JP6904736B2 - Combustion device - Google Patents

Description

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

As one type of combustion device, for example, there is a "waste incinerator" 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 Japanese Unexamined Patent Publication No. 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. 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. Boil-off gas is a gas generated by vaporization of liquefied natural gas in an LNG storage tank. For example, in Patent Document 2, of the boil-off gas generated in the cargo tank of a liquefied gas carrier, the surplus that cannot be treated as fuel is liquefied again and recovered in the cargo tank, or is used in a gas incinerator or the like. There is a statement that incineration is required (Patent Document 2; paragraph 0002), and a gas treatment device is used in the latter case.

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 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 a 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 4 ; 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 the inner combustion space, is air sent from outside to together Covering the inner cylinder An outer cylinder that forms a flowable space between the inner cylinder, a burner that penetrates the inner cylinder and is provided on the outer cylinder so that fuel can be ejected into the combustion space, and a separate body from the burner. It is provided with a cylinder that covers the periphery of the burner in the radial direction of the burner shaft and the periphery of the fuel ejection direction, and the exhaust gas discharged from the upstream side of the pipe through which the exhaust gas of the external engine flows is burned. possible flow into the downstream side of the pipe by way of the space, the downstream side of the upstream and the pipe of the pipe is communicated to each of the inside the cylinder, the leading end portion of the tubular body is exposed to the combustion space, The base end portion of the cylinder body is located on the side opposite to the fuel ejection direction of the burner and is exposed in the space portion in the outer cylinder, and between the base end portion and the outer cylinder. Is technically characterized in that a gap is formed.

Further, in the combustion apparatus according to claim 1, the combustion apparatus according to claim 2 circulates the space portion at the end of the inner cylinder on the side through which the burner penetrates. A technical feature is that a hole is provided in which air is injected into the combustion space along the inner peripheral surface of the inner cylinder.

Further, the combustion apparatus according to claim 3 described in the claims is the combustion apparatus according to claim 1 or 2, wherein the tubular body has a tip portion of the pipe located in the fuel ejection direction of the burner. The technical feature is that it is located outside the range of the virtual path that connects the upstream side and the downstream side of the pipe at the shortest distance.

Further, the combustion apparatus according to claim 4 described in the claims is the combustion apparatus according to any one of claims 1 to 3, wherein the cylinder has a tip located in the fuel ejection direction of the burner. The technical feature is that the portion opens in the shape of an end of an oblique cylinder.

Further, the combustion apparatus according to claim 5 described in the claims is the combustion apparatus according to any one of claims 1 to 4, wherein the burner has a fuel ejection direction from the downstream side of the pipe. The technical feature is that it is on the upstream side of the pipe.

Further, the combustion apparatus according to claim 6 described in the claims is a connection portion connected to the downstream side of the pipe on the exhaust gas downstream side of the combustion space in the combustion apparatus according to claim 5. A second inner cylinder having an inner diameter smaller than the inner diameter of the pipe is provided so as to communicate with the downstream side of the pipe.

Further, in the combustion apparatus according to claim 7, the piping through which the exhaust gas of the external engine flows is before the combustion apparatus according to any one of claims 1 to 6 is installed. The combustion device is already provided in the equipment space from the above, and the combustion device is technically characterized in that it can be connected in the middle of the piping without requiring a change in the arrangement of the piping.

In the invention of claim 1, the burner provided on the outer cylinder so that fuel can be ejected into the combustion space is covered with a cylinder provided separately from the burner around the fuel ejection direction in the burner shaft radial direction. Therefore, when a flame is formed from the burner to the combustion space of the inner cylinder, the cylinder covers the flame forming range, so that the direct radiant heat from the flame is blocked by the cylinder. As a result, it becomes possible to reduce the amount of radiant heat transfer directly transmitted from the flame of the burner to the inner wall of the inner cylinder, and the temperature rise of the inner cylinder is suppressed. Further, since the exhaust gas of the external engine flowing from the upstream side of the pipe to the downstream side of the pipe via the combustion space flows through the inner cylinder, the inner cylinder is cooled by such exhaust gas. Therefore, it may not be necessary to provide a refractory material or the like on the inner cylinder, so that the weight can be reduced as compared with the case where the refractory material or the like is provided. Further, since the outer dimensions of the inner cylinder can be reduced by the thickness of the refractory material or the like, the size can be reduced. In addition, the tip of the cylinder is exposed in the combustion space, and the base end is located on the opposite side of the burner from the fuel ejection direction and is exposed in the space inside the outer cylinder. A gap is formed between the base end and the outer cylinder. As a result, the base end portion of the tubular body is cooled by the air from the outside flowing through the space portion, so that it is possible to slow down the progress of deterioration and embrittlement due to the heat of the tubular body. Further, since the base end portion of the cylinder body is physically separated from the outer cylinder by the gap portion, it is possible to suppress heat transfer from the cylinder body to the outer cylinder.

In the invention of claim 2, the end portion of the inner cylinder on the side through which the burner penetrates is provided with a hole portion in which air flowing through the space portion is injected into the combustion space along the inner peripheral surface of the inner cylinder. This makes it possible to cool the inner peripheral surface of the inner cylinder.

In the invention of claim 3, the tubular body is located outside the range of the virtual path in which the tip portion located in the fuel ejection direction of the burner connects the upstream side of the pipe and the downstream side of the pipe at the shortest distance. As a result, the cylinder is unlikely to become a resistance to the flow of exhaust gas from the upstream side to the downstream side of the pipe, so that it is possible to suppress an increase in the pressure loss of the exhaust gas flowing through the combustion space and the pipe. ..

In the invention of claim 4, the tip of the cylinder, which is located in the fuel ejection direction of the burner, opens in the shape of the end of an oblique cylinder. At such a tip portion, there are a long portion having a large axial length and a short portion having a small axial length. Therefore, for example, the cylinder body is arranged so that the long portion is located on the peripheral wall side of the inner cylinder and the short portion is located on the center side of the inner cylinder. As a result, the direct radiant heat from the flame is larger on the long side than on the short side in the axial direction of the cylinder wall, so that the long side is in the direction of the peripheral wall of the inner cylinder. It becomes possible to reduce the amount of radiant heat transfer toward it. Therefore, it is possible to suppress an increase in the temperature of the inner cylinder. Further, the high-temperature combustion gas generated by the combustion of fuel by the flame of the burner is discharged from the cylinder in a shorter distance on the short portion side than on the long portion side and toward the center side of the inner cylinder. Therefore, the combustion gas flowing on the long portion side can be drawn into the center side of the inner cylinder. Further, since the high-temperature combustion gas is collected on the center side of the inner cylinder rather than the peripheral wall side, it is possible to further suppress the temperature rise of the inner cylinder.

In the invention of claim 5, since the fuel ejection direction is from the downstream side of the pipe to the upstream side of the pipe, the burner is arranged in the opposite direction to the flow of the exhaust gas from the upstream side to the downstream side of the pipe. Has been done. As a result, the vertical component in the traveling direction of the combustion gas released from the burner and the vertical component in the traveling direction of the exhaust gas are in opposite directions as compared with the case where such radiant heat or the like travels in the same direction as the flow of the exhaust gas. Since they face each other, convection mixing due to collision is promoted, and combustion gas and exhaust gas can be efficiently mixed. Therefore, since the degree of uniformity of the temperature of the exhaust gas is increased, the temperature unevenness of the exhaust gas can be suppressed, and the space required for mixing can be reduced, so that the inner cylinder and eventually the furnace body can be made compact.

In the invention of claim 6, a second inner cylinder having an inner diameter smaller than the inner diameter of the connecting portion connected to the downstream side of the pipe communicates with the downstream side of the pipe on the downstream side of the exhaust gas of the combustion space. It is provided. As a result, on the downstream side of the exhaust gas, the second inner cylinder prevents the low-temperature air that cools the inner cylinder from flowing into the downstream side of the pipe. It is possible to suppress a decrease in the temperature of the exhaust gas flowing in the vicinity. Further, since more exhaust gas flowing on the central side than the peripheral wall side of the inner cylinder is collected in the second inner cylinder, the exhaust gas having less temperature unevenness can flow out to the downstream side of the pipe.

In the invention of claim 7, the pipe through which the exhaust gas of the external engine flows is an existing pipe, and the combustion device can be connected in the middle of the pipe without requiring a change in the arrangement of the pipe. This makes it easy to apply to existing equipment, so 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.

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. It is a schematic cross-sectional view which looked at the cross section of line III-III shown in FIG. 2 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 a front view which shows an example of the whole structure of the exhaust gas heating apparatus which concerns on 2nd 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 2nd Embodiment. 7 is a schematic cross-sectional view of the IX-IX line cross sections shown in FIGS. 7 and 10 as viewed from the same arrow-viewing direction. 9 is a schematic cross-sectional view of the X-ray cross section shown in FIG. 9 as viewed from the same arrow-viewing direction. FIG. 5 is a schematic enlarged cross-sectional view within the alternate long and short dash line XI shown in FIG. It is a schematic cross-sectional view seen from the direction of the arrow XII shown in FIG. It is explanatory drawing which shows the modification 1 of the exhaust gas heating apparatus of this 2nd Embodiment. It is a schematic enlarged cross-sectional view in the alternate long and short dash line XIV shown in FIG. It is explanatory drawing which shows the modification 2 of the exhaust gas heating apparatus of this 2nd Embodiment. FIG. 5 is a schematic enlarged cross-sectional view within the alternate long and short dash line XVI shown in FIG. FIG. 17A is a schematic enlarged cross-sectional view within the alternate long and short dash line XVII-A shown in FIG. Further, FIG. 17B is a schematic explanatory view seen from the direction of the arrow XVII-B shown in FIG. 17A. It is explanatory drawing which shows the modification 3 of the exhaust gas heating apparatus of this 2nd Embodiment. FIG. 19A is a schematic enlarged cross-sectional view within the alternate long and short dash line XIX-A shown in FIG. Further, FIG. 19B is a schematic explanatory view seen from the direction of the arrow XIX-B shown in FIG. 19A. It is explanatory drawing which shows the application example of the modification 3 of the exhaust gas heating apparatus of this 2nd Embodiment. 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. 21 is a schematic cross-sectional view of the XXIII-XXIII line cross sections shown in FIGS. 21 and 24 as viewed from the same arrow direction. It is a schematic cross-sectional view of the XXIV-XXIV line cross section shown in FIG. 23 seen from the same arrow viewing direction. It is explanatory drawing which shows the example of the flow of radiant heat and the exhaust gas in the exhaust gas heating apparatus of this 3rd Embodiment.

Hereinafter, embodiments of the combustion device of the present invention will be described with reference to the drawings. A first embodiment in which the combustion device of the present invention is applied to an exhaust gas heating device will be described with reference to FIGS. 1 to 6.

[First Embodiment]
The exhaust gas heating device 10 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 through which the exhaust gas of a diesel engine (external engine) flows. , A marine combustion device mounted on a ship.

As shown in FIGS. 1 to 6, the exhaust gas heating device 10 mainly includes an outer cylinder 11, an inner cylinder 12, a plurality of burner units 13, an exhaust gas injection pipe 19, a first blower fan 2, a second blower fan 3, and the like. It is composed of.

The outer cylinder 11 is, for example, a cylinder having a bottomed cylindrical shape and is made of a steel plate. That is, the peripheral wall portion 11a formed in a cylindrical shape is opened so that one end side thereof is surrounded by an annular base end portion 11b having an inwardly bent flange shape, and the other end side is a circular flat plate shape. It is blocked by the tip portion 11c. The peripheral wall portion 11a is formed with connecting portions 11d and 11g extending in a cylindrical shape in the radial direction of the outer cylinder 11, and flange portions 11e and 11h are provided at the tips thereof, respectively. That is, the connecting portions 11d and 11g are formed so as to extend in a direction orthogonal to the cylinder axis J of the outer cylinder 11 (or the inner cylinder 12) (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 11 or the inner cylinder 12 is arranged with the cylinder axis J facing in the direction orthogonal to or substantially orthogonal to the existing pipe 100).

The connecting portions 11d and 11g are arranged so that their respective cylinder shafts have the same shaft K, and the connecting portions 11d and 11g and the respective flange portions 11e and 11h 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 11d and 11g of the exhaust gas heating device 10 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 11d 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 11e, and the downstream side of the exhaust gas is also connected. A connecting portion 11g is connected to the downstream pipe 100b of the above via a flange portion 11h. An intake port 11f for taking in the exhaust gas is formed in the connection portion 11d on the upstream side of the exhaust gas.

The intake 11f is covered above the intake (in the direction of the arrow tip of the Z axis of the coordinate system shown in each figure) by a cover 17 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 17 so that a part of the exhaust gas flowing from the upstream pipe 100a easily flows into the intake port 11f. An exhaust gas duct 18 is connected to the intake port 11f. The exhaust gas duct 18 is connected to the exhaust gas injection pipe 19. As a result, the exhaust gas flowing from the intake port 11f can be introduced into the exhaust gas injection pipe 19. In addition, the intake ports 11i and 11j 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 14, 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 15 as the base end portion 12b, and the other end side is also closed by the circular flat plate-shaped tip portion 12c. In the vicinity of the other end side of the peripheral wall portion 12a, an inflow portion 12d for allowing exhaust gas to flow from the upstream pipe 100a into the inner cylinder 12, that is, into the combustion space, and an inflow portion 12d for flowing exhaust gas from the combustion space to the downstream pipe 100b. The outflow portion 12e and the outflow portion 12e are formed respectively. That is, the peripheral wall portion 12a is formed with an inflow portion 12d connected to 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 upstream pipe 100a can communicate with each other. Further, an outflow portion 12e extending in a cylindrical shape toward the inside of the connecting portion 11g is formed so that the combustion space of the inner cylinder 12 and the inner space of the downstream pipe 100b can communicate with each other. 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.

The base end portion 12b (inner cylinder base end plate 15) of such an inner cylinder 12 is provided with an exhaust gas injection pipe 19 that penetrates the center thereof substantially coaxially with the cylinder shaft J of the inner cylinder 12, and also exhaust gas. A plurality of burner units 13 and a plurality of air injection nozzles 15c and 15d are provided so as to surround the periphery of the injection pipe 19. In the first embodiment, six burner units 13 are provided, and petroleum-based fuel (for example, light oil, heavy fuel oil A, etc.) is supplied to each burner unit 13 from the fuel pipe 90. A refractory material (for example, castable) is not provided on the inner peripheral surface of the inner cylinder 12 for the reason described later.

The burner unit 13 is attached to an outer cylinder base end plate 14 that closes one end side of the outer cylinder 11. In the first embodiment, the burner unit 13 is fixed to the outer cylinder base end plate 14 by a fixing structure (not shown). A fuel pipe 90 to which fuel such as light oil or heavy fuel oil A is supplied is connected to the burner unit 13. The configuration of the burner unit 13 and the inner cylinder base end plate 15 will be described in detail later with reference to FIGS. 5 and 6. The burner unit 13 is located outside the range of the virtual path Rv in which the tip of the cylinder 13b (combustion cylinder 20) located in the fuel ejection direction of the burner 13a connects the upstream pipe 100a and the downstream pipe 100b at the shortest distance. ing. As a result, the cylinder 13b (combustion cylinder 20) is unlikely to become a resistance to the flow of exhaust gas from the upstream pipe 100a to the downstream pipe 100b, so that an increase in pressure loss of exhaust gas flowing through the combustion space and piping is suppressed. can do.

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 14. Has been done. The air flow passage Ra communicates with the intake port 11i formed in the peripheral wall portion 11a of the outer cylinder 11, and the air flow passage Rb communicates with the intake port 11j formed in the peripheral wall portion 11a. .. In the first embodiment, a dividing plate 16 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 air fan 2 via a flange portion 6a is connected to the air intake port 11i, and the air from the second air fan 3 is blown to the air intake port 11j. A second intake duct 7 connected to the mouth via a flange portion 7a is connected.

The first blower fan 2 and the second blower fan 3 are both blower fans in which the impeller rotates by using an electric motor as a drive source. The first blower fan 2 is connected to the first intake port 4, and the second blower 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 blower port. (Pushing). In the first embodiment, the air pumped from the first blower fan 2 is sent to the intake port 11i of the outer cylinder 11 via the first intake duct 6. Further, the air pumped from the second blower fan 3 is sent to the intake port 11j 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 11i and 11j, respectively, flows in the direction of the dotted arrow shown in FIGS. 3 and 4, for example. Therefore, the inner cylinder 12 can be air-cooled by the air sent from the outside coming into contact with the outer surface of the inner cylinder 12.

The air flow passage Ra and the air flow passage Rb are separated by a dividing plate 16. 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 is close to the burner unit 13. It sends air to be injected into the base end of the furnace body and the combustion space. That is, as will be described later, the air flowing through the air flow passage Rb also enters the combustion space of the inner cylinder 12 via the air injection nozzles 15c and 15d of the base end portion 12b (inner cylinder base end plate 15) of the inner cylinder 12. Inflow. 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 exhaust gas heating device 10 configured in this way is provided on the base frame 1. In the first embodiment, for example, the furnace body including the outer cylinder 11 and the inner cylinder 12 is formed along the length direction of the base frame 1 with the legs 8a erected at a plurality of positions in 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 these legs 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 15, the exhaust gas injection pipe 19, and the like will be described with reference to FIGS. 5 and 6. A circular flat plate having a circular exhaust gas injection pipe mounting port 14b opening at the center of the base end portion 11b of the outer cylinder 11 and a plurality of burner mounting ports 14a opening so as to surround the exhaust gas injection pipe mounting port 14b. The shape-shaped outer cylinder base end plate 14 is fixed by bolts and nuts. The burner mounting port 14a is a circular hole that allows the burner unit 13 to be fixed to the outer cylinder base end plate 14 by a fixing structure (not shown), and is closed by the plate 13c constituting the burner unit 13. Further, the exhaust gas injection pipe mounting port 14b is set to have an inner diameter slightly larger than the outer diameter of the exhaust gas injection pipe 19, and allows the exhaust gas injection pipe 19 to penetrate.

The burner unit 13 is mainly composed of a burner portion 13a, a tubular body 13b, and a plate 13c. The burner unit 13 is attached to the outer cylinder base end plate 14 so that the burner 13a protrudes into the combustion space substantially parallel to the cylinder shaft J of the inner cylinder 12 toward the combustion space. 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 tubular body 13b. The combustion cylinder 20 as the cylinder body 13b is formed in a cylindrical shape, for example, and is arranged so that the base end portion 20a located on the connecting side of the fuel pipe 90 is exposed to the air flow passage Rb. As a result, the base end portion 20a of the combustion cylinder 20 is cooled by the air flow flowing through the air flow passage Rb, so that it is possible to slow down the progress of deterioration and embrittlement due to heat of the combustion cylinder 20.

The combustion cylinder 20 is arranged so that the base end portion 20a forms a gap Sa at a predetermined interval between the plate 13c and the outer cylinder base end plate 14. As a result, a part of the air flowing through the air flow passage Rb contributes to combustion by entering the combustion cylinder 20 through the gap Sa (thick solid line arrow shown in FIG. 5). Further, by forming a gap Sa between the plate 13c or the outer cylinder base end plate 14 and the base end portion 20a of the combustion cylinder 20, the base end portion 20a of the combustion cylinder 20 is physically separated from the outer cylinder. Therefore, it is possible to suppress heat transfer from the combustion cylinder 20 to the plate 13c and the outer cylinder base end plate 14.

Further, in the combustion cylinder 20, the tip portion 20b of the combustion cylinder 20 located in the fuel ejection direction of the burner 13a is not perpendicular to the end shape of the oblique cylinder, that is, the cylinder axis of the combustion cylinder 20, and is inclined by, for example, 45 degrees. And it opens diagonally. That is, the tip portion 20b is opened in an elliptical shape instead of a circular shape. In the first embodiment, as shown in FIG. 5, six burner units 13 are arranged so that the opening of the tip portion 20b of the combustion cylinder 20 faces in the cylinder axis J direction of the inner cylinder 12. As a result, the short portion side of the cylinder wall of the combustion cylinder 20 having a small axial length faces the cylinder axis J direction of the inner cylinder 12, and the long portion side of the cylinder wall of the combustion cylinder 20 having a large axial length faces the inner cylinder 12. It faces the direction of the peripheral wall portion 12a. Therefore, the direct radiant heat from the flame of the burner 13a can reduce the amount of radiant heat transferred toward the peripheral wall portion 12a of the inner cylinder 12 by the long portion side of the combustion cylinder 20, and the inner cylinder 12 can be reduced. The rise in temperature can be suppressed.

Further, the high-temperature combustion gas generated by the combustion of fuel by the flame of the burner 13a is released from the cylinder in a shorter distance when flowing near the short portion (short portion side) than on the long portion side of the combustion cylinder 20. Then, it goes toward the center side of the inner cylinder (thin broken line arrow in the combustion cylinder 20 shown in FIG. 5). Therefore, the combustion gas flowing near the center of the combustion cylinder 20 or near the long portion (long portion side) can be drawn into the cylinder shaft J (center side) of the inner cylinder 12 (combustion cylinder 20 shown in FIG. 5). Fine one-dot chain arrow and thin two-dot chain arrow). As a result, the high-temperature combustion gas can be collected on the cylinder axis J side rather than on the peripheral wall portion 12a side of the inner cylinder 12, so that the temperature rise of the inner cylinder 12 can be further suppressed.

The inner cylinder base end plate 15 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 the first embodiment, the inner cylinder base end plate 15 (base end portion 12b) is integrally formed with the peripheral wall portion 12a. An inner cylinder base end plate 15 may be formed separately from the peripheral wall portion 12a and fixed to the peripheral wall portion 12a by a fixed structure (not shown).

At the center of the inner cylinder base end plate 15, an exhaust gas injection pipe through port 15a set to an inner diameter slightly larger than the outer diameter of the exhaust gas injection pipe 19 is formed. Further, a plurality of air injection nozzles 15c protruding toward the combustion space side are formed on the circumference concentric with the inner cylinder base end plate 15 so as to surround the exhaust gas injection pipe through port 15a, and these air injections are further formed. A plurality of air injection nozzles 15d projecting toward the combustion space side are formed on the circumference of concentric circles surrounding the nozzle 15c. In the first embodiment, the air injection nozzles 15c and 15d are formed at six locations. The six air injection nozzles 15d are arranged at equal intervals on the circumference, and six combustion cylinder through ports 15b are provided so as to be sandwiched between the air injection nozzles 15d on the same circumference.

That is, as shown in FIG. 6, six air injection nozzles 15d and six burner units 13 are alternately arranged on the circumference surrounding the air injection nozzle 15c at a central angle of 30 degrees of the inner cylinder base end plate 15. Has been done. Further, the burner unit 13 is arranged at a position separated from the peripheral wall portion 12a of the inner cylinder 12 by a predetermined gap Sb. As a result, the burner unit 13 is cooled by the air flow injected from the air injection nozzle 15d, and the peripheral wall portion 12a of the inner cylinder 12 can also be cooled. The six air injection nozzles 15c are arranged at intervals of 60 degrees at the central angle of the inner cylinder base end plate 15.

The numbers of the air injection nozzles 15c and 15d and the exhaust gas injection pipe 19 are examples, and are 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 nozzles 15c and 15d and the burner unit 13 do not need to be provided at equal intervals. Since the inner space of these air injection nozzles 15c and 15d communicates with the air flow passage Rb, the air that is pressure-fed from the second blower fan 3 and flows into the air flow passage Rb from the intake port 11j is, for example, FIG. As shown by the broken arrow, the air is injected into the internal space of the peripheral wall portion 12a, that is, the combustion space via the air injection nozzles 15c and 15d.

Further, when the exhaust gas injection pipe 19 is connected to the exhaust gas duct 18, the exhaust gas injection pipe 19 communicates with the intake port 11f of the connection portion 11d. Therefore, the exhaust gas taken in from the intake port 11f of the connecting portion 11d connected to the upstream pipe 100a and flowing into the exhaust gas duct 18 is inside from the exhaust gas injection pipe 19 as shown by the alternate long and short dash line arrow in FIG. 5, for example. It is injected into the combustion space of the cylinder 12. The exhaust gas temperature is 300 ° C. or lower, while the temperature of the 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, the state in which air is injected from the specific air injection nozzles 15c and 15d is shown, but all the air injections provided on the inner cylinder base end plate 15 are shown. Air is injected from the nozzles 15c and 15d.

The air flow capacity of the second blower fan 3, the quantity, arrangement and spacing of the burner unit 13 and the air injection nozzles 15c and 15d are determined based on the results of experiments and computer simulations as described above. It is set as appropriate within the range in which the effect of Further, the size of the gap Sb formed between the peripheral wall portion 12a of the inner cylinder 12 and the combustion cylinder 20 of the burner unit 13 is also affected by the air flow as described above based on the results of experiments and computer simulations. Is set as appropriate within the range in which can be exhibited.

As described above, in the exhaust gas heating device 10 of the first embodiment, the combustion cylinder 20 (cylinder body 13b) is around the burner 13a of the burner unit 13 provided in the outer cylinder so that fuel can be ejected into the combustion space in the fuel ejection direction. Covered by. Therefore, when a flame is formed from the burner 13a to the combustion space of the inner cylinder 12, the combustion cylinder 20 covers the flame forming range, so that the direct radiant heat from the flame is blocked by the combustion cylinder 20. As a result, it is possible to reduce the amount of radiant heat transferred directly from the flame of the burner 13a to the peripheral wall portion 12a (inner wall) of the inner cylinder 12, and the temperature rise of the inner cylinder 12 is suppressed. Further, since the exhaust gas taken in from the intake port 11f of the connecting portion 11d and injected from the exhaust gas injection pipe 19 flows through the inner cylinder 12, the inner cylinder 12 is also cooled by such exhaust gas. Therefore, it may not be necessary to provide the inner cylinder 12 with a refractory material (for example, castable) or the like, so that the weight can be reduced as compared with the case where the refractory material or the like is provided. Further, since the external dimensions of the inner cylinder 12 can be reduced by the thickness of the refractory material or the like, the size can be reduced.

In the exhaust gas heating device 10 described above, petroleum-based fuels such as light oil and heavy A oil have been exemplified as the fuel supplied from the fuel pipe 90. For example, gaseous fuel such as liquefied natural gas is supplied from the fuel pipe 90. It may be supplied to the exhaust gas heating device 10. 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, for example, by arranging the air injection nozzle 15d close to the peripheral wall portion 12a of the inner cylinder 12, the air flow is injected from the air injection nozzle 15d along the inner peripheral surface of the inner cylinder 12, thereby causing the inner circumference. The surface is covered with airflow. 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 of the inner cylinder 12 can also be reduced, so that the temperature of the inner peripheral surface of the inner cylinder 12 can be reduced. Can be further reduced. Further, the temperature of the inner peripheral surface of the inner cylinder 12 is further lowered by adopting a configuration in which the blowing capacity of the second blowing fan 3 is increased to increase the flow rate of the air injected from the air injection nozzles 15c and 15d. You can also.

Further, since the connection portions 11d and 11g of the exhaust gas heating device 10 are connected in the middle of the pipe 100 without changing the arrangement of the pipes with respect to the existing pipe 100 through which the exhaust gas of the diesel engine (external engine) flows, the existing pipe 100 is used. It will be possible to easily apply it 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], as disclosed in FIGS. 2 and 3 of the same document, the apparatus is concerned. It is necessary to change the arrangement of the existing piping (the same document; the flue 14) according to the shape of the (the same document; the burner portion 15), and the layout of the equipment and other pipes arranged in the surrounding space is changed. Can be forced. Along with this, maintenance work may become difficult. That is, the technique of Patent Document 3 has a problem that it is difficult to be familiar with retrofit.

Further, in the exhaust gas heating device 10 described above, after a part of the exhaust gas flowing from the upstream pipe 100a into the connection portion 11d is taken in from the inlet 11f, the exhaust gas injection pipe 19 to the inner cylinder 12 (combustion space) are taken through the exhaust gas duct 18. ), For example, the intake port 11f, the cover 17, the exhaust gas duct 18, and the exhaust gas injection pipe 19 are abolished, and the exhaust gas is ejected from the base end portion 12b side of the inner cylinder 12. You may adopt a configuration that does not occur. As a result, the configuration of the exhaust gas heating device is simplified, and the equipment cost can be reduced. Further, the weight of the exhaust gas heating device can be reduced because the intake port 11f, the cover 17, the exhaust gas duct 18, and the exhaust gas injection pipe 19 are not required.

[Second Embodiment]
Subsequently, a second 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. 7 to 14. Similar to the exhaust gas heating device 10 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 also has a plurality of burner units in the same manner as the exhaust gas heating device 10 of the first embodiment, but the furnace body is vertical and the blower fan is one. It differs from the exhaust gas heating device 10 of the first embodiment in that the exhaust gas injection pipe 19 is not provided. The same components as those of the exhaust gas heating device 10 of the first embodiment are designated by the same reference numerals to simplify the description.

As shown in FIGS. 7 to 12, the exhaust gas heating device 30 is mainly composed of an outer cylinder 31, an inner cylinder 32, a plurality of burner units 13', a first blower fan 2, and the like.

The outer cylinder 31 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 31 is opened so as to be surrounded by the annular base end portion 31b having an inwardly bent flange shape with respect to the peripheral wall portion 31a formed in a cylindrical shape, and the outer cylinder 31 is also opened. The other end side is also opened so as to be surrounded by an annular tip portion 31c having an inwardly bent flange shape. That is, both ends of the outer cylinder 31 are open. The base end portion 31b of the outer cylinder 31 is provided with a connecting portion 31d that extends cylindrically to the outside in the axial direction of the outer cylinder 31, and the tip portion 31c is also provided with a cylindrical shape to the outside in the axial direction of the outer cylinder 31. An extending connecting portion 31f is provided.

The connecting portions 31d and 31f are arranged so that their respective cylinder shafts L and M overlap (coaxially) with the cylinder shaft J of the outer cylinder 31, and flange portions 31e and 31g are formed at their respective tips. There is. The connecting portions 31d and 31f and the flange portions 31e and 31g, respectively, are set to have a shape specification that can be connected to the piping already provided in the ship. As a result, for example, with respect to the existing piping provided in the vertical direction (Z-axis direction of the coordinate system shown in each figure), the exhaust gas heating device 30 is installed in the middle of the piping without changing the position of the piping. The connecting portions 31d and 31g of the above can be connected.

In the second embodiment, the exhaust gas flows from the connecting portion 31d into the inner cylinder 32 in the outer cylinder 31 and flows out from the connecting portion 31f. That is, the exhaust gas flows in the direction from top to bottom (the direction of the arrow base of the Z axis of the coordinate system shown in each figure). Therefore, the connecting portion 31d on the upstream side of the exhaust gas is provided so as to project into the inside of the inner cylinder 32 described below, that is, into the combustion space. As a result, the inside of the downstream pipe of the pipe through which the exhaust gas flows and the air flow passage Ra, which will be described later, are configured so as not to communicate with each other. On the other hand, the base end of the connecting portion 31f on the downstream side of the exhaust gas is connected to the periphery of the opening of the tip portion 31c of the outer cylinder 31, and does not protrude into the combustion space of the inner cylinder 32.

In the exhaust gas heating device 30 of the second embodiment, as shown in FIGS. 10 and 12, a swivel blade portion 40 is provided in the connecting portion 31f on the downstream side of the exhaust gas. The swirling blade portion 40 includes a blade portion 41 capable of applying a swirling flow to a fluid by arranging a plurality of blades 42 in an annular shape, and a ring that holds the blade portion 41 in an annular shape and forms a space portion 45 inside. It is composed of a plate (holding portion) 43. The blade 42 is, for example, a rectangular flat plate, and is fixed to the ring plate 43 so as to be able to maintain a constant inclination of, for example, 10 to 20 degrees with respect to the cylinder axis J. The width of the blade 42 is set to be larger than the predetermined gap Sd described later in the state where the swivel blade 40 is attached to the connecting portion 31f, but when the width becomes larger than necessary, the space 45 Since the inner diameter of the swirl blade portion 40 becomes smaller, the pressure loss of the exhaust gas passing through the swirl blade portion 40 increases. Therefore, the width of the blade 42 is set so that the pressure loss of the exhaust gas passing through the space 45 does not exceed the maximum allowable value.

By configuring the swivel blade portion 40 in this way, the exhaust gas flowing from the combustion space around the cylinder shaft J center portion and the cylinder shaft J center portion of the inner cylinder 32 does not pass through the blade portion 41 and is not passed through the blade portion 41. Flows into the downstream pipe of the pipe. On the other hand, the exhaust gas flowing in the peripheral portion and the vicinity of the peripheral portion of the discharge portion 32e of the inner cylinder 32, which will be described later, flows through the blade portion 41 and flows into the downstream pipe of the pipe without passing through the space portion 45. .. Further, the air flow flowing from the air flow passage Ra through the gap portion Sd described later into the connecting portion 31f also flows through the blade portion 41 and flows into the downstream pipe of the pipe without passing through the space portion 45.

As a result, when both the exhaust gas flowing in the peripheral edge portion of the discharge portion 32e and the vicinity of the peripheral edge portion and the air flow flowing into the connecting portion 31f via the gap portion Sd pass through the blade portion 41, the exhaust gas is exhausted by the blade portion 42. A swirling flow is applied to the gas and air flow. Therefore, since such exhaust gas and air are mixed by swirling by the blade portion 41 and then flow into the downstream pipe, it is possible to suppress temperature unevenness of the exhaust gas in the downstream pipe. In particular, the discharge portion 32e of the inner cylinder 32 may be deformed due to deterioration or embrittlement due to heat, so that the flow rate balance should be maintained due to the deformation of the tip peripheral portion of the discharge portion 32e. When it becomes impossible to do so, the mixing of the exhaust gas and the air by the swivel blade portion 40 is effective in suppressing the temperature unevenness of the exhaust gas.

The inner cylinder 32 is a cylinder that is housed inside the outer cylinder 31 and forms a combustion space inside. The inner cylinder 32 is formed in a bottomed cylindrical shape like the outer cylinder 31. The inner cylinder 32 is opened so that one end side of the cylindrical peripheral wall portion 32a is surrounded by an annular base end portion 32b having an inwardly bent flange shape, and the other end side of the inner cylinder 32 is also inwardly bent. It is opened so as to be surrounded by a flange-shaped annular tip portion 32c. That is, both ends of the inner cylinder 32 are also open. A through hole 32d through which the connecting portion 31d of the outer cylinder 31 is inserted is formed in the base end portion 32b of the inner cylinder 32, and the tip portion 32c extends cylindrically outward in the axial direction of the inner cylinder 32. A discharge portion 32e that enters the connection portion 31f of the outer cylinder 31 is provided. The discharge portion 32e is set to an outer diameter dimension smaller than the inner diameter of the connection portion 31f of the outer cylinder 31, and a predetermined gap Sd is provided between the inner peripheral wall of the connection portion 31f and the outer peripheral wall of the discharge portion 32e. It is configured to be able to form.

By configuring the inner cylinder 32 in this way, an air flow passage Ra is formed between the outer cylinder 31 and the inner cylinder 32. The inner cylinder 32 of the second embodiment is provided with a plurality of ventilation holes 32f in the peripheral wall portion 32a. As shown in FIG. 10, in the second embodiment, for example, a plurality of ventilation holes 32f are arranged in a row at equal intervals and formed in an annular shape on the peripheral wall portion 32a in the circumferential direction. Further, the positions of forming the plurality of ventilation holes 32f with respect to the axial direction of the combustion cylinder 20 are set on the downstream side of the exhaust gas and in the vicinity of the tip portion 20b of the tip portion 20b of the combustion cylinder 20 of the burner unit 13. As a result, the inside of the inner cylinder 32, that is, the combustion space and the air flow passage Ra communicate with each other through these ventilation holes 32f. Therefore, as shown by the thick broken line shown in FIG. 11, a part of the air flow flowing through the air flow passage Ra can enter the combustion space via the ventilation hole 32f.

The base end portion 32b (inner cylinder base end plate 35) of the inner cylinder 32 is provided with a plurality of burner units 13'and a plurality of air injection nozzles 35c so as to surround the periphery of the connecting portion 31d. The inner cylinder base end plate 35 corresponding to the inner cylinder base end plate 15 of the first embodiment is a disk-shaped member, and forms a combustion space together with the peripheral wall portion 32a and the tip portion 32c of the inner cylinder 32. In the second embodiment, the inner cylinder base end plate 35 (base end portion 32b) is integrally formed with the peripheral wall portion 32a. An inner cylinder base end plate 35 may be formed separately from the peripheral wall portion 32a and fixed to the peripheral wall portion 32a by a fixed structure (not shown).

The exhaust gas heating device 30 of the second embodiment does not include the exhaust gas injection pipe 19, and the connecting portion 31d penetrates the inner cylinder base end plate 35. Therefore, a through hole 32d is formed in the central portion of the inner cylinder base end plate 35, and the combustion space side is formed on the circumference concentric with the inner cylinder base end plate 35 so as to surround the circumference of the through hole 32d. A plurality of air injection nozzles 35c protruding toward the surface are formed. In the second embodiment, the air injection nozzles 35c are formed at six locations. The six air injection nozzles 35c are arranged at equal intervals on the circumference, and six combustion cylinder through ports 35a are provided so as to be sandwiched between the air injection nozzles 35c on the same circumference. The combustion cylinder 20 is inserted through the combustion cylinder through port 35a.

That is, as shown in FIG. 9, six air injection nozzles 35c and six burner units 13'are alternately arranged on the circumference surrounding the through hole 32d at a central angle of 30 degrees of the inner cylinder base end plate 35. Has been done. Further, the burner unit 13'is arranged at a position separated from the peripheral wall portion 32a of the inner cylinder 32 by a predetermined gap Sb. As a result, the burner unit 13'is cooled by the air flow injected from the air injection nozzle 35c, and the peripheral wall portion 32a of the inner cylinder 32 can also be cooled.

The number of the air injection nozzles 35c 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 injection nozzle 35c and the burner unit 13'do not need to be provided at equal intervals. Since the inner space of these air injection nozzles 35c communicates with the air flow passage Ra, the air that is pressure-fed from the first blower fan 2 and flows into the air flow passage Ra from the intake port 31i is shown in FIG. 11, for example. As shown by the broken line arrow, the air is injected into the internal space of the peripheral wall portion 32a, that is, the combustion space via the air injection nozzle 35c. It is also injected into the combustion space via the ventilation hole 32f of the peripheral wall portion 32a.

The burner unit 13'is configured in substantially the same manner as the burner unit 13 of the first embodiment, and the contents described for each in the first embodiment can be quoted substantially. As shown in FIG. 10, in the combustion cylinder 20, which is the cylinder body 13b of the burner unit 13', the combustion cylinder 20 and its tip portion 20b are connected to the connecting portion 31d (upstream side of the pipe) and the connecting portion 31f (downstream side of the pipe). ) Is arranged so as to be located outside the range of the virtual path Rv that connects with the shortest distance. This is to prevent the combustion cylinder 20 and the tip portion 20b from becoming a resistance to the exhaust gas flowing through the combustion space, thereby suppressing an increase in the pressure loss of the exhaust gas. In addition, in FIG. 10, the two burner units 13'that appear to exist in the virtual path Rv are actually arranged in the direction of the arrow tip of the Y axis of the same figure coordinate system from the virtual path Rv. Please note.

Further, the combustion cylinder 20 is formed with a plurality of ventilation holes 22 at the base end portion 20a. Also in the burner unit 13'of the second embodiment, the base end 20a and the plate so that the base end 20a of the combustion cylinder 20 does not come into direct contact with the plate 13c of the burner unit 13'and the connection portion 31d of the outer cylinder 31. The burner unit 13'is configured to be attachable to the outer cylinder 31 so that a gap Sc can be formed between the 13c and the connecting portion 31d. However, since the gap Sc is narrower than the gap Sa of the first embodiment, it is necessary to increase the amount of air that flows into the combustion cylinder 20 and contributes to combustion. Therefore, the combustion cylinder 20 has a plurality of ventilation holes 22. Is provided.

Further, also in the burner unit 13'of the second embodiment, as shown in FIG. 10, the six burner units 13 are oriented so that the opening of the tip portion 20b of the combustion cylinder 20 faces in the cylinder axis J direction of the inner cylinder 32. 'Is placed. As a result, the short portion side of the cylinder wall of the combustion cylinder 20 having a small axial length faces the cylinder axis J direction of the inner cylinder 32, and the long portion side of the cylinder wall of the combustion cylinder 20 having a large axial length faces the inner cylinder 32. It faces the direction of the peripheral wall portion 32a. Therefore, the direct radiant heat or the like from the flame of the burner 13a can reduce the amount of radiant heat transferred toward the peripheral wall portion 32a of the inner cylinder 32 by the long portion side of the combustion cylinder 20, and the inner cylinder 32 can be reduced. The rise in temperature can be suppressed.

Further, the high-temperature combustion gas generated by the combustion of fuel by the flame of the burner 13a is released from the cylinder in a shorter distance when flowing near the short portion (short portion side) than on the long portion side of the combustion cylinder 20. Then, it goes toward the center side of the inner cylinder (thin broken line arrow in the combustion cylinder 20 shown in FIG. 11). Therefore, the combustion gas flowing near the center of the combustion cylinder 20 or near the long portion (long portion side) can be drawn into the cylinder shaft J (center side) of the inner cylinder 32 (combustion cylinder 20 shown in FIG. 11). Fine one-dot chain arrow and thin two-dot chain arrow). As a result, the high-temperature combustion gas can be collected on the cylinder axis J side rather than on the peripheral wall portion 32a side of the inner cylinder 32, so that the temperature rise of the inner cylinder 32 can be further suppressed.

Further, in the second embodiment, as described above, the air that has been pressure-fed from the first blower fan 2 and has flowed into the air flow passage Ra from the intake port 31i passes through, for example, the ventilation hole 32f of the peripheral wall portion 32a. It is also injected into the combustion space (dashed arrow shown in FIG. 11). More specifically, an air flow is injected in the direction of the cylinder axis J of the inner cylinder 32 in the vicinity of the exhaust gas downstream side of the tip portion 20b of the combustion cylinder 20. Therefore, the high-temperature gas discharged from the combustion cylinder 20 can be pushed out in the direction of the cylinder axis J of the inner cylinder 32 by the air flow injected from the ventilation hole 32f. As a result, the high-temperature combustion gas can be more efficiently collected on the cylinder shaft J side, so that the temperature rise of the inner cylinder 32 can be further suppressed. Therefore, it is not necessary to provide a refractory material such as a castable on the inner wall of the inner cylinder 32, and the weight of the exhaust gas heating device 30 (the furnace body) can be reduced.

The first blower fan 2 and the first intake port 4 are configured in substantially the same manner as in the case of the first embodiment described above. Therefore, with respect to these configurations, the contents described for each of the first embodiments can be almost quoted. The air pumped from the first blower fan 2 is sent to the intake port 31i of the outer cylinder 31 via the first intake duct 6. As a result, the air flowing into the air flow passage Ra from the intake port 31i comes into contact with the outer surface of the inner cylinder 32, so that the inner cylinder 32 can be air-cooled. Although not shown, the exhaust gas heating device 30 is also provided on the base frame.

As described above, in the exhaust gas heating device 30 of the second embodiment, the furnace body (outer cylinder 31 and inner cylinder) so that the cylinder axis J of the inner cylinder 32 rises in the vertical direction (Z-axis direction of the coordinate system shown in each figure). 32). Further, by providing the burner unit 13 at the upper end of the furnace body, a flame is formed downward (in the direction of gravity) from the burner portion 13a. As a result, the width of the exhaust gas heating device 30 is smaller than that in the case where the furnace body is arranged sideways (in the direction of expansion of the XY plane in the coordinate system shown in each figure) as in the exhaust gas heating device 10 of the first embodiment. It becomes possible to do. That is, the size of the furnace body can be reduced.

Therefore, the exhaust gas heating device 30 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 pipes through which the exhaust gas discharged from the diesel engine (external engine) flows are laid out (arranged) in the vertical direction, the exhaust gas heating device 30 is interposed in the middle of such existing pipes. 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. Further, in the exhaust gas heating device 30, one blower fan is sufficient as the furnace body is miniaturized. Therefore, as compared with the exhaust gas heating device 10 of the first embodiment, the number of required blower fans is reduced by one, so that the weight of the furnace body can be further reduced and the weight of the exhaust gas heating device 30 can be further reduced.

The exhaust gas heating device 30 of the second embodiment may be placed horizontally. That is, the furnace body (outer cylinder 31 and inner cylinder 32) so that the cylinder axis J of the inner cylinder 32 is substantially parallel to the floor surface of the installation location (in the X-axis or Y-axis direction of the coordinate system shown in each figure). ) May be placed horizontally. As a result, the exhaust gas flows along the cylinder axis J direction of the furnace body (outer cylinder 31 and inner cylinder 32), so that the length (axis) in the cylinder axis J direction is compared with that of the exhaust gas heating device 10 of the first embodiment. Long) is small. Therefore, the floor area required for installation is smaller than that of the exhaust gas heating device 10 of the first embodiment even if it is placed horizontally.

If the configuration of the swivel blade portion 40 described above is grasped as a creation of a technical idea, it can be expressed as follows. The swivel blade portion 40 is an example of the following "swivel blade device", and the inner space of the connecting portion 31f is an example of the following "outer cylinder inner space". Further, the ring plate 43 is an example of the following "holding portion", and the discharge portion 32e is an example of the following "downstream end portion of the inner cylinder". The air flow passage Ra is an example of the following "air flow space".

"While forming a combustion space inside, the exhaust gas discharged from the upstream side of the pipe through which the exhaust gas of the external engine flows can flow into the downstream side of the pipe via the combustion space. An inner cylinder that communicates with the upstream side and the downstream side of the pipe, respectively.
An outer cylinder that covers the inner cylinder and forms an air circulation space in which air sent from the outside can flow between the inner cylinder and the inner cylinder.
A burner that penetrates the inner cylinder and is provided so as to be able to supply fuel into the combustion space is provided.
The inner cylinder located on the downstream side of the exhaust gas has an outer cylinder inner space for communicating the downstream side of the pipe and the combustion space at the downstream end of the outer cylinder located on the downstream side of the exhaust gas. A swivel vane provided in a combustion device in which a gap portion connecting the air flow space and the outer cylinder inner space is formed between the downstream end of the cylinder and the downstream end of the outer cylinder. It ’s a device,
A blade portion in which a plurality of blades capable of giving a swirling flow to a fluid are arranged in a ring shape
A holding portion that holds the plurality of blades in an annular shape and forms a space portion inside is provided.
The swivel blade device is provided in the space inside the outer cylinder.
The exhaust gas flowing from the combustion space around the shaft center portion of the downstream end portion of the inner cylinder and the shaft center portion flows through the space portion and flows into the downstream side of the pipe.
The exhaust gas flowing from the combustion space to the peripheral edge portion of the downstream end portion of the inner cylinder and the vicinity of the peripheral edge portion, and the air flowing from the air flow space to the outer cylinder inner space through the gap portion. Is a swivel blade device characterized in that the blade portion flows through the blade portion and flows into the downstream side of the pipe. "

<Modification 1 of the second embodiment>
As a modification 1 of the exhaust gas heating device 30, for example, as shown in FIGS. 13 and 14, the burner unit 13'is provided so that the tip portion 20b of the combustion cylinder 20 faces obliquely in the direction of the cylinder axis J of the inner cylinder 32. A configuration may be adopted in which the outer cylinder 31 is attached. As a result, the high-temperature combustion gas generated by burning the fuel with the flame of the burner 13a can be discharged from the combustion cylinder 20 in the direction of the exhaust gas flowing through the virtual path Rv, so that the high-temperature combustion gas and the exhaust gas can be discharged. It becomes possible to efficiently promote mixing with. The same components as those of the exhaust gas heating device 30 described above are designated by the same reference numerals, and the description thereof will be omitted. Note that FIG. 13 is a schematic cross-sectional view corresponding to FIG.

As shown in FIGS. 13 and 14, in the modification 1 of the exhaust gas heating device 30, tapered portions 51a and 52a are provided in the outer cylinder 51 and the inner cylinder 52, respectively. More specifically, a tapered portion 51a is provided between the base end portion 31b of the outer cylinder 51 and the peripheral wall portion 31a, and a tapered portion 52a is provided between the base end portion 32b of the inner cylinder 52 and the peripheral wall portion 32a. .. Then, the burner unit 13'is fixed to the tapered portion 51a of the outer cylinder 51 via the flange portion 24. A combustion cylinder through port 52b is formed in the tapered portion 52a, and by inserting the combustion cylinder 20 through the combustion cylinder through port 52b, the combustion cylinder is oblique to the cylinder axis J of the inner cylinder 52. 20 protrudes into the combustion space.

In the first modification of the second embodiment, the inclination angles of the tapered portions 51a and 52a and the angle of the oblique opening of the tip portion 20b of the combustion cylinder 20 are matched. As a result, by fixing the burner unit 13'almost perpendicularly (perpendicularly) to the tapered portion 51a of the outer cylinder 51, as shown in FIG. 13, the contour line of the opening surface of the combustion cylinder 20 that opens diagonally , The boundary line (two-dot chain line) of the virtual path Rv can be arranged substantially parallel or on the same line. In the modified example 1 of the second embodiment, the tip portion 20b of the combustion cylinder 20 is outside the range of the virtual path Rv so as not to be within the range of the virtual path Rv connecting the upstream pipe and the downstream pipe at the shortest distance. It is positioned. As a result, the cylinder body 13b (combustion cylinder 20) is unlikely to become a resistance to the flow of exhaust gas from the upstream pipe to the downstream pipe, so that an increase in pressure loss of exhaust gas flowing through the combustion space and piping can be suppressed. Can be done.

As described above, in the first modification of the second embodiment, the tip portion 20b of the combustion cylinder 20 is projected into the combustion space so as to be oblique to the cylinder axis J of the inner cylinder 52. That is, the tip portion 20b is directed toward the inside of the combustion space. As a result, the high-temperature combustion gas can be discharged from the combustion cylinder 20 in the direction of the exhaust gas flowing through the virtual path Rv, so that the mixing of the high-temperature combustion gas and the exhaust gas can be efficiently promoted. Further, the high-temperature combustion gas is discharged from the combustion cylinder 20 in a direction away from the peripheral wall portion 32a of the inner cylinder 52. On the other hand, exhaust gas having a temperature lower than that of the high-temperature combustion gas flows through the virtual path Rv. Therefore, the peripheral wall portion 32a is easily cooled.

<Modification 2 of the second embodiment>
Further, as a modification 2 of the exhaust gas heating device 30, for example, as shown in FIGS. 15 to 17, a burner unit 13 "in which the baffle device 26 is provided inside the combustion cylinder 20 is provided by the tip portion 20b of the combustion cylinder 20. A configuration may be adopted in which the combustion cylinder 20 is attached to the outer cylinder 31 so that the inner cylinder 32 faces in the direction of the cylinder axis J and a part of the combustion cylinder 20 is within the range of the virtual path Rv. Although the cylinder body 13b (combustion cylinder 20) acts as a resistance to the flow of exhaust gas toward the downstream pipe, the baffle device 26 provided in the combustion cylinder 20 can create a large number of vortex flows of combustion gas having a small vortex. It is possible to efficiently promote the mixing of the high-temperature combustion gas and the exhaust gas. The components substantially the same as those of the exhaust gas heating device 30 described above are designated by the same reference numerals and the description thereof will be omitted. Note that FIG. 15 is a schematic cross-sectional view corresponding to FIG. 10, but the flow of the exhaust gas is in the opposite direction (direction from bottom to top (direction of the tip of the arrow on the Z axis of the coordinate system shown in the figure)). ) Please note that it is.

As shown in FIGS. 15 to 17, in the second modification of the exhaust gas heating device 30, the burner unit 13 ”is fixed to the peripheral wall portion 31a of the outer cylinder 31 via the flange portion 24. 32 g of a combustion cylinder through port is formed in the above, and by inserting the combustion cylinder 20 through the combustion cylinder through port 32 g, the combustion cylinder 20 is burned so as to be orthogonal to the cylinder axis J of the inner cylinder 32. The combustion cylinder 20 of the burner unit 13 "protrudes into the space, so that the tip portion 20b and the like of the combustion cylinder 20 are arranged within the range of the virtual path Rv, and the exhaust gas heating device 30 described above (see FIG. 10). The outer diameters of the inner cylinder 32 and the outer cylinder 31 can be made smaller than those in the case of or the modified example 1 (see FIG. 13). Further, the combustion cylinder 20 is provided in the combustion space so that the long portion side having a large axial length of the cylinder wall faces the exhaust gas upstream direction (the short portion side having a small axial length of the cylinder wall faces the exhaust gas downstream direction). Make it stick out. As a result, as will be described next, the vortex flow generated from the baffle device 26 is made less likely to collapse due to the flow of the exhaust gas. In the second modification, the length of the combustion cylinder 20 is set so that the tip portion 20b reaches the cylinder shaft J of the inner cylinder 32. However, as will be described later, the length of the combustion cylinder 20 is set. May have variations.

Further, in the second modification of the second embodiment, the baffle device 26 is provided in the combustion cylinder 20. As shown in FIG. 16, the baffle device 26 has two strip-shaped plates 26a combined in a cross shape in the combustion cylinder 20, and a circular plate-shaped plate 26a lying down at the intersection of these two plates 26a. It is composed of a cover 26b. The outer diameter of the cover 26b is set to, for example, 1/3 (1/3) or more and 1/5 (1/5) or less of the inner diameter of the combustion cylinder 20. The cover 26b is provided to prevent the flame from coming out of the combustion cylinder 20. By configuring the baffle device 26 in this way, for example, as shown in FIG. 17A, the high-temperature combustion gas generated by burning the fuel with the flame of the burner 13a passes through the baffle device 26. As a result, it becomes a vortex of combustion gas with a small vortex and is discharged in the direction of the tip portion 20b (vortex flow represented by a broken line in FIG. 17 (A)).

As a result, the vortex flow of the combustion gas having a small vortex is discharged from the combustion cylinder 20 while entraining the exhaust gas flowing around the vortex. When the baffle device 26 is not provided, a vortex flow of the combustion gas having a larger vortex than the vortex flow of the combustion gas is generated. Therefore, in the second modification of the second embodiment, the baffle device 26 is provided. It is possible to efficiently mix the combustion gas and the exhaust gas as compared with the case where the combustion gas and the exhaust gas are not used. Further, in the second modification of the second embodiment, the combustion cylinder 20 projects into the combustion space so that the long portion side thereof faces the exhaust gas upstream direction (the short portion side faces the exhaust gas downstream direction), so that the exhaust gas is exhausted. The long side in the upstream direction protects the vortex of combustion gas from the flow of exhaust gas. As a result, the vortex flow of the combustion gas is less affected by the flow of the exhaust gas, so that the vortex flow generated on the long portion side of the combustion cylinder 20 can have a longer duration.

Further, in the burner unit 13 ”, the combustion cylinder 20 is intentionally positioned within the range of the virtual path Rv, and the long portion side of the combustion cylinder 20 is in the upstream direction of the exhaust gas (the short portion side of the combustion cylinder 20 is in the downstream direction of the exhaust gas). ), The combustion cylinder 20 is projected into the combustion space. Therefore, as shown in FIG. 17 (B), the exhaust gas in the virtual path Rv is from the long portion side to the short portion of the combustion cylinder 20. It flows while forming a vortex so as to wrap around to the side. As a result, an exhaust gas vortex is formed on the outside of the combustion cylinder 20 (particularly on the outside of the short portion side of the combustion cylinder 20). The combustion gas and the exhaust gas can also be mixed by the vortex flow. Further, by intersecting the vortex of the exhaust gas with the vortex of the combustion gas generated by the baffle device 26, a more complicated vortex flow is formed, so that the combustion gas And exhaust gas can be mixed more effectively.

<Modification 3 of the second embodiment>
Further, as a modification 3 of the exhaust gas heating device 30, as shown in FIGS. 18 to 20, instead of the combustion cylinder 20 as described above, a cylindrical half in the radial direction is cut into a half moon shape at the tip portion 120b. A configuration may be adopted in which the missing combustion cylinder 120 is used. The same components as those of the modification 2 of the exhaust gas heating device 30 described above are designated by the same reference numerals, and the description thereof will be omitted. Note that FIG. 18 is a schematic cross-sectional view corresponding to FIG.

As shown in FIGS. 18 to 20, in the modified example 3 of the exhaust gas heating device 30, the cylinder wall near the tip portion 120b of the combustion cylinder 120 is cut out in a semi-cylindrical shape by half in the radial direction. Hereinafter, the shape of such a notch portion 121 is referred to as a "half-split shape". As a result, the length of the cylinder wall in the vicinity of the tip portion 120b of the combustion cylinder 120 is discontinuously (rapidly) switched from the large long wall portion 122 to the small short wall portion 123. That is, there is no tubular wall in the half-split short wall portion 123.

Therefore, as shown in FIG. 19B, the long wall portion 122 to the short wall of the combustion cylinder 120 is compared with the case of the above-mentioned modification 2 in which the length of the cylinder wall in the vicinity of the tip portion 20b continuously changes. The vortex of the exhaust gas formed by the exhaust gas flowing around the portion 123 penetrates into the inside of the combustion cylinder 120 (the vortex shown by the broken line in the figure). As a result, the vortex flow of the combustion gas having a small vortex generated from the baffle device 26 in the combustion cylinder 120 is easily affected by the vortex flow of the exhaust gas that enters the inside of the combustion cylinder 120. That is, as shown in FIG. 19A, the vortex flow of the combustion gas having a small vortex tends to collapse in the short wall portion 123 having a half-split shape.

On the other hand, in the half-split long wall portion 122, a tubular wall exists up to the tip portion 120b. Therefore, the vortex of the exhaust gas formed by the exhaust gas flowing from the long wall portion 122 of the combustion cylinder 120 to the short wall portion 123 does not enter the inside of the long wall portion 122. As a result, the vortex flow of the combustion gas having a small vortex generated from the baffle device 26 in the combustion cylinder 120 is protected by the half-split long wall portion 122, so that it is not easily affected by the vortex flow of the exhaust gas. That is, in the half-split long wall portion 122, a vortex flow of combustion gas having a small vortex is likely to remain as compared with the case of the modified example 2 of the exhaust gas heating device 30 (see FIG. 19 (A)).

By adopting the configuration of the modified example 3 in this way, the duration of the vortex flow of the combustion gas having a small vortex generated from the baffle device 26 can be made longer than that of the modified example 2 of the exhaust gas heating device 30. In addition, it becomes possible to increase the vortex flow of the combustion gas having a small vortex. It should be noted that the longer the axial length of the half-split long wall portion 122, the more the vortex flow of the combustion gas having such a small vortex can be increased, but at the same time, it also causes the pressure loss of the exhaust gas. Can be connected. Therefore, the axial length of the half-split long wall portion 122 is determined by the comparative consideration between the mixing efficiency of the combustion gas and the exhaust gas and the pressure loss of the exhaust gas. Further, the axial length of the half-split long wall portion 122 can also be determined based on the results of experiments and computer simulations.

Further, as an application example of the modification 3, the burner units 13 having different lengths of the combustion cylinder 20 and the combustion cylinder 120 may be arranged in the order of the combustion cylinders 20 and 120 from the exhaust gas upstream side to the exhaust gas downstream side. For example, as shown in FIG. 20, when burner units 13X and 13Z having different lengths of the combustion cylinders 20 are provided with respect to the burner units 13 "(13Y) of the above-mentioned modification 2, the longest combustion cylinder 20x The burner unit 13X including the above is arranged on the upstream side of the exhaust gas, the burner unit 13Z having the shortest combustion cylinder 20z is arranged on the downstream side of the exhaust gas, and the burner unit 13Y (13 ") is arranged at an intermediate position between them. These 13X, 13Y, and 13Z are arranged on a straight line along the cylinder axis J of the inner cylinder 32.

In this way, the length of the combustion cylinder 20 becomes longer toward the upstream side of the exhaust gas, and the length of the combustion cylinder 20 becomes shorter toward the downstream side of the exhaust gas. This is because the flow of the combustion gas discharged from the combustion cylinder 20x of the burner unit 13X located on the upstream side of the exhaust gas is not obstructed by the burner units 13Y and 13Z located on the downstream side.

As a result, since the burner unit 13X includes the longest combustion cylinder 20x, the combustion gas and the exhaust gas and the exhaust gas in the vicinity of the peripheral wall portion 32a located in the direction of the tip of the X-axis arrow in the coordinate system among the peripheral wall portions 32a of the inner cylinder 32. Mix with gas. On the other hand, since the burner unit 13Z includes the shortest combustion cylinder 20z, the combustion gas is located in the vicinity of the peripheral wall portion 32a located in the direction of the base of the X-axis arrow in the coordinate system among the peripheral wall portions 32a of the inner cylinder 32. And the exhaust gas are mixed. Further, the burner unit 13 Y including the combustion cylinder 20y set to the length between the combustion cylinder 20x and the combustion cylinder 20z mixes the combustion gas and the exhaust gas in the vicinity of the cylinder shaft J. Therefore, by using the burner units 13X, 13Y, and 13Z having variations in the length of the combustion cylinder 20, it becomes possible to efficiently mix the combustion gas and the exhaust gas in the combustion space of the inner cylinder 32.

[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. Similar to the exhaust gas heating device 10 of the first embodiment and the exhaust gas heating device 30 of the second embodiment, the exhaust gas heating device 130 of the third embodiment also has, for example, a pipe 100 through which the exhaust gas of a 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.

The second embodiment of the exhaust gas heating device 130 has a plurality of burner units, a vertical furnace body, one blower fan, and no exhaust gas injection pipe 19. It is common with the exhaust gas heating device 30 of. However, it differs from the exhaust gas heating device 30 of the second embodiment in that the fuel ejection direction of the burner 13a is opposite to the direction in which the exhaust gas flows, and that the exhaust cylinder 133 is provided on the downstream side of the exhaust gas. The same components as those of the exhaust gas heating device 30 of the second embodiment are designated by the same reference numerals, and the description thereof will be omitted.

As shown in FIGS. 21 to 24, the exhaust gas heating device 130 is mainly composed of an outer cylinder 31, an inner cylinder 132, a plurality of burner units 113, a first blower fan 2, and the like.

In the third embodiment, the exhaust gas flows from the connecting portion 31f into the inner cylinder 132 in the outer cylinder 31 and flows out from the connecting portion 31d. That is, the upstream pipe 100a is connected to the flange portion 31g of the connecting portion 31f, the downstream pipe 100b is connected to the flange portion 31e of the connecting portion 31d, and the directions from below the paper surface to above the paper surface in FIGS. Exhaust gas flows in the direction of the tip of the arrow on the Z axis of the coordinate system shown in. Therefore, on the downstream side of the exhaust gas, a discharge cylinder 133, which will be described later, is provided so as to project from the inside of the inner cylinder 132 into the connecting portion 31d. As a result, the inside of the downstream pipe of the pipe through which the exhaust gas flows and the air flow passage Ra, which will be described later, are configured so as not to communicate with each other. On the other hand, the base end of the connecting portion 31f on the upstream side of the exhaust gas is connected to the periphery of the opening of the tip portion 31c of the outer cylinder 31, and does not protrude into the inner cylinder 132.

The inner cylinder 132 is a cylinder that is housed inside the outer cylinder 31 and forms a combustion space inside. The inner cylinder 132 is formed in a bottomed cylindrical shape like the outer cylinder 31. The inner cylinder 132 is opened so that one end side of the cylindrical peripheral wall portion 32a is surrounded by an annular base end portion 32b having an inwardly bent flange shape, and the other end side of the inner cylinder 132 is a tapered portion 132a. It is opened so as to be surrounded by an annular tip portion 32c having an inwardly bent flange shape. That is, the inner cylinder 132 is provided with a tapered portion 132a in which both ends are open and the connecting portion between the peripheral wall portion 32a and the tip portion 32c is chamfered on the entire circumference. Further, a through hole 32d through which the discharge cylinder 133 is inserted is formed in the base end portion 32b of the inner cylinder 132. By configuring the inner cylinder 132 in this way, an air flow passage Ra is formed between the outer cylinder 31 and the inner cylinder 132.

The discharge cylinder 133 is a cylinder formed in a cylindrical shape having a diameter smaller than the inner diameter of the connecting portion 31d connected to the downstream pipe 100b, and is made of a steel plate. The discharge cylinder 133 has neither a bottom nor a lid, and its axial length is set to, for example, 50% or more and 80% or less of the axial length of the inner cylinder 132. In the third embodiment, the discharge end 133a side of the discharge cylinder 133 penetrates the through hole 32d of the base end portion 32b of the inner cylinder 132, and the cylinder shaft N overlaps with the cylinder shaft J of the inner cylinder 132 (coaxial). It is arranged so as to become). Then, the discharge cylinder 133 is the base end portion 31b of the outer cylinder 31 (or the base end portion of the inner cylinder 132) so that the discharge end 133a is located in the connection portion 31d and the introduction end 133b is located in the inner cylinder 132. It is fixed to 32b) by the fixed structure shown in the figure. As a result, in the third embodiment, the introduction end 133b of the discharge cylinder 133 is located near the center of the inner cylinder 132 in the J-direction of the cylinder axis. A gap Se communicating with the air flow passage Ra is formed between the connecting portion 31d and the discharge cylinder 133.

The base end portion 32b (inner cylinder base end plate 35) of the inner cylinder 132 is provided with a plurality of burner units 113 and a plurality of air injection nozzles 35d so as to surround the periphery of the discharge cylinder 133. The inner cylinder base end plate 35 corresponding to the inner cylinder base end plate 15 of the first embodiment is a disk-shaped member, and forms a combustion space together with the peripheral wall portion 32a and the tip portion 32c of the inner cylinder 132. In the third embodiment, the inner cylinder base end plate 35 (base end portion 32b) is integrally formed with the peripheral wall portion 32a. An inner cylinder base end plate 35 may be formed separately from the peripheral wall portion 32a and fixed to the peripheral wall portion 32a by a fixed structure (not shown).

The exhaust gas heating device 130 of the third embodiment is on the combustion space side on the circumference concentric with the inner cylinder base end plate 35 so as to surround the circumference of the through hole 32d through which the discharge cylinder 133 penetrates, that is, the circumference of the discharge cylinder 133. A plurality of air injection nozzles 35d projecting toward the combustion space are formed, and a plurality of air injection nozzles 35e projecting toward the combustion space side are formed on the circumference of concentric circles surrounding the periphery of these air injection nozzles 35d. In the third embodiment, the air injection nozzles 35d and 35e are formed at six locations. The six air injection nozzles 35d are arranged at equal intervals on the circumference, and six combustion cylinder through ports 35a provided at the same equal intervals on the circumference having a diameter larger than the circumference are sandwiched in the radial direction. As described above, six air injection nozzles 35e are arranged at the same equal intervals on the circumference having a larger diameter.

That is, the air injection nozzles 35d and 35e and the combustion cylinder through port 35a are provided on the circumferences having different diameters, for example, at intervals of 60 degrees at the central angle of the inner cylinder base end plate 35. The combustion cylinder 20 is inserted through the combustion cylinder through port 35a. As a result, the burner unit 113 is cooled by the air flow injected from the air injection nozzles 35d and 35e, and the peripheral wall portion 32a of the inner cylinder 132 can also be cooled by the air flow injected from the air injection nozzle 35e. Like the air injection nozzle 35c of the second embodiment, the air injection nozzles are six air injection nozzles 35d on the circumference surrounding the through hole 32d at a central angle of 30 degrees of the inner cylinder base end plate 35. (Or the air injection nozzle 35e) and the six burner units 113 may be arranged alternately.

The quantities of the air injection nozzles 35d and 35e are examples, and are appropriately set within a range in which the effects of the air flow and the exhaust gas flow can be exhibited. Further, the air injection nozzles 35d and 35e and the burner unit 113 do not need to be provided at equal intervals. Since the inner space of these air injection nozzles 35d and 35e communicates with the air flow passage Ra, the air that is pressure-fed from the first blower fan 2 and flows into the air flow passage Ra from the intake port 31i is, for example, FIG. 24. As shown by the broken arrow, the air is injected into the internal space of the peripheral wall portion 32a, that is, the combustion space via the air injection nozzles 35d and 35e.

The burner unit 113 is the same as the burner unit 13'of the second embodiment except that the fuel ejection direction of the burner 13a is opposite to the direction in which the exhaust gas flows and the length of the cylinder is different. It is configured. That is, as shown in FIGS. 24 and 25, the combustion cylinder 20, which is the cylinder 113b of the burner unit 113, has the tip 20b located closer to the tip 32c than the center of the inner cylinder 132 in the J-direction. The axial length of the combustion cylinder 20 is set to. More specifically, the cylinder 113b has a length such that the flame of the burner 13a does not go out from the tip 20b of the combustion cylinder 20, and the tip 20b opens beyond the introduction end 133b of the discharge cylinder 133. Moreover, the length is set before the tip portion 20b reaches the position of the tapered portion 132a of the inner cylinder 132.

Also in the burner unit 113 of the third embodiment, the six burner units 113 are arranged so that the opening of the tip portion 20b of the combustion cylinder 20 faces in the cylinder axis J direction of the inner cylinder 132. As a result, the short portion side of the cylinder wall of the combustion cylinder 20 having a small axial length faces the cylinder axis J direction of the inner cylinder 132, and the long portion side of the cylinder wall of the combustion cylinder 20 having a large axial length faces the inner cylinder 132. It faces the direction of the peripheral wall portion 32a. Therefore, the direct radiant heat from the flame of the burner 13a can reduce the amount of radiant heat transferred toward the peripheral wall portion 32a of the inner cylinder 132 by the long portion side of the combustion cylinder 20, and the inner cylinder 132 can be reduced. The rise in temperature can be suppressed.

As shown in FIG. 25, the high-temperature combustion gas generated by the combustion of fuel by the flame of the burner 13a flows in the vicinity of the short portion (short portion side) rather than the long portion side of the combustion cylinder 20 for a shorter distance. Is released from the cylinder and heads toward the center of the inner cylinder (thin dashed arrow in the figure). Therefore, it is possible to draw the combustion gas flowing near the center of the combustion cylinder 20 or the vicinity of the long portion (long portion side) to the tubular shaft J (center side) of the inner cylinder 132 (the fine alternate long and short dash arrow in the figure). And fine alternate long and short dash arrow). As a result, the high-temperature combustion gas can be collected on the cylinder axis J side rather than on the peripheral wall portion 32a side of the inner cylinder 132, so that the temperature rise of the inner cylinder 132 can be further suppressed.

In the third embodiment, as described above, the tip portion 20b of the combustion cylinder 20 (cylinder body 113b) is located on the tip portion 32c side of the center of the inner cylinder 132 in the cylinder axis J direction. Therefore, the exhaust gas flowing into the inner cylinder 132 from the connection portion 31f (thick solid line arrow in FIG. 25) is the combustion gas released from the burner 13a on the exhaust gas upstream side of the inner cylinder 132 (thin broken line arrow in FIG. It is mixed with the chain line arrow and the fine two-dot chain line arrow). As a result, as compared with the exhaust gas heating device 30 of the second embodiment in which the flow of radiant heat and the like and the flow of the combustion gas and the flow of the exhaust gas are in the same direction, the vertical component in the traveling direction of the combustion gas released from the burner 13a and the vertical component in the traveling direction are generated. The vertical component in the traveling direction of the exhaust gas is opposite to that in the opposite direction. Therefore, since the convection mixing generated by the collision of the combustion gas and the exhaust gas is promoted, the distance required for mixing is shortened, and the combustion gas and the exhaust gas can be efficiently mixed (second embodiment). When the flow of the combustion gas and the flow of the exhaust gas are in the same direction as in the exhaust gas heating device 30 of the above, the distance required for mixing the two gases becomes long). Therefore, since the degree of uniformity of the temperature of the exhaust gas is increased, it is possible to suppress the temperature unevenness of the exhaust gas. Further, as compared with the exhaust gas heating device 30 of the second embodiment, the space required for mixing the combustion gas and the exhaust gas can be narrowed, so that the inner cylinder 132 can be made compact, and eventually the furnace body ( The size of the outer cylinder 31 and the inner cylinder 132) and the exhaust gas heating device 130 can be reduced.

Further, in the present invention of the third embodiment, an exhaust cylinder 133 having an inner diameter smaller than the inner diameter of the connecting portion 31d of the outer cylinder 31 is provided on the downstream side of the exhaust gas in the inner cylinder 132 so as to communicate with the downstream pipe 100b. Has been done. As a result, on the downstream side of the exhaust gas, low-temperature air injected from the air injection nozzles 35d and 35e (particularly the air injection nozzle 35d) to cool the inner cylinder 132 is prevented from flowing into the downstream pipe 100b. Therefore, it is possible to prevent the temperature of the exhaust gas flowing in the vicinity of the downstream side of the exhaust gas in the inner cylinder 132 from being lowered by the low-temperature air injected from the air injection nozzles 35d and 35e (particularly the air injection nozzle 35d). .. Further, the exhaust cylinder 133 collects a larger amount of exhaust gas flowing on the central side than on the peripheral wall portion 32a side of the inner cylinder 132. Therefore, the exhaust gas having less temperature unevenness can flow out to the downstream pipe 100b.

In each of the above-described embodiments, the cylindrical combustion cylinder 20 has been described as an example, but if it is a cylinder, for example, the cross-sectional shape is a polygonal rectangular cylinder such as a quadrangle, a hexagon, or an octagon. It may be a combustion cylinder.

Further, in each of the above-described embodiments, there is an example of an exhaust gas heating device in which the number of combustion cylinders (burners) is 6, but the number of combustion cylinders (burners) is 7 even if the number is 5 or less. It may be more than one (for example, two, three, eight, ten, etc.). That is, the number of combustion cylinders (burners) is arbitrary (one or a plurality of combustion cylinders may be used). The number of combustion cylinders (burners) is set, for example, to match the required amount of heat.

Further, in each of the above-described embodiments, there is an example of an exhaust gas heating device in which a plurality of combustion cylinders (burners) are arranged on the same circumference, but the configuration is limited to the configuration in which the plurality of combustion cylinders (burners) are arranged on the same circumference. I can't. For example, a plurality of combustion cylinders (burners) may be arranged in a matrix like a grid. Further, a plurality of combustion cylinders (burners) may be arranged irregularly.

Further, in each of the above-described embodiments, there is an example of an exhaust gas heating device in which the lengths (shaft lengths) of the six combustion cylinders are all set to the same length, but the combustion cylinders (burners) are illustrated. ) May be different, or there may be one set or a plurality of sets having the same length. For example, the lengths (shaft lengths) of the six combustion cylinders may all be different, there are three sets of two of the same length, or two sets of three of the same length. It may exist. This makes it possible to suppress, for example, the acoustic resonance of the combustion cylinder, which can cause combustion noise.

Further, in each of the above-described embodiments, there is an example of an exhaust gas heating device in which the inner diameters of the six combustion cylinders are all set to the same value, but the inner diameters of the combustion cylinders are different from each other. However, there may be one set or a plurality of sets having the same inner diameter. For example, the inner diameters of the six combustion cylinders may all be different, three sets of two having the same inner diameter may exist, or two sets of three having the same inner diameter may exist. .. This makes it possible to secure the required total amount of heat while suppressing the acoustic resonance of the combustion cylinder, which may cause combustion noise, for example.

Further, in each of the above-described embodiments, those having a relatively long shaft length and having a shape in which the tip opening thereof expands to one side in the radial direction, such as the combustion cylinders 20 and 120, have been illustrated and described. However, it is not limited to the combustion cylinders 20 and 120 having such a shape. For example, a combustion cylinder having a castable shape and a tip shape that opens toward one side in the radial direction. May be configured. As a result, as compared with the combustion cylinders 20 and 120 of each of the above-described embodiments, the inner cylinder 32 emits high-temperature combustion gas generated by burning the fuel due to the direct radiant heat from the flame of the burner 13a or the flame of the burner. , 132 can be directed toward the center (near the cylinder axis J), and exhaust gas with less temperature unevenness can flow out to the downstream pipe 100b.

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 can clearly indicate the correspondence between the terms used in each of the above-described embodiments and the terms described in the claims.

10, 30, 130 ... Exhaust gas heating device (combustion device)
11, 31, 51 ... Outer cylinder 12, 32, 52, 132 ... Inner cylinder 13, 13', 13 ", 13X, 13Y, 13Z, 113 ... Burner unit 13a ... Burner 13b, 113b ... Cylinder body 20, 20x, 20y , 20z, 120 ... Combustion cylinder (cylinder body)
20a, 120a ... Base end 20b, 120b ... Tip 31d ... Connection (connection connected to the downstream side of the pipe)
90 ... Fuel pipe 100 ... Piping (Piping through which exhaust gas from external engines flows)
100a ... Upstream pipe (upstream side of piping)
100b ... Downstream pipe (downstream side of piping)
133 ... Discharge cylinder (second inner cylinder)
J, K, L, M, N ... Cylindrical shaft Ra, Rb ... Air flow passage (space)
Rv ... Virtual path Sa, Sb, Sc, Sd, Se ... Gap

Claims (7)

The inner cylinder that forms the combustion space inside,
An outer cylinder air sent from outside to together Covering the inner cylinder to form a space portion can flow between the inner cylinder,
A burner provided on the outer cylinder so as to penetrate the inner cylinder and eject fuel into the combustion space.
A cylinder provided separately from the burner and covering the periphery of the burner in the radial direction of the burner including the periphery of the burner in the fuel ejection direction is provided.
The exhaust gas discharged from the upstream side of the pipe through which the exhaust gas of the external engine flows can flow into the downstream side of the pipe via the combustion space, and the upstream side of the pipe and the downstream side of the pipe are inside the above. respectively communicated with the cylinder,
The tip end portion of the cylinder body is exposed in the combustion space, and the base end portion of the cylinder body is located on the opposite side of the fuel ejection direction of the burner and is exposed in the space portion in the outer cylinder. A combustion device characterized in that a gap is formed between the base end portion and the outer cylinder. The end of the inner cylinder on the side through which the burner penetrates is provided with a hole in which air flowing through the space is injected into the combustion space along the inner peripheral surface of the inner cylinder. The combustion apparatus according to claim 1. The cylinder is characterized in that the tip portion of the burner located in the fuel ejection direction is located outside the range of the virtual path connecting the upstream side of the pipe and the downstream side of the pipe at the shortest distance. The combustion apparatus according to claim 1 or 2. The combustion apparatus according to any one of claims 1 to 3, wherein the tubular body has a tip end portion located in the fuel ejection direction of the burner that opens in the shape of an end portion of an oblique cylinder. The combustion device according to any one of claims 1 to 4, wherein the burner has a fuel ejection direction from the downstream side of the pipe to the upstream side of the pipe. On the downstream side of the exhaust gas of the combustion space, a second inner cylinder having an inner diameter smaller than the inner diameter of the connecting portion connected to the downstream side of the pipe is provided so as to communicate with the downstream side of the pipe. The combustion apparatus according to claim 5. The pipe through which the exhaust gas of the external engine flows is already provided in the equipment space before the combustion device according to any one of claims 1 to 6 is installed, and the combustion device is the pipe of the pipe. A combustion device characterized in that it can be connected in the middle of the piping without requiring a rearrangement change.

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