JP6809795B2 - Combustion device - Google Patents

Description

The present invention relates to a combustion apparatus including an inner cylinder forming a combustion space, an outer cylinder covering the inner cylinder, and a burner for supplying fuel into the combustion space. Further, the present invention relates to a combustion device provided with a cylinder forming a combustion space and a burner for supplying fuel into the combustion space.

As one type of combustion device, for example, there is a "waste incineration device" disclosed in Patent Document 1 below. In this device, the outer cylinder is arranged around the inner cylinder forming the inside (combustion space) of the incinerator, and the inside of the inner cylinder is covered with a refractory material. As a result, the inner cylinder made of steel plate or the like is protected from the high temperature environment in the furnace of about 1000 ° C. The refractory material is, for example, a refractory concrete called castable, which is a mixture of an aggregate having excellent fire resistance and alumina cement. In addition to incinerators, there are many combustion devices that use refractory materials for the lining inside the furnace.

Japanese Unexamined Patent Publication No. 2001-74221 JP-A-2015-158263 Japanese Unexamined Patent Publication No. 2012-82804 Japanese Unexamined Patent Publication No. 2004-257325

By the way, as shown in FIGS. 1 and 2 of Patent Document 1, the refractory material may be provided thickly inside the inner cylinder because it is necessary to block high temperature to protect the inner cylinder from heat. There are many. Such a thick refractory material causes an increase in the weight of the combustion device. In particular, a marine combustion device used for a ship, such as the incinerator of Patent Document 1, is preferably lightweight, and the weight of the combustion device may be a problem depending on the ship on which the combustion device is mounted.

In addition to such incinerators, marine combustion devices include, for example, gas treatment devices that process boil-off gas. The boil-off gas is a gas generated by vaporization of liquefied natural gas in an LNG storage tank, and is hereinafter referred to as "BOG". For example, in Patent Document 2, of the BOG generated in the cargo tank of a liquefied gas carrier, the surplus that cannot be treated as fuel is liquefied again and collected in the cargo tank, or incinerated by a gas combustion device or the like. There is a statement that it needs to be treated (Patent Document 2; paragraph 0002), and in the latter case a gas treatment device is used.

Further, as disclosed in Patent Document 3, in a ship using a diesel engine as a propulsion engine, it is necessary to reduce NOx emissions, so that exhaust gas is released into the atmosphere after passing through a denitration device. In some cases, when the exhaust gas temperature is 300 ° C. or lower, the exhaust gas is heated to a temperature at which the denitration catalyst is sufficiently activated and then passed through the denitration device (Patent Document 3; paragraphs 0004 to 0007). The exhaust gas heating device used for heating such exhaust gas is also a kind of marine combustion device.

In addition, in order to purify NOx by the denitration device, the exhaust gas reducing agent is hydrolyzed in the exhaust gas path by spraying the exhaust gas reducing agent (urea water) in the piping path on the upstream side of the denitration catalyst. Ammonia is produced and NOx is purified by the denitration catalyst. However, as disclosed in Patent Document 4, when the exhaust gas temperature is low, the generation of ammonia by the hydrolysis of the exhaust gas reducing agent may not proceed sufficiently, and as a countermeasure, the exhaust gas reducing agent is prepared in advance. Is known as a method of heating and supplying the reducing agent gas into the exhaust gas (Patent Document 3; paragraphs 0002 to 0008). In a ship using a diesel engine as a propulsion engine, urea water is injected into a high temperature gas (combustion gas) and hydrolyzed to generate a reducing agent gas (ammonia), and the high temperature gas containing this reducing agent gas is used as a diesel engine. There is a method of supplying it into the exhaust gas from. A combustion gas supply device that supplies high-temperature gas (combustion gas) in such a system is also a type of marine combustion device.

In this way, there are various types of marine combustion equipment such as incinerators, gas treatment equipment, exhaust gas heating equipment, and combustion gas supply equipment (high temperature gas generator), but in each case the equipment weight is light. It is desirable to have. The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a combustion device capable of reducing the weight of the device.

To achieve the above object, a combustion apparatus according to claim 1 of the appended claims, the inner cylinder forming a combustion space in the inner portion, between the one end side of the peripheral wall and the inner cylinder of said inner tube An outer cylinder that covers the inner cylinder by forming a space through which air sent from the outside can flow, and the outer cylinder that can supply fuel into the combustion space through the burner through hole on one end side. A combustion device including a burner attached to the above, and the upstream side and the downstream side of the pipe are the same in the middle of the pipe without changing the arrangement of the pipe with respect to the existing pipe through which the exhaust gas of the external engine flows. The exhaust gas discharged from the upstream side flows into the downstream side through the combustion space and communicates with the other end side of the inner cylinder from the center of the cylinder shaft of the inner cylinder. The technical feature is that it is heated in the space.
Further, the combustion apparatus according to claim 2 of the claims includes, in the combustion apparatus according to claim 1, a space around the burner that supplies air for combustion around the burner. On one end side of the inner cylinder, the air flowing through the space portion can be injected into the combustion space separately from the burner peripheral space portion as air for cooling the inner peripheral surface along the inner peripheral surface of the inner cylinder. and technical features in that the air injection hole or an air jet nozzle, such is al provided.

Further, the combustion apparatus according to claim 3 of the claims is the combustion apparatus according to claim 1 or 2 , in the case where the upstream side and the downstream side of the pipe are arranged linearly. The inner cylinder is arranged so that the cylinder shaft is oriented in an orthogonal direction or a substantially orthogonal direction of the pipe, and the exhaust gas discharged from the upstream side can flow through the combustion space to the downstream side. The technical feature is that the inlet and outlet are formed in the air.

Further, the combustion apparatus according to claim 4 of the claims is the combustion apparatus according to claim 1 or 2 , wherein the upstream side and the downstream side of the pipe are arranged orthogonally. The inner cylinder is arranged in a direction in which the cylinder shaft is arranged coaxially or substantially coaxially with either the upstream side or the downstream side of the pipe, and is orthogonal or substantially orthogonal to the other of the upstream side or the downstream side of the pipe. The exhaust gas discharged from the upstream side penetrates the combustion space while being arranged or in a direction in which the tubular shaft is orthogonal to or substantially orthogonal to both the upstream side and the downstream side of the pipe. The technical feature is that the inflow port and the outflow port are formed so as to be able to flow into the downstream side.

Further, the combustion device according to claim 5 of the scope of the patent claim is sent from an external engine to one end side of the inner cylinder in the combustion device according to any one of claims 1 to 4. An exhaust gas injection hole or an exhaust gas injection nozzle capable of injecting exhaust gas having a temperature lower than the temperature in the combustion space during combustion into the combustion space along the inner peripheral surface of the inner cylinder. Being Bei Ete exhaust gas ejection portion having a technical feature of.

The combustion apparatus according to claim 6 of the appended claims, the cylindrical body forming the combustion space in the inner portion, the fuel into the combustion space through said one end of the burner through hole can be supplied A combustion device including a burner attached to one end side of the pipe, and the upstream side of the pipe in the middle of the pipe without changing the arrangement of the pipe with respect to the existing pipe through which the exhaust gas of the external engine flows. And the downstream side communicates with each other in the other end side of the cylinder from the center of the cylinder shaft of the cylinder, and the exhaust gas discharged from the upstream side flows into the downstream side via the combustion space. The technical feature is that the combustion space is heated in the combustion space.
Further, the combustion device according to claim 7 of the scope of the patent claim includes the burner peripheral space portion for supplying combustion air around the burner in the combustion device according to claim 6, and the cylinder. On one end side of the body, air sent from the outside can be injected into the combustion space separately from the burner peripheral space as air for cooling the inner peripheral surface along the inner peripheral surface of the cylinder. and technical features in that the injection holes or air jet nozzles are al provided.

Further, the combustion apparatus according to claim 8 of the claims is the combustion apparatus according to claim 6 or 7 , in the case where the upstream side and the downstream side of the pipe are arranged linearly. The cylinder is arranged so that the cylinder axis is directed in the direction orthogonal to or substantially orthogonal to the pipe, and the exhaust gas discharged from the upstream side can flow through the combustion space to the downstream side. The technical feature is that the inlet and outlet are formed.

Further, the combustion apparatus according to claim 9 of the claims is the combustion apparatus according to claim 6 or 7 , in the case where the upstream side and the downstream side of the pipe are arranged orthogonally. The tubular body is arranged so that the tubular shaft is coaxially or substantially coaxially arranged on either the upstream side or the downstream side of the pipe, and is orthogonal or substantially orthogonal to the other on the upstream side or the downstream side of the pipe. The exhaust gas discharged from the upstream side penetrates the combustion space while being arranged or in a direction in which the tubular shaft is orthogonal to or substantially orthogonal to both the upstream side and the downstream side of the pipe. The technical feature is that the inflow port and the outflow port are formed so as to be able to flow into the downstream side.

Further, the combustion apparatus according to claim 10 of the scope of the patent claim is the combustion apparatus according to any one of claims 6 to 9, and the combustion apparatus is sent from an external engine to one end side of the cylinder. It has an exhaust gas injection hole or an exhaust gas injection nozzle capable of injecting exhaust gas having a temperature lower than the temperature in the combustion space during combustion into the combustion space along the inner peripheral surface of the cylinder. Being Bei Ete exhaust gas ejection section and technical features of.

In the inventions of claims 1 to 10 , the inner cylinder of the combustion device is connected in the middle of the pipe without changing the arrangement of the pipe with respect to the existing pipe through which the exhaust gas flows. Therefore, it is easy to apply to existing equipment, and it is easy to correspond to the so-called retrofit, in which the old model is modified and changed to the new model that can be used after that.

In the invention of claim 2, a space around the burner for supplying combustion air is provided around the burner. Then, on one end side of the inner cylinder, air flowing through the space portion can be injected into the combustion space separately from the burner surrounding space portion as air for cooling the inner peripheral surface along the inner peripheral surface of the inner cylinder. An injection hole or an air injection nozzle is provided. As a result, the air injected from the air injection hole or the air injection nozzle becomes an air flow along the inner peripheral surface of the inner cylinder and flows in the combustion space. Therefore, the inner peripheral surface of the inner cylinder is caused by this air flow. Further cooled. Therefore, the temperature of the inner cylinder in the combustion space can be further lowered as compared with the case where such an air injection hole or an air injection nozzle is not provided. Therefore, when the refractory material is provided on the inner peripheral surface of the inner cylinder, the thickness thereof can be further reduced, so that the weight of the combustion device can be further reduced.
In the invention of claim 3 , when the upstream side and the downstream side of the existing pipe are arranged linearly, the exhaust gas flowing in from the inflow port is mixed with the combustion gas generated in the combustion space during burner combustion. Since the exhaust gas is discharged to the outlet at the shortest distance, the exhaust gas sent from the external engine can pass through the combustion space with less resistance. In addition, since a space through which air sent from the outside can flow is formed between the inner cylinder and the outer cylinder and the inner cylinder is air-cooled, in the process of mixing the exhaust gas and the combustion gas, For example, even if temperature unevenness occurs in the combustion space where a high temperature portion or a low temperature portion occurs, it is not necessary to provide a fireproof material for covering the high temperature portion. Therefore, the weight of the device can be reduced from the viewpoint that a refractory material for measures against temperature unevenness in such a mixing process is not required.

In the invention of claim 4 , when the upstream side and the downstream side of the existing pipe are arranged orthogonally, the inner cylinder has a cylinder shaft coaxial with or substantially coaxial with either the upstream side or the downstream side of the pipe. It is arranged and is arranged in a direction orthogonal to or substantially orthogonal to the other of the upstream side or the downstream side of the pipe. Alternatively, the inner cylinder is arranged in a direction in which the cylinder shaft is orthogonal to or substantially orthogonal to both the upstream side and the downstream side of the pipe. As a result, the exhaust gas flowing in from the inflow port is mixed with the combustion gas generated in the combustion space during burner combustion and flows out to the outflow port in the shortest distance, so that the exhaust gas sent from the external engine has a small resistance. It becomes possible to pass through the combustion space. In addition, since a space through which air sent from the outside can flow is formed between the inner cylinder and the outer cylinder and the inner cylinder is air-cooled, in the process of mixing the exhaust gas and the combustion gas, For example, even if temperature unevenness occurs in the combustion space where a high temperature portion or a low temperature portion occurs, it is not necessary to provide a fireproof material for covering the high temperature portion. Therefore, the weight of the device can be reduced from the viewpoint that a refractory material for measures against temperature unevenness in such a mixing process is not required.

In the invention of claim 5, the exhaust gas injected from the exhaust gas injection hole or the exhaust gas injection nozzle becomes an exhaust gas flow along the inner peripheral surface of the inner cylinder and flows in the combustion space, so that the inner peripheral surface of the inner cylinder Is further cooled by this exhaust gas flow. Therefore, the temperature of the inner cylinder in the combustion space can be further lowered as compared with the case where such an exhaust gas injection portion is not provided. Therefore, when the refractory material is provided on the inner peripheral surface of the inner cylinder, the thickness thereof can be further reduced or the refractory material can be abolished, so that the weight of the combustion device can be further reduced. be able to.

In the invention of claim 7, a burner peripheral space portion for supplying combustion air is provided around the burner. Then, on one end side of the cylinder, air sent from the outside can be injected into the combustion space separately from the burner surrounding space as air for cooling the inner peripheral surface along the inner peripheral surface of the cylinder. An injection hole or an air injection nozzle is provided. As a result, the air injected from the air injection hole or the air injection nozzle becomes an air flow along the inner peripheral surface of the cylinder and flows in the combustion space, so that the inner peripheral surface of the cylinder is caused by this air flow. Further cooled. Therefore, it is possible to lower the temperature of the cylinder in the combustion space as compared with the case where such an air injection hole or an air injection nozzle is not provided. Therefore, when the refractory material is provided on the inner peripheral surface of the cylinder, the thickness thereof can be further reduced, so that the weight of the combustion device can be reduced.

In the invention of claim 10, the exhaust gas injected from the exhaust gas injection hole or the exhaust gas injection nozzle becomes an exhaust gas flow along the inner peripheral surface of the cylinder and flows in the combustion space, so that the inner peripheral surface of the cylinder is formed. Is further cooled by this exhaust gas flow. Therefore, the temperature of the cylinder in the combustion space can be further lowered as compared with the case where such an exhaust gas injection portion is not provided. Therefore, when a refractory material is provided on the inner peripheral surface of the cylinder, the thickness thereof can be further reduced or the refractory material can be abolished, so that the weight of the combustion device can be further reduced. be able to.

It is a front view which shows an example of the whole structure of the gas processing apparatus which concerns on the reference embodiment which concerns on this invention. It is a top view which shows an example of the whole structure of the gas processing apparatus of this reference embodiment . It is a schematic cross-sectional view of the cross section of line III-III shown in FIG. 2 seen from the direction of the arrow. It is a schematic cross-sectional view of the IV-IV line cross section shown in FIG. 3 seen from the same arrow viewing direction. It is a schematic enlarged cross-sectional view in the alternate long and short dash line V shown in FIG. It is a schematic cross-sectional view seen from the direction of the arrow VI shown in FIG. It is explanatory drawing which shows the other use example of the gas processing apparatus of this reference embodiment . It is a front view which shows an example of the whole structure of the exhaust gas heating apparatus which concerns on 1st Embodiment of this invention. It is a top view which shows an example of the whole structure of the exhaust gas heating apparatus of this 1st Embodiment. 9 is a schematic cross-sectional view of the X-ray cross section shown in FIG. 9 as viewed from the direction of the arrow. FIG. 5 is a schematic cross-sectional view of the XI-XI line cross section shown in FIG. 10 as viewed from the same arrow direction. It is an enlarged cross-sectional view corresponding to the inside of the alternate long and short dash line XII shown in FIG. 11, and is a schematic enlarged cross-sectional view of the XII-XII line cross section shown in FIG. It is a schematic cross-sectional view seen from the direction of arrow XIII shown in FIG. FIG. 12 is a cross-sectional view corresponding to FIG. 12 showing another configuration example of the exhaust gas heating device of the first embodiment, and is a schematic enlarged cross-sectional view of the XIV-XIV line cross section shown in FIG. 15 as viewed from the same arrow direction. It is a schematic cross-sectional view seen from the direction of the arrow XV shown in FIG. It is explanatory drawing which shows the modification 1 of the exhaust gas heating apparatus of this 1st Embodiment. It is explanatory drawing which shows the modification 2 of the exhaust gas heating apparatus of this 1st Embodiment. It is sectional drawing which shows the structural example of the furnace body of the exhaust gas heating apparatus which concerns on 2nd Embodiment of this invention. 6 is a schematic cross-sectional view of the XIX-XIX line cross section shown in FIG. 18 as viewed from the direction of the arrow. 9 is a schematic cross-sectional view of the XX-XX line cross section shown in FIG. 19 as viewed from the same arrow direction. It is a front view which shows an example of the whole structure of the exhaust gas heating apparatus which concerns on 3rd Embodiment of this invention. It is a top view which shows an example of the whole structure of the exhaust gas heating apparatus of this 3rd Embodiment. FIG. 6 is a schematic cross-sectional view of the XXIII-XXIII line cross section shown in FIG. 22 as viewed from the direction of the arrow. FIG. 3 is a schematic cross-sectional view of the XXIV-XXIV line cross section shown in FIG. 23 as viewed from the direction of the arrow. FIG. 5 is a schematic cross-sectional view of the XXV-XXV line cross section shown in FIG. 24 as viewed from the direction of the arrow. It is a front view which shows an example of the whole structure of the exhaust gas heating apparatus which concerns on 4th Embodiment of this invention. It is a top view which shows an example of the whole structure of the exhaust gas heating apparatus of this 4th Embodiment. FIG. 6 is a schematic cross-sectional view of the XXVIII-XXVIII line cross section shown in FIG. 27 as viewed from the direction of the arrow. 9 is a schematic cross-sectional view of the XXIX-XXIX line cross section shown in FIG. 28 as viewed from the direction of the arrow. It is a schematic cross-sectional view which looked at the cross section of the line XXX-XXX shown in FIG. 29 from the direction of the arrow.

Hereinafter, embodiments of the combustion device of the present invention will be described with reference to the drawings. First, before the description of each embodiment , a reference embodiment in which the technique related to the present invention is applied to the gas treatment apparatus will be described with reference to FIGS. 1 to 7.

[ Reference form ]
The gas processing device 10 of the reference form is, for example, an incineration device that burns and processes BOG (boil-off gas) or the like, and is a marine combustion device mounted on a ship. As shown in FIGS. 1 to 4, the gas treatment device 10 is mainly composed of an outer cylinder 11, an inner cylinder 12, a burner unit 13, a burner holder 17, an exhaust pipe 19, a first fan 2, a second fan 3, and the like. Has been done.

The outer cylinder 11 is, for example, a cylinder having a bottomed cylindrical shape and is made of a steel plate. That is, one end side of the outer cylinder 11 is opened so as to be surrounded by the annular base end portion 11b having an inwardly bent flange shape with respect to the peripheral wall portion 11a formed in a cylindrical shape, and the outer cylinder 11 is also opened. The other end side is closed by a circular flat plate-shaped tip portion 11c. A connecting portion 11d extending cylindrically in the radial direction of the outer cylinder 11 is formed on the peripheral wall portion 11a, and the exhaust cylinder 19 can be connected via a flange portion 11e provided at the tip thereof. In addition, intake ports 11f and 11g are also opened in the peripheral wall portion 11a, and the first intake duct 6 and the second intake duct 7 described later are connected to these. The opening of the base end portion 11b is covered and closed by the circular flat plate-shaped outer cylinder base end plate 15, as will be described later.

The inner cylinder 12 is a cylinder that is housed inside the outer cylinder 11 and forms a combustion space inside, and is formed in a bottomed cylindrical shape like the outer cylinder 11. In the inner cylinder 12, one end side of the cylindrical peripheral wall portion 12a is closed by the inner cylinder base end plate 16 as the base end portion 12b, and the other end side is also closed by the circular flat plate-shaped tip portion 12c. An exhaust portion 12d that emits smoke or the like to the outside is formed near the other end side of the peripheral wall portion 12a. That is, the peripheral wall portion 12a is formed with an exhaust portion 12d extending in a cylindrical shape toward the inside of the connecting portion 11d of the outer cylinder 11, so that the combustion space of the inner cylinder 12 and the inner space of the exhaust cylinder 19 can communicate with each other. I have to. The other end side of the inner cylinder 12 may be configured to be openable without being blocked by the tip portion 12c or the like.

A refractory material 14 is provided on the inner peripheral surface of such an inner cylinder 12. As will be described later, the inner cylinder 12 is provided with a burner unit 13 at the base end portion 12b (inner cylinder base end plate 16) on one end side, and a flame is formed in the inner cylinder 12 from the burner portion 13a, that is, in the combustion space. Will be done. Therefore, the refractory material 14 is arranged on the inner peripheral surface of the inner cylinder 12 to protect the peripheral wall portion 12a, the base end portion 12b, and the tip portion 12c from the radiant heat of the flame. The refractory material 14 is, for example, a mixture of refractory concrete called castable and refractory aggregate. In this reference embodiment , for example, V-shaped hooks (or anchors) are attached to a plurality of locations on the inner peripheral surface of the inner cylinder 12, and alumina cement or the like is applied to a thick wall using these hooks as aggregates. The refractory material 14 is formed. In each of the embodiments described below including this reference embodiment , the cross-sectional portion of the refractory material 14 is hatched in a shaded manner for convenience in drawing representation, and the surface portion of the refractory material 14 is provided. Please note that the is painted in light ink.

The main body of the exhaust stack 19 is formed in a cylindrical shape like the outer cylinder 11. The base end side of the exhaust stack 19 is provided with a flange portion 19a that is open and outwardly bent so as to be connectable to the connection portion 11d of the outer cylinder 11, and can be connected to the flange portion 11e of the connection portion 11d of the outer cylinder 11. It is configured. These connections are performed, for example, by screwing nuts to a plurality of bolts penetrating the flange portions 11e and 19a. On the other hand, the tip end side of the exhaust stack 19 is closed in a circular flat plate shape, and a connecting portion 19b extending in the radial direction of the main body is formed. This connecting portion 19b is connected to an exhaust duct or the like in the ship.

The burner unit 13 is provided so as to penetrate the base end portion 12b of the inner cylinder 12, that is, the center of the inner cylinder base end plate 16. That is, the inner cylinder base end plate 16 is formed in a thick disk shape coated with the refractory material 14, and the burner unit 13 penetrates the central portion thereof and a plurality of penetrations so as to surround the center portion thereof. The hole 14a is formed. The burner unit 13 is attached to an outer cylinder base end plate 15 that closes one end side of the outer cylinder 11. In this reference embodiment , the burner unit 13 is fixed to the outer cylinder base end plate 15 via the burner holder 17. A fuel pipe 90 to which fuel such as BOG is supplied is connected to the burner unit 13. The configuration of the burner unit 13, the inner cylinder base end plate 16 and the burner holder 17 will be described in detail later with reference to FIGS. 5 and 6.

In the furnace body configured in this way, a gap is formed between the outer cylinder 11 and the inner cylinder 12. That is, air flow passages Ra and Rb are formed between the outer surface of the inner cylinder 12 (peripheral wall portion 12a, base end portion 12b and tip portion 12c) and the inner surface of the outer cylinder 11 including the outer cylinder base end plate 15. Has been done. The air flow passage Ra communicates with the intake port 11f formed in the peripheral wall portion 11a of the outer cylinder 11, and the air flow passage Rb communicates with the intake port 11g formed in the peripheral wall portion 11a. .. In this reference embodiment , a dividing plate 18 is provided that connects the peripheral wall portion 11a of the outer cylinder 11 and the peripheral wall portion 12a of the inner cylinder 12 to partition these air flow passages Ra and Rb. Further, a first intake duct 6 connected to the air outlet of the first fan 2 via a flange portion 6a is connected to the air intake port 11f, and the air intake port 11g is connected to the air outlet of the second fan 3. A second intake duct 7 connected via a flange portion 7a is connected.

Both the first fan 2 and the second fan 3 are blower fans in which the impeller rotates by using an electric motor as a drive source. The first fan 2 is connected to the first intake port 4, and the second fan 3 is connected to the second intake port 5, and the air sucked from the respective intake ports 4a and 5a is discharged from the air outlet (pressure feeding). ). In this reference embodiment , the air pumped from the first fan 2 is sent to the intake port 11f of the outer cylinder 11 via the first intake duct 6. Further, the air pumped from the second fan 3 is sent to the intake port 11g of the outer cylinder 11 via the second intake duct 7. As a result, the air that has flowed into the air flow passages Ra and Rb from the intake ports 11f and 11g, respectively, flows in the direction of the dotted arrow shown in FIGS. 3 and 4, for example. Therefore, when the air sent from the outside comes into contact with the outer surface of the inner cylinder 12, the inner cylinder 12 can be air-cooled.

The air flow passage Ra and the air flow passage Rb are separated by a dividing plate 18. In this reference embodiment , the first blower fan 2 mainly sends air for cooling the middle portion and the tip portion of the furnace body away from the burner unit 13, and the second blower fan 3 is a furnace body close to the burner unit 13. It sends the air to be injected into the base end of the fire and the combustion space. That is, as will be described later, the air flowing through the air flow passage Rb also flows into the combustion space of the inner cylinder 12 via the through hole 14a of the base end portion 12b (inner cylinder base end plate 16) of the inner cylinder 12. .. By dividing the blower fan that sends air into the furnace body into the first blower fan 2 and the second blower fan 3, it is possible to individually control the blower amount (air pressure feed amount) as needed. Therefore, for example, the amount of air blown through the air flow passage Rb can be controlled based on the temperature data of the inner cylinder 12.

The gas treatment device 10 configured in this way is provided on the base frame 1. In the present reference embodiment , for example, the furnace body composed of the outer cylinder 11 and the inner cylinder 12 has legs 8a erected at a plurality of locations in the longitudinal direction of the base frame 1 and these along the longitudinal direction of the base frame 1. It is supported on the base frame 1 by a leg frame 8 composed of two side members 8b fixed to the leg 8a. Further, the two blower fans 2 and 3 and the intake ports 4 and 5 are fixed to the base frame 1 by fixing metal fittings, stays and the like.

Next, the configurations of the burner unit 13, the inner cylinder base end plate 16, the burner holder 17, and the like will be described with reference to FIGS. 5 and 6. A circular flat plate-shaped outer cylinder base end plate 15 having a circular burner attachment port 15a opening at the center thereof is fixed to the base end portion 11b of the outer cylinder 11 by bolts and nuts. The burner mounting port 15a is a circular hole that can be fixed to the outer cylinder base end plate 15 in a state where the burner holder 17 holding the burner unit 13 is inserted. In this reference embodiment , the mechanical strength of the burner mounting port 15a is increased. Therefore, the flange portion of the inward bending is formed in an annular shape along the inner circumference thereof.

The burner unit 13 is mainly composed of a burner portion 13a and a skirt portion 13b. The burner portion 13a is provided with, for example, a truncated cone-shaped nozzle portion at the tip, and a fuel pipe 90 for supplying fuel is connected to the burner portion 13a. The radial circumference of the burner portion 13a is covered with a tubular skirt portion 13b. The skirt portion 13b has an enlarged diameter on the front end side of the burner portion 13a facing the nozzle portion, whereas the rear end side has a cylindrical shape having the same diameter. When the burner unit 13 is held by the burner holder 17 and fixed to the outer cylinder base end plate 15, the burner portion 13a is exposed in the inner space of the inner cylinder 12, that is, in the combustion space, and is supplied from the fuel pipe 90. Fuel is injected from the nozzle section. A space portion ( space portion around the burner) is formed in the burner holder 17 around the rear end side of the skirt portion 13b, and a part of the air flow flowing through the air flow passage Rb passes through this space portion in FIG. It flows into the skirt portion 13b by the path of the solid line arrow shown in. This air contributes to the combustion of the fuel injected from the nozzle portion of the burner portion 13a.

The burner holder 17 is composed of a cylindrical portion 17a, a holding body 17b, an outer plate 17c, and the like. The cylindrical portion 17a has flange portions for outer bending formed at both ends, and the tip portion is set to an outer diameter dimension slightly smaller than the inner diameter of the burner mounting port 15a of the outer cylinder base end plate 15. With this tip inserted into the burner mounting port 15a, the flange portion (one of the flange portions at both ends) provided on the rear end side of the tip portion by the height of the annular flange portion of the burner mounting port 15a is bolted. The burner holder 17 is attached to the outer cylinder base end plate 15 by being fixed to the outer cylinder base end plate 15 by the nut and the nut. The holding body 17b housed in the cylindrical portion 17a is a structure that holds the burner unit 13 at the axial center of the cylindrical portion 17a by a fixed structure (not shown). The outer plate 17c is a circular flat plate that closes the rear end side opening of the cylindrical portion 17a, and is fixed to the other flange portion of the cylindrical portion 17a with bolts and nuts.

The inner cylinder base end plate 16 is a disk-shaped member corresponding to the base end portion 12b of the inner cylinder 12, and forms a combustion space together with the peripheral wall portion 12a and the tip portion 12c of the inner cylinder 12. In this reference embodiment , the outer diameter of the inner cylinder base end plate 16 is set so that the diameter of the refractory material 14 applied to the inner peripheral surface of the peripheral wall portion 12a is smaller than the inner diameter of the peripheral wall portion 12a. There is. A burner through port 16a set to an inner diameter slightly larger than the outer diameter of the rear end side same diameter portion of the skirt portion 13b of the burner unit 13 is formed in the central portion of the inner cylinder base end plate 16. Further, on the outer peripheral edge of the inner cylinder base end plate 16, a flange portion 16c that rises toward the combustion space side in a state of being assembled to the peripheral wall portion 12a is formed in an annular shape. Further, between the burner through port 16a and the flange portion 16c, a plurality of air injection nozzles 16b protruding toward the combustion space side are formed on the circumference concentric with the inner cylinder base end plate 16.

That is, as shown in FIG. 6, the plurality of air injection nozzles 16b are arranged in the vicinity of the flange portion 16c so as to surround the periphery of the burner unit 13 arranged at the center of the inner cylinder base end plate 16. In this reference embodiment , for example, 16 air injection nozzles 16b are provided at intervals of 22.5 degrees at a central angle of the inner cylinder base end plate 16. This quantity is an example, and is appropriately set within a range in which the effect of the air flow described later can be exhibited. Further, the air injection nozzles 16b do not need to be provided at equal intervals. In a state where the inner cylinder base end plate 16 is assembled to the peripheral wall portion 12a, the inner space of such an air injection nozzle 16b communicates with the air flow passage Rb. Therefore, the air that has been pressure-fed from the second blower fan 3 and has flowed into the air flow passage Rb from the intake port 11g passes through the air injection nozzle 16b and enters the peripheral wall portion 12a, for example, as shown by the broken line arrow in FIG. It is injected into the space, that is, the combustion space. In the figure, for convenience of drawing representation, a state in which air is injected from a specific air injection nozzle 16b is shown, but air is injected from all the air injection nozzles 16b.

Similar to the inner cylinder 12, for example, a V-shaped hook (or anchor) is attached to the inner side surface of the inner cylinder base end plate 16 which faces the combustion space side when assembled to the peripheral wall portion 12a. Further, a refractory material 14 obtained by applying alumina cement or the like to a thick wall using these hooks as an aggregate is formed on such an inner surface surface. In the reference embodiment , the refractory material 14 is formed so that the thickness of the refractory material 14 exceeds the axial length of the air injection nozzle 16b because it is necessary to protect the air injection nozzle 16b from the radiant heat of the flame. Therefore, a through hole 14a communicating with the injection hole of the air injection nozzle 16b is formed in the refractory material 14.

As described above, the gas processing apparatus 10 of the present reference embodiment adopts a configuration in which a plurality of air injection nozzles 16b are provided in an annular shape in the vicinity of the flange portion 16c in the inner cylinder base end plate 16. Therefore, in a state where the inner cylinder base end plate 16 is assembled to the peripheral wall portion 12a, a plurality of air jets are injected near the surface of the refractory material 14 applied to the peripheral wall portion 12a and over substantially the entire inner circumference of the refractory material 14. The nozzle 16b is arranged. As a result, when the air in the air flow passage Rb pumped from the second blower fan 3 is injected into the combustion space from the air injection nozzle 16b, it flows along the surface of the fireproof material 14 forming the combustion space. ..

That is, the air injected from the air injection nozzle 16b becomes an air flow along the inner peripheral surface of the inner cylinder 12 (the surface of the refractory material 14) and flows in the combustion space, so that the inner peripheral surface of the inner cylinder 12 (The surface of the refractory material 14) is cooled by this air flow. Therefore, the thickness of the refractory material 14 can be reduced as compared with the case where the plurality of air injection nozzles 16b are not provided, so that the weight of the gas processing device 10 can be reduced. it can.

In particular, when the fuel supplied from the fuel pipe 90 is a gaseous fuel such as BOG, it is formed by the burner portion 13a because the carbon content is lower than that of petroleum-based fuels such as light oil, A heavy oil and waste oil. The amount of convection heat transfer is relatively larger than the amount of radiant heat transfer from the flame. Therefore, when the gas treatment device 10 incinerates unnecessary gas generated from a volatile liquid fuel such as BOG, the inner peripheral surface of the inner cylinder 12 has a convection heat transfer amount rather than the radiant heat amount due to the flame of the burner portion 13a. Is more susceptible. Therefore, by injecting an air flow from the air injection nozzle 16b along the inner peripheral surface (the surface of the refractory material 14) of the inner cylinder 12, the inner peripheral surface is covered with the air flow. As a result, in addition to the relatively small amount of radiant heat transfer, the amount of convection heat transfer that reaches the inner peripheral surface (the surface of the refractory material 14) of the inner cylinder 12 can also be reduced. The temperature of the inner peripheral surface of 12 can be lowered. Therefore, the thickness of the refractory material 14 can be reduced, and the weight of the gas treatment device 10 can be reduced. Further, by optimizing the air flow rate, it may be possible to eliminate the need for the refractory material 14, which in turn makes it possible to reduce the size.

Further, the temperature of the inner peripheral surface of the inner cylinder 12 can be further lowered by adopting a configuration in which the air blowing capacity of the second blowing fan 3 is increased to increase the flow rate of the air injected from the air injection nozzle 16b. Become. As a result, for example, the refractory material 14 itself can be abolished (so-called metal throat), so that the weight of the gas treatment device 10 can be further reduced. It should be noted that the blowing capacity of the second blowing fan 3 and the quantity, arrangement, and intervals of the air injection nozzles 16b can exhibit the above-mentioned effect of the air flow based on the results of experiments and computer simulations. It is set appropriately within the range.

In the above-mentioned reference embodiment , the case of BOG has been illustrated as an object to be incinerated by the gas treatment apparatus 10 (fuel supplied from the fuel pipe 90), but the object of the incineration treatment is, for example, waste oil. It may be a petroleum-based fuel such as. Further, the gas treatment device 10 is used as a waste incineration device for burning solid waste by providing the outer cylinder 11 and the inner cylinder 12 with a waste input port and a lid portion that covers the input port so as to be openable and closable. It is also possible. In this case, the fuel supplied from the fuel pipe 90 is assumed to be, for example, BOG, light oil, A heavy oil, or the like.

Further, the gas processing device 10 of this reference embodiment can function as a combustion gas supply device (high temperature gas generator). For example, in a ship using a diesel engine as a propulsion engine, urea water is injected into a high-temperature gas (combustion gas) supplied using this combustion gas supply device and hydrolyzed to generate a reducing agent gas (ammonia). By supplying the high temperature gas containing the reducing agent gas into the exhaust gas from the diesel engine, NOx can be purified by the denitration device. In this case, as shown in FIG. 7 (A), the urea water hydrolysis unit 104 is arranged at the outlet of the connection portion 11d or the exhaust pipe 19 of this reference embodiment , and the diesel engine (external engine) is located downstream thereof. The pipe 100 through which the exhaust gas of the above flows flows is connected. In this case, the fuel supplied from the fuel pipe 90 is assumed to be, for example, liquefied natural gas, light oil, heavy fuel oil A, or the like. It is also possible to integrate the urea water hydrolysis unit 104 and the combustion gas supply device into a urea water hydrolysis device.

Further, as shown in FIG. 7B, the connection portion 11d or the exhaust pipe 19 of the gas processing device 10 of the reference embodiment is used by being connected in the middle of the pipe 100 through which the exhaust gas of the diesel engine (external engine) flows. Is also good. In this case, a connection portion 101 is formed in the existing pipe 100, and the connection portion 11d or the exhaust pipe 19 of the gas treatment device 10 is connected to the connection portion 101, so that the inner space (exhaust gas flow passage) of the pipe 100 and the inner cylinder 12 are connected. It is configured so that it communicates with the inner space (combustion space) of. A refractory material 103 is arranged around the pipe 100 and the connection portion 101 to prevent the pipe 100 and the like in a high temperature state from being exposed to the outside.

As a result, the high-temperature exhaust discharged from the connection portion 11d or the exhaust stack 19 flows into the exhaust gas flow passage and mixes with the exhaust gas of the diesel engine (external engine). Therefore, it is possible to send the exhaust gas to the denitration device on the downstream side in a state where the exhaust gas temperature is raised to a temperature at which the denitration catalyst is sufficiently activated. That is, in the usage example shown in FIG. 7B, the gas treatment device 10 can function as an exhaust gas heating device. In FIG. 7B, the right side of the paper surface may be the upstream side (downstream side) of the pipe 100, or the left side of the paper surface may be the upstream side (downstream side) of the pipe 100.

The connection mode to the existing pipe 100 may be configured as shown in FIG. 7 (C), for example. That is, even in the gas treatment device 10A in which the connection portion 11d or the exhaust pipe 19 is connected to the tip portion 11c so as to project along the cylinder shaft J of the outer cylinder 11, the gas treatment device 10A is also connected to the connection portion 101 of the pipe 100. By connecting, the gas treatment device 10A can function as an exhaust gas heating device as in the case of FIG. 7B. In FIG. 7C, the upper side of the paper surface may be the upstream side (downstream side) of the pipe 100, or the lower side of the paper surface may be the upstream side (downstream side) of the pipe 100.

First Embodiment
Next, the first embodiment in which the combustion device of the present invention is applied to the exhaust gas heating device will be described with reference to FIGS. 8 to 17. The exhaust gas heating device 20 of the first embodiment is, for example, a heating device that raises the exhaust gas temperature to a temperature at which the denitration catalyst is sufficiently activated by connecting to the middle of a pipe 100 through which the exhaust gas of a diesel engine (external engine) flows. Yes, it is a marine combustion device mounted on a ship. The same components as those of the gas processing apparatus 10 of the reference embodiment are designated by the same reference numerals to simplify the description.

As shown in FIGS. 8 to 11, the exhaust gas heating device 20 is mainly composed of an outer cylinder 21, an inner cylinder 22, an exhaust gas injection unit 26, a burner unit 13, a burner holder 17, a first fan 2, a second fan 3, and the like. It is configured.

The outer cylinder 21 is, for example, a cylinder having a bottomed cylindrical shape and is made of a steel plate. That is, the peripheral wall portion 21a formed in a cylindrical shape is opened so that one end side thereof is surrounded by an annular base end portion 21b having an inwardly bent flange shape, and the other end side is a circular flat plate shape. It is blocked by the tip portion 21c. The peripheral wall portion 21a is formed with connecting portions 21d and 21g extending in a cylindrical shape in the radial direction of the outer cylinder 21, and flange portions 21h and 21e are provided at the tips thereof, respectively. That is, the connecting portions 21d and 21g are formed so as to extend in a direction orthogonal to the cylinder axis J of the outer cylinder 21 (or the inner cylinder 22) (a direction along the axis K) or a direction substantially orthogonal to the cylinder axis J (the direction along the axis K). The outer cylinder 21 or the inner cylinder 22 is arranged with the cylinder axis J facing in the direction orthogonal to or substantially orthogonal to the existing pipe 100).

The connecting portions 21d and 21g are arranged so that their respective cylinder shafts have the same shaft K, and the connecting portions 21d and 21g and the respective flange portions 21e and 21h are pipes 100 already provided in the ship. It is set to a shape specification that can be connected to. Thereby, for example, the connection portions 21d and 21g of the exhaust gas heating device 20 can be connected in the middle of the existing pipe 100 without changing the position of the existing pipe 100. In the first embodiment, of the pipe 100, the connecting portion 21d is connected to the upstream pipe 100a on the upstream side of the exhaust gas to which the diesel engine (external engine) is connected via the flange portion 21e, and the downstream side of the exhaust gas is also connected. A connecting portion 21g is connected to the downstream pipe 100b of the above via a flange portion 21h. An intake port 21f for taking in the exhaust gas is formed in the connection portion 21d on the upstream side of the exhaust gas.

The intake 21f is covered above it (in the direction of the arrow tip of the Z axis of the coordinate system shown in each figure) by a cover 27 that opens in the upstream pipe 100a direction and closes in the combustion space direction. As a result, the flow of the exhaust gas is controlled by the cover 27 so that a part of the exhaust gas flowing from the upstream pipe 100a easily flows into the intake port 21f. An exhaust gas duct 28 is connected to the intake 21f. The exhaust gas duct 28 is connected to an exhaust gas injection unit 26 described later. As a result, the exhaust gas flowing from the intake port 21f can be introduced into the exhaust gas injection unit 26. In addition, the intake ports 21i and 21j are also opened in the peripheral wall portion 21a, and the first intake duct 6 and the second intake duct 7 described later are connected to these. The opening of the base end portion 21b is covered and closed by the circular flat plate-shaped outer cylinder base end plate 23, as will be described later.

The inner cylinder 22 is a cylinder that is housed inside the outer cylinder 21 and forms a combustion space inside, and is formed in a bottomed cylindrical shape like the outer cylinder 21. In the inner cylinder 22, one end side of the cylindrical peripheral wall portion 22a is closed by the inner cylinder base end plate 24 as the base end portion 22b, and the other end side is also closed by the circular flat plate-shaped tip portion 22c. In the vicinity of the other end side of the peripheral wall portion 22a, an inflow portion 22d for inflowing the exhaust gas from the upstream pipe 100a into the inner cylinder 22, that is, the combustion space, and an inflow portion 22d for flowing the exhaust gas from the combustion space to the downstream pipe 100b. The outflow portion 22e and the outflow portion 22e are formed respectively. That is, the peripheral wall portion 22a is formed with an inflow portion 22d connected to the connecting portion 21d of the outer cylinder 21, so that the combustion space of the inner cylinder 22 and the inner space of the upstream pipe 100a can communicate with each other. Further, an outflow portion 22e extending in a cylindrical shape toward the inside of the connecting portion 21g is formed so that the combustion space of the inner cylinder 22 and the inner space of the downstream pipe 100b can communicate with each other. The other end side of the inner cylinder 22 may be configured to be openable without being blocked by the tip portion 22c or the like.

A refractory material 14 is provided on the inner peripheral surface of such an inner cylinder 22. That is, in the inner cylinder 22, a burner unit 13 is provided at the base end portion 22b (inner cylinder base end plate 24) on one end side, and a flame is formed from the burner portion 13a in the combustion space of the inner cylinder 22. In the first embodiment, petroleum-based fuel (for example, light oil, heavy fuel oil A, etc.) is supplied to the burner unit 13 from the fuel pipe 90. Therefore, the refractory material 14 is arranged on the inner peripheral surface of the inner cylinder 22 to protect the peripheral wall portion 22a, the base end portion 22b, and the tip portion 22c from the radiant heat of the flame. The refractory material 14 is, for example, castable, as in the case of the above-mentioned reference form . The refractory material 14, the burner unit 13, and the burner holder 17 are configured in the same manner as in the case of the above-mentioned reference form , and the contents described for each in the reference form can be substantially quoted. In this case, it should be noted that the description of the outer cylinder base end plate 15 in the reference form needs to be replaced with the outer cylinder base end plate 23. That is, the outer cylinder base end plate 15 needs to be replaced with the outer cylinder base end plate 23, and the burner mounting port 15a needs to be replaced with the burner mounting port 23a.

In the furnace body configured in this way, a gap is formed between the outer cylinder 21 and the inner cylinder 22. That is, air flow passages Ra and Rb are formed between the outer surface of the inner cylinder 22 (peripheral wall portion 22a, base end portion 22b and tip portion 22c) and the inner surface of the outer cylinder 21 including the outer cylinder base end plate 23. Has been done. The air flow passage Ra communicates with the intake port 21i formed in the peripheral wall portion 21a of the outer cylinder 21, and the air flow passage Rb communicates with the intake port 21j formed in the peripheral wall portion 21a. .. Also in the case of the first embodiment, the dividing plate 18 for partitioning the air flow passages Ra and Rb is provided.

In the first embodiment, the exhaust gas injection portion 26 is provided between the base end portion 22b of the inner cylinder 22 and the outer cylinder base end plate 23 of the outer cylinder 21. The exhaust gas injection unit 26 is connected to the exhaust gas duct 28, and makes it possible to inject the exhaust gas introduced from the exhaust gas duct 28 into the combustion space of the inner cylinder 22 via the exhaust gas gallery 26a and the exhaust gas injection nozzle 26d . .. The configuration of the exhaust gas injection unit 26 will be described in detail later with reference to FIGS. 12 and 13.

Further, the intake port 21i is connected to the first intake duct 6 connected to the air outlet of the first fan 2 via the flange portion 6a, and the intake port 21j is connected to the air outlet of the second fan 3. A second intake duct 7 connected via a flange portion 7a is connected. The first blower fan 2, the second blower fan 3, the first intake port 4, the second intake port 5, the first intake duct 6, and the second intake duct 7 are also configured as in the case of the above-described reference form. There is. Therefore, with respect to these configurations, the contents described for each can be almost quoted in the reference form .

The air pumped from the first fan 2 is sent to the intake port 21i of the outer cylinder 21 via the first intake duct 6, and the air pumped from the second fan 3 passes through the second intake duct 7. Is sent to the intake port 21j of the outer cylinder 21. As a result, the air flowing into the air flow passages Ra and Rb from the intake ports 21i and 21j, respectively, flows in the direction of the dotted arrow shown in FIGS. 10 and 11, and comes into contact with the outer surface of the inner cylinder 22. This makes it possible to cool the inner cylinder 22 with air.

The air flow passage Ra and the air flow passage Rb are separated by a dividing plate 18. Also in the first embodiment, the first blower fan 2 mainly sends air for cooling the middle portion and the tip portion of the furnace body away from the burner unit 13, and the second blower fan 3 sends the second blower fan 3 to the burner unit 13. It sends air to be injected into the base end of a nearby furnace body and the combustion space. That is, as will be described later, the air flowing through the air flow passage Rb also flows into the combustion space of the inner cylinder 22 via the through hole 14a of the base end portion 22b (inner cylinder base end plate 24) of the inner cylinder 22. .. By dividing the blower fan that sends air into the furnace body into the first blower fan 2 and the second blower fan 3, it is possible to individually control the blower amount (air pressure feed amount) as needed. Therefore, for example, the amount of air blown through the air flow passage Rb can be controlled based on the temperature data of the inner cylinder 22.

The exhaust gas heating device 20 configured in this way is also provided on the base frame 1 like the gas treatment device 10 of the reference form . The base frame 1 and the leg frame 8 is also configured similarly to the case of the reference embodiment, it is possible to substantially quote contents described for each at the reference embodiment.

Next, the configurations of the burner unit 13, the burner holder 17, the inner cylinder base end plate 24, the exhaust gas injection unit 26, and the like will be described with reference to FIGS. 12 and 13. A circular burner mounting port 23a opens in the center of the base end portion 21b of the outer cylinder 21, and is closer to the connection portion 21d side (toward the root direction of the arrow of the Y axis of the coordinate system shown in FIG. 12). ), The circular flat plate-shaped outer cylinder base end plate 23 through which the exhaust gas input pipe mounting port 23b opens is fixed by bolts and nuts. The burner mounting port 23a is a circular hole that can be fixed to the outer cylinder base end plate 23 with the burner holder 17 holding the burner unit 13 inserted, and is the burner mounting port 15a of the outer cylinder base end plate 15 of the reference form. It is configured in the same way. Further, the exhaust gas input pipe attachment port 23b is set to have an inner diameter slightly larger than the outer diameter of the exhaust gas input pipe 26c of the exhaust gas injection unit 26, and enables the exhaust gas input pipe 26c to penetrate.

The inner cylinder base end plate 24 is a disk-shaped member corresponding to the base end portion 22b of the inner cylinder 22, and forms a combustion space together with the peripheral wall portion 22a and the tip portion 22c of the inner cylinder 22. In the first embodiment, the outer diameter of the inner cylinder base end plate 24 is set so that the diameter is smaller than the inner diameter of the peripheral wall portion 22a by the wall thickness dimension of the refractory material 14 applied to the inner peripheral surface of the peripheral wall portion 22a. Has been done. A burner through port 24a set to an inner diameter slightly larger than the outer diameter of the rear end side same diameter portion of the skirt portion 13b of the burner unit 13 is formed in the central portion of the inner cylinder base end plate 24. Further, on the outer peripheral edge of the inner cylinder base end plate 24, a flange portion 24c that rises toward the combustion space side in a state of being assembled to the peripheral wall portion 22a is formed in an annular shape. Further, between the burner through port 24a and the flange portion 24c, a plurality of air injection nozzles 24b protruding toward the combustion space side are formed on the circumference concentric with the inner cylinder base end plate 24.

In the first embodiment, the inner cylinder base end plate 24 has a through hole 24d on the same circumference in addition to the air injection nozzle 24b formed on the circumference concentric with the inner cylinder base end plate 24. Is forming. For example, the air injection nozzles 24b and the through holes 24d are arranged so as to be alternately positioned at equal intervals on the same circumference. The exhaust gas injection nozzle 26d of the exhaust gas injection unit 26 is inserted through the through hole 24d.

The exhaust gas injection unit 26 is formed in a hollow disk shape set to have an outer diameter dimension substantially the same as the outer diameter of the inner cylinder 22, and has an annular exhaust gas gallery 26a inside. Further, the exhaust gas gallery 26a has a through hole 26b formed in the central portion through which the cylindrical portion 17a of the burner holder 17 can penetrate. The exhaust gas injection unit 26 is assembled to the burner holder 17 via, for example, a mounting structure (not shown). The exhaust gas injection portion 26 assembled to the burner holder 17 is arranged between the inner cylinder base end plate 24 and the outer cylinder base end plate 23 so as to surround the cylindrical portion 17a of the burner holder 17.

Further, the exhaust gas injection unit 26 includes an exhaust gas input pipe 26c protruding toward the outer cylinder base end plate 23 side, and a plurality of injection nozzles 26d protruding toward the inner cylinder base end plate 24 side. All of these communicate with the exhaust gas gallery 26a. The exhaust gas input pipe 26c is connected to the exhaust gas duct 28, and the exhaust gas introduced from the exhaust gas duct 28 flows into the exhaust gas gallery 26a via the exhaust gas input pipe 26c. Further, the exhaust gas that has flowed into the exhaust gas gallery 26a from the exhaust gas input pipe 26c is injected from the plurality of exhaust gas injection nozzles 26d. By inserting the exhaust gas injection nozzle 26d into the through hole 24d of the inner cylinder base end plate 24 described above, it becomes possible to inject the exhaust gas into the combustion space of the inner cylinder 22.

Since it is necessary to protect the air injection nozzle 24b and the exhaust gas injection nozzle 26d from the radiant heat of the flame, the thickness of the refractory material 14 should exceed the shaft length of the air injection nozzle 24b and the shaft length of the insertion portion of the exhaust gas injection nozzle 26d. A refractory material 14 is formed on the surface. Therefore, a through hole 14a communicating with the injection hole of the air injection nozzle 24b is formed in the refractory material 14. Further, a through hole 14b communicating with the injection hole of the exhaust gas injection nozzle 26d is formed in the refractory material 14. Similar to the inner cylinder 22, for example, a V-shaped hook (or anchor) is attached to the inner side surface of the inner cylinder base end plate 24 that faces the combustion space side while being assembled to the peripheral wall portion 22a. Further, a refractory material 14 obtained by applying alumina cement or the like to a thick wall using these hooks as an aggregate is formed on such an inner surface surface.

That is, as shown in FIG. 13, the plurality of air injection nozzles 24b and the plurality of exhaust gas injection nozzles 26d are placed on the flange portion 24c so as to surround the burner unit 13 arranged at the center of the inner cylinder base end plate 24. It is located in the vicinity. In the first embodiment, for example, eight air injection nozzles 24b are provided on the circumference at intervals of 45 degrees at the center angle of the inner cylinder base end plate 24, and the center angle is only 22.5 degrees on the same circumference. Eight exhaust gas injection nozzles 26d are provided at staggered positions at intervals of 45 degrees at the same central angle. As a result, the air injection nozzle 24b (through hole 14a) and the exhaust gas injection nozzle 26d (through hole 14b) are alternately arranged at the same central angle of 22.5 degrees.

The quantity of the air injection nozzle 24b and the exhaust gas injection nozzle 26d is an example, and is appropriately set within a range in which the effects of the air flow and the exhaust gas flow described later can be exhibited. Further, the air injection nozzle 24b and the exhaust gas injection nozzle 26d do not need to be provided at equal intervals. When the inner cylinder base end plate 24 is assembled to the peripheral wall portion 22a, the inner space of these air injection nozzles 24b communicates with the air flow passage Rb. Therefore, the air that has been pumped from the second blower fan 3 and has flowed into the air flow passage Rb from the intake port 21j passes through the air injection nozzle 24b and is inside the peripheral wall portion 22a, as shown by the broken line arrow in FIG. It is injected into the space, that is, the combustion space.

Further, when the exhaust gas injection unit 26 is assembled to the burner holder 17 and the exhaust gas injection nozzle 26d is inserted into the through hole 24d of the inner cylinder base end plate 24, the exhaust gas gallery 26a of the exhaust gas injection unit 26 communicates with the exhaust gas duct 28. .. Therefore, the exhaust gas taken in from the intake port 21f of the connecting portion 21d connected to the upstream pipe 100a and flowing into the exhaust gas duct 28 is, for example, the exhaust gas gallery 26a and the exhaust gas injection as shown by the one-point chain line arrow shown in FIG. It is injected into the combustion space of the peripheral wall portion 22a via the nozzle 26d. The exhaust gas temperature is 300 ° C. or lower, while the temperature of BOG or the like (combustion gas) burned by the burner portion 13a exceeds 1000 ° C. That is, the temperature of the exhaust gas is lower than the temperature of the combustion gas from the burner portion 13a. In the figure, for convenience of drawing expression, a state in which air or exhaust gas is injected from a specific air injection nozzle 24b or exhaust gas injection nozzle 26d is shown, but it is provided on the inner cylinder base end plate 24. Air is injected from all the air injection nozzles 24b, and exhaust gas is injected from all the exhaust gas injection nozzles 26d provided in the exhaust gas injection unit 26.

As described above, in the exhaust gas heating device 20 of the first embodiment, a plurality of air injection nozzles 24b are provided in an annular shape in the vicinity of the flange portion 24c in the inner cylinder base end plate 24, and the flange portion 24c is also provided in the exhaust gas injection portion 26. A plurality of exhaust gas injection nozzles 26d are provided in an annular shape in the vicinity of the above. Therefore, when the inner cylinder base end plate 24 and the exhaust gas injection portion 26 are assembled to the peripheral wall portion 22a or the like, the vicinity of the surface of the refractory material 14 coated on the peripheral wall portion 22a and the substantially entire circumference of the inner circumference of the fireproof material 14 A plurality of air injection nozzles 24b and exhaust gas injection nozzles 26d are arranged over the area. As a result, when the air in the air flow passage Rb pumped from the second blower fan 3 is injected into the combustion space from the air injection nozzle 24b, it flows along the surface of the fireproof material 14 forming the combustion space. .. Further, when the exhaust gas introduced into the exhaust gas injection unit 26 from the connection portion 21d connected to the upstream pipe 100a via the exhaust gas duct 28 is also injected into the combustion space from the exhaust gas injection nozzle 26d, the combustion space is created. It flows along the surface of the fireproof material 14 to be formed.

As a result, the air injected from the air injection nozzle 24b flows in the combustion space as an air flow along the inner peripheral surface (surface of the fireproof material 14) of the inner cylinder 22, and is also injected from the exhaust gas injection nozzle 26d. The exhaust gas also flows in the combustion space as an exhaust gas flow along the inner peripheral surface (surface of the fireproof material 14) of the inner cylinder 22. The exhaust gas temperature is 300 ° C. or lower. Therefore, since the inner peripheral surface of the inner cylinder 22 (the surface of the refractory material 14) is cooled by both the air flow and the exhaust gas flow, such a plurality of air injection nozzles 24b and exhaust gas injection nozzles 26d are used. It is possible to further reduce the thickness of the refractory material 14 as compared with the case where it is not provided. Therefore, the weight of the gas processing device 10 can be further reduced. That is, the exhaust gas heating device 20 of the first embodiment can further reduce the weight of the device as compared with the gas treatment device 10 of the reference embodiment .

In the exhaust gas heating device 20 described above, petroleum fuels such as light oil and heavy A oil have been exemplified and described as fuels supplied from the fuel pipe 90. For example, gas fuels such as liquefied natural gas are supplied from the fuel pipe 90. It may be supplied to the exhaust gas heating device 20. Gaseous fuels such as liquefied natural gas have a lower carbon content than petroleum-based fuels. Therefore, the amount of convective heat transfer is relatively larger than the amount of radiant heat transfer from the flame by the gaseous fuel. Therefore, the inner peripheral surface can be raised by injecting an air flow from the air injection nozzle 24b or an exhaust gas flow from the exhaust gas injection nozzle 26d along the inner peripheral surface (the surface of the refractory material 14) of the inner cylinder 22. Be covered. As a result, in addition to the relatively small amount of radiant heat transfer, the amount of convection heat transfer that reaches the inner peripheral surface (the surface of the refractory material 14) of the inner cylinder 12 can also be reduced. The temperature of the inner peripheral surface of 22 can be lowered. Therefore, the thickness of the refractory material 14 can be reduced, and the weight of the exhaust gas heating device 20 can be reduced.

Further, since the connection portions 21d and 21g of the exhaust gas heating device 20 are connected in the middle of the pipe 100 without changing the arrangement of the pipes to the existing pipe 100 through which the exhaust gas of the diesel engine (external engine) flows, the existing pipe 100 is used. It can be easily applied to the equipment of. As a result, it is possible to easily cope with the so-called retrofit, in which the old model is modified and changed to the new model that can be used thereafter. On the other hand, for example, in the technique of Patent Document 3 (Japanese Unexamined Patent Publication No. 2012-82804) mentioned in the column of [Background Art], the apparatus is described as disclosed in FIGS. 2 and 3 of the same document. It is necessary to change the arrangement of the existing piping (same document; flue 24) according to the shape of the (literature; burner portion 15), and the layout of the equipment and other piping arranged in the surrounding space is changed. Can be forced. As a result, maintenance work can become difficult. That is, the technique of Patent Document 3 has a problem that it is difficult to be familiar with retrofit.

It is also possible to further reduce the temperature of the inner peripheral surface of the inner cylinder 22 by adopting a configuration in which the air blowing capacity of the second blowing fan 3 is increased to increase the flow rate of the air injected from the air injection nozzle 24b. Become. As a result, for example, the refractory material 14 itself can be abolished (so-called metal throat), so that the weight of the exhaust gas heating device 20 can be further reduced. It should be noted that the blowing capacity of the second blowing fan 3 and the quantity, arrangement, and intervals of the air injection nozzles 24b can exhibit the effects of the air flow as described above based on the results of experiments and computer simulations. It is set appropriately within the range.

In the above-described configuration example, the exhaust gas input pipe 26c is connected to the disc-shaped exhaust gas injection unit 26 from the axial direction. For example, the exhaust gas injection unit 26 is tangent to the disk-shaped exhaust gas injection unit 26. The exhaust gas input pipe 26c may be connected from the direction or the radial direction. Since the space of the exhaust gas gallery 26a is annular, it is possible to reduce the inflow resistance of the exhaust gas as compared with the case where the exhaust gas input pipe 26c is connected in the axial direction. Therefore, since the inflow amount of the exhaust gas flowing into the exhaust gas gallery 26a increases, the injection amount of the exhaust gas injected from the exhaust gas injection unit 26 can be increased.

<Modification 1 of the first embodiment>
As a modification 1 of the exhaust gas heating device 20, for example, the exhaust gas injection unit 26 provided in the air flow passage Rb may be provided in the inner cylinder 22. This makes it possible to easily configure an exhaust gas heating device 20 equivalent to the first embodiment based on the configuration of the gas treatment device 10 of the reference embodiment , for example.

As shown in FIGS. 14 and 15, in the modification 1 of the exhaust gas heating device 20, the exhaust gas injection unit 29 is provided in the inner space of the inner cylinder 22, that is, the combustion space. The exhaust gas injection unit 29 has an air flow passage 29c at the corresponding portion by the reduction of the exhaust gas injection nozzles, instead of halving the number of the exhaust gas injection nozzles 29d with respect to the exhaust gas injection unit 26 described above. It is different from the exhaust gas injection unit 26 described above.

The inner cylinder base end plate 25 has a structure similar to that of the inner cylinder base end plate 16 of the reference form . That is, the inner cylinder base end plate 25 is the same as the inner cylinder base end plate 16 except that the plurality of air injection nozzles 16b included in the inner cylinder base end plate 16 are deleted for each jump. It is composed. Therefore, since the burner through port 16a corresponds to the burner through port 25a, the air injection nozzle 16b corresponds to the air injection nozzle 25b, and the flange portion 16c corresponds to the flange portion 25c, the description of each configuration will be omitted. In the inner cylinder base end plate 25, for example, eight air injection nozzles 25b are provided at intervals of 45 degrees at a central angle of the inner cylinder base end plate 25.

The exhaust gas injection portion 29 is a hollow ring having an outer diameter set to be substantially the same as the outer diameter of the inner cylinder base end plate 25 and an inner diameter larger than the opening diameter of the skirt portion 13b of the burner unit 13. It is formed in a shape. The exhaust gas injection unit 29 is provided with an exhaust gas gallery 29a inside, and an exhaust gas input pipe (not shown) connected to the exhaust gas duct 28 communicates with the exhaust gas injection unit 29 . The exhaust gas injection unit 29 is assembled to the inner cylinder base end plate 25 by a fixed structure (not shown). Further, the exhaust gas injection unit 29 includes a plurality of air flow passages 29c communicating the inner cylinder base end plate 25 side and the combustion space side, and a plurality of injection nozzles 29d protruding toward the combustion space side. The exhaust gas injection nozzle 29d communicates with the exhaust gas gallery 29a and communicates with the air injection nozzle 25b of the inner cylinder base end plate 25 in a state of being assembled to the inner cylinder base end plate 25.

As a result, as shown in FIG. 15, the plurality of air flow passages 29c and the plurality of exhaust gas injection nozzles 29d are flanged so as to surround the periphery of the burner unit 13 arranged at the center of the inner cylinder base end plate 25. It is placed in the vicinity of 25c. In this modification 1, for example, eight air flow passages 29c are provided on the circumference at intervals of 45 degrees at the central angle of the inner cylinder base end plate 25, and the center angle is shifted by 22.5 degrees on the same circumference. Eight exhaust gas injection nozzles 29d are provided at the same central angle at intervals of 45 degrees. As a result, the air flow passages 29c and the exhaust gas injection nozzles 29d are alternately arranged at the same central angle of 22.5 degrees. The quantity of the air flow passage 29c and the exhaust gas injection nozzle 29d is an example, and is appropriately set within a range in which the effects of the air flow and the exhaust gas flow can be exhibited. Further, the air flow passages 29c and the exhaust gas injection nozzles 29d do not need to be provided at equal intervals.

In the modified example 1 of the exhaust gas heating device 20, the inner cylinder base end plate 25 and the exhaust gas injection portion 29 are configured in this way, so that the air flow passage 29c is in a state where they are assembled to the peripheral wall portion 22a. The inner space communicates with the air flow passage Rb. Therefore, the air that has been pumped from the second blower fan 3 and has flowed into the air flow passage Rb from the intake port 21j passes through the air injection nozzle 24b and is inside the peripheral wall portion 22a, for example, as shown by the broken line arrow in FIG. It is injected into the space, that is, the combustion space. Further, from the exhaust gas injection nozzle 29d, the exhaust gas taken in from the intake port 21f of the connecting portion 21d connected to the upstream pipe 100a and flowing into the exhaust gas duct 28 is, for example, as shown by the alternate long and short dash line arrow in FIG. It is injected into the combustion space of the peripheral wall portion 22a. In the figure, for convenience of drawing expression, a state in which air or exhaust gas is injected from a specific air flow passage 29c or an exhaust gas injection nozzle 29d is shown, but the exhaust gas injection unit 29 is provided. Air is injected from all the air flow passages 29c, and exhaust gas is injected from all the exhaust gas injection nozzles 29d.

In the exhaust gas heating device 20 described above, the outer cylinder 21 or the inner cylinder 22 is arranged so that the cylinder axis J is directed in the direction orthogonal to or substantially orthogonal to the existing pipe 100, but this is limited to this. Various configurations can be made according to the existing layout (existing arrangement) of the pipe 100 (upstream pipe 100a and downstream pipe 100b).

For example, as shown in FIG. 16A, the connecting portion 21d projects from the tip portion 21c along the cylinder axis J of the outer cylinder 21 (or inner cylinder 22) with respect to the configuration of the exhaust gas heating device 20 described above. The exhaust gas heating device 20A may be configured as described above. On the contrary, the connecting portion 21g may be configured to protrude from the tip portion 21c along the cylinder axis J of the outer cylinder 21. As a result, for example, when either one of the upstream pipe 100a or the downstream pipe 100b is arranged coaxially or substantially coaxially with respect to the tubular axis J, and the other is arranged in a direction orthogonal to or substantially orthogonal to the same. In, the upstream pipe 100a can be connected to the connecting portion 21d and the downstream pipe 100b can be connected to the connecting portion 21g at such an L-shaped bent portion.

Further, for example, as shown in FIG. 16B, with respect to the configuration of the exhaust gas heating device 20 described above, either one of the connecting portion 21d and the connecting portion 21g is the cylinder shaft of the outer cylinder 21 (or the inner cylinder 22). The exhaust gas heating device 20B may be configured so as to project in a direction rotated by 90 degrees about J. As a result, for example, when the upstream pipe 100a and the downstream pipe 100b are arranged in an L shape in the direction orthogonal to the cylinder axis J, the upstream pipe 100a is connected to the connecting portion 21d at such an L-shaped bent portion. It becomes possible to connect the downstream pipe 100b to the connecting portion 21g.

Further, for example, as shown in FIG. 16C, the connecting portion 21d and the connecting portion 21g are arranged so as to be orthogonal or substantially orthogonal on the same plane, and the plane is the cylinder of the outer cylinder 21 (or the inner cylinder 22). The exhaust gas heating device 20C may be configured so that both the connecting portions 21d and 21g project in a V shape from the peripheral wall portion 21a and the tip portion 21c so as to include the shaft J. As a result, for example, when the orthogonal upstream pipes 100a and the downstream pipes 100b are arranged in a V shape along the cylinder axis J, the upstream pipes 100a are connected at such V-shaped bending points. It becomes possible to connect to the portion 21d and to connect the downstream pipe 100b to the connecting portion 21g.

By configuring the exhaust gas heating devices 20A to 20C in this way, the exhaust gas heating devices 20A to 20C can be retrofitted at locations where the existing pipes 100 are orthogonal to each other without changing the existing layout of the pipes 100. The pipes 100 illustrated in FIG. 16 are all based on the assumption that the upstream pipe 100a and the downstream pipe 100b are orthogonal to each other, but the angle at which these pipes bend is not limited to 90 degrees. For example, it may be 45 degrees, 60 degrees, 120 degrees, or the like.

<Modification 2 of the first embodiment>
Further, as a modification 2 of the exhaust gas heating device 20, for example, an inner pipe 21x having a reduced diameter shape may be provided in the connecting portion 21d connected to the upstream pipe 100a. This makes it possible to easily draw the exhaust gas flowing from the upstream pipe 100a into the combustion space of the inner cylinder 22.

As shown in FIG. 17A, in the exhaust gas heating device 20D of the modified example 2, the inner pipe 21x is provided in the internal space of the connecting portion 21d in which the exhaust gas flows in from the existing pipe 100. The inner pipe 21x has a hollow truncated cone shape in which the tip portion 21x-1 corresponding to the upstream side of the exhaust gas expands in diameter toward the tip end direction (upstream direction of the exhaust gas) in a state of being provided in the connection portion 21d. It is formed in a (reverse taper shape). In other words, the tip portion 21x-1 is formed in a hollow truncated cone shape (tapered shape) whose diameter is reduced from the tip end side toward the base end direction (downstream direction of the exhaust gas). Further, the base end portion 21x-2 corresponding to the downstream side of the exhaust gas of the inner pipe 21x is connected to the minimum diameter portion of the tip portion 21x-1 and is formed in a cylindrical shape having the same diameter. The downstream end of the base end portion 21x-2 extends from the tubular shaft J of the inner cylinder 22 to the connecting portion 21g side (exhaust gas downstream side).

As a result, when the exhaust gas flowing from the upstream pipe 100a into the connecting portion 21d flows into the inner pipe 21x, the flow velocity of the exhaust gas increases at the base end portion 21x-2 having an inner diameter smaller than that of the tip portion 21x-1. Since the pressure at the outlet portion of the base end portion 21x-2 is lowered, the combustion gas in the inner cylinder 22 generated by the burner portion 13a can be easily drawn toward the outlet portion of the base end portion 21x-2.

Instead of such an inner pipe 21x, the shape of the connecting portion 21d may be formed into a tapered shape in which the diameter is reduced toward the downstream side of the exhaust gas. That is, as shown in FIG. 17B, the connection portion 21d'is the tip portion 21d'-1 formed to have substantially the same diameter as the upstream pipe 100a of the pipe 100 and the internal space (combustion space) of the inner cylinder 22. That is, the base end portion 21d'-2 formed in a tapered shape whose diameter is reduced toward the downstream side of the exhaust gas is provided. A plurality of V-shaped hooks (or anchors) are attached to the peripheral surface of the base end portion 21d'-2, and alumina cement or the like is applied to a thick wall using these hooks as an aggregate to make a refractory material 14. Is formed. A cylindrical portion is formed at the tip of the base end portion 21d'-2 in order to stabilize the flow of exhaust gas and facilitate the formation of the refractory material 14.

As a result, when the exhaust gas flowing from the upstream pipe 100a into the connecting portion 21d'flows into the tapered base end portion 21d'-2, the flow velocity of the exhaust gas increases as compared with the tip portion 21d'-1. Since the pressure at the outlet of the base end 21d'-2 is reduced, the combustion gas in the inner cylinder 22 generated by the burner portion 13a can be easily drawn toward the outlet of the base end 21d'-2. ..

[ Second Embodiment]
Subsequently, a second embodiment of applying the combustion apparatus to the exhaust gas heating apparatus of a plurality burners type of the present invention will be described with reference to FIGS. 18 to 20. Similar to the exhaust gas heating device 20 of the first embodiment, the exhaust gas heating device 30 of the second embodiment also has a sufficient denitration catalyst by being connected in the middle of the pipe 100 through which the exhaust gas of the diesel engine (external engine) flows, for example. It is a heating device that raises the exhaust gas temperature to a temperature at which it is active, and is a marine combustion device mounted on a ship.

The exhaust gas heating device 30 is different from the exhaust gas heating device 20 of the first embodiment in that the exhaust gas heating device 30 includes a plurality of burner units 33, and these burner units 33 are provided on the peripheral wall portion 22a of the inner cylinder 32. The same components as those of the gas treatment device 10 of the reference embodiment and the exhaust gas heating device 20 of the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

As shown in FIGS. 18 to 20, the exhaust gas heating device 30 is mainly composed of an outer cylinder 31, an inner cylinder 32, a burner unit 33, an exhaust gas injection pipe 38, a first fan 2, a second fan 3, and the like. There is.

The outer cylinder 31 is configured in substantially the same manner as the outer cylinder 21 of the first embodiment, but the configuration of the circular flat plate-shaped outer cylinder base end plate 23 that closes the opening of the base end portion 21b of the outer cylinder 31 is slightly configured. different. That is, the exhaust gas input pipe attachment port 23b is formed in the center of the outer cylinder base end plate 23, and the exhaust gas injection pipe 38 is inserted through the exhaust gas input pipe attachment port 23b and attached to the outer cylinder base end plate 23. Be done. The exhaust gas injection pipe 38 is connected to the exhaust gas duct 28, and the exhaust gas taken in from the intake port 21f of the connecting portion 21d is introduced into the exhaust gas injection pipe 38 via the exhaust gas duct 28. As a result, the exhaust gas injection pipe 38 can inject the exhaust gas into the internal space of the inner cylinder 32, that is, the combustion space.

The inner cylinder 32 is also configured to be substantially the same as the inner cylinder 22 of the first embodiment, except that a plurality of burner units 33 can be attached to the peripheral wall portion 22a. That is, the inner cylinder 32 includes a burner holder 32a that projects outward in the radial direction, and a plurality of burner holes 32b are formed in the burner holder 32a. The burner hole 32b is a mounting hole for mounting the burner unit 33. In the second embodiment, the inner cylinder 32, and bus Nahoru 32b is formed on each of the three Banahoruda 32a facing different levels. That is, the inner cylinder 32 of the exhaust gas heating device 30 of the second embodiment includes six burner units 33.

The burner unit 33 is mainly composed of a burner portion 33a and a case 33b. The burner portion 33a is provided with, for example, a truncated cone-shaped nozzle portion at the tip, and a fuel pipe 90 for supplying fuel is connected to the burner portion 33a. The radial circumference of the burner portion 33a is covered with a tubular case portion 33b. The case portion 33b is attached to a burner hole 32b formed in the burner holder 32a of the inner cylinder 32 so that the burner unit 33 can be fixed to the inner cylinder 32. The burner holder 32a is covered with a cover portion 35. In the second embodiment, as shown in FIG. 20, the burner units 33 are arranged so as to face each other in a stepped manner and to radiate a flame along the tangential direction of the peripheral wall portion 22a, and each of the three burner units 33. Are located so as to line up in the J direction of the cylinder axis. As a result, the gas burned by the flame of the burner portion 33a can be swirled in the circumferential direction along the peripheral wall portion 22a.

As described above, in the exhaust gas heating device 30 of the second embodiment, a plurality of burner units 33 are provided on the peripheral wall portion 22a of the inner cylinder 32 so that flames are radiated along the tangential direction, and the base end of the inner cylinder 32. An exhaust gas injection pipe 38 is provided at the center of the portion 22b, and a plurality of air injection nozzles 24b are provided in an annular shape in the vicinity of the flange portion 24c. Therefore, in a state where the inner cylinder base end plate 24 is assembled to the peripheral wall portion 22a, a plurality of air jets are injected near the surface of the refractory material 14 applied to the peripheral wall portion 22a and over substantially the entire inner circumference of the refractory material 14. The nozzle 24b is arranged. Further, the exhaust gas injection pipe 38 is arranged on the central axis J of the inner cylinder 32.

As a result, when the air in the air flow passage Rb pumped from the second blower fan 3 is injected into the combustion space from the air injection nozzle 24b, it flows along the surface of the fireproof material 14 forming the combustion space. .. Further, when the exhaust gas introduced into the exhaust gas injection pipe 38 from the connection portion 21d connected to the upstream pipe 100a via the exhaust gas duct 28 is injected from the exhaust gas injection pipe 38, it is formed in the combustion space along the cylinder shaft J. It induces the generation of an air flow flowing along the central axis and toward the tip portion 22c (the tip direction of the combustion space). On the other hand, a flame is radiated from the burner portion 33a of the burner unit 33 along the peripheral wall portion 22a in the circumferential direction.

Therefore, the inner peripheral surface of the inner cylinder 32 (the surface of the refractory material 14) is cooled by the air flow from the air injection nozzle 24b, so that when such a plurality of air injection nozzles 24b are not provided. In comparison, the thickness of the refractory material 14 can be further reduced. Further, the gas burned by the flame of the burner portion 33a is sent out toward the tip of the combustion space by the exhaust gas flow flowing through the central axis of the combustion space from the exhaust gas injection pipe 38 while swirling in the peripheral wall portion 22a in the circumferential direction. Therefore, it is possible to heat the exhaust gas over almost the entire combustion space. Therefore, the combustion efficiency can be improved and the weight of the exhaust gas heating device 30 can be reduced.

The quantity, arrangement, interval, and the like of the burner unit 33 and the air injection nozzle 24b are appropriately set within a range in which the above-mentioned effect on combustion efficiency can be exhibited based on the results of experiments and computer simulations. To.

[ Third Embodiment]
Subsequently, a third embodiment in which the combustion device of the present invention is applied to a vertical type exhaust gas heating device will be described with reference to FIGS. 21 to 25. The exhaust gas heating device 40 of the third embodiment is also the same as the exhaust gas heating device 20 of the first embodiment and the exhaust gas heating device 30 of the second embodiment, for example, in the pipe 100 through which the exhaust gas of the diesel engine (external engine) flows. It is a heating device that raises the exhaust gas temperature to a temperature at which the denitration catalyst is sufficiently activated by connecting it in the middle, and is a marine combustion device mounted on a ship.

Exhaust gas heating device 40 are that a plurality of burner units 33 has a of burner unit 33 is provided at the base end portion 42b of the inner cylinder 42, and the point the furnace body is a vertical, first It is different from the exhaust gas heating device 20 of the embodiment. The same components as those of the gas treatment device 10 of the reference embodiment , the exhaust gas heating device 20 of the first embodiment, and the exhaust gas heating device 30 of the second embodiment are designated by the same reference numerals to simplify the description. ..

As shown in FIGS. 21 to 25, the exhaust gas heating device 40 is mainly composed of an outer cylinder 41, an inner cylinder 42, an outer pipe 43, an inner pipe 44, a burner unit 33, a first fan 2, a second fan 3, and the like. It is configured.

The outer cylinder 41 is, for example, a cylinder having a bottomed square cylinder shape, and is made of a steel plate. That is, one end side of the outer cylinder 41 is opened so as to be surrounded by the angular annular base end portion 41b having an inwardly bent flange shape with respect to the peripheral wall portion 41a formed in the shape of a square cylinder. The other end side of 41 is closed by a rectangular flat plate-shaped tip portion 41c. In the third embodiment, the outer cylinder 41 connects the peripheral wall portions to each other in a state where the outer pipe 43 and the cylinder shaft described later are arranged in parallel. Therefore, among the four wall bodies forming the peripheral wall portion 41a, the wall body located on the outer pipe 43 side is omitted. That is, the peripheral wall portion 41a of the outer cylinder 41 is composed of three wall bodies.

The inner cylinder 42 is a cylinder that is housed inside the outer cylinder 41 and forms a combustion space inside, and is formed in the shape of a bottomed square cylinder like the outer cylinder 41. In the inner cylinder 42, one end side of the square tubular peripheral wall portion 42a is closed by the base end portion 42b, and the other end side is also closed by the rectangular flat plate-shaped tip portion 42c. Near the other end side of the peripheral wall portion 42a, a connecting portion 42d is formed in which exhaust gas flows and communicates with the inner pipe 44 covered by the outer pipe 43. That is, the peripheral wall portion 42a is formed with a connecting portion 42d extending in a square tube shape toward the peripheral wall portion 44a of the inner pipe 44, so that the combustion space of the inner cylinder 42 and the inner space of the inner pipe 44 can communicate with each other. ing.

A refractory material 14 is provided on the inner peripheral surface of such an inner cylinder 42. As will be described later, the inner cylinder 42 is provided with a burner unit 33 at the base end portion 42b on one end side, and a flame is formed from the burner portion 33a in the inner cylinder 42, that is, in the combustion space. Therefore, the refractory material 14 is arranged on the inner peripheral surface of the inner cylinder 42 to protect the peripheral wall portion 41a, the base end portion 41b, and the tip portion 41c from the radiant heat of the flame. The refractory material 14 is, for example, a mixture of refractory concrete called castable and refractory aggregate. In the third embodiment, for example, V-shaped hooks (or anchors) shown in the drawing are attached to a plurality of locations on the inner peripheral surface of the inner cylinder 12, and these hooks are used as aggregates to thicken alumina cement or the like. By applying it, the refractory material 14 is formed.

The outer pipe 43 is a cylindrical body having a cylindrical shape that covers the peripheral wall portion 44a of the inner pipe 44, and the axial length thereof is set to be the same as the axial length of the outer cylinder 41. The outer pipe 43 covers both ends of the air flow passage Rb formed between the outer pipe 43 and the inner cylinder 42 in addition to the peripheral wall portion 44a of the inner pipe 44. Therefore, the outer pipe 43 is formed with a base end portion 43b and a tip end portion 43c so that both ends thereof form an inwardly bent flange shape. Flange portions 45 and 46 that can be connected to the pipe through which the exhaust gas flows are connected to the base end portion 43b and the tip end portion 43c, respectively. In the third embodiment, the flange portions 45 and 46 have a circular outer peripheral shape, and therefore, as a pipe through which the exhaust gas flows, for example, as described in the first embodiment and the second embodiment described above. Cylindrical piping 100 can be connected.

The inner pipe 44 is a tubular body having a square cylinder shape with both ends open, and exhaust gas flowing in from an existing pipe or the like flows through the inner pipe 44. Since the inner cylinder 42 has a square cylinder shape as described above, the shape of the inner pipe 44 is also set to the square cylinder shape from the viewpoint of ease of joining with the inner cylinder 42 and pressure loss. In consideration of the fact that cylindrical pipes through which exhaust gas flows are often used, the cylindrical body provided around the inner pipe 44 is set to the cylindrical outer pipe 43 as described above.

Burner unit 33 is configured similarly to the second embodiment described above, it is possible to substantially quote contents described for each in the second embodiment. Since the case portion 33b of the burner unit 33 can be attached to the burner hole 42f formed in the base end portion 42b of the inner cylinder 42, the burner unit 33 is configured to be attached to the base end portion 42b of the inner cylinder 42. Is fixed to. In the third embodiment, the burner units 33 are arranged in, for example, 3 rows and 2 columns (or 2 rows and 3 columns), and a total of 6 burner units 33 are attached to the inner cylinder 42.

The first blower fan 2, the second blower fan 3, the first intake port 4, and the second intake port 5 are configured in substantially the same manner as in the case of the above-described reference embodiment . Therefore, with regard to these configurations, the contents described for each can be almost quoted in the reference form . The air pumped from the first fan 2 is sent to the intake port 41i of the outer cylinder 41 via the first intake duct 6. Further, the air pumped from the second fan 3 is sent to the intake port 43j of the outer pipe 43 via the second intake duct 7. As a result, the air that has flowed into the air flow passage Ra from the intake port 41i comes into contact with the outer surface of the inner cylinder 42, so that the inner cylinder 42 can be air-cooled. Further, the air flowing into the air flow passage Rb from the intake port 43j comes into contact with the outer surface of the inner pipe 44, so that the inner pipe 44 can be air-cooled.

The air flow passage Ra and the air flow passage Rb are separated by a dividing plate 48. In the third embodiment, the peripheral wall portion 43a of the outer pipe 43 of the split plate 48 fulfills its function. Therefore, as described in the first to third embodiments, it is not necessary to separately provide a dedicated member (split plate 18) as the split plate. Further, although not shown, the exhaust gas heating device 40 is also provided on the base frame.

As described above, in the exhaust gas heating device 40 of the third embodiment, the furnace body (outer cylinder 41 and inner cylinder) so that the cylinder axis J of the inner cylinder 42 rises in the vertical direction (Z-axis direction of the coordinate system shown in each figure). 42) constitutes. Further, by providing the burner unit 33 at the upper end of the furnace body, a flame is formed downward (in the direction of gravity) from the burner portion 33a. As a result, the width of the exhaust gas heating device 40 can be narrowed as compared with the case where the furnace body is arranged sideways (in the direction in which the XY plane spreads in the coordinate system shown in each figure).

Therefore, the exhaust gas heating device 40 can be installed even in a place where the floor area is relatively small, such as an engine room or a boiler room in a ship, when there is a margin in the height direction. become. Further, when the piping through which the exhaust gas discharged from the diesel engine (external engine) flows is laid out (arranged) in the vertical direction, the exhaust gas heating device 40 is interposed in the middle of such existing piping. It is possible to raise the exhaust gas temperature to a temperature at which the denitration catalyst is sufficiently activated. That is, retrofit can be easily dealt with.

[ Fourth Embodiment]
Subsequently, a fourth embodiment in which the combustion device of the present invention is applied to a vertical type exhaust gas heating device will be described with reference to FIGS. 26 to 30. The exhaust gas heating device 50 of the fourth embodiment is obtained by modifying the configuration of the exhaust gas heating device 40 of the third embodiment to have two furnace bodies. Therefore, the same components as those of the exhaust gas heating device 40 of the third embodiment are designated by the same reference numerals, and the description thereof will be omitted.

As shown in FIGS. 26 to 30, the exhaust gas heating device 50 mainly includes outer cylinders 41, 51, inner cylinders 42, 52, outer pipe 43, inner pipe 44, burner unit 33, first fan 2, second. It is composed of a fan 3 and the like.

One furnace body composed of an outer cylinder 41, an inner cylinder 42, a refractory material 14, a burner unit 33, etc., and another furnace body composed of an outer cylinder 51, an inner cylinder 52, a refractory material 14, a burner unit 33, etc. Is symmetrically configured with the inner pipe 44 through which the exhaust gas flows and the outer pipe 43 surrounding the peripheral wall portion 44a thereof. Therefore, by replacing the reference numerals 41 and 41x (x is a, b, c, etc.) with the reference numerals 51 and 51x (x is a, b, c, etc.), the contents described in the third embodiment can be described. It can also be applied to the other furnace body. The cylinder shaft J is replaced with the cylinder shaft L. Further, the first intake duct 6 connected to the first fan 2 is distributed in two paths on the way, one is connected to the intake port 41i of the outer cylinder 41, and the other is connected to the intake port 51i of the outer cylinder 51. Be connected.

As described above, in the exhaust gas heating device 50 of the fourth embodiment, the outer cylinder 51 and the inner cylinder are located at symmetrical positions of one of the furnace bodies composed of the outer cylinder 41, the inner cylinder 42, the refractory material 14, the burner unit 33, and the like. The 52, the refractory material 14, the burner unit 33, and the like are arranged, and the inner pipe 44 through which the exhaust gas flows and the outer pipe 43 surrounding the peripheral wall portion 44a thereof are sandwiched between them so as to be symmetrically configured. Further, as compared with the third embodiment, in the fourth embodiment, the plurality of burner units 33 are symmetrically distributed. As a result, the combustion gas is evenly supplied to the left and right sides of the exhaust gas flowing through the inner pipe 44, so that the temperature unevenness is reduced and the exhaust gas temperature is raised to a temperature at which the denitration catalyst is sufficiently activated in a short time. Can be done. The number of furnace bodies is doubled as compared with the exhaust gas heating device 40 of the third embodiment (the exhaust gas heating device 40 has one furnace body, whereas the exhaust gas heating device 50 has two furnace bodies). .. As a result, the heating capacity for the exhaust gas flowing through the inner pipe 44 is doubled, so that the exhaust gas temperature can be raised to a temperature at which the denitration catalyst is sufficiently activated in a short time. Further, even if the number of furnace bodies is increased to two, in each furnace body, the cylinder axis J of the inner cylinder 42 and the cylinder axis L of the inner cylinder 52 rise in the vertical direction (Z-axis direction of the coordinate system shown in each figure). Since the furnace bodies are configured as described above, the width of the exhaust gas heating device 50 is narrower than that in the case where either or both of the furnace bodies are arranged sideways (the direction in which the XY plane spreads in the coordinate system shown in each figure). It becomes possible to do.

In each of the above-described embodiments, the combustion device for ships has been illustrated and described, but the combustion device of the present invention is not limited to the combustion device used for ships, and is installed in, for example, a building. It can also be applied to combustion equipment.

Although specific examples of the present invention have been described in detail above, these are merely examples and do not limit the scope of claims. The techniques described in the claims include various modifications or modifications of the above-mentioned specific examples. In addition, the technical elements described in the present specification or the drawings exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. Furthermore, the techniques illustrated in this specification or drawings achieve a plurality of objectives at the same time, and achieving one of the objectives itself has technical usefulness. The description in parentheses in the [Explanation of Code] column clearly indicates the correspondence between the terms used in each of the above-described embodiments and the terms described in the claims.

10, 10A, 20A to 20E, 30, 40, 50 ... Gas treatment device (combustion device)
11,21,31,41,51 ... Outer cylinder 12,22,32,42,52 ... Inner cylinder 12a, 22a, 32a, 42a, 52a ... Circumferential wall portion (peripheral wall of inner cylinder)
12b, 22b, 32b, 42b, 52b ... Base end (one end side of inner cylinder)
13, 33 ... Burner unit 13a, 33a ... Burner part (burner)
14 ... Refractory material 15, 23 ... Outer cylinder base end plate 16, 24, 25, 34 ... Inner cylinder base end plate 16b, 24b ... Air injection nozzle 17 ... Burner holder 18, 48 ... Split plate 19 ... Exhaust pipe 22d ... Inflow (Inlet)
22e ... Outflow part (outlet)
26, 29 ... Exhaust gas injection section 26d, 29d ... Exhaust gas injection nozzle 38 ... Exhaust gas injection pipe 90 ... Fuel pipe 100 ... Piping (existing piping)
J, K, L ... Cylindrical shaft Ra, Rb ... Air flow passage (space)

Claims (10)

Inner cylinder forming a combustion space in the inner portion,
An outer cylinder that covers the inner cylinder by forming a space through which air sent from the outside can flow between the peripheral wall of the inner cylinder and one end side of the inner cylinder.
A combustion device including a burner attached to the outer cylinder so as to be able to supply fuel into the combustion space through the burner through hole on one end side .
In the middle of the piping, the upstream side and the downstream side of the piping are the other end of the inner cylinder rather than the center of the cylinder shaft of the inner cylinder without changing the arrangement of the pipe with respect to the existing pipe through which the exhaust gas of the external engine flows. A combustion device that communicates with each other in the side, and the exhaust gas discharged from the upstream side flows into the downstream side via the combustion space and is heated in the combustion space. A space around the burner that supplies combustion air is provided around the burner.
On one end side of the inner cylinder, the air flowing through the space portion is injected into the combustion space separately from the burner peripheral space portion as air for cooling the inner peripheral surface along the inner peripheral surface of the inner cylinder. combustion apparatus according to claim 1, capable of air injection holes or air injection nozzle, characterized in that are al provided. When the upstream side and the downstream side of the pipe are arranged in a straight line,
The inner cylinder is arranged so that the cylinder shaft faces in an orthogonal direction or a substantially orthogonal direction of the pipe, and the exhaust gas discharged from the upstream side can penetrate the combustion space and flow into the downstream side. The combustion apparatus according to claim 1 or 2, wherein an inlet and an outlet are formed in the combustion apparatus. When the upstream side and the downstream side of the pipe are arranged orthogonally,
The inner cylinder
The tubular shaft is arranged coaxially or substantially coaxially with either the upstream side or the downstream side of the pipe, and is arranged in a direction orthogonal to or substantially orthogonal to the other of the upstream side or the downstream side of the pipe. , Or
The tubular shaft is arranged in a direction orthogonal to or substantially orthogonal to both the upstream side and the downstream side of the pipe, and
The combustion apparatus according to claim 1 or 2, wherein an inflow port and an outflow port are formed so that the exhaust gas discharged from the upstream side penetrates the combustion space and flows into the downstream side. .. On one end side of the inner cylinder, the exhaust gas sent from an external engine and having a temperature lower than the temperature in the combustion space during combustion is burned along the inner peripheral surface of the inner cylinder. combustion device according to any one of claims 1 to 4, characterized in that there Bei Ete exhaust gas ejection portion having a jettable gas injection holes or exhaust gas injection nozzle into the space. A cylindrical body which forms a combustion space in the inner portion,
A combustion device including a burner attached to the one end side so as to be able to supply fuel into the combustion space through the burner through hole on the one end side .
In the middle of the pipe, the upstream side and the downstream side of the pipe are the other end of the cylinder rather than the center of the cylinder shaft of the cylinder without changing the arrangement of the pipe with respect to the existing pipe through which the exhaust gas of the external engine flows. A combustion device that communicates with each other in the side, and the exhaust gas discharged from the upstream side flows into the downstream side via the combustion space and is heated in the combustion space. A space around the burner that supplies combustion air is provided around the burner.
At one end side of the cylinder, air sent from the outside can be injected into the combustion space separately from the burner peripheral space as air for cooling the inner peripheral surface along the inner peripheral surface of the cylinder. combustion apparatus according to claim 6, the air injection hole or an air jet nozzle, such is characterized in that is al provided. When the upstream side and the downstream side of the pipe are arranged in a straight line,
The cylinder is arranged so that the cylinder shaft is oriented in an orthogonal direction or a substantially orthogonal direction of the pipe, and the exhaust gas discharged from the upstream side can flow through the combustion space to the downstream side. The combustion apparatus according to claim 6 or 7, wherein an inlet and an outlet are formed in the combustion apparatus. When the upstream side and the downstream side of the pipe are arranged orthogonally,
The cylinder is
The tubular shaft is arranged coaxially or substantially coaxially with either the upstream side or the downstream side of the pipe, and is arranged in a direction orthogonal to or substantially orthogonal to the other of the upstream side or the downstream side of the pipe. , Or
The tubular shaft is arranged in a direction orthogonal to or substantially orthogonal to both the upstream side and the downstream side of the pipe, and
The combustion apparatus according to claim 6 or 7, wherein the inflow port and the outflow port are formed so that the exhaust gas discharged from the upstream side penetrates the combustion space and flows into the downstream side. .. At one end side of the cylinder, exhaust gas sent from an external engine and having a temperature lower than the temperature in the combustion space during combustion is burned along the inner peripheral surface of the cylinder. combustion device according to any one of claims 6-9, characterized in that there Bei Ete exhaust gas ejection portion having a jettable gas injection holes or exhaust gas injection nozzle into the space.