 ° C and combustion of the waste refrigerant together with the combustion air is completed, the exhaust gas is moved through the discharge flow path 13. At this time, the exhaust gas is moved at a temperature of about 850 to 1100 ° C at 281 kr / hr and 221 Nm ³ / hr. This gas is converted into an exhaust gas of 283 kr / hr and 224 Nm ³ / hr while passing through a heat exchanger 50 having a Urea of 2.6 kr / hr and a concentration of 4 wt%. At this time, the temperature reaches approximately 80 to 180 ° C. Next, the exhaust gas is converted to 446 g / hr and 422 Nm 3 / hr while passing through the cleaning tower 70 having the process number of 118 rpm / hr and the compressed air of 45 r / hr. At this time, the temperature reaches about 60 to 120 ° C.

Some of which are transferred to the vaporization zone 30 through the recycle line 5a. The remaining exhaust gas is discharged through the ID fan 4 and the chimney 5.

The exhaust gas that has been transferred to the recycle pipe 5a is mixed with the waste refrigerant through the vaporization section 30 and is supplied to the supply chamber 12 in an elevated temperature state. The temperature of the recycle pipe 5a is increased or the waste refrigerant in a vaporized state is supplied to the combustion furnace 11 so that the internal temperature of the combustion furnace can be prevented from being lowered due to the heat of the waste refrigerant vaporization in the combustion furnace.

As described above, since the thermal destruction processing and detoxification system for waste refrigerant only according to the present invention is applied to waste or solid fuel in the case of conventional air-cooling type ointment technology, the excess air ratio is 1.8 to 2.2, It was possible to burn while supplying. At this time, the oxygen concentration in the combustion gas is about 12 vol%.

In the combustion furnace 11, heat energy is generated in the combustion process. In order to withstand this thermal energy, conventionally, an expensive heat-resistant metal material is used as the inner side to prevent damage to the equipment. The outer wall of the combustor was cooled by using the refractory having a low heat transfer rate. In the case of refractories, the heat capacity is very large, so it has a lot of heat energy, which leads to energy loss. Therefore, cooling of the inner side by the combustion air required for combustion instead of refractory can reduce the energy loss of the refractory, and at the same time, the combustion air is preheated during the cooling process of the outer wall of the combustor.

Further, it is possible to ensure complete combustion through the swirling flow of the combustion air supplied into the combustion furnace 11, prevention of local high-temperature region, and residence time in the combustion furnace 11. [

The internal feed rate is very important for swirl flow formation. In order to prevent the internal supply speed of the combustion furnace 11 from decreasing when the combustion air supply amount is reduced to lower the excess air ratio, the interval between the guide member 140 and the outer wall is reduced until the outer wall temperature becomes 80 DEG C, A guide member (40) is provided near the tubes (21, 31) to maintain the feed rate.

In the present invention, since the target waste is a waste refrigerant and LNG is used as the auxiliary fuel, the excess air ratio can be operated at a relatively low value of 1.3 to 1.4. Therefore, as the supply amount of the combustion air decreases, Is further required. In the present invention, a combustion gas for forcedly blowing outside air with a fluid for cooling the outer wall of the combustion furnace (11) is used.

The air-cooled type combustor 10 prevents the gas being burned from being brought into contact with the inner side surface of the combustion furnace 11 due to the rotating swirl flow introduced into the inner side of the combustion furnace 11, so that corrosion by HF can be prevented originally.

In addition, the vaporization zone 30 vaporizes the waste refrigerant by mixing waste liquid in the liquid state with exhaust gas. In the case where the heat exchanger is installed to raise the temperature of the waste refrigerant by the heat of the exhaust gas, the equipment for installing the heat exchanger and the installation space for installing the heat exchanger must be secured and the heat exchanger is easily damaged due to the exhaust gas. When the vaporization section 30 is provided, the installation space is reduced, and the mixed gas in which the exhaust gas and the waste refrigerant are mixed is directly supplied to the combustion chamber 20 through the supply chamber 12, thereby improving the thermal efficiency.

A secondary combustion chamber may be additionally provided at the rear end of the air-cooled combustor 10 for securing the residence time of the thermal decomposition gas and inducing complete combustion.

The ID fan 4 and the chimney 5 are disposed in the treated combustion exhaust gas atmosphere 4 and the flue 5 in the treated combustion exhaust gas atmosphere, Discharge and pollutant monitoring.

In the present invention, it is economical to prevent the internal temperature of the combustion chamber from being reduced when the waste refrigerant is supplied into the combustion furnace, and to supply the heat energy required for vaporization of the refrigerant from outside the system. Further, by applying the exhaust gas recirculation method in which the exhaust gas is supplied again to the combustion chamber 20 of the combustion furnace, the nitrogen oxides generated in the combustion of the waste refrigerant can be reduced. That is, the vaporization zone 30 of the waste refrigerant combustion system can lower the nitrogen oxide concentration discharged from the combustor at the same time as the vaporization heat of the waste refrigerant is supplied.

In the present invention, it is possible to use a cleaning tower 70 made of a synthetic resin material by lowering the temperature of the exhaust gas to 80 to 180 ° C through heat exchange between the exhaust gas and water through the heat exchanger 50. At this time, the use of the washing tower 70 made of synthetic resin prevents corrosion by the exhaust gas, so that the impurities contained in the exhaust gas can be removed for a sufficient time. By supplying the steam generated in the heat exchanger 50 to the combustion chamber 20 in the combustion furnace 11, it is possible to suppress the generation of intermediate products that are difficult to decompose, such as carbon tetrachloride, which is generated upon combustion of the waste refrigerant .

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined in the appended claims and their equivalents. Of course, such modifications are within the scope of the claims.

5a: Recirculation piping
7: Waste refrigerant tank
7a: a waste refrigerant supply path
10: Air-cooled combustor
11: Combustion furnace
12: Supply Room
30: Vaporization section
31: vortex generating projection
33: Orifice part
50: heat exchanger
51: Wall
52: Water pipe
53: First header
54: Second header
55: supply pipe
70: washing tower

Claims

A waste refrigerant tank (7) for supplying waste refrigerant discharged from the exhaust gas containing hydrogen fluoride through the waste refrigerant supply path (7a) during combustion;
A supply chamber 12 in which a heating burner 16 is installed and a combustion chamber 16 for burning the waste refrigerant delivered from the waste refrigerant tank 7 in an internal temperature range of 900 to 1200 ° C by the heating burner 16 A combustion furnace (11) equipped with a combustion chamber (20);
And a recycling pipe (5a) for recovering part of the exhaust gas discharged from the combustion furnace (11) to the waste refrigerant supply path (7a)
And the waste refrigerant is supplied to the combustion furnace (11) in a state where the waste refrigerant is vaporized by an exhaust gas having a temperature of 60 to 120 占 폚 passing through the recycling line (5a).

The method according to claim 1, wherein the vaporization section (30) connected to the combustion chamber (20) after the recycle piping (5a) is combined with the waste refrigerant supply passage (7a) is a waste refrigerant combustion system .

The exhaust gas recycling apparatus according to claim 1, wherein the amount of exhaust gas recovered through the recycling line (5a) in the exhaust gas discharged through the combustion furnace (11)
Recirculation rate (%) = k * (60 / recirculated exhaust gas temperature)
Where k is a value between 18 and 22.

The system according to claim 1, wherein the inner circumferential surface of the vaporization section (30) is provided with a vortex generation projection (31) for promoting mixing of the waste refrigerant and the exhaust gas.

5. The system according to claim 4, wherein the vortex generating protrusions (31) protrude toward the center of the vaporization section (30) and extend in a screw shape along the inner circumferential surface.

The apparatus according to claim 1, wherein the vaporization section (30) is provided with an orifice section (33) whose inner diameter is reduced at the inlet side connected to the recycle piping (5a), and the orifice section (33) (7a) are connected to each other.

The waste refrigerant combustion system according to claim 6, wherein an inner diameter of the waste refrigerant supply path (7a) is smaller than an inner diameter of the vaporization section (30).

2. The apparatus according to claim 1, wherein a first check valve (5c) for preventing the waste refrigerant from flowing back to the recycle line (5a) is provided at a front end of a portion connected to the waste refrigerant supply line (7a) from the recycle line Mounted waste refrigerant combustion system.

The air conditioner according to claim 8, wherein a second check valve (5b) for preventing air outside the chimney from flowing back toward the recycling pipe (5a) is mounted in a channel connected to the chimney (5) through the connecting portion of the recycle pipe Waste refrigerant combustion system.

The heat exchanger according to claim 1, further comprising: a heat exchanger (50) for exchanging heat between the exhaust gas discharged from the combustion furnace (11) and water to cool the combustion gas to 80 to 180 deg. C, And
And a cleaning tower (70) for removing impurities including hydrogen fluoride contained in the combustion gas passing through the heat exchanger (50)
The cleaning tower (70) is made of a resin material so as to be in contact with the exhaust gas so as to prevent corrosion by the impurities,
The steam is supplied to the combustion chamber 20,
C ₂ H ₂ F ₄ + 4H ₂ O? 4HF + 3H ₂ + 2CO ₂ ?????
Of the waste refrigerant combustion system.

11. The cleaning apparatus according to claim 10, wherein the cleaning tower (70) has an inner wall
A thermosetting resin is applied, a glass fiber is adhered to a thermosetting resin-coated portion, a thermosetting resin is further applied on the thermosetting resin, and after bubbles are removed by pressing, the thermosetting resin is cured to form an F-