KR100836261B1 - Burner for regeneration of dpf and diesel particulate filter using it - Google Patents

Abstract

A burner for regenerating a catalyzed particulate filter for a diesel engine and a catalyzed particulate filter using the same are provided to obtain economical advantage by using heat of flame in evaporating fuel through a heat transferring member. A burner for regenerating a catalyzed particulate filter for a diesel engine comprises evaporators(10,20), a combustor(30) and a heat transferring member(37). Liquefied fuel is injected into the evaporator and then evaporated. The combustor is provided at a side of the evaporator to remix mixed gas exhausted from the evaporator and then ignite the mixed gas. The heat transferring member has a first end, which is in contact with the evaporator, and a second end, which is exposed to flame in the combustor.

Description

Burner for Diesel Engine Soot Filter Regeneration and Diesel Engine Soot Filter Using It {Burner for regeneration of DPF and Diesel Particulate Filter using it}

The present invention relates to a burner for regenerating a diesel engine particulate filter and a diesel engine particulate filter (DPF) using the same, and more particularly, to reduce smoke by filtering particulates contained in exhaust gas of a diesel engine. It relates to a diesel engine soot filtration device for regeneration burner and a diesel engine soot filtration device using the same.

The use of diesel engines is common in trains, ships, and industrial vehicles, and the use of diesel engines is gradually increasing with the recent launch of diesel passenger cars.

This trend of increasing usage of diesel engines is increasing the emissions of particulate matter (PM), such as soot and SOF (Soluble Organic Fraction), contained in the exhaust gas emitted from diesel engines. Regulations are gradually being tightened due to environmental pollution, especially air pollution.

In order to solve the above problems of environmental pollution, various methods for the diesel particulate filter (DPF) for collecting and treating soot to prevent the emission of soot particles generated from diesel vehicles, etc. into the air are studied. It is becoming.

FIG. 13 shows a burner for regenerating a diesel engine smoke reduction device disclosed in Korean Patent No. 10-0622135 as an example of a conventional diesel engine smoke reduction device for reducing the smoke of a diesel engine.

Referring to FIG. 13, a burner 1000 for regenerating a diesel engine particulate smoke reducing device is disposed in front of a combustion chamber and disposed on the same axis as the combustion chamber 110 so that exhaust gas of an engine flows into the combustion chamber 110. A vaporizer 120 for vaporizing a liquid fuel such as a flow path 300, diesel oil, and the like, and a mixture of fuel and air supplied into the combustion chamber 110 by mixing vaporized fuel and combustion air. A fuel injection nozzle 130, a combustor 140 installed in the combustion chamber 110 to inject a mixture gas supplied from the fuel injection nozzle 130 to form a flame, and a mixture injected from the combustor 140. An igniter 150 for igniting a flame in the gas and a flame detector 160 for detecting the presence of flame on the surface of the combustor 140.

[Document 1] Republic of Korea Patent No. 10-0622135

As described above, the conventional burner for regenerating the diesel particulate smoke reducing device requires a lot of external energy because the heat of vaporization is continuously required to atomize and vaporize the fuel.

The present invention has been made in order to solve the above-mentioned problems, the liquid fuel is injected, a vaporizer for vaporizing the injected fuel is discharged to the mixed gas state; A combustor provided on one side of the vaporizer and configured to ignite after finally remixing the mixed gas discharged from the vaporizer; And a heat transfer member having one end in contact with the carburetor and the other end being exposed to the flame of the combustor to transfer heat of the flame generated from the combustor to the carburetor. .

The apparatus of claim 1, further comprising: a temperature increase chamber positioned in front of the combustor and configured to increase a temperature of exhaust gas discharged from the diesel engine by flame heat generated from the combustor; An exhaust gas inlet passage communicating with the temperature increase room and connected to the exhaust gas passage of the diesel engine for introducing the exhaust gas is further included.

The apparatus of claim 1, further comprising: a swirler disposed between the exhaust end of the exhaust gas inlet passage and the temperature increase chamber to introduce the exhaust gas introduced through the exhaust gas inlet passage into the temperature increase chamber in a swirling flow state. More preferred.

The vaporizer includes: a primary vaporizer configured to inject a liquid fuel and vaporize the injected fuel into a primary mixed gas with air, and a discharge side of the primary vaporizer; It is preferable that the primary vaporizer discharged from the primary vaporizer is introduced, and the secondary liquid vaporizer to discharge the secondary liquid gas in the secondary liquid by the second vaporization of the fuel in the remaining liquid state in the primary gas mixture. Do.

In the above, the primary carburetor, the air inlet is formed at one end, the discharge port for discharging the primary mixed gas is formed at the other end, the outer body having at least one nozzle communicating with the inside and One end is provided on the outside of the body, the other end is disposed in the body and the fuel supply pipe for supplying fuel to the inside of the body, coupled to the outer surface of the body, is in communication with the nozzle, Primary air inlet space for supplying high-pressure, high-speed external air to the front of the fuel supply pipe through, and one end is in communication with the interior of the primary air inlet space, the other end is in communication with the outside primary flow It is preferable to include at least one primary air inlet composed of an air inlet pipe.

In the above, it is preferable that the heat transfer member further extends from one end and includes an extension part in contact with the secondary vaporizer and the body.

In the above, the fuel supply pipe is preferably connected to the fuel preheating means for preheating the supplied fuel.

In the above, the fuel supply pipe is preferably provided with a fuel amount adjusting means for adjusting the flow rate of the fuel supplied.

In the above, it is preferable that the primary air inlet pipe is provided with primary air preheating means for preheating the air blown into the body through the nozzle.

In the above, the body is preferably provided with a body heating means for improving the initial vaporization performance of the fuel.

In the above, the secondary vaporizer, one side is in communication with the outlet of the primary vaporizer, the secondary vaporization chamber into which the primary mixed gas flows, and the secondary vaporization chamber is provided on the outer peripheral surface of the secondary vaporization chamber Secondary vaporization chamber heating means for initial heating, Venturi-shaped mixed gas spray nozzle for discharging the mixed gas introduced into the secondary vaporization chamber in a secondary mixed gas state, and one end of the secondary gas In communication with the interior of the fire chamber, the other end is preferably in communication with the outside includes a secondary air inlet pipe to which the outside air flows.

In the above, it is also preferable that the secondary vaporization chamber heating means is provided on the outer peripheral surface or the wall of the secondary vaporization chamber.

In the above, the secondary vaporization chamber and the inner wall surface of the body is preferably provided with a heat transfer area increasing means protruding therein for efficient transfer of heat.

In the above, it is preferable that the secondary air inlet pipe is provided with an air amount adjusting means for adjusting the flow rate of the external air introduced.

In the above, the secondary air inlet pipe is preferably further provided with air preheating means for preheating the incoming air.

In the above, the combustor is provided at the boundary of the mixing chamber and the mixing chamber for final mixing of the secondary mixed gas discharged from the mixed gas jet nozzle by communicating with the mixed gas jet nozzle, and at least one or more layers It is preferable to include a flame surface of a porous medium having a different porosity, a flame space in which a flame is formed along the circumference of the flame surface, and an igniter for igniting a mixed gas discharged into the flame space through the flame surface. Do.

In the above, the porous medium is preferably any one selected from perforated plate, metal mesh, metal mat, ceramic, heat-resistant fiber.

In the above, it is preferable that the combustor further comprises a blocking plate which closes one end of the mixing chamber and prevents the straight flow of the secondary mixed gas injected from the mixed gas injection nozzle.

In the above description, it is preferable that the blocking plate includes at least one arc-shaped plate which is in contact with the mixing chamber and has an arc shape with a convex cross section.

In the above, it is preferable to further include a blocking plate wings extending along the circumference of the blocking plate in contact with the flame space.

In the above, it is preferable that the flame position adjusting portion is further provided in the portion adjacent to the blocking plate of the flame surface so as to prevent the secondary mixed gas from passing through.

In the above, preferably between the flame surface and the outer circumferential surface of the mixed gas injection nozzle further comprises a flame induction space so that the flame is generated in the entire flame space.

In the above, the combustor, preferably further comprises a flame detector for detecting the presence of flame in the flame space.

In the above, one side of the heat transfer member is spaced apart from the flame surface is provided surrounding the circumference of the flame surface, the other side is in contact with the outer peripheral surface of the secondary vaporization chamber flame heat in the flame space is the secondary vaporization It is desirable to deliver in thread.

In the above, the combustor, spaced apart from the heat transfer member is provided surrounding the heat transfer member, preferably further comprises a flame stabilizer for stabilizing the flame in the flame space from the exhaust gas of the diesel engine.

In the above, it is preferable that the combustor further comprises a heat insulator provided between the heat transfer member and the insulator to prevent heat loss of the heat transfer member.

In the above, the exhaust gas inlet passage has a central axis equal to the central axis of the flame surface, one end is open and the other end is a closed double pipe structure, the inner pipe is coupled to the outer cylinder and one end is the Preferably, the exhaust gas flow passage is in communication with the other end, and the other end is in communication with the inner space of the outer cylinder, and constitutes an exhaust gas inflow pipe into which the exhaust gas of the diesel engine flows.

In the above, it is also preferable that the exhaust gas inlet pipe is tangentially connected to the exterior of the outer cylinder to communicate with the inner space of the outer cylinder.

In the above, it is also preferable that the exhaust gas inlet pipe is connected to the closed one end of the outer cylinder to communicate with the inner space of the outer cylinder.

In the above-mentioned, the swirler is a plate-shaped support plate having the same central axis as the central axis of the flame surface, at least one gas passage hole through which the exhaust gas passes through the front and rear surfaces of the support plate, It is coupled to the support plate, at least one wing of the support plate and at least one wing that serves as a guide surface for generating a turning flow with respect to the central axis of the flame surface when the exhaust gas passes through the gas passage hole It is also preferable to.

In the above, it is preferable to further include a swing strength adjusting means for arbitrarily adjusting the angle of the blade in the non-powered state in accordance with the flow rate of the exhaust gas flowing into the swirler.

In the above, it is preferable to further include a swing strength adjusting means for arbitrarily adjusting the angle of the blade by the power in accordance with the change in the flow rate of the exhaust gas flowing into the swirler.

In the above, it is preferable that one end of the temperature rise chamber communicates with the discharge end of the swirler, and the combustor is disposed therein.

In the above, it is preferable that the other end of the temperature increase room is further provided with gas mixing means made of a porous medium.

In the above, the gas mixing means is a truncated conical or triangular pyramid shape inside, the side is perforated, the bottom is open is connected to the discharge end of the temperature rise room, the top is closed to the inside of the temperature rise room It is preferably arranged in.

On the other hand, the present invention has been made in order to solve the above-mentioned problems, the liquid fuel is injected, a vaporizer for vaporizing the injected fuel and discharged in a mixed gas state; A combustor provided at one side of the vaporizer and ignited after final mixing of the mixed gas discharged from the vaporizer; A heat transfer member whose one end is in contact with the vaporizer and the other end is exposed to the flame of the combustor and transfers heat of flame generated in the combustor to the vaporizer; A temperature increase room located in front of the combustor and configured to increase a temperature of exhaust gas discharged from the diesel engine by flame heat generated from the combustor; An exhaust gas inlet passage communicating with the temperature increase room and connected to the exhaust gas passage of the diesel engine to introduce the exhaust gas; A diesel engine smoke using a burner for regenerating a burner for regenerating a diesel engine comprising: and a smoke filter configured to communicate with a discharge end of the temperature increase room, the casing having an internal space, and a smoke filter provided in the casing. Provide a filtration device.

In the above, it is preferable that the oxidation catalyst is provided in front of the soot filter material.

In the above, the other end of the temperature rise chamber, the inside is hollow truncated conical or triangular pyramid shape, the side is perforated, the bottom is open and connected to the discharge end of the temperature rise room, the upper surface is closed to the temperature rise It is preferable that the gas mixing means arranged inside the chamber is provided.

In the above, it is preferable that a flow homogenizing means made of a porous medium is combined with the open end face of the gas mixing means.

In the above, it is preferable that an adapter having a diameter smaller than that of the temperature increase chamber and the smoke filter is provided between the temperature increase chamber and the smoke filter.

In the above, it is preferable that a fluid homogenization means made of a porous medium is provided between the adapter and the soot filtration unit.

In the above, the hole of the flow homogenizing means is preferably formed to increase in size toward the outside.

The exhaust gas flow passage may include a main flow passage through which a portion of the exhaust gas discharged from a diesel engine flows into the exhaust gas inflow passage, and branched from the main flow passage to allow the remaining exhaust gas to flow into the soot filtration unit. It is preferable to include a branch pipe.

In the above, it is preferable that the branch pipe is provided with an exhaust gas flow rate adjusting means for adjusting the flow rate of the exhaust gas flowing through the oil passage.

In addition, the present invention has been made in order to solve the above-described problems, the fuel in the liquid state is injected, the vaporizer for vaporizing the injected fuel in a mixed gas state; A combustor provided at one side of the vaporizer and ignited after final mixing of the mixed gas discharged from the vaporizer; A heat transfer member whose one end is in contact with the vaporizer and the other end is exposed to the flame of the combustor and transfers heat of flame generated in the combustor to the vaporizer; A connection pipe which is located in front of the combustor and into which combustion gas of flame generated from the combustor flows; One side is in communication with the connecting pipe, the exhaust gas discharged from the diesel engine is introduced is mixed with the combustion gas curved section of the curved cross-section; Diesel engine smoke filter using a burner for regenerating the diesel engine smoke filter comprising a; and a smoke filter comprising a casing having an inner space, and the smoke filter is provided in the casing, the communication with the discharge end of the curved pipe portion; To provide.

According to the burner for regenerating the diesel engine particulate filter of the present invention and the diesel engine particulate filter using the same, the following effects are obtained.

First, very small external energy is required only in the step of vaporizing and then vaporizing the initially preheated fuel, and after ignition to form a flame, the heat of the flame is used as the heat of vaporization of the fuel by the heat transfer member. No external energy is needed for the fuel, and even the lowest external energy enables very smooth fuel vaporization, which is advantageous in terms of economics and is very advantageous in maintaining burner stabilization in exhaust gas.

Second, since a flame is formed in a flame space independent of the diesel engine exhaust gas flow, a stable flame state that is not affected by a change in operating conditions of the engine can be maintained.

Third, the vaporization unit, the combustion unit, and the exhaust gas inlet passage are integrated, and the size is very compact in a very simple structure, and the space occupancy is very small when attached to the diesel vehicle.

Fourth, since external air is sucked in when liquid fuel is atomized, it is possible to minimize the flow rate of the forced secondary air for combustion or to completely replace the secondary air for combustion with the intake air. Even if a compressor, compressor, etc. are not needed or needed, a very small air supply is required, so the system can be miniaturized and very economical.

Fifth, since the fuel-air mixture gas is injected through a flame surface composed of one or more layers of porous materials having different porosities, it is easy to control the injection speed and the injection pressure of the mixture gas, so that even in the exhaust gas flow, It is possible to ignite and extinguish and maintain a stable flame without being extinguished even when the flow rate and pressure of exhaust gas change rapidly.

Sixth, the burner for regenerating the diesel engine soot filtration device of the present invention and the diesel engine soot filtration device using the same can be used for filter regeneration of the exhaust gas soot reduction device of all engines using diesel engines such as trains, ships and diesel vehicles. It is a burner for other uses besides diesel engine, and its applicability is very wide and it is useful in terms of environmental pollution prevention.

Seventh, the swirling intensity of the exhaust gas flow flowing into the temperature rise room is changed in conjunction with the RPM and load size of the diesel engine through the swirling device between the temperature rise room and the exhaust gas inlet passage. The length and width are kept constant regardless of the operating conditions of the engine to maximize the flame stability of the burner.

Eighth, the flame stabilized by the swirler can reduce the size of the temperature rise room and the size of the variable swirler, so that the size of the diesel engine particulate filter regeneration burner and the diesel engine particulate filter using the same are very small. Can be designed.

Ninth, the flame of the burner can be very stabilized even at high load operation of a large-capacity engine when the amount of exhaust gas introduced into the burner is controlled by the exhaust gas branch pipe and the exhaust flow control valve.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. Prior to this, terms or words used in the present specification and claims should not be construed as being limited to the common or dictionary meanings, and the inventors should properly explain the concept of terms in order to best explain their own invention. Based on the principle that it can be defined, it should be interpreted as meaning and concept corresponding to the technical idea of the present invention.

Therefore, the embodiments described in the specification and the drawings shown in the drawings are only one of the most preferred embodiments of the present invention and do not represent all of the technical idea of the present invention, various modifications that can be replaced at the time of the present application It should be understood that there may be equivalents and variations.

In the term used herein, the burner for regenerating the diesel engine particulate filter is the same meaning as the burner for regenerating the DPF, and the diesel particulate filter is the term having the same meaning as the diesel exhaust filter or the DPF system.

1 is a side cross-sectional view showing a burner for reproducing a DPF according to an embodiment of the present invention.

1, the DPF regeneration burner according to an embodiment of the present invention is the primary vaporizer 10 and the primary vaporizer for discharging the fuel in the liquid state at the same time as the primary vaporization to discharge to the primary mixed gas state Secondary vaporizer 20 connected to the discharge side of the (10) to transfer the primary mixture gas discharged from the primary vaporizer 10 to the combustor 30, and at the same time secondary vaporization of the remaining liquid droplets in the primary mixture gas (20) And a combustor 30 connected to one side of the secondary vaporizer 20 to form a flame by remixing a mixed gas of fuel and air transferred from the secondary vaporizer 20.

As shown in FIG. 1, the primary vaporizer 10 preferably includes a body 11, a fuel supply pipe 13, and a primary air injection unit 14.

The body 11 is a member through which air and fuel flow, and an air inlet 11a is formed at one end of the body 11, and an outlet through which the primary mixed gas, which is a mixture of fuel and air, is discharged. 11b) is formed, the wall of the body 11 is provided with at least one nozzle 12 in which the outside and the inside communicates with the outside air is injected at a high speed into the body (11).

It is also preferable that the air inlet 11a is further provided with an intake air amount adjusting means 11c for adjusting the flow rate of the inflowing air.

One end of the fuel supply pipe 13 is disposed inside the body 11, and the other end is located outside the body 11 to supply fuel to the inside of the body 11.

In addition, the fuel supply pipe 13 may further include fuel preheating means 13a such as an electric heater, flame heat generated by the flame in the combustor 30, and exhaust gas heat of the engine, in order to preheat the fuel supplied thereto. In addition, it is also preferable to further include a fuel flow rate control means (13b) such as a fuel pump, a solenoid valve which is adjustable in flow rate in order to adjust the flow rate of the fuel supplied to the fuel supply pipe (13).

The primary air inlet 14 is a high-speed compressed air inside the body 11 through the nozzle 12 to atomize the fuel supplied into the body 11 through the fuel supply pipe 13 into a fine droplet state. Is provided on the outer circumferential surface of the body 11 and communicates with the nozzle 12 to supply high-speed compressed air to the front of the fuel supply pipe 13 through the nozzle 12.

The primary air inlet 14 is preferably provided with a primary air inlet pipe 14a in which one end communicates with the nozzle 12 and the other end communicates with the outside to supply air from the outside.

Here, in order to preheat the air flowing into the primary air inlet pipe 14a, primary air preheating means 14b, such as an electric heater, flame heat caused by the flame of the combustor 30, and exhaust gas heat, may be further provided. It may be.

In addition, it is also preferable that the air flow rate adjusting means 14c for adjusting the flow rate of the air flowing into the primary air inlet pipe (14a) is further provided.

Looking at the operation of the primary vaporizer 10 according to the above configuration, the air introduced into the primary air inlet 14 through the primary air inlet pipe 14a is a state of high pressure, high speed through the nozzle 12 It is injected into the body (11).

At this time, the high-speed air injected through the nozzle 12 is a pressure state inside the body 11 is lower than the pressure outside the body 11 according to the Bernoulli principle, and thus the external air at the air inlet 11a Is sucked into the body (11).

At this time, the liquid fuel supplied through the fuel supply pipe 13 is also sucked to the nozzle 12 side inside the body 11, and the sucked fuel collides with the high-speed air introduced through the nozzle 12, Due to the difference in momentum between the fuels, atomization occurs in the state of droplets of fine size.

Here, when the air preheated by the primary air preheating means 14b is injected into the body through the nozzle 12 or the fuel preheated by the fuel preheating means 13a is supplied through the fuel supply pipe 13. For example, liquid fuel may be atomized into finer droplets, and atomized fuel may be vaporized by very small thermal energy, such as by preheating air or by its own heat. have.

In other words, the primary vaporizer 10 is the atomization and vaporization process of the liquid fuel is generated at the same time, the complete vaporized fuel and the liquid vaporized residual liquid fuel and the external air sucked from the air inlet (11a) is mixed with each other It is discharged through the outlet 11b in the state of primary mixed gas, and flows into the secondary vaporizer 20.

The primary vaporizer 10 is atomized and vaporized the liquid fuel at the same time by the same principle as in the above-described process, the vaporized gas fuel is flame heat in the combustor 30 described later through the heat transfer member 37 Since the second carburetor 20 and the first carburetor 10 can be used as the vaporization energy, a more smooth and normal fuel vaporization process occurs in a normal operating state.

On the other hand, the secondary carburetor 20 is in communication with the outlet 11b of the body 11 of the primary vaporizer 10, one end is in communication with the mixing chamber 31 of the combustor 30, the primary carburetor ( The primary mixed gas discharged from 10) is introduced to vaporize the fuel in the remaining liquid state in the primary mixed gas to secondary vaporize and discharge to the combustor 30 in the fully vaporized secondary mixed gas state.

As shown in FIG. 1, the secondary vaporizer 20 is configured to initially heat the secondary vaporization chamber 21 and the secondary vaporization chamber 21, which are spaces in which the primary mixed gas flows to generate secondary vaporization. A mixed gas spray nozzle 22 for discharging the secondary vaporization chamber heating means 21a and a secondary gas mixture, which is a mixture of secondary vaporized fuel and air, in the secondary vaporization chamber 21 to the combustor 30; , One end is in communication with the interior of the secondary vaporization chamber 21, the other end is in communication with the outside includes a secondary air inlet pipe 23 through which the outside air flows.

The mixed gas jet nozzle 22 extends from the neck 22b and the neck 22b extending from the reduction tube 22a, the cross section being gradually reduced, and the same, with the cross section being kept in the reduced state. It is preferable that the Venturi shape is constituted by an enlarged tube 22c whose cross-sectional area is gradually enlarged.

The secondary air inlet pipe 23 is a member for supplying combustion air for combustion of the secondary mixed gas, and the secondary air inlet pipe 23 has an amount of air such as a solenoid valve for adjusting the flow rate of external air introduced therein. It is preferable that the adjusting means 23a be provided.

Referring to the operation of the secondary vaporizer 20 according to the above configuration, the primary mixed gas discharged from the primary vaporizer 10 is introduced into the secondary vaporization chamber 21, the secondary vaporization chamber heating means 21a Is initially vaporized.

At this time, the flame heat of the combustor 30 transmitted to the secondary vaporization chamber 21 through the heat transfer member 37 to be described below is a residual droplet state included in the primary mixed gas introduced into the secondary vaporization chamber 21. Completely vaporize the fuel.

The fully vaporized primary mixed gas is mixed with the secondary air supplied through the secondary air inlet pipe 23 and discharged through the mixed gas spray nozzle 22 in the state of the secondary mixed gas, and of the combustor 30 It flows into the mixing chamber 31.

In the above, the secondary air supplied through the secondary air inlet pipe 23, when passing through the neck 22b, the speed at the neck 22b is faster than the speed at the inlet of the reduction tube 22a, thereby Due to the Venturi effect at 22b, the pressure at the neck 22b is maintained at a lower pressure than the inlet of the reduction tube 22a, so that the primary mixed gas introduced into the secondary vaporization chamber 21 is the secondary vaporization chamber 21. It is preferable that the mixed gas jet nozzle 22 is venturi-shaped since it is sucked into the neck 22b and mixed with the secondary air 23 and discharged to the combustor 30 very smoothly.

In addition, the discharge performance of the secondary mixed gas is affected by the flow rate of the secondary air introduced through the secondary air inlet pipe 23, and the secondary air introduced through the secondary air inlet pipe 23 is a combustor. Since it is used as combustion air when combustion occurs in the (30) it will be preferable to further provide an air flow rate adjusting means (23a) for controlling the amount of air flowing into the secondary air inlet pipe (23).

On the other hand, the combustor 30 is provided on one side of the secondary vaporizer 20, the secondary mixed gas discharged through the mixed gas injection nozzle 22 of the secondary vaporizer 20 is introduced into the final air and gas fuel It is a member that forms a flame by ignition after mixing.

As shown in FIG. 1, the combustor 30 includes a mixing chamber 31, a flame surface 32, a blocking plate 33, a flame space 34, an igniter 35, and a flame detector 36.

The mixing chamber 31 is a space for further increasing the mixing of the secondary mixed gas discharged through the mixed gas injection nozzle 22 of the secondary vaporizer 20 to make the final mixed gas state used for combustion.

The flame surface 32 is coupled to the mixed gas spray nozzle 22 and surrounds the mixing chamber 31. The flame surface 32 is a surface on which the gas finally mixed in the mixing chamber 31 is ejected to form a flame. For this purpose, it is preferable to configure a porous medium having at least one or more different porosities.

As shown in FIG. 2, the porous medium 32a of the flame surface 32 is preferably any one selected from a perforated plate, a metal mesh, a metal mat, a ceramic, a heat resistant fiber, and the like.

The blocking plate 33 is provided to close the open end face of the flame surface 32 in the combustor 30 so as to prevent the mixture of the secondary mixed gas injected from the mixed gas jet nozzle 22.

As shown in FIG. 1, the blocking plate 33 is in contact with the mixing chamber 31 and includes an arc-shaped plate 33a and a blocking plate blade 33b.

The at least one arc-shaped plate 33a is an arc-shaped convex cross section outwardly so that the final mixing of the fuel and air is achieved.

The blocking plate blade 33b increases the local concentration of the mixed gas ejected from the flame surface 32 so that the ignition on the flame surface 32 can be smoothly performed even at high load operation of the engine. In order to adjust the length of the flame formed on the flame surface 32 and to increase the width of the flame, it extends along the edge of the arc-shaped plate 33 to be in contact with the flame surface 32.

Although FIG. 1 shows the blocking plate 33 which consists of one arc-shaped plate 33a, FIG. 3 shows the blocking plate 33 which consists of two arc-shaped plate 33a 33a1, 33a2. ), The number of arc-shaped plates 33a can be changed according to the embodiment.

4A-4C illustrate another embodiment of flame surface 32.

Referring to FIG. 4A, the flame position adjusting part 32b is further provided at a portion adjacent to the blocking plate 33 of the flame surface 32, in which the mixed gas is not ejected from the mixing chamber 31 so that no flame is formed. It is.

The flame position control unit 32b closes a part of the flame surface 32 to further increase the ejection speed of the mixed gas ejected through the flame surface 32, and thus is stable to flame stability even at high load operation of the engine. Since the flame is formed at a position farther away from the blocking plate 33 and the heat transfer member 37, the flame heat can be more effectively transmitted to the secondary vaporizer 20 by maximizing the contact between the heat transfer member 37 and the flame.

Referring to FIG. 4B, the mixed gas injection nozzle 22 penetrates into the mixing chamber 31, and a flame induction space 32c is provided between the outer surface of the injection nozzle 22 and the flame surface 32, so that the flame Flame is formed on the entire surface 32 so that the entire surface of the heat transfer member 37 may be in contact with the flame.

Referring to FIG. 4C, the portion adjacent to the blocking plate 33 of the flame surface 32 having the flame induction space 32c is closed so that the mixed gas is not ejected from the mixing chamber 31 so that no flame is formed. Phosphorus flame position adjusting section 32b is provided. In addition, a flame guide space 32c is provided between the outer surface of the injection nozzle 22 and the flame surface 32.

The flame space 34 is a space in which a flame is formed by igniting the mixed gas ejected through the flame surface 32, as shown in FIG.

The igniter 35 is a member for igniting a secondary mixed gas ejected from the flame surface 32 by a high voltage spark or the like.

Flame detector 36 is a sensor for detecting the presence of flame in the flame space (34).

The heat transfer member 37 has the same central axis as the central axis of the flame surface 32, one end is provided to surround the flame space 34 at a position spaced apart from the flame surface 32, the other end is a secondary vaporizer ( 20 is a member for transferring heat of the flame formed in the flame space 34 in contact with the secondary vaporizer 20.

The heat transfer member 37 may be separated from one end thereof in contact with one side of the secondary vaporizer 20, or may be provided integrally with the secondary vaporizer 20.

5 is a view showing another embodiment of the heat transfer member 34.

Referring to FIG. 5, the heat transfer member 37 may be in surface contact with the entire outer circumferential surface of the secondary vaporizer 20 or may be in surface contact with the outer circumferential surface of the secondary vaporizer 20 and the outer circumferential surface of the body 11 at the same time. It further includes.

The heat transferred by the heat transfer member 37 is used as a heat source for secondary vaporizing the primary mixed gas introduced into the secondary vaporization chamber 21 from the outlet 11b of the body 10 and at the same time the primary vaporizer ( It is also transmitted to the body 11 of 10) can be used as a heat source for continuously evaporating fuel in the form of droplets of a fine size formed inside the body 11 without supply of external energy such as an electric heater.

In addition, as shown in FIG. 5, the heat transfer area increasing means 37b such as fins protruding therein is provided on the inner wall surfaces of the secondary vaporization chamber 21 and the body 11 to efficiently transfer heat. It is preferable in terms of.

As shown in FIG. 1, the heat insulating material 37c surrounds the heat transfer member 37, the mixed gas injection nozzle 22, and a part of the body 11 to prevent loss of heat transferred from the heat transfer member 37. It is a member.

The injector 38 has the same central axis as the central axis of the flame surface 32 and is provided at a position spaced apart from the heat transfer member 37 by a predetermined distance, so that the flame is discharged in the flame space 34 to an external air flow such as an engine exhaust gas. It stabilizes from and prevents heat from radiating from the heat transfer member 37 to the external exhaust gas stream. The base 38 may be made of a porous medium such as a perforated plate.

In FIG. 1, reference numeral 39 denotes a support on which the base 38 is installed.

Referring to the operation of the combustor 30 according to the above configuration, the secondary mixed gas discharged from the mixed gas jet nozzle 22 flows into the mixing chamber 31 and cannot go straight due to the blocking plate 33 and the mixing chamber. After final mixing in (31), it is ejected to the flame space (34) through the flame surface (32).

When the mixed gas ejected through the flame surface 32 is ignited by the igniter 35, a flame is formed in the flame space 34, and when the flame is detected by the operation of the flame detector 36, the igniter 35 is operated. This stops and maintains a stable flame.

The flame is mixed with the exhaust gas emitted from the engine of the vehicle having a specific flame width and flame length beyond the blocking plate blade 33b, and at this time, the flame space 34 from the engine exhaust gas by the flame gun 38. The flames in are protected.

Referring to the operation according to an embodiment of the burner for regenerating the diesel engine particulate filter according to the above configuration with reference to Figure 1, the air preheated by the primary air preheating means (14b) is the primary air inlet pipe (14a) When the primary air injection unit 14 is introduced through the preheated air, the preheated air is injected into the body 11 at a high pressure and high speed through the nozzle 12 at high speed.

At this time, the inside of the body 11 is a pressure state lower than the pressure of the outside of the body 11 by Bernoulli's principle, thereby the outside air is sucked into the body 11 from the air inlet (11a).

At this time, when the fuel preheated by the fuel preheating means 13a is supplied into the body 11 through the fuel supply pipe 13, the liquid fuel is also sucked to the nozzle 12 side, and the sucked fuel is nozzle 12 Collided with high-speed air flowing through) and atomized into droplets of fine size due to difference in momentum between air and fuel, and atomized fuel is vaporized by its preheated air or its own heat of preheated fuel. The fully vaporized fuel and the unvaporized residual liquid fuel in the droplet state and the external air sucked from the air inlet 11a are mixed with each other and flow into the secondary vaporizer 20 through the outlet 11b in a primary mixed gas state. do.

The primary mixed gas introduced into the secondary vaporization chamber 21 of the secondary vaporizer 20 is completely vaporized by the transfer of flame heat through the heat transfer member 37, and the flow rate is controlled by the air flow control means 23a. And mixed with the secondary air supplied through the secondary air inlet pipe 23 and introduced into the mixing chamber 31 of the combustor 30 through the mixed gas injection nozzle 22 in a secondary mixed gas state. .

The secondary mixed gas introduced into the mixing chamber 31 of the combustor 30 does not go straight due to the blocking plate 33 but is finally mixed in the mixing chamber and then ejected to the flame surface 32.

When the mixed gas ejected through the flame surface 32 is ignited by the operation of the igniter 35 to form a flame in the flame space 34 and then the flame is detected by the operation of the flame detector 36, the operation of the igniter 35 is performed. Is stopped, and a stable flame state having a specific flame width and flame length is maintained and mixed with the exhaust gas of the engine to raise the temperature of the exhaust gas, where the flame in the flame space is exhausted by the flame gun 38. It is protected from gas intrusion and can maintain a stable flame state.

At this time, the flame heat formed in the flame space 34 is transferred to the secondary vaporization chamber 21 through the heat transfer member 37 and the remaining droplet state included in the primary mixed gas introduced into the secondary vaporization chamber 21. It is used as the energy to completely vaporize the fuel, resulting in a continuous stable vaporization and combustion process under normal operating conditions.

On the other hand, as shown in Figure 6, the DPF regeneration burner is the exhaust gas inlet passage 40, which is a passage through which the exhaust gas flows from the engine and the exhaust gas discharged from the exhaust gas inlet passage 40 It is preferable to further include a swirler 50 for converting the swing flow and a temperature rise chamber 60 which is a space where the exhaust gas and the flame heat passing through the swirler 50 are mixed with each other.

7 shows embodiments of the exhaust gas inflow passage 40.

Referring to FIGS. 7A and 7B, the exhaust gas inflow passage 40 includes an outer cylinder 41 and at least one exhaust gas inflow pipe 43.

The outer cylinder 41 is disposed to have the same central axis as the central axis of the flame surface 32, and is open at one end portion 42 and a closed other end portion 41c opened by a double tube consisting of an inner tube 41a and an outer tube 41b. ), The inner tube (41a) is coupled to the prosthesis (38).

One end of the at least one exhaust gas inlet pipe 43 communicates with the exhaust gas flow path of the engine, and the other end communicates with the internal space of the outer cylinder 41. Such exhaust gas inlet pipe 43 is preferably provided in a tangential direction to the outer pipe (41b) of the outer cylinder (41).

As shown in FIG. 7C, when the exhaust gas introduced through the exhaust gas inlet pipe 43 is discharged to the open end 42 of the outer cylinder 41, the uniformity of the flow velocity distribution is maintained. In order to achieve this, a flow rate homogenizer 46 such as a perforated plate may be further provided in front of the open end 42 of the outer cylinder 41.

In Fig. 7, reference numerals 44 and 45 denote outer cylinder fixing flanges and flange holes, respectively.

As shown in FIG. 6, the swirler 50 has the same central axis as the central axis of the flame surface 32 and is disposed between the open end 42 of the outer cylinder 41 and the temperature increase chamber 60. It is provided, and the exhaust gas discharged through the open end 42 of the outer cylinder 41 is a member for flowing into the temperature rise chamber 60 in a swirl flow state that rotates about the central axis of the combustor (30).

8A-8C show embodiments of swirler 50.

Referring to FIG. 8A, the swinger 50 includes a plate-shaped support plate 51, at least one gas passage hole 52, and at least one wing 53 and a support plate 51 for fixing the outer plate 55. ) And an internal fixing stand 56.

At least one gas passage hole 52 partially passes through the front and rear surfaces of the support plate 51 to allow the exhaust gas to pass therethrough.

At least one wing 53 is coupled to the support plate 51 and formed at an angle with the front or rear surface of the support plate 51 so that the exhaust gas passes through the gas passage hole 52. Generates a swirl flow about the central axis.

The number and arrangement of the gas passage holes 52 and the blades 53 formed in the support plate 51 shown in FIG. 8A of the present specification are only one embodiment.

In addition, as shown in Figure 8b, there is no support plate 51 and the gas between the plurality of wings (53 ') and the wings (53') fixed to the outer fixing ring 55 'and the inner fixing ring 56'. It can be changed and implemented according to the embodiment, such as the structure that passes through, and all means for the purpose of converting the exhaust gas flow to the linearization flow state may be said to be a turning machine of the same purpose.

In the above, the flame stabilization of the DPF regeneration burner is greatly affected by the flow rate and pressure of the exhaust gas flowing from the engine, and the size of the swing strength of the swirl flow formed when the exhaust gas passes through the swirler 50. Accordingly, the width and length of the flame formed in the flame space 34 are greatly affected.

Therefore, in order to maintain a constant flame width and flame length formed in the flame space 34 during the operation of the DPF regeneration burner regardless of the operating conditions of the engine, the optimum swivel strength of each exhaust gas flow rate is varied for various exhaust gas flow rates. Need to maintain

That is, when the angle between the blade 53 and the support plate 51 of the swinger 50 is fixed, the swinging strength of the exhaust gas passing through the swinger 50 varies depending on the flow rate of the exhaust gas flowing therein.

In other words, in order to maintain the swing flow intensity of the exhaust gas by the swirler 50 in an optimal state irrespective of the operating conditions of the engine, the blades 53 and the blades 53 may be used according to the flow rate of the exhaust gas flowing into the swirler 50. When the angle between the support plates 51 is variable, the turning strength of the exhaust gas can be maintained at an optimum state regardless of the operating state of the engine.

Referring to the drawings, as shown in FIG. 8C, when the flow rate of the exhaust gas is small, the angle between the support plate 51 and the blade 53 is decreased (φ ₁ ) to increase the turning strength, and conversely, When the flow rate of the exhaust gas increases, the rotational strength can be kept constant according to the flow rate of the exhaust gas by increasing the angle between the support plate 51 and the blade 53 (φ ₂ ) to decrease the turning strength.

Referring again to FIGS. 8A and 8B, in order to maintain the optimum swing flow intensity of the exhaust gas irrespective of the operating conditions of the engine, the swing strength adjusting means 54 capable of arbitrarily adjusting the angle of the blade 53 is provided. It may be provided.

Swivel strength adjusting means 54, as well as non-powered turning strength adjusting means (54, 54 ') such as a spring, a hinge that causes displacement by the amount of momentum caused by the flow rate of the incoming exhaust gas, wing 53 and the support plate ( 51) Even if different methods, such as a turning strength adjusting device (not shown) using a power such as a motor to adjust the angle between the same, both in the concept of the turning strength adjusting means 54 may be the same purpose and method.

In the burner for regenerating the DPF, the temperature increase chamber 60 is in communication with the swirler 50 at one end thereof and opened at the other end thereof, and is a space including a combustor 30 inside the exhaust chamber. The gas is introduced and mixed with the hot combustion gas generated in the flame space 34 of the combustor 30 to increase the temperature of the exhaust gas.

Hereinafter, a first embodiment of the diesel engine soot filtration apparatus including the burner for regenerating the DPF described above will be described.

Referring to FIG. 9A, a diesel engine particulate filter (DPF system) including a DPF regeneration burner according to the first embodiment includes a primary vaporizer 10, a secondary vaporizer 20, a combustor 30, DPF regeneration burner and adapter 80 and the exhaust filter 70 is provided with an exhaust gas inlet passage 40, a swirler 50, a temperature rise chamber 60.

In the above description, since the burner for reproducing the DPF has been described above in detail, a detailed description thereof will be omitted.

The soot collector 70 is composed of a casing 71, a soot filtration material 72, a filler 73, and a fluid homogenization means 74.

The casing 71 has one end in communication with one end of the adapter 80, the other end in communication with the outside, and the inside of the exhaust filter using a porous medium such as ceramics, metal fibers, etc. 72 is provided, and a filler 73 is provided between the inner wall of the casing 71 and the outer wall of the soot filter material 72 to prevent physical damage to the soot filter material 71 from vibration or the like.

In the soot collector 70, the front end of the soot filter 72 is preferably provided with a flow homogenizing means 74 to ensure uniformity of the exhaust gas flow flowing into the soot filter 72.

In addition, it is also preferred that an oxidation catalyst 75 is further provided between the soot filter material 71 and the fluid homogenizing means 74.

Further, it is preferable that various types of adapters 80 are provided between the soot filtration unit 70 and the temperature increase room 50.

An integrated adapter 80 ', which is one embodiment of the adapter, is shown in Figure 10A.

Referring to FIG. 10A, the integrated adapter 80 ′ according to an embodiment may include a gas mixing unit 81 and a connection pipe 82.

The gas mixing means 81 has a truncated cone or a truncated pyramid shape, the top surface 81a is closed, the bottom surface is open, and the side surface 81b is formed of a perforated plate.

One end of the connection pipe 82 communicates with the open end of the temperature rise chamber 60, and the other end communicates with the casing 71 of the soot filtration unit 70 and the open bottom of the gas mixing means 81. It is combined with the edge.

Another embodiment of an adapter is shown in FIG. 10B, which is a scaled-down adapter 80 ″.

Referring to FIG. 10B, one end of the reduced enlarged adapter 80 ″ communicates with the temperature increase room 60, the other end communicates with the casing 71 of the soot filter 70, and the reduced tube 83. And an enlarged tube 84 and a constant section tube 85.

Referring to FIG. 9 again, the operation of the diesel engine particulate filter including the DPF regeneration burner having the configuration as described above, the exhaust gas discharged from the diesel engine through the exhaust gas inlet pipe (41) 40, the swirler 50 and the temperature rise chamber 60 pass through the soot collector 70.

At this time, the soot contained in the exhaust gas is collected by the soot filter material 71, and the collection amount increases as the collection time increases, and when the collection amount reaches a certain level, it is not expressed but the operation of the burner for regenerating the DPF by electronic signals This begins and a flame is formed in the flame space 34.

The combustion gas of the high temperature due to the flame generated in the flame space 34 is mixed with the exhaust gas introduced into the temperature rise chamber 50 so that the temperature of the exhaust gas rises above the oxidation temperature of the soot, and the exhaust gas mixing means 55 ) And the temperature distribution and flow velocity distribution of the mixed gas at the inlet of the soot collector 70 passing through the fluid homogenization means 56 are introduced into the soot filter 71 in a very uniform state and collected in the soot filter 71. Is oxidized.

Meanwhile, FIG. 11 shows a second embodiment of a diesel engine particulate filter including a burner for regenerating DPF.

Referring to FIG. 11, the diesel engine soot filtration apparatus including the burner for regenerating the DPF according to the second embodiment includes a primary vaporizer 10, a secondary vaporizer 20, a combustor 30, and an exhaust gas inflow passage. 40, a swirler 50, a burner for regenerating a DPF composed of a temperature increase chamber 60, a soot filtration unit 70, a branched connection pipe 80c, and an exhaust gas flow path 90.

In the second embodiment, the burner for regenerating the DPF and the soot filtration unit 70 are sufficiently described in the first embodiment. Therefore, the differences from the first embodiment will be described here.

The exhaust gas flow path 90 of the diesel engine particulate filter according to the second embodiment is composed of a fuel flow path 91, a branch pipe 92, and an exhaust gas flow rate adjusting means 93.

The branch pipe 92 branches from the oil passage 91 and communicates with the branch connection pipe 80c.

The branch pipe 92 is preferably provided with exhaust gas flow rate adjusting means 93 such as a valve for adjusting the flow rate of the exhaust gas flowing into the DPF regeneration burner through the oil passage 91.

Looking at the operation of the diesel engine soot filtration device including a regeneration burner having the configuration as described above, the exhaust gas discharged from the diesel engine is separated into the gas passage (91) and branch pipe (92) to the gas passage (91) The exhaust gas is introduced into the exhaust gas inflow passage 50 of the DPF regeneration burner, and the exhaust gas flowing into the branch pipe 92 flows into the branch connection pipe 80c.

 At this time, the amount of exhaust gas flowing into the main oil passage 91 by the exhaust gas flow rate adjusting means 93 is adjusted to flow into the temperature increase chamber 60 through the exhaust gas inflow passage 50 of the DPF regeneration burner.

The exhaust gas introduced into the DPF regeneration burner through the gas passage 91 is discharged to the branch connection pipe 80c after the temperature is elevated, and the heated exhaust gas is introduced through the branch pipe 150. The total exhaust gas discharged from the engine mixed with the gas is heated to flow into the soot filtration unit 70.

In the case of the diesel engine soot filtration device according to the second embodiment, when the diesel engine having a large displacement is operated with a very high load in an RPM, the exhaust gas is discharged because of high flow rate and high pressure. When all the exhaust gas flows into the exhaust gas inflow passage 40, the flame generated in the flame space 34 of the combustor 30 may be extinguished, and thus may have a great influence on the state of the flame.

As such, when the operating condition of the diesel engine is under high load, a part of the diesel engine flows directly into the connecting pipe 80c provided at the front end of the soot filtration unit 70 through the branch pipe 92 branched from the gas passage 91. The flow rate of the combustor 30 is not extinguished because the flow rate of the diesel engine is lower than that of the diesel engine and flows into the DPF regeneration burner through the gas passage 91 to operate the burner at a much lower load than the engine operating conditions. Operation in a stable flame state is possible.

On the other hand, a third embodiment of a diesel engine soot filtration apparatus including a burner for DPF regeneration is shown in FIG.

Referring to FIG. 12, the diesel engine soot filtration apparatus including the burner for regenerating the DPF according to the third embodiment includes a primary vaporizer 10, a secondary vaporizer 20, and a burner 30. It includes a burner, a connecting pipe (80d), a curved pipe part 100 and a soot filtration part (70).

Since the burner for reproducing the DPF in the third embodiment has been sufficiently described in the first embodiment, the following description will focus on differences from the first embodiment.

The connection pipe 80d is located in front of the combustor 30, and the combustion gas of flame generated from the combustor 30 flows in.

One side of the curved pipe section 100 having a curved cross section is in communication with the connection pipe 80d, and the exhaust gas discharged from the diesel engine is introduced to mix with the combustion gas.

The gas mixing means 101 may be provided in the curved pipe part 100.

The soot filtration unit 70 is provided at one side of the curved tube part 100, a mixed gas discharged from the curved tube part 100 is introduced therein, and a soot filter material 71 is provided therein.

The soot filtration unit 70 is preferably disposed at the position of the DPF regeneration burner and a straight line.

Looking at the operation of the diesel engine particulate filter including a DPF regeneration burner having the configuration as described above, the exhaust gas discharged from the diesel engine is passed through the curved pipe 100 to increase the flow straightness.

The burner is operated as the DPF regeneration burner without the inflow of exhaust gas, and the exhaust gas flowing through the curved pipe part 100 flow path does not penetrate into the connection pipe 80d flow path by maintaining the straightness, so that the flame stabilization of the burner may be achieved.

As described above, although described with reference to a preferred embodiment of the present invention, those skilled in the art various modifications of the present invention without departing from the spirit and scope of the invention described in the claims below. Or it may be modified.

1 is a side cross-sectional view showing a burner for regenerating a diesel engine particulate filter according to an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view of a portion of FIG. 1; FIG.

3 is a sectional view showing another embodiment of the blocking plate.

4A-4C are cross-sectional views showing another embodiment of the flame surface.

5 is a sectional view showing another embodiment of a heat transfer member.

6 is a cross-sectional view showing an embodiment in which the exhaust gas inflow passage, the swirler, and the temperature increase chamber are further included in the burner for reproducing the DPF of FIG. 1.

7 illustrates embodiments of the exhaust gas inflow passage.

8a-8c show embodiments of a swirler;

Figure 9 is a side cross-sectional view showing a first embodiment of a diesel engine particulate filter including a burner for DPF regeneration.

10A and 10B illustrate embodiments of an adapter.

11 is a side cross-sectional view showing a second embodiment of a diesel engine particulate filter including a burner for regenerating DPF.

12 is a side sectional view showing a third embodiment of a diesel engine particulate filter including a burner for regenerating a DPF;

13 is a view showing an example of a conventional diesel engine particulate filter.

<Explanation of symbols for the main parts of the drawings>

10: primary carburetor 11: body

11a: air inlet 11b: outlet

11c: suction air volume control means 12: nozzle

13 fuel supply pipe 13a fuel preheating means

13b: fuel amount adjusting means 14: primary air injection unit

14a: primary air inlet pipe 14b: primary air preheating means

14c: primary air volume control means 20: secondary vaporizer

21: secondary vaporization chamber 21a: secondary vaporization chamber heating means

22: mixed gas spray nozzle 22a: tube

22b: Thurs 22c: Enlargement Tube

23: secondary air inlet pipe 23a: secondary air volume control means

30: combustor 31: mixing chamber

32: flame surface 32a: porous medium

32b: flame position control unit 32c: flame induction space

33: blocking plate 33a, 33a ': arc-shaped plate

33b, 33b ': Closure blade wing 33c: arc part

34: flame space 35: igniter

36: flame detector 37: heat transfer member

37a: heat transfer area increase means 37b: insulation

38: flameproof 39: fixed bracket

40: exhaust gas inlet passage 41: outer cylinder

41a: outer cylinder inner tube 41b: outer cylinder outer tube

41c: External cylinder closed surface 42: External cylinder open surface

43: exhaust gas inlet pipe 44: flange for fixing the outer cylinder

45: flange hole for fixing the outer cylinder 46: uniformity of the flow rate distribution

50: turning machine 51: support plate

52: gas passage hole 53,53 ': guide surface

54,54 ': Turning strength adjusting means 55,55': External fixation

56,56 ': Internal fixing 60: Temperature rise room

70: soot filter 71: casing

72: soot filter material 73: filling material

74 flow homogenization means 75 oxidation catalyst

80: connection adapter 80a: integrated adapter

80b: Zoom-out Adapter 80c: Branch Adapter

81 gas mixing means 81a impingement plate

81b: side 82: connector

83: reduction tube 84: expansion tube

85: constant cross section 86: mixing means

90: exhaust gas passage 91: gas passage

92: branch pipe 93: exhaust gas flow rate adjusting means

100: curved portion 101: gas mixing means

Claims (52)

A vaporizer for injecting a liquid fuel and vaporizing the injected fuel in a mixed gas state; A combustor provided on one side of the vaporizer and configured to ignite after finally remixing the mixed gas discharged from the vaporizer; And And a heat transfer member having one end in contact with the carburetor and the other end being exposed to the flame of the combustor to transfer heat of the flame generated from the combustor to the carburetor. The method of claim 1, A temperature increase room located in front of the combustor and configured to increase a temperature of exhaust gas discharged from the diesel engine by flame heat generated from the combustor; And an exhaust gas inlet passage communicating with the temperature increase room and connected to the exhaust gas passage of the diesel engine to introduce the exhaust gas. The method of claim 2, And a swirler installed between the discharge end of the exhaust gas inlet passage and the temperature increase chamber to introduce the exhaust gas introduced through the exhaust gas inlet passage into the temperature increase chamber in a swirling flow state. Burner for regeneration of diesel engine particulate filter. The method of claim 3, wherein The carburetor, A primary vaporizer which injects a liquid fuel and vaporizes the injected fuel into a primary mixed gas with air; It is connected to the discharge side of the primary vaporizer, the primary mixed gas discharged from the primary vaporizer is introduced, the residual liquid state fuel in the primary mixed gas secondary vaporization and discharged to the secondary mixed gas state Burner for regeneration of the diesel engine particulate filter, characterized in that consisting of a secondary vaporizer. The method of claim 4, wherein The primary vaporizer is a burner for regenerating the diesel engine particulate filter, characterized in that the inlet of the liquid fuel is formed at one end, the outlet for discharging the fuel in the form of atomized droplets is formed at the other end. The method of claim 5, A burner for regenerating a diesel engine particulate filter, characterized in that a high pressure air inlet is further provided at one end of the primary carburetor, and an outlet for discharging the fuel in the form of atomized droplets is discharged at the other end. The method according to claim 5 or 6, Burner for regeneration of the diesel engine particulate filter, characterized in that the outlet of the primary vaporizer is further provided with a heating means for heating the outlet. The method of claim 4, wherein The primary vaporizer, An air inlet is formed at one end, a discharge port at which the primary mixed gas is discharged is formed at the other end, and an outer body having at least one nozzle communicating with the inside; A fuel supply pipe having one end provided at an outer side of the body and the other end disposed inside the body to supply fuel to the inside of the body; It is coupled to the outer surface of the body and in communication with the nozzle, the primary air inlet space for supplying high-pressure, high-speed external air to the front of the fuel supply pipe through the nozzle, one end of the primary air inlet space A burner for regenerating a diesel engine particulate filter, characterized in that it communicates with the inside, and the other end includes at least one primary air inlet configured to form a primary air inlet pipe through which external air is introduced. The method of claim 8, The heat transfer member extends from one end of the burner for regenerating the diesel engine particulate filter, characterized in that it further comprises an extension in contact with the secondary vaporizer and the body. The method of claim 8, And a fuel preheating means for preheating the fuel supplied to the fuel supply pipe. The method of claim 8, The fuel supply pipe burner for regenerating the diesel engine particulate filter, characterized in that the fuel amount adjusting means for controlling the flow rate of the supplied fuel. The method of claim 8, The primary air inlet pipe is provided with a primary air preheating means for preheating the air blown into the body through the nozzle burner for regenerating diesel engine smoke filter. The method of claim 8, Burner for regenerating diesel engine particulate filter, characterized in that the outer body is provided with a body heating means for improving the initial vaporization performance of the fuel. The method of claim 4, wherein The secondary vaporizer, One side is in communication with the outlet of the primary vaporizer, the secondary vaporization chamber into which the primary mixed gas flows; Secondary vaporization chamber heating means for initially heating the secondary vaporization chamber is provided on the outer circumferential surface or wall of the secondary vaporization chamber, A mixed gas spray nozzle for discharging the mixed gas introduced into the secondary vaporization chamber in a secondary mixed gas state; Burner for regenerating the diesel engine particulate filter, characterized in that the one end is in communication with the interior of the secondary vaporization chamber, the other end is in communication with the outside, the secondary air inlet pipe to which external air flows. The method of claim 14, The mixed gas injection nozzle is a burner for regenerating a diesel engine particulate filter, characterized in that the Venturi (Ventury) shape. The method of claim 14, Burner for regeneration of the diesel engine particulate filter, characterized in that the secondary vaporization chamber heating means is provided on the outer circumferential surface or wall of the secondary vaporization chamber. The method of claim 14, Burner for regenerating the diesel engine soot filter device is provided in the secondary vaporization chamber and the inner wall surface of the body is provided with a heat transfer area increasing means protruding therein for efficient heat transfer. The method of claim 14, The secondary air inlet pipe is a burner for regenerating the diesel engine particulate filter, characterized in that the air amount adjusting means for controlling the flow rate of the external air introduced. The method of claim 14, The secondary air inlet pipe is a burner for regenerating the diesel engine particulate filter, characterized in that the air preheating means for preheating the incoming air is further provided. The method of claim 14, The combustor, A mixing chamber in final communication with the secondary mixed gas discharged from the mixed gas spray nozzle in communication with the mixed gas spray nozzle; A flame surface made of a porous medium provided at the boundary of the mixing chamber and having at least one or more different porosities; A flame space in which a flame is formed along a circumference of the flame surface; And a igniter for igniting the mixed gas discharged into the flame space through the flame surface. The method of claim 20, The porous medium is a burner for regenerating a diesel engine particulate filter, characterized in that any one selected from perforated plate, metal mesh, metal mat, ceramic, heat-resistant fiber. The method of claim 20, The combustor, And a blocking plate which closes one end of the mixing chamber and prevents a straight line of the secondary mixed gas injected from the mixed gas spray nozzle. The method of claim 22, The blocking plate, And a burner for regenerating the diesel engine particulate filter, which is in contact with the mixing chamber and includes at least one arc-shaped plate having an arcuate cross section. The method of claim 22, Burner for regenerating diesel engine particulate filter, characterized in that it further comprises a blocking plate wings extending along the circumference of the blocking plate in contact with the flame space. The method of claim 22, And a flame position adjusting unit for closing the secondary mixing gas so as to prevent passage of the secondary mixed gas in a portion adjacent to the blocking plate of the flame surface. The method of claim 20, Burner for regenerating the diesel engine soot filter device further comprising a flame induction space between the flame surface and the outer peripheral surface of the mixed gas injection nozzle to generate a flame in the entire flame space. The method of claim 20, The combustor, Burner for regeneration of the diesel engine smoke filter device further comprises a flame detector for detecting the presence of flame in the flame space. The method of claim 20, One side of the heat transfer member is spaced apart from the flame surface is provided to wrap the circumference of the flame surface, the other side is coupled to the secondary vaporization chamber and the flame heat in the flame space is characterized in that to transmit to the secondary vaporization chamber Burner for regeneration of diesel engine particulate filter. The method of claim 20, The combustor, The burner for regenerating the diesel engine particulate filter, characterized in that it is spaced apart from the heat transfer member to surround the heat transfer member, and further comprising a flame stabilizer to stabilize the flame in the flame space from the exhaust gas of the diesel engine. The method of claim 29, The combustor, The burner for regenerating the diesel engine soot filtration device, provided between the heat transfer member and the flame retarder, further comprises an insulation for preventing heat loss of the heat transfer member. The method of claim 20, The exhaust gas inlet passage has the same central axis as the central axis of the flame surface, one end is open, the exhaust gas is introduced, the other end is in communication with the temperature rise room burner for regenerating diesel engine particulate filter. The method of claim 20, The exhaust gas inflow passage, It has the same central axis as the central axis of the flame surface, one end is open and the other end is a closed double tube structure, the inner tube is the outer tube coupled to the prosthesis, A burner for regenerating the diesel engine particulate filter, characterized in that the one end is in communication with the exhaust gas flow passage, the other end is in communication with the inner space of the outer cylinder and the exhaust gas inlet pipe into which the exhaust gas of the diesel engine is introduced. The method of claim 32, Burner for regenerating diesel engine particulate filter, characterized in that the exhaust gas inlet pipe is tangentially connected to the appearance of the outer cylinder to communicate with the inner space of the outer cylinder. The method of claim 32, The exhaust gas inlet pipe is connected to the closed end of the outer cylinder is in communication with the inner space of the outer cylinder diesel exhaust smoke filter regeneration burner, characterized in that. The method of claim 20, The turner, A plate-shaped support plate having the same central axis as the central axis of the flame surface, At least one gas passage hole through which the exhaust gas passes through the front and rear surfaces of the support plate partially; At least one wing coupled to the support plate and acting as a guide surface for generating pivotal flow with respect to the central axis of the flame surface when the exhaust gas passes through the gas through hole at an angle with one end surface of the support plate; Burner for regenerating diesel engine particulate filter comprising a. The method of claim 35, wherein Burner for regenerating the diesel engine smoke filter device characterized in that it further comprises a swing strength adjusting means for arbitrarily adjusting the angle of the blade in the non-powered state according to the flow rate of the exhaust gas flowing into the swirler. The method of claim 35, wherein Burner for regenerating diesel engine soot filtration device further comprises a swing strength adjusting means for arbitrarily adjusting the angle of the blade by using power in accordance with the flow rate of the exhaust gas flowing into the swirler. The method of claim 20, The turner, A ring-shaped inner holder having the same central axis as the central axis of the flame surface; A ring-shaped outer holder disposed at an outer side of the inner holder at intervals from the inner holder; One or more guide surfaces disposed between the inner holder and the outer holder, one end and the other of which are hinged to the inner holder and the outer holder, respectively, for generating swinging flow as the exhaust gas of the engine passes through; ; And Burner for regenerating the diesel engine particulate filter comprising a; turning angle adjusting means for adjusting the angle between the guide surface and the flow direction of the exhaust gas. The method of claim 38, The turning angle adjusting means is a burner for regenerating the diesel engine soot filtration device, characterized in that the angle adjustment of the guide surface is made non-powered in accordance with the change of the momentum due to the change in the flow rate of the exhaust gas. The method of claim 38, The turning angle adjusting means is a burner for regenerating the diesel engine particulate filter, characterized in that the angle adjustment of the guide surface is made by using a power corresponding to the change in the flow rate of the exhaust gas. The method of claim 35 or 38, The temperature increase room is the exhaust gas flows in, the burner for regenerating the diesel engine particulate filter, characterized in that the combustor is disposed therein. The method of claim 35 or 38, Burner for regenerating the diesel engine particulate filter, characterized in that the temperature rise chamber is one end is in communication with the discharge end of the swirler, the combustor is disposed therein. The method of claim 35 or 38, At the other end of the temperature increase room, Burner for regenerating diesel engine particulate filter, characterized in that the gas mixing means further comprises a porous medium. The method of claim 43, The gas mixing means has a hollow truncated cone or a truncated pyramid shape, the side is perforated, the bottom is open and connected to the discharge end of the temperature rise room, the top is closed and disposed inside the temperature rise room A burner for regenerating a diesel engine particulate filter. A vaporizer for injecting a liquid fuel and vaporizing the injected fuel in a mixed gas state; A combustor provided at one side of the vaporizer and ignited after final mixing of the mixed gas discharged from the vaporizer; A heat transfer member whose one end is in contact with the vaporizer and the other end is exposed to the flame of the combustor and transfers heat of flame generated in the combustor to the vaporizer; A temperature increase room located in front of the combustor and configured to increase a temperature of exhaust gas discharged from the diesel engine by flame heat generated from the combustor; An exhaust gas inlet passage communicating with the temperature increase room and connected to the exhaust gas passage of the diesel engine to introduce the exhaust gas; And A diesel engine soot filtration using a burner for regenerating the diesel engine soot filtration device, including; Device. The method of claim 45, A diesel engine particulate filter using a burner for regenerating a diesel engine particulate filter, characterized in that an oxidation catalyst is provided in front of the particulate filter. The method of claim 45, A diesel engine particulate filter using a burner for regenerating a diesel engine particulate filter, wherein an adapter having a diameter smaller than that of the temperature increasing chamber and the particulate filter is provided between the temperature increasing chamber and the particulate filter. The method of claim 47, A diesel engine particulate filter using a burner for regenerating a diesel engine particulate filter, wherein a flow homogenizing means made of a porous medium is provided between the adapter and the particulate filter. The method of claim 48, The hole of the flow homogenizing means is a diesel engine smoke filter using a diesel engine smoke filter regeneration burner, characterized in that the size is formed to increase toward the outside. The method of claim 45, The exhaust gas flow path, A main oil passage for allowing a portion of the exhaust gas discharged from the diesel engine to flow into the exhaust gas inflow passage; A diesel engine particulate filter using a burner for regenerating a diesel engine particulate filter, characterized in that it comprises a branch pipe for branching from the oil passage to allow the remaining exhaust gas to flow into the particulate filter. 51. The method of claim 50, The branch pipe is provided with an exhaust gas flow rate adjusting means for regulating the flow rate of the exhaust gas flowing through the oil supply passage, the diesel engine smoke filter device using a diesel engine smoke filter device regeneration burner. A vaporizer for injecting a liquid fuel and vaporizing the injected fuel in a mixed gas state; A combustor provided at one side of the vaporizer and ignited after final mixing of the mixed gas discharged from the vaporizer; A heat transfer member whose one end is in contact with the vaporizer and the other end is exposed to the flame of the combustor and transfers heat of flame generated in the combustor to the vaporizer; A connection pipe which is located in front of the combustor and into which combustion gas of flame generated from the combustor flows; One side is in communication with the connecting pipe, the exhaust gas discharged from the diesel engine is introduced is mixed with the combustion gas, the curved pipe section of the cross section; And A diesel engine particulate filter using a burner for regenerating a diesel engine particulate filter comprising a; and a particulate filter communicating with the discharge end of the curved pipe portion, the casing having an inner space, and a particulate filter provided in the casing.

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