JP5152494B2 - Opposed combustion boiler device and operation method thereof - Google Patents

Description

  The present invention relates to an opposed combustion boiler apparatus having an opposed combustion boiler in which a group of burners each formed by arranging a plurality of burners in a vertical and horizontal direction on the can front wall and the can rear wall facing each other, and an operation method thereof. is there.

  Conventionally, as the above-described counter-fired boiler apparatus, for example, there is a coal-fired boiler apparatus. In this coal-fired boiler apparatus, pulverized coal and primary / secondary air as fuel are supplied to a plurality of burners of a burner group in the counter-fired boiler. On the other hand, thermal NOx is supplied by supplying secondary air into the opposed combustion boiler through the two-stage combustion ports respectively installed above the burner groups on the front and rear walls of the opposed combustion boiler. It tried to reduce it.

In this coal fired boiler apparatus, a plurality of two-stage combustion ports of the opposed combustion boiler are formed in the lateral direction on the front wall of the can and the rear wall of the can, and the supply amount of secondary air between the left and right two-stage combustion ports Thus, the flow of combustion gas in the opposed combustion boiler is adjusted (for example, Patent Document 1).
JP 07-12310 A

  However, in the above-described coal fired boiler apparatus, the state of the flow of the combustion gas in the opposed combustion boiler changes depending on the combination of the burners used among the plurality of burners of the burner group. Accordingly, the burner is bypassed. Thus, the optimum flow rate distribution of the secondary air supplied into the opposed combustion boiler via the two-stage combustion port varies depending on the state of combustion gas flow and the boiler load.

  That is, in the above-mentioned coal fired boiler apparatus, as the combination of many burners changes, the state of combustion gas flow changes in many patterns under both high and low load conditions of the boiler. In response to these changes, the secondary air flow balance cannot be maintained optimally, and as a result, it is difficult to maintain a stable operating state. It was an issue.

  The present invention has been made paying attention to the above-described conventional problems, and corrects the flow state of the combustion gas in the opposed combustion boiler in both the high load state and the low load state of the opposed combustion boiler. Therefore, an object of the present invention is to provide an opposed combustion boiler apparatus that can be operated in a stable state at all times and an operation method thereof.

  In order to achieve the above-mentioned object, the invention according to claim 1 of the present invention is a burner formed by arranging a plurality of burner rows in the vertical direction in which a plurality of burners to which fuel and primary air are supplied are arranged in the horizontal direction. A can front wall and a can rear wall which are opposed to each other and have a two-stage combustion port which is located above the burner group and passes secondary air supplied by bypassing the burner group. The counter-combustion boiler provided, and the can front damper and the can rear side for adjusting the amount of secondary air supplied into the counter combustion boiler through the respective two-stage combustion ports on the front and rear walls of the counter combustion boiler In the opposed combustion boiler apparatus provided with the damper, the influence on the flow of the combustion gas in the opposed combustion boiler with respect to each of the plurality of burner rows in each burner group arranged on the front wall and the rear wall of the can. A control unit is provided that assigns an influence gain according to the balance and indexes the combustion gas flow pattern by a numerical index calculated based on the influence gain assigned to the burner row used during operation. The control unit associates the numerical index representing the combustion gas flow pattern with the load status in the opposed combustion boiler, and each of the two-stage combustion ports on the front and rear walls of the can in the opposed combustion boiler. The can front side damper and the can rear side damper are actuated to optimize the amount of secondary air supplied into the counter combustion boiler through the counter combustion boiler device. It is a means for solving the conventional problems.

  Further, in the opposed combustion boiler apparatus according to claim 2 of the present invention, the control unit is configured such that the flow pattern of the combustion gas in each of a situation where the inside of the opposed combustion boiler is a high load and a situation where the load is low. In order to optimize the amount of secondary air supplied into the opposing combustion boiler through the two-stage combustion ports on the front wall and rear wall of the opposing combustion boiler in accordance with the magnitude of the numerical index representing In the counter-combustion boiler apparatus according to claim 3 of the present invention, the control unit includes two types of control programs for operating the front damper and the can rear damper, respectively. In addition, it is configured to automatically switch according to the magnitude of the numerical index representing the combustion gas flow pattern.

  On the other hand, the invention according to claim 4 of the present invention has a burner group formed by arranging a plurality of burner rows in a vertical direction by arranging a plurality of burners to which fuel and primary air are supplied in a horizontal direction. An opposed combustion boiler having a plurality of two-stage combustion ports positioned above the burner group and through which secondary air supplied by bypassing the burner group is passed, the front and back walls of the can facing each other A combustion gas flow in the opposed combustion boiler for each of a plurality of burner rows in each burner group arranged on the front wall of the can and the rear wall of the can An influence gain according to the degree of influence on the combustion gas is assigned, and the flow pattern of the combustion gas is determined by a numerical index calculated based on the influence gain assigned to the burner train used during operation. And the load condition in the opposed combustion boiler is applied to the numerical index representing the flow pattern of the combustion gas, and the two-stage combustion ports on the front wall and the rear wall of the can in the opposed combustion boiler are used. The configuration is such that the amount of secondary air supplied into the opposed combustion boiler is optimized, and the configuration of the operation method of the opposed combustion boiler device is a means for solving the above-described conventional problems.

  Moreover, in the operation method of the opposed combustion boiler apparatus according to claim 5 of the present invention, when the numerical index representing the combustion gas flow pattern is a predetermined value or less, using one control program, A numerical index representing the flow pattern of the combustion gas while optimizing the amount of secondary air supplied into the opposing combustion boiler through the respective two-stage combustion ports on the front and rear walls of the opposed combustion boiler Is greater than a predetermined value, the amount of secondary air supplied into the opposing combustion boiler through the respective two-stage combustion ports on the front wall and rear wall of the opposing combustion boiler using the other control program. In the operation method of the opposed combustion boiler apparatus according to claim 6 of the present invention, the one control program and the other control program are configured to generate a flow pattern of the combustion gas. It has a configuration which switches automatically in accordance with the magnitude of the numerical index representing.

  Here, in the above-described counter-fired boiler apparatus, the left-right deviation of the flow of the combustion gas G above the counter-fired boiler 10 shown in FIG. In each of the two-stage combustion ports 5 on the can front wall 11 and the can rear wall 12, the flow state of the combustion gas G in the opposed combustion boiler 10 is provided by providing a difference in the supply amount of the secondary air on the left side and the right side thereof. Are averaged in the horizontal direction.

  At this time, the state of the flow of the combustion gas G in the opposed combustion boiler 10 by combining the burner rows to be used among the plurality of burner rows of each burner group of the can front wall 11 and the can rear wall 12 in the opposed combustion boiler 10. Therefore, in consideration of the load conditions such as the amount of combustion gas in the opposed combustion boiler 10 and the excess air ratio, the opposed combustion boilers 10 face each other through the two-stage combustion ports 5 on the front wall 11 and the rear wall 12 of the can. It becomes necessary to appropriately distribute the flow rate of the secondary air supplied into the combustion boiler 10.

  Thus, in order to appropriately distribute the flow rate of the secondary air supplied from the respective two-stage combustion ports 5 of the can front wall 11 and the can rear wall 12 into the counter combustion boiler 10, the counter combustion boiler according to the present invention is used. In the apparatus and its operating method, first, as shown in FIG. 4, the three-stage burner row 4 is provided on the can front wall 11 and the two-stage burner row 4 is provided on the can rear wall 12. In the case of the combustion boiler 10, an influence gain is assigned to each burner row 4 as follows.

  That is, the upper burner row 4U of the can front wall 11 and the two burner rows 4U and 4L of the can rear wall 12 have a great influence on the flow of combustion gas in the opposed combustion boiler 10, and therefore the burner row 4 Assigns an influence gain (2), respectively, while the middle and lower burner rows 4M, 4L of the can front wall 11 are two burner rows of the upper burner row 4U and the can rear wall 12 of the can front wall 11, respectively. Since the influence on the flow of the combustion gas in the opposed combustion boiler 10 is not large compared to 4U and 4L, an influence gain (1) is assigned to each of these burner rows 4, and the influence is exerted when neither of them is operating. It was decided to treat it as a degree gain (0).

  Then, after assigning the influence gain to each burner row 4 of the opposed combustion boiler 10 in this way, as shown in the equation (1), the total influence gain of the burner row 4 of the can front wall 11 during operation is shown. The value Np obtained by subtracting the total influence gain R of the burner row 4 of the can rear wall 12 from F is used as a numerical index for indexing the combustion gas flow pattern, and a predetermined value for dividing this numerical index into large and small (0 ).

FR = Np (Formula 1)
In the opposed combustion boiler apparatus and the operation method thereof according to the present invention, when the numerical index of the combustion gas flow pattern obtained as described above is not larger than a predetermined value, that is, when Np ≦ 0, it is low. Under the load condition, as shown in FIG. 5, the combustion gas G is largely drifted toward the can front wall 11, and therefore the amount of secondary air is reduced on the can front wall 11 using the control program shown in the graph of FIG. 6. As shown in FIG. 7, the combustion gas drifts toward the can rear wall 12 side and the oxygen concentration on the can rear wall 12 side becomes lower as shown in FIG. The amount of secondary air is controlled to be biased toward the second stage combustion port 5 side of the rear wall 12 of the can. On the other hand, when the numerical index of the combustion gas flow pattern exceeds a predetermined value, that is, when Np> 0 Under low load condition, shown in Fig.8 In this way, the combustion gas is greatly drifted to the can rear wall 12 side, so the amount of secondary air is biased to the two-stage combustion port 5 side on the can rear wall 12 side using the control program shown in the graph of FIG. Under high load conditions, as shown in FIG. 10, the combustion gas drifts to the can front wall 11 side and the oxygen concentration on the can front wall 11 side becomes low, so the amount of secondary air is reduced on the can front wall 11 side. Control is performed so as to bias the second combustion port 5 side.

  In the operation method of the opposed combustion boiler device according to claim 1 and the opposed combustion boiler device according to claim 4 of the present invention, the above-described configuration is adopted. Therefore, under either the high load condition or the low load condition of the opposed combustion boiler, In this case, the flow state of the combustion gas in the opposed combustion boiler is corrected, so that it is possible to operate in a stable state at all times.

  Further, since the operation method of the opposed combustion boiler apparatus according to claim 2 and the opposed combustion boiler apparatus according to claim 5 of the present invention is configured as described above, excessive combustion gas flow under a low load condition of the opposed combustion boiler is provided. Therefore, it is possible to appropriately introduce the combustion oxygen into the boiler under the high load condition of the opposed combustion boiler. In the operation method of the combustion boiler device and the opposed combustion boiler device according to the sixth aspect, since the above-described configuration is adopted, a very excellent effect that it is possible to cope with a wide range of operation burner patterns is brought about.

Hereinafter, an opposed combustion boiler apparatus and an operation method thereof according to the present invention will be described with reference to the drawings.
FIGS. 1-10 has shown one Embodiment of the opposed combustion boiler apparatus which concerns on this invention, In this embodiment, the case where an opposed combustion boiler apparatus is a coal fired boiler apparatus is mentioned as an example, and is demonstrated.
As shown in FIGS. 1 and 2, the coal fired boiler apparatus 1 has a can front wall 11 and a can rear wall 12 facing each other, and a superheater 13 and a reheater 14 arranged at the top. And a coal-fired boiler (power transmission capacity 700,000 kW) 10 in the form of a box.

  On the can front wall 11 of the coal-fired boiler 10, there are three vertical stages of burner rows 4 in which a plurality of burners 3 to which pulverized coal, primary air, and secondary air are supplied via the control damper 2 are arranged in the horizontal direction. A burner group which is formed by being arranged is provided, and on the rear wall 12 of the can, a burner in which a plurality of burners 3 to which pulverized coal, primary air and secondary air are supplied via the control damper 2 are arranged in the horizontal direction is also provided. Burner groups formed by arranging the rows 4 in two stages in the vertical direction are provided (only the burner mounting hole 3a is shown in FIG. 1), and the can front wall 11 and the can rear wall 12 are provided above the respective burner groups. , Two-stage combustion ports 5 that are arranged side by side in the horizontal direction and pass secondary air supplied by bypassing the burner group are arranged, and the two-stage combustion ports 5 located at both ends are provided as side ports. 5A.

  Further, the coal fired boiler apparatus 1 adjusts the amount of secondary air supplied into the coal fired boiler 10 through the two-stage combustion ports 5 of the can front wall 11 and the can rear wall 12 in the coal fired boiler 10. A can front side damper 6 and a can rear side damper 7 are provided, and the amount of secondary air supplied into the coal-fired boiler 10 through the respective two-stage combustion ports 5 on the can front wall 11 and the can rear wall 12 is appropriate. In order to achieve this, a control unit 20 for operating the front can damper 6 and the rear can damper 7 is provided.

  In this case, as shown in FIG. 3 (b), the control unit 20 uses the secondary air on the left and right sides of each of the two-stage combustion ports 5 on the can front wall 11 and the can rear wall 12 in the coal burning boiler 10. In addition to controlling the flow state of the combustion gas G in the coal-fired boiler 10 to be averaged in the left and right directions, the burners on the front wall 11 and the rear wall 12 of the can Secondary air supplied into the coal-fired boiler 10 from each of the two-stage combustion ports 5 on the can front wall 11 and the can rear wall 12 according to the combination of the burner rows 4 to be used among the plurality of burner rows 4 in the group. It is controlled so that the flow rate is properly distributed.

  Specifically, as shown in FIG. 4, an influence gain (2) is assigned to the upper burner row 4U of the can front wall 11 and the two burner rows 4U and 4L of the can rear wall 12, respectively. An influence gain (1) is assigned to each of the middle and lower burner rows 4M and 4L of the front wall 11 and is treated as an influence gain (0) when neither is operating. As shown in the equation (1), the value Np obtained by subtracting the total influence gain R of the burner row 4 of the can rear wall 12 from the total influence gain F of the burner row 4 of the can front wall 11 during operation is burned. A numerical index for indexing the gas flow pattern is defined, and a predetermined value that divides the numerical index into large and small is defined as (0).

  In this embodiment, when the numerical index of the combustion gas flow pattern is not larger than a predetermined value, that is, when Np ≦ 0, under the low load condition, as shown in FIG. Since G is large and drifts toward the can front wall 11 side, the amount of secondary air is biased toward the two-stage combustion port 5 side of the can front wall 11 using the control program shown in the graph of FIG. Below, as shown in FIG. 7, since the combustion gas G drifts to the can rear wall 12 side and the oxygen concentration on the can rear wall 12 side becomes low, the amount of secondary air is reduced by two-stage combustion on the can rear wall 12. When the numerical index of the combustion gas flow pattern exceeds a predetermined value, that is, when Np> 0, under a low load condition, as shown in FIG. , Combustion gas G is large and drifts to the rear wall 12 side Therefore, using the control program shown in the graph of FIG. 9, the amount of secondary air is biased to the second combustion port 5 side of the can rear wall 12, and under a high load condition, as shown in FIG. Since the combustion gas G drifts to the can front wall 11 side and the oxygen concentration on the can front wall 11 side becomes low, control is performed to bias the amount of secondary air to the two-stage combustion port 5 side of the can front wall 11. I am doing so.

In the control unit 20, the two types of control programs shown in FIGS. 6 and 9 are automatically switched according to the magnitude of the numerical index representing the combustion gas flow pattern.
[Example 1]
Next, an embodiment of a method for operating the coal fired boiler apparatus 1 will be described.

The broken lines in FIG. 11 indicate when the upper and middle burner rows 4U and 4M of the can front wall 11 and the lower burner row 4L of the can rear wall 12 in the coal burning boiler 10 of the coal burning boiler apparatus 1 are used. The flow of unstable combustion gas G when the inside of the coal-fired boiler 10 is in a low load state is shown.
In this situation, the control unit 20 affects the burner rows 4U and 4M of the can front wall 11 and the burner row 4L of the can rear wall 12 in operation in the manner described above in the influence gains (2), (1), (2). Are assigned, and numerical index Np = 1> 0 is calculated using equation (1). Based on this result, the control program shown in the graph of FIG. As shown in FIG. 12, the opening degree of the can front side damper 6 is reduced and the opening degree of the can rear side damper 7 is increased, as shown in FIG.

In this way, when the amount of secondary air is biased toward the second-stage combustion port 5 side of the can rear wall 12, the flow of the combustion gas G is corrected as shown by the thick line in FIG. As shown in FIG. 5, both NOx fluctuation and outlet temperature fluctuation of the reheater 14 are stabilized.
[Example 2]
FIG. 15A shows the case where the upper, middle and lower burner rows 4U, 4M and 4L of the can front wall 11 in the coal burning boiler 10 of the coal burning boiler apparatus 1 are used, and the inside of the coal burning boiler 10 is inside. In a low load situation, the flow of the combustion gas G drifts toward the rear wall 12 of the can, and the residence time in the coal-fired boiler 10 increases, so that the front wall 11 of the flow of the combustion gas G This shows a situation in which a space S is formed on the side and the tendency becomes unstable.

  In this situation, as shown in FIG. 15 (b), in the control unit 20, the influence gains (2), (1), After assigning each (1), the numerical index Np = 4> 0 is calculated using the equation (1), and based on this result, the control program shown in the graph of FIG. 9 is automatically adopted, In order to bias the amount of secondary air toward the second combustion port 5 side of the can rear wall 12, the opening of the can front side damper 6 is reduced and the opening of the can rear side damper 7 is increased.

In this way, when the amount of secondary air is biased toward the second-stage combustion port 5 side of the can rear wall 12, the flow of the combustion gas G is corrected, and both NOx fluctuations and outlet temperature fluctuations of the reheater 14 are both changed. It will be stable.
[Example 3]
FIG. 16A shows a case where the lower burner row 4L of the can front wall 11 and the upper and lower burner rows 4U and 4L of the can rear wall 12 in the coal burning boiler 10 of the coal burning boiler apparatus 1 are used. When the inside of the coal-fired boiler 10 is in a low load state, the flow of the combustion gas G drifts to the can front wall 11 side, and the residence time in the coal-fired boiler 10 is reduced. This shows a situation in which a space S is generated on the side of the rear wall 12 of the flow and the tendency becomes unstable.

  In this situation, as shown in FIG. 16 (b), the control unit 20 affects the burner row 4L of the can front wall 11 and the burner rows 4U and 4L of the can rear wall 12 in the above-described manner. After assigning 1), (2), and (2), the numerical index Np = −3 ≦ 0 is calculated using the equation (1). Based on this result, the control program shown in the graph of FIG. In order to bias the amount of secondary air to the second combustion port 5 side of the can front wall 11, the opening of the can front damper 6 and the opening of the can rear damper 7 are increased. Decrease.

In this way, when the amount of secondary air is biased toward the second stage combustion port 5 side of the can front wall 11, the flow of the combustion gas G is corrected, and both NOx fluctuations and outlet temperature fluctuations of the reheater 14 are corrected. It will be stable.
[Example 4]
FIG. 17 (a) uses the upper, middle and lower burner rows 4U, 4M, 4L of the can front wall 11 and the lower burner row 4L of the can rear wall 12 in the coal fired boiler 10 of the coal fired boiler apparatus 1. In the case where the coal burning boiler 10 is in a high load state, the flow of the combustion gas G drifts to the can front wall 11 side, and oxygen on the can front wall 11 side above the coal burning boiler 10 It shows a situation where the concentration is low.

  In this situation, the control unit 20 affects the burner rows 4U, 4M, 4L of the can front wall 11 and the burner row 4L of the can rear wall 12 in the manner described above, as shown in FIG. After assigning the gains (2), (1), (1), and (2), the numerical index Np = 2> 0 is calculated using the equation (1). The control program shown in the graph is automatically adopted to increase the opening of the front damper 6 and the rear side of the can in order to bias the amount of secondary air toward the second combustion port 5 side of the front wall 11 of the can. The opening degree of the damper 7 is decreased.

In this way, when the amount of secondary air is biased toward the second stage combustion port 5 side of the can front wall 11 to supply and correct oxygen necessary for combustion, the flow of the combustion gas G at the outlet of the coal-fired boiler 10 is stabilized. Will be.
[Example 5]
18 (a) uses the middle and lower burner rows 4M and 4L of the can front wall 11 and the upper and lower burner rows 4U and 4L of the can rear wall 12 in the coal fired boiler 10 of the coal fired boiler apparatus 1. FIG. When the inside of the coal-fired boiler 10 is in a high load state, the flow of the combustion gas G drifts to the can rear wall 12 side, and the oxygen concentration on the can rear wall 12 side above the coal fired boiler 10 Indicates a situation where the value is low.

  In this situation, as shown in FIG. 18B, the control unit 20 affects the burner rows 4M and 4L of the can front wall 11 and the burner rows 4U and 4L of the can rear wall 12 in the manner described above. After assigning the gains (1), (1), (2), and (2), the numerical index Np = −2 ≦ 0 is calculated using the equation (1), and based on this result, FIG. The control program shown in the graph is automatically adopted to reduce the opening of the front damper 6 and the rear side of the can in order to bias the amount of secondary air to the second combustion port 5 side of the rear wall 12 of the can. The opening degree of the damper 7 is increased.

As described above, when the amount of secondary air is biased toward the second combustion port 5 side of the rear wall 12 of the can to correct supply of oxygen necessary for combustion, the flow of the combustion gas G at the outlet of the coal-fired boiler 10 is stabilized. Will be.
As described above, in the coal fired boiler apparatus 1 according to this embodiment, the flow state of the combustion gas G in the coal fired boiler 10 is corrected regardless of whether the coal fired boiler 10 is in a high load state or a low load state. Thus, the vehicle can always be operated in a stable state.

It is a perspective explanatory view of a coal burning boiler which is an opposed combustion boiler showing one embodiment of an opposed combustion boiler device concerning the present invention. It is system | strain explanatory drawing which shows the air supply system and control system of a coal fired boiler apparatus which is an opposing combustion boiler apparatus in FIG. FIG. 1 is a perspective explanatory view showing a state where the combustion gas flow in the coal burning boiler in FIG. 1 is deviated left and right, and a state where the combustion gas flow is averaged by biasing the amount of secondary air to the left and right. It is a perspective explanatory view (b). FIG. 2 is an explanatory diagram of an influence gain assignment procedure performed on a burner in order to numerically index a combustion gas flow pattern in the coal burning boiler in FIG. 1. FIG. 2 is an explanatory diagram of a bias procedure when a numerical index of combustion gas flow in the coal burning boiler in FIG. 1 is equal to or less than a predetermined value and when the inside of the coal burning boiler is in a low load state. It is a graph which shows the control program used when the numerical index of the combustion gas flow in the coal burning boiler in FIG. 1 is below a predetermined value. FIG. 3 is an explanatory diagram of a bias procedure when a numerical index of a combustion gas flow in the coal burning boiler in FIG. 1 is equal to or less than a predetermined value and when the inside of the coal burning boiler is in a high load state. FIG. 2 is an explanatory diagram of a bias procedure when the numerical index of the combustion gas flow in the coal burning boiler in FIG. 1 exceeds a predetermined value and when the inside of the coal burning boiler is in a low load state. It is a graph which shows the control program used when the numerical index of the combustion gas flow in the coal burning boiler in FIG. 1 exceeds predetermined. FIG. 2 is an explanatory diagram of a bias procedure when a numerical index of a combustion gas flow in the coal burning boiler in FIG. 1 exceeds a predetermined value and when the inside of the coal burning boiler is in a high load state. It is bias point explanatory drawing which shows the operation method by one Example of the coal burning boiler apparatus which is an opposing combustion boiler apparatus in FIG. It is a graph which shows the damper opening degree during driving | operation of the coal burning boiler apparatus of FIG. It is a graph which shows transition of NOx fluctuation | variation during operation | movement of the coal burning boiler apparatus of FIG. It is a graph which shows transition of the reheater exit temperature fluctuation | variation in the driving | operation of the coal burning boiler apparatus of FIG. It is state explanatory drawing (a), (b) of the combustion gas flow before and behind the bias of the amount of secondary air which shows the operating method by the other Example of the coal burning boiler apparatus which is an opposing combustion boiler apparatus of FIG. FIG. 6 is an explanatory diagram (a) and (b) of the state of combustion gas flow before and after the bias of the secondary air amount, showing an operation method according to still another embodiment of the coal burning boiler device which is the opposed combustion boiler device of FIG. 1. FIG. 6 is an explanatory diagram (a) and (b) of the state of combustion gas flow before and after the bias of the secondary air amount, showing an operation method according to still another embodiment of the coal burning boiler device which is the opposed combustion boiler device of FIG. 1. FIG. 6 is an explanatory diagram (a) and (b) of the state of combustion gas flow before and after the bias of the secondary air amount, showing an operation method according to still another embodiment of the coal burning boiler device which is the opposed combustion boiler device of FIG. 1.

Explanation of symbols

1 Coal-fired boiler equipment (opposed combustion boiler equipment)
3 Burner 4 (4U, 4M, 4L) Burner row 5 (5A) Two-stage combustion port 6 Can front side damper 7 Can rear side damper 10 Coal-fired boiler (opposed combustion boiler)
11 Can front wall 12 Can rear wall 20 Control part G Combustion gas Np Numerical index

Claims (6)

A burner group formed by arranging a plurality of burner rows in which a plurality of burners to which fuel and primary air are supplied are arranged in the horizontal direction and arranged in a plurality of stages in the vertical direction; and the burner group positioned above the burner group An opposed combustion boiler having a can front wall and a can rear wall facing each other and having a two-stage combustion port for passing secondary air supplied by bypassing
The opposed combustion boiler provided with a can front side damper and a can rear side damper for adjusting the amount of secondary air supplied into the opposed combustion boiler through the respective two-stage combustion ports on the front and rear walls of the opposed combustion boiler In the device
Assigning an influence gain corresponding to the degree of the influence on the flow of combustion gas in the opposed combustion boiler to each of a plurality of burner rows in each burner group arranged on the can front wall and the can rear wall, A control unit that indexes the flow pattern of the combustion gas by a numerical index calculated based on the influence gain assigned to the burner row used during operation;
The control unit associates the load index in the opposed combustion boiler with the numerical index representing the combustion gas flow pattern, and passes through the two-stage combustion ports on the front wall and the rear wall of the opposed combustion boiler. The counter-combustion boiler apparatus, wherein the can front side damper and the can rear side damper are operated so as to optimize the amount of secondary air supplied into the counter combustion boiler.   The control unit is configured such that the can in the counter-combustion boiler is in accordance with the magnitude of the numerical index representing a combustion gas flow pattern in each of a high-load condition and a low-load condition in the counter-combustion boiler. Two kinds of control programs for operating the can front side damper and the can rear side damper, respectively, in order to optimize the amount of secondary air supplied into the opposing combustion boiler through the two-stage combustion ports on the front wall and the rear wall of the can The opposing combustion boiler apparatus of Claim 1 which has.   3. The opposed combustion boiler apparatus according to claim 2, wherein in the control unit, the two types of control programs are automatically switched according to the magnitude of a numerical index representing the combustion gas flow pattern. A burner group formed by arranging a plurality of burner rows in which a plurality of burners to which fuel and primary air are supplied are arranged in the horizontal direction and arranged in a plurality of stages in the vertical direction; and the burner group positioned above the burner group A method of operating an opposed combustion boiler apparatus having an opposed combustion boiler having a can front wall and a can rear wall facing each other having a plurality of two-stage combustion ports through which secondary air supplied by bypassing is passed. ,
Assigning an influence gain corresponding to the degree of the influence on the flow of combustion gas in the opposed combustion boiler to each of a plurality of burner rows in each burner group arranged on the can front wall and the can rear wall, The flow pattern of combustion gas is indexed by a numerical index calculated based on the influence gain assigned to the burner row used during operation,
By applying the load condition in the counter combustion boiler to the numerical index representing the flow pattern of the combustion gas, the counter combustion boiler has a two-stage combustion port on the front wall and the rear wall of the counter combustion boiler. A method for operating an opposed combustion boiler device, characterized by optimizing the amount of secondary air supplied to the boiler.   When the numerical index indicating the flow pattern of the combustion gas has a magnitude equal to or smaller than a predetermined value, one control program is used to set each two-stage combustion port on the front wall and the rear wall of the counter combustion boiler. When the numerical index indicating the flow pattern of the combustion gas exceeds a predetermined value, the other control program is used to optimize the amount of secondary air supplied to the counter combustion boiler through the counter control boiler. The operation method of the opposing combustion boiler apparatus of Claim 4 which optimizes the quantity of the secondary air supplied in this opposing combustion boiler through each two-stage combustion port of the can front wall and can rear wall in a combustion boiler.   The operation method of the opposed combustion boiler apparatus according to claim 5, wherein the one control program and the other control program are automatically switched according to the magnitude of a numerical index representing the combustion gas flow pattern.

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