KR20130134088A - Boiler - Google Patents

Abstract

A boiler is provided in which a heat exchanger such as a superheater or a reheater is provided to reduce a temperature deviation of combustion gas flowing through a heat exchange part of a boiler in which heat exchange is performed.
Boiler according to an embodiment of the present invention comprises a combustion unit 200 including a burner 210 for supplying fuel and air so that fuel and air is burned while turning; A nose unit 300 connected to the combustion unit 200 and configured to reduce a cross-sectional area in a flow direction of the combustion gas; And a heat exchanger 400 connected to the nose unit 300 and having a heat exchanger 410 configured to flow water that becomes steam by being heated by the combustion gas. At least one of the combustion unit 200, the nose unit 300 and the heat exchange unit 400 may be configured to reduce the temperature deviation of the combustion gas flowing through the heat exchange unit 400.
According to the above configuration, the present invention can prevent the swirl flow from remaining in the combustion gas flowing in the heat exchange part of the boiler in which heat exchange between the combustion gas and the heat exchanger is performed, and prevent the combustion gas from drifting in the heat exchange part of the boiler. It is possible to reduce the temperature deviation of the combustion gas in the heat exchanger of the boiler, reduce the temperature deviation of the steam flowing through the heat exchanger, and prevent the pipes included in the heat exchanger and the steam flowing from being ruptured. .

Description

Boiler {BOILER}

The present invention relates to a boiler for heating high-temperature, high-pressure steam or hot water by heating water, and more particularly, a temperature deviation of the combustion gas flowing through the heat exchange part of the boiler where heat exchange is performed by providing a heat exchanger such as a superheater or a reheater. As far as the boiler is concerned.

A boiler is a device that heats water to produce steam or hot water of high temperature and high pressure, and is used for driving a heating facility or a turbine for power generation.

9 and 10 show a corner combustion type coal combustion boiler 10 using pulverized coal as fuel, which is used to drive a steam turbine for power generation (not shown) among such boilers. The boiler 10 includes a combustion unit 20, a nose unit 30, and a heat exchange unit 40 as shown.

The combustion unit 20 includes a burner 21 as shown in FIG. The burner 21 supplies fuel and air to the combustion unit 20 so that fuel and air are burned while turning. To this end, the burner 21 is provided at each corner of the combustion section 20 having a rectangular cross section, as shown in FIG. When the fuel and air are injected to the combustion unit 20 at a predetermined angle by the burner 21, the fuel and air are combusted while the fuel 20 is rotated in the combustion unit 20 as shown.

As shown in FIG. 9, the burner 21 includes a plurality of fuel supply ports 21a and air supply ports 21b and 21c in multiple stages. Also, as shown, a fuel air supply port 21d for supplying oil and air together is also provided.

The combustion section 20 next to the burner 21 is provided with excess air supply section 22, as shown in FIG. The excess air supply unit 22 may also be provided at each corner of the combustion unit 20 as shown in FIG. The excess air supply unit 22 injects air to the combustion unit 20 at a predetermined angle as shown. As a result, the unburned component is burned. The excess air supply part 22 is provided with a plurality of excess air supply ports 22a as shown in FIG.

The nose part 30 is connected to the combustion part 20 as shown in FIG. In addition, the nose portion 30 decreases in cross-sectional area toward the combustion gas flow direction, that is, toward the top. Accordingly, the combustion gas passes through the nose portion 30 as shown.

As shown in FIG. 9, the heat exchange part 40 is connected to the nose part 30. Accordingly, the combustion gas flows to the heat exchange unit 40. The heat exchanger 40 includes a heat exchanger such as a split superheater 41a, a plate superheater 41b, a final reheater 41c, and a final superheater 41d, including a plurality of tubes through which water flows, as shown. Group 41 is provided.

Therefore, the combustion gas is heat-exchanged with the water flowing through the heat exchanger 41 while the heat exchanger 40 flows, so that the water is heated to become steam. This steam is supplied to a steam turbine (not shown) to drive the steam turbine to generate power.

Conventionally, in the heat exchanger 40 of the boiler 10 having such a configuration, there is a problem that a temperature deviation appears in the combustion gas flowing through the heat exchanger 40. Such fluctuations in temperature of the combustion gas are caused by the swirling flow in the combustion unit 20 and the nose unit 30 remaining in the combustion gas flowing through the heat exchange unit 40, causing the combustion gas to drift in the heat exchange unit 40.

That is, in the split type superheater 41a and the plate superheater 41b of the heat exchanger 400, the combustion gas flows to the right side, and the temperature of the combustion gas or steam is higher on the right side, and then passes through the final superheater 41d. Combustion gas drifts to the left, so that the temperature of the combustion gas or steam is higher on the left.

11 is a view showing the temperature distribution of the combustion gas in the final superheater 41d portion of the heat exchanger 40 of the conventional boiler 10, (a) is a figure showing the result of numerical analysis, (b) is It is a figure which shows the result of a measurement. From this, it can be seen that the temperature of the combustion gas at the lower left of the heat exchanger 40 is higher than the other parts.

Due to the temperature deviation of the combustion gas, there is a problem that the temperature deviation also appears in the steam flowing through the heat exchanger 41 included in the heat exchanger (40). In particular, in the final superheater 41d having a higher steam temperature than other heat exchangers 41, there is a problem in that it is locally overheated by the above-described temperature deviation.

That is, as shown in Fig. 11, in the final superheater 41d portion of the heat exchanger 40, the lower left side of the final superheater 41d is overheated because the temperature of the combustion gas at the lower side is higher than the temperature of the other portion. As a result, the temperature of the steam flowing in the lower left portion of the final superheater 41d is higher than that of other portions, and the tube located at the lower left side of the final superheater 41d is ruptured. As such, the ruptured tube has a problem that it takes time and cost to repair.

In addition, as described above, when the steam having a temperature deviation flows into the steam turbine, thermal unbalance occurs in the steam turbine, thereby degrading the life of the steam turbine.

In order to prevent this, conventionally, by using the designed coal to reduce the temperature of the steam, increase the material of the pipe included in the heat exchanger (41), or control the steam flow through the heat exchanger (41) Orifices and the like were installed to reduce the temperature deviation.

However, the design shot is difficult to use in practice, it is expensive to raise the material of the pipe, it is difficult to selectively increase the material of the pipe only in the part where the pipe ruptures, and the installation cost is high when installing the orifice. If the orifice hole is clogged or the design is wrong, there is a problem that the tube ruptures on a large scale.

The present invention is made by recognizing at least one of the needs or problems occurring in the conventional boiler as described above.

One aspect of the present invention is to reduce the temperature deviation of the combustion gas in the heat exchange portion of the boiler is a heat exchange between the combustion gas and the heat exchanger.

Another aspect of the object of the present invention is to reduce the temperature deviation of the steam flowing through the heat exchanger.

Another aspect of the object of the present invention is to prevent the rupture of the tubes, which are included in the heat exchanger and in which the steam flows.

A boiler related to an embodiment for realizing at least one of the above problems may include the following features.

The present invention is based on the fact that a heat exchanger such as a superheater or a reheater is basically provided to reduce the temperature deviation of the combustion gas flowing through the heat exchanger of the boiler in which the heat exchange is performed.

Boiler according to an embodiment of the present invention comprises a combustion unit including a burner for supplying fuel and air so that fuel and air is burned while turning; A nose part connected to the combustion part and configured to reduce a cross-sectional area in a flow direction of the combustion gas; And a heat exchanger connected to the nose part and having a heat exchanger configured to flow water in which a combustion gas flows and is heated by the combustion gas and becomes steam. It is configured to include, at least one of the combustion unit, the nose portion and the heat exchanger may be configured to reduce the temperature deviation of the combustion gas flowing through the heat exchanger.

In this case, at least one of the combustion unit and the nose unit may be configured such that swirl flow does not remain in the combustion gas flowing in the heat exchange unit, so that the combustion gas does not drift in the heat exchange unit.

In addition, the nose portion may be provided with a turning reducing member for reducing the turning strength of at least a portion of the combustion gas flowing through the nose portion.

The turning reducing member may be provided at a position such that swirl flow does not remain in the combustion gas flowing in the heat exchange unit.

In addition, the turning reducing member may have a triangular cross section.

The heat exchange part may be configured to supply a relatively low temperature exhaust gas.

In addition, the exhaust gas may be supplied to a portion in which the combustion gas flowing through the heat exchange unit is drift.

The burner next to the burner is provided with a plurality of excess air supply parts for supplying air in turn for combustion of unburned components, and the excess air supply part includes a plurality of excess air supply ports arranged in multiple stages to supply air. In addition, by varying the air injection angle of the excess air supply port for each stage can be reduced the turning strength of the combustion gas from the combustion unit.

In addition, the combustion section next to the burner is provided with a plurality of excess air supply parts for supplying air for combustion of unburned components, and the excess air supply parts are provided on one of a plurality of surfaces constituting the combustion part, respectively, and combustion gas coming out of the combustion part. It can reduce the turning strength of.

And, the burner is provided in a plurality of stages are provided with a plurality of air supply port for supplying air, it is possible to reduce the turning strength of the combustion gas from the combustion unit by configuring the air injection angle of the air supply port differently for each stage.

In addition, the heat exchanger includes a final superheater, the final superheater may be connected to the other superheater so that the temperature deviation of the steam flowing through the final superheater is reduced.

As described above, according to the exemplary embodiment of the present invention, it is possible to prevent the swirl flow from remaining in the combustion gas flowing in the heat exchange part of the boiler in which heat exchange between the combustion gas and the heat exchanger is performed.

In addition, according to an embodiment of the present invention, it is possible to prevent the combustion gas from flowing in the heat exchange part of the boiler.

In addition, according to the embodiment of the present invention, it is possible to reduce the temperature deviation of the combustion gas in the heat exchange unit of the boiler.

In addition, according to an embodiment of the present invention, it is possible to reduce the temperature deviation of the steam flowing through the heat exchanger.

In addition, according to an embodiment of the present invention, it is possible to prevent the tube included in the heat exchanger and the steam flows to rupture.

In addition, according to an embodiment of the present invention, the thermal imbalance does not occur in the steam turbine to which steam is supplied, so that the life of the steam turbine may not be reduced.

1 is a front sectional view showing an embodiment of a boiler according to the present invention.
(A) is sectional drawing along the line A-A 'of FIG. 1, (b) is sectional drawing along the line B-B', (c) is sectional drawing along the line C-C ', (d) is D It is sectional drawing along the line -D '.
3 is a view showing the supply of exhaust gas to the heat exchange unit of the boiler according to the present invention.
Figure 4 (a) is a view showing the temperature distribution of the heat exchanger in the heat exchanger of the conventional boiler, (b) is a view showing the temperature distribution of the heat exchanger in the heat exchanger of the boiler according to the present invention.
Figure 5 is a front sectional view showing another embodiment of the boiler according to the present invention.
(A) is sectional drawing along the line E-E 'of FIG. 5, (b) is sectional drawing along the line F-F', (c) is sectional drawing along the G-G 'line, (d) is H It is sectional drawing along the line -H '.
Figure 7 (a) is a view showing the temperature distribution of the heat exchanger of the upper portion of the nose of the conventional boiler, (b) is a view showing the temperature distribution of the heat exchanger of the upper portion of the nose of the boiler according to the present invention.
Figure 8 (a) is a view showing the connection of the heat exchanger in the conventional boiler, (b) is a view showing the connection of the heat exchanger in the boiler according to the present invention.
9 is a front sectional view showing a conventional boiler.
(A) is sectional drawing along the II 'line of FIG. 9, (b) is sectional drawing along the line J-J' of FIG. 9, (C) is sectional drawing along the line K-K 'of FIG. (d) is sectional drawing along the L-L 'line | wire of FIG.
11 is a view showing the temperature distribution of the combustion gas in the heat exchanger of the conventional boiler according to the line M-M 'of FIG. 9, (a) is a figure showing the results of numerical analysis, (b) is a measurement result It is a figure which shows.

In order to help the understanding of the features of the present invention as described above, it will be described in more detail with respect to the boiler associated with the embodiment of the present invention.

Hereinafter, exemplary embodiments will be described based on embodiments best suited for understanding the technical characteristics of the present invention, and the technical features of the present invention are not limited by the illustrated embodiments, It is to be understood that the present invention may be implemented as illustrated embodiments. Accordingly, the present invention may be modified in various ways within the technical scope of the present invention through the embodiments described below, and such modified embodiments fall within the technical scope of the present invention. In order to facilitate understanding of the embodiments to be described below, in the reference numerals shown in the accompanying drawings, among the constituent elements which perform the same function in each embodiment, the related constituent elements are indicated by the same or an extension line number.

Embodiments related to the present invention are basically provided with a heat exchanger such as a superheater or a reheater to reduce the temperature deviation of the combustion gas flowing through the heat exchanger of the boiler where the heat exchange is performed.

The boiler 100 according to the present invention may include a combustion unit 200, a nose unit 300, and a heat exchange unit 400 as shown in the embodiment illustrated in FIGS. 1 and 5.

Hereinafter, in the drawings, the X axis indicates the front and rear directions, the Y axis indicates the left and right directions, and the Z axis indicates the upward direction.

As shown in FIGS. 1 and 5, the combustion unit 200 may include a burner 210. The burner 210 may supply fuel and air so that fuel and air are burned while turning. Since fuel and air are burned while turning, fuel and air can be mixed well. Accordingly, the combustion efficiency can be increased.

Combustion unit 200 may be formed of a plurality of surfaces. Combustion unit 200 may have a quadrangular cross section by forming four surfaces as shown in the embodiment shown in Figure 2 (c) and (d). The burner 210 may be provided at a portion to which a plurality of surfaces of the combustion unit 200 are connected.

As shown in FIG. 2D, the burner 210 may be provided at each corner of the combustion unit 200 having a rectangular cross section. In addition, the fuel and air may be injected into the combustion unit 200 from the burner 210 at a predetermined angle as shown in (d) of FIG. Accordingly, fuel and air can be burned while turning as shown in FIG. 2 (d).

The nose unit 300 may be connected to the combustion unit 200 as shown in FIGS. 1 and 5. Therefore, as shown in FIGS. 1 and 2 (b) and 5 and 6 (b), the combustion gas may flow in the nose part 300. In addition, the nose portion 300 may have a cross-sectional area that decreases toward the flow direction of the combustion gas, that is, toward the top in the illustrated embodiment.

With this configuration, the combustion gas combusted in the combustion unit 200 may flow through the nose unit 300 and flow to the heat exchange unit 400 without directly flowing to the heat exchange unit 400. Accordingly, sufficient combustion may be made in the combustion unit 200.

As shown in FIGS. 1 and 5, the heat exchanger 400 may be connected to the nose unit 300. Accordingly, the combustion gas may flow in the heat exchange part 400 as in the illustrated embodiment. The heat exchanger 400 may include a heat exchanger 410. Water may flow into the heat exchanger 410.

Therefore, as described above, heat transfer may be performed from the relatively high temperature combustion gas flowing through the heat exchange part 400 to the water flowing into and flowing into the heat exchanger 410. Then, the water flowing through the heat exchanger 410 may be heated to become steam. Such steam may be supplied to a steam turbine (not shown) for power generation to drive the steam turbine.

On the other hand, at least one of the above-described combustion unit 200, the nose unit 300 and the heat exchange unit 400 of the boiler 100 according to the present invention so that the temperature deviation of the combustion gas flowing through the heat exchange unit 400 is reduced Can be configured. Therefore, the heat exchanger 410 provided in the heat exchanger 400 may not be locally heated further, and thus the temperature deviation of the steam flowing through the heat exchanger 410 may be reduced. In addition, a tube (not shown) included in the heat exchanger 410 and in which water flows may be locally overheated and not ruptured.

As such, since the temperature deviation of the steam flowing through the heat exchanger 410 is reduced, thermal imbalance may not occur in the steam turbine (not shown) to which the steam is supplied. Therefore, the life deterioration due to thermal imbalance of the steam turbine can be prevented.

In order to reduce the temperature deviation of the combustion gas flowing through the heat exchange unit 400, at least one of the combustion unit 200 and the nose unit 300 does not have swirl flow in the combustion gas flowing through the heat exchange unit 400. It may be configured to not. That is, as shown in FIGS. 2 (c) and (d) and 6 (c) and (d), the swirl flow of the combustion gas flowing through the combustion unit 200 and the nose unit 300 flows. The heat exchanger 400 may be configured not to appear.

As such, if swirl flow does not remain in the combustion gas flowing through the heat exchange part 400, the combustion gas may not drift in the heat exchange part 400. That is, in the heat exchange part 400, the combustion gas may flow relatively uniformly without being biased toward one side. Accordingly, since the temperature distribution of the combustion gas flowing through the heat exchange part 400 becomes relatively uniform, the temperature deviation of the combustion gas in the heat exchange part 400 may be reduced.

To this end, the nose portion 300 may be provided with a turning reducing member 310 as shown in the embodiment shown in Figures 1 and 2 and 5 and 6. By the turning reducing member 310, the turning strength of at least a portion of the combustion gas flowing through the nose part 300 may be reduced. Accordingly, the swirl flow may not remain in the combustion gas flowing through the nose unit 300 and the heat exchange unit 400.

The swing reducing member 310 may be provided at a position such that the swirl flow does not remain in the combustion gas flowing through the heat exchange part 400. As shown in FIGS. 2B and 6B, the turning reducing member 310 may be provided on the left side of the nose part 300. Accordingly, as shown, the swirl flow of the combustion gas in the nose unit 300 may be disturbed.

In the embodiment shown in Figures 2 and 6, the swing flow of the combustion gas flowing outside the nose portion 300 as shown in (b) and 6 (b) of Figure 2 may be disturbed. . As a result, the turning strength of the combustion gas flowing through the outside of the nose part 300 which causes the swirl flow to remain in the heat exchange part 400 can be reduced. Therefore, swirl flow may not remain in the combustion gas flowing through the heat exchange part 400.

As shown in FIGS. 1 and 2 and 5 and 6, the turning reducing member 310 may have a triangular cross section. As such, when the cross section of the turning reducing member 310 is a triangle, as illustrated in FIGS. 2B and 6B, the combustion gas flowing outside the nose part 300 forms a triangle. The inclined surface of the turning member 310 may be formed to flow to the other inclined surface.

Accordingly, the turning strength of the combustion gas can be reduced without significantly affecting the overall flow of the combustion gas flowing through the nose part 300. For example, when the cross section of the swing reducing member 310 is rectangular, the swing gas reducing member 310 after the combustion gas flowing outside the nose portion 300 hits one surface of the swing reducing member 310 forming a quadrangle. May not flow beyond. In addition, the combustion gas that strikes one surface of the turning reducing member 310 may make another turning flow separately.

As a result, the total flow of the combustion gas flowing through the nose unit 300 is greatly influenced, thereby lowering the combustion efficiency in the combustion unit 200, or a material such as NOx (nitrogen oxide) or SOx (sulfur oxide). This can be prevented or reduced.

However, the shape of the cross section of the turning reducing member 310 is not limited to a triangle as in the illustrated embodiment, and any shape may be used as long as it reduces the turning strength of the combustion gas flowing through the nose part 300.

The heat exchange part 400 may be configured to supply a flue gas having a relatively low temperature as in the embodiment illustrated in FIG. 3. To this end, as illustrated in FIGS. 1 and 2 (a) and 5 and 6 (a), the heat exchange part 400 may be provided with an exhaust gas supply port 420. In addition, the exhaust gas supply port 420 may be connected to an exhaust gas supply source as in the embodiment shown in FIG. 3, and in the illustrated embodiment, to the exhaust gas flow pipe before the desulfurization oxide tower T2.

Such exhaust gas may be supplied to a portion where the combustion gas flowing through the heat exchange part 400 flows. The portion of the heat exchange part 400 in which the combustion gas drifts may have a relatively higher temperature than the portion of the other heat exchange part 400. Accordingly, when the exhaust gas having a relatively low temperature is supplied to the portion of the heat exchange part 400 in which the combustion gas flows, the temperature deviation of the combustion gas flowing through the heat exchange part 400 may be reduced.

As shown in Fig. 11, in the conventional boiler 10, the left side of the lower part of the heat exchanger 40 has a part of the final superheater 41d, which causes drift to the lower left side so that the temperature of the combustion gas in the lower left side is lower than that of the other parts. Becomes high. Then, the temperature of the steam at the lower left of the final superheater 41d is higher than the temperature of the other part.

Since the steam flowing in the final superheater 41d is higher than the temperature of the steam flowing in the other superheaters 41a and 41b connected thereto, the steam flowing in the lower left of the final superheater 41d may be superheated. Thereby, the tube located in the lower left of the final superheater 41d can be ruptured.

Therefore, in order to prevent this, in the embodiments shown in FIGS. 1 and 2 (a) and FIGS. 5 and 6 (a), the lower left portion of the final superheater 414 portion of the heat exchanger 400 in which the combustion gas flows. To supply flue gas. And, in order to supply the exhaust gas to the lower left of the final superheater 414 of the heat exchanger 400, the embodiment shown in Figures 1 and 2 (a) and 5 and 6 (a). As described above, the exhaust gas supply port 420 may be provided at a lower left portion of the final superheater 414 of the heat exchanger 400.

However, the position in the heat exchange part 400 of the exhaust gas supply port 420 for supplying the exhaust gas is not limited to the illustrated embodiment, and the exhaust gas can be supplied to the part of the heat exchange part 400 in which the combustion gas flows. If it is a position, any position of the heat exchange part 400 is possible.

In FIG. 3, reference numeral 'S' denotes a vessel for loading and transporting fuel F, reference numeral 'F' denotes fuel such as pulverized coal, and reference numeral 'B' stores fuel F. Denotes a fuel bunker, reference numeral 'M' denotes a fuel mill, reference numeral 'T1' denotes a denitrification oxide tower, reference numeral 'H' denotes an air heater, and reference numeral 'K' denotes a chimney. .

Meanwhile, as illustrated in FIGS. 1 and 2, and 5 and 6, a plurality of excess air supply units 220 may be provided in the combustion unit 200 next to the burner 210. The excess air supply unit 220 may supply air to the combustion unit 200 as shown in FIGS. 1 and 2 (c) and 5 and 6 (c). As such, the unburned component may be combusted by the air supplied from the excess air supply unit 220 to the combustion unit 200.

The excess air supply unit 220 may pivotally supply air to the combustion unit 200 as shown in the embodiment shown in FIGS. 1 and 2 (c). To this end, the excess air supply unit 220 may be provided at each corner of the combustion unit 200 having a rectangular cross section as shown in (c) of FIG. In addition, air may be injected into the combustion unit 200 from the excess air supply unit 220 at a predetermined angle as shown in (c) of FIG. 2. As a result, as shown in FIG. 2C, air can be supplied to be turned.

In this case, as shown in FIG. 1, the excess air supply unit 220 may include a plurality of excess air supply ports 221 arranged in multiple stages to supply air. In addition, as shown in the embodiment of FIG. 2C, the air injection angle of the excess air supply port 221 may be configured differently by stages. Accordingly, it is possible to reduce the turning strength of the combustion gas coming from the combustion unit 200. In addition, it is possible to prevent the swirl flow from remaining in the combustion gas flowing through the heat exchange part 400. As a result, the combustion gas flowing through the heat exchange part 400 may not flow.

4 (a) shows the temperature distribution of the heat exchanger 41 in the heat exchanger 40 of the conventional boiler 10, in which the air injection angle of the excess air supply port 22a is not configured differently in stages. . And, Figure 4 (b) is the temperature distribution of the heat exchanger 410 in the heat exchange unit 400 of the boiler 100 according to the present invention, the air injection angle of the excess air supply port 221 configured differently by stages Indicates.

As can be seen from this, if the air injection angle of the excess air supply port 221 is configured differently by stages, combustion that flows through the heat exchange part 400 by reducing the turning strength of the combustion gas coming from the combustion part 200. It is possible to prevent the swirl flow from remaining in the gas. Accordingly, the combustion gas flowing through the heat exchange part 400 does not drift so that the temperature deviation of the combustion gas may be reduced.

In addition, as shown in FIG. 5, the excess air supply unit 220 may be provided on one of a plurality of surfaces constituting the combustion unit 200. Accordingly, the air supplied from the excess air supply unit 220 may not be pivotally supplied as shown in FIG. 6C, as shown in FIG. 6C. As a result, it is possible to reduce the turning strength of the combustion gas coming from the combustion unit 200. Even if it is supplied to turn, it is possible to reduce the turning strength of the combustion gas coming from the combustion unit 200.

Accordingly, it is possible to prevent the swirl flow from remaining in the combustion gas flowing through the heat exchange part 400. As a result, the combustion gas flowing through the heat exchange part 400 may not drift.

7 (a) is a heat exchange portion of the upper portion of the nose portion 30 of the conventional boiler 10 provided at the corners, that is, the portions where the excess air supply portion 22 forms the combustion portion 20 is connected. The temperature distribution of the part 40 is shown. And, (b) of 7 is the heat exchanger portion of the upper portion of the nose portion 300 of the boiler 100 according to the present invention, each of the excess air supply unit 220 is provided on one of the plurality of surfaces forming the combustion unit 200 ( The temperature distribution of 400) is shown.

In this case, when the excess air supply unit 220 is provided on one of the plurality of surfaces constituting the combustion unit 200 so that no air is supplied to the combustion unit 200, the turning strength is reduced to the nose unit 300. It can be seen that the temperature distribution of the upper heat exchanger 400 becomes uniform.

In this case, too, as in the embodiment shown in FIG. 5, the excess air supply unit 220 may include a plurality of excess air supply ports 221 arranged in multiple stages to supply air.

On the other hand, the burner 210 described above may include a fuel supply port 211 is arranged in multiple stages to supply fuel. In addition, the burner 210 may also include a plurality of air supply ports 212 and 213 disposed in multiple stages to supply air. And, as shown in the embodiment shown in Figure 6 (d), the air injection angle of the excess air supply port 221 can also be configured differently for each stage.

Accordingly, it is possible to reduce the turning strength of the combustion gas coming from the combustion unit 200. In addition, the swirl flow may be prevented from remaining in the combustion gas flowing through the heat exchange part 400, so that the combustion gas flowing through the heat exchange part 400 may not be drift.

Reference numeral '214', which is not described, is a fuel air supply port, through which oil and air may be supplied to the combustion unit 200 together.

On the other hand, the heat exchanger 400 is connected to the split type superheater 411 and the split type superheater 411 as shown in FIGS. 1 and 2 (a) and 5 and 6 (a). Plate superheater 412, the final superheater 414 connected to the plate superheater 412. Among these, the superheater 414 is another superheater, in the illustrated embodiment, the plate superheater 412 in order to reduce the temperature deviation of the steam flowing through the final superheater 414, as shown in the embodiment shown in FIG. Can be connected to.

As shown in (a) of FIG. 8, in the conventional boiler 10, the plate-shaped superheater 41b and the final superheater 41d cross each other. This is because the temperature of the right side of the divided superheater 41a and the plate superheater 41b of the heat exchanger 40 is higher in the temperature of the left side, and the temperature of the lower left of the final superheater 41d is higher than the temperature of the other portion. Because it is high.

Accordingly, the steam flowing through the split superheater 41a and the plate superheater 41b has a higher temperature on the right side than the temperature on the left side, and the steam flowing through the final superheater 41d has a temperature lower than that of other parts. Becomes higher.

Since the steam flowing through the final superheater 41b is higher than the temperature of the steam flowing through the other superheaters 41a and 41b connected thereto, spray water (not shown) in the plate superheater 41b in the superheat reducer (not shown). To reduce the left and right temperature deviations of the vapor and then enter the final superheater 41d.

However, even if steam is introduced into the final superheater 41d without temperature variation, the temperature of the combustion gas in the part different from the temperature of the combustion gas at the lower left of the final superheater 41d portion of the heat exchanger 40 is different as described above. Because of the high temperature, left and right temperature variations occur in the steam exiting the final superheater 41d.

Accordingly, in the boiler 100 of the present invention, as shown in (b) of FIG. 8, the plate superheater 412 and the final superheater 414 are connected without crossing left and right. Since the temperature of the steam flowing through the plate superheater 412 is higher than the temperature of the left side, the steam is introduced into the final superheater 414 with the temperature of the right side higher than the temperature of the left side.

Further, since the temperature of the combustion gas at the lower side of the final superheater 414 portion of the heat exchanger 400 is higher than the temperature of the combustion gas at the other portion, the steam flowing through the final superheater 414 is lower than the other portion. Is heated more. As described above, since the temperature entering the final superheater 414 is higher than the temperature at the left side, the temperature deviation of the steam exiting the final superheater 414 may be reduced.

This configuration eliminates the need for overheating reduction as in the prior art, and further reduces the temperature deviation of the steam exiting the final superheater 414 without spraying spray water onto the plate superheater 412.

As described above, when the boiler according to the present invention is used, it is possible to prevent the swirl flow from remaining in the combustion gas flowing in the heat exchange part of the boiler in which heat is exchanged with the combustion gas and the heat exchanger, and the combustion gas flows in the heat exchange part of the boiler. Can reduce the temperature deviation of the combustion gas in the heat exchange part of the boiler, reduce the temperature deviation of the steam flowing through the heat exchanger, and rupture the pipe that is included in the heat exchanger It is possible to prevent and prevent thermal unbalance from occurring in the steam turbine to which steam is supplied, so that the life of the steam turbine may not be reduced.

The boiler described above may not be limitedly applied to the configuration of the above-described embodiment, but the embodiments may be configured by selectively combining all or some of the embodiments so that various modifications can be made.

10,100: boiler 20,200: burner
21,210: Burner 21a, 211: Fuel supply port
21b, 21c, 212,213: Air supply port 21d, 214: Fuel air supply port
22,220: excess air supply part 22a, 221: excess air supply port
30,300: nose part 310: turning reducing member
40,400: heat exchanger 41,410: heat exchanger
41a, 411: Split Superheater 41b, 412: Plate Superheater
41c, 413: Final Reheater 41d, 414: Final Superheater
420: exhaust gas supply port S: ship
F: Fuel B: Fuel Bunker
M: Fuel Mill T1: Denitrification Oxide Tower
H: Air Heater T2: Desulfurization Tower
K: chimney

Claims (11)

Combustion unit 200 including a burner 210 for supplying fuel and air so that fuel and air is burned while turning;
A nose unit 300 connected to the combustion unit 200 and configured to reduce a cross-sectional area in a flow direction of the combustion gas; And
A heat exchange part 400 connected to the nose part 300 and having a heat exchanger 410 configured to flow water that becomes steam by being heated by the combustion gas and heated by the combustion gas; And,
At least one of the combustion unit (200), the nose unit (300) and the heat exchange unit (400) is configured to reduce the temperature deviation of the combustion gas flowing through the heat exchange unit (400). The method of claim 1, wherein at least one of the combustion unit 200 and the nose unit 300 is configured so that swirl flow does not remain in the combustion gas flowing through the heat exchange unit 400, so that combustion is performed in the heat exchange unit 400. A boiler characterized in that the gas does not drift. 3. The boiler according to claim 2, wherein the nose part (300) is provided with a turning reducing member (310) for reducing the turning strength of at least a portion of the combustion gas flowing through the nose part (300). The boiler according to claim 3, wherein the swirl reducing member (310) is provided at a position such that swirl flow does not remain in the combustion gas flowing through the heat exchange part (400). The boiler according to claim 3, wherein the turning reducing member (310) is triangular in cross section. The boiler according to claim 1, wherein the heat exchange part (400) is configured to supply a flue gas having a relatively low temperature. The boiler according to claim 6, wherein the exhaust gas is supplied to a portion where the combustion gas flowing through the heat exchange part (400) flows. According to claim 2 or 6, The combustion unit 200 after the burner 210 is provided with a plurality of excess air supply unit 220 for supplying air to turn for combustion of unburned components,
The excess air supply unit 220 includes a plurality of excess air supply ports 221 arranged in multiple stages to supply air,
Boiler, characterized in that for reducing the rotational strength of the combustion gas coming from the combustion unit 200 by configuring the air injection angle of the excess air supply port (221) for each stage. According to claim 2 or 6, The combustion unit 200 after the burner 210 is provided with a plurality of excess air supply unit 220 for supplying air for combustion of unburned components,
The excess air supply unit 220 is provided on one of a plurality of surfaces constituting the combustion unit 200, respectively, boiler characterized in that to reduce the turning strength of the combustion gas from the combustion unit (200). According to claim 2 or 6, The burner 210 is provided with a plurality of air supply port 212 is arranged in multiple stages to supply air,
Boiler, characterized in that for reducing the turning intensity of the combustion gas coming from the combustion unit 200 by configuring the air injection angle of the air supply port (212) for each stage. The method of claim 1, wherein the heat exchange unit 400 includes a final superheater 414,
A boiler characterized in that the final superheater (414) is connected to another superheater (412) so that the temperature deviation of the steam flowing through the final superheater (414) is reduced.

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