JP2013155975A - Pressure fluidized furnace system and control method thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pressure fluidized furnace system that can effectively utilize a combustion exhaust gas that is exhausted from a pressure fluidized furnace and can stably drive a supercharger that supplies a combustion air to the pressure fluidized furnace and to provide a control method thereof.SOLUTION: The above problem is solved by executing the following steps: a first step of maintaining a temperature of combustion exhaust gas that is exhausted from a pressure fluidized furnace at a predetermined temperature, a second step of maintaining an exhaust amount of combustion air that is exhausted from a compressor of a supercharge at a predetermined flow rate, and a third step of increasing an exhaust amount of the combustion air that is exhausted from the compressor of the supercharger when a temperature in the pressure fluidized furnace becomes higher than the predetermined temperature in the first step.

Description

  The present invention relates to a pressurized fluidized furnace system for burning an object to be treated such as sewage sludge, biomass, dust, sewage sludge, municipal waste, and more specifically, combustion exhaust gas discharged from a pressurized fluidized furnace. The present invention relates to a pressurized fluidized furnace system provided with a waste heat boiler on the upstream side of a supercharger that supplies combustion air to the pressurized fluidized furnace in order to increase the utilization rate.

2. Description of the Related Art A pressurized flow furnace system that performs a combustion treatment of a workpiece under pressure is known. In this system, the turbocharger is driven using the thermal energy and pressure of the combustion exhaust gas discharged from the pressurized fluidized furnace to generate compressed air, and this compressed air is required for combustion in the pressurized fluidized furnace. It is a combustion system characterized by making it into the combustion air. Since combustion air can be generated from the combustion exhaust gas generated when the object to be processed is burned in this way, there is no need to provide a blower for supplying the combustion air, and development is progressing as an energy-saving combustion facility. .
In such a pressurized fluidized furnace system, a waste heat boiler is disposed downstream of a supercharger that supplies combustion air to the pressurized fluidized furnace, heat recovery is performed, and steam discharged from the waste heat boiler is removed. There has been proposed a pressurized incinerator facility that reduces the amount of combustion exhaust gas that is reduced to the upstream side of the supercharger and supplied to the supercharger (Patent Document 1). Conventionally, in a normal pressure fluidized bed combustion furnace, a waste heat boiler is arranged in parallel with the air preheater. The combustion air supplied into the furnace controls the temperature supplied into the furnace by bypassing a part of the combustion air supplied from the supply fan to the air preheater. On the other hand, control is performed to adjust the amount of exhaust gas supplied to the waste heat boiler so that the inlet temperature of the dust collector falls within a predetermined range (Patent Document 2).

JP-A-63-46313 JP 2008-25965 A

Since the waste heat boiler described in Patent Document 1 is disposed only on the downstream side of the supercharger, heat from the combustion exhaust gas is generated due to heat radiation from the pipes and equipment on the way, and consumption of thermal energy by the supercharger. There was a possibility that the recovery rate was low.
Since the invention described in Patent Document 2 limits the amount of exhaust gas supplied to the waste heat boiler so that the inlet temperature of the dust collector is in a predetermined range, the ability of the waste heat boiler could not be sufficiently exhibited. . In recent years, when the moisture content of the material to be treated has been decreasing and a material to be treated with a high calorific value is supplied, an air damper installed in a pipe for supplying combustion air to the incinerator without using an air preheater is installed. Even if it is fully opened, the furnace temperature may not decrease.

  Therefore, the main problem of the present invention is to realize a pressurized fluidized furnace system that increases the heat recovery rate of the combustion exhaust gas discharged from the pressurized fluidized furnace, while ensuring the amount of combustion air supplied from the supercharger, It is to implement a control for performing heat recovery more simply.

The present invention and effects obtained by solving the above problems are as follows.
The first invention includes a pressurized fluidizing furnace that combusts an object to be processed, a turbine that is rotated by combustion exhaust gas discharged from the pressurized fluidizing furnace, and a compressor that is rotated as the turbine rotates. A supercharger, an air preheater and steam for exchanging heat between the combustion exhaust gas discharged from the pressurized fluidized furnace and the combustion air supplied to the pressurized fluidized furnace between the pressurized fluidized furnace and the supercharger In a pressurized fluidized furnace system with waste heat boilers that generate
A first step of maintaining the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace at a predetermined temperature;
A second step of maintaining the discharge amount of the combustion air discharged from the compressor of the supercharger at a predetermined flow rate;
In the first step, a third step of increasing the discharge amount of combustion air discharged from the compressor of the supercharger when the in-furnace temperature of the pressurized fluidized furnace becomes higher than a predetermined temperature. It is characterized by performing.

(Function and effect)
A first step of maintaining the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace at a predetermined temperature, and a second step of maintaining the discharge amount of the combustion air discharged from the compressor of the supercharger at a predetermined flow rate. Thus, the pressurized fluidized furnace system can be stably operated by the combustion exhaust gas. Further, in the first procedure, there is provided a third step of increasing the discharge amount of the combustion air discharged from the compressor of the supercharger when the in-furnace temperature of the pressurized flow furnace becomes higher than a predetermined temperature. Therefore, the abnormal rise in the furnace temperature is suppressed and the safety of the pressurized fluidized furnace system is excellent.

  According to a second aspect of the present invention, in the configuration of the first aspect of the present invention, in the first step, when the in-furnace temperature of the pressurized fluidized furnace becomes higher than a predetermined temperature, an object to be processed into the pressurized fluidized furnace. It is characterized by comprising the 4th process which reduces supply_amount | feed_rate.

(Function and effect)
Since the fourth step of reducing the supply amount of the object to be processed to the pressurized fluidized furnace is provided, an abnormal rise in the furnace temperature can be quickly suppressed, and the safety of the pressurized fluidized furnace system is improved.

  A third invention is characterized in that, in the configuration of the second invention, the fourth step is performed after the third step.

(Function and effect)
Since the 4th process is performed after the 3rd process, the amount of change of the processed object consumed by combustion can be controlled, and the processed object can be burned and incinerated systematically.

  According to a fourth invention, in the configuration of the first to third inventions, the first step is performed by changing a ratio of a combustion exhaust gas amount supplied to the air preheater and a combustion exhaust gas amount supplied to the waste heat boiler. And

(Function and effect)
The first step is performed by changing the ratio of the amount of combustion exhaust gas supplied to the air preheater and the amount of combustion exhaust gas supplied to the waste heat boiler, so that heat recovery of the combustion exhaust gas is excellent, and the temperature of the combustion exhaust gas is set to a predetermined temperature. It can be adjusted quickly.

  According to a fifth aspect of the present invention, in the configuration of the first to third aspects of the invention, the second step is performed by increasing or decreasing the amount of boiler water supplied to the waste heat boiler, or by opening and closing a flow regulator provided near the supply port of the supercharger. It is characterized by performing.

(Function and effect)
The second step is performed by increasing / decreasing the amount of boiler water supplied to the waste heat boiler, or by opening / closing a flow regulator provided in the vicinity of the supply port of the supercharger, so that the temperature of the combustion exhaust gas supplied to the supercharger is adjusted. It can be adjusted quickly and over a wide range.

  According to a sixth aspect of the present invention, in the configuration of the first to third aspects, the third step is performed by increasing or decreasing the amount of boiler water supplied to the waste heat boiler, or by opening and closing a flow regulator provided in the vicinity of the supply port of the supercharger. It is characterized by performing.

(Function and effect)
This is done by increasing or decreasing the amount of boiler water supplied to the waste heat boiler, or by opening and closing the flow regulator provided in the vicinity of the supply port of the supercharger, so that the temperature of the combustion exhaust gas supplied to the supercharger can be quickly and widely Can be adjusted.

  According to a seventh aspect of the invention, in the configuration of the second or third aspect of the invention, in the fourth step, the rotational speed of the input pump that conveys the object to be processed is reduced, or the flow rate adjusting valve installed in the pipe that supplies the object to be processed It is performed by opening and closing.

(Function and effect)
The fourth step is performed by decelerating the rotation speed of the input pump that conveys the object to be processed, or by opening and closing the flow rate adjustment valve installed in the pipe that supplies the object to be processed. Increase can be suppressed.

According to an eighth aspect of the present invention, there is provided a pressurized fluidizing furnace that combusts the workpiece, a turbine that is rotated by the combustion exhaust gas discharged from the pressurized fluidizing furnace, and a compressor that is rotated as the turbine rotates. A supercharger, an air preheater and steam for exchanging heat between the combustion exhaust gas discharged from the pressurized fluidized furnace and the combustion air supplied to the pressurized fluidized furnace between the pressurized fluidized furnace and the supercharger In a pressurized fluidized furnace system with waste heat boilers that generate
A first step of maintaining the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace at a predetermined temperature;
A second step of maintaining the discharge amount of the combustion air discharged from the compressor of the supercharger at a predetermined flow rate;
In the first procedure, a third step of increasing the discharge amount of combustion air discharged from the compressor of the supercharger when the in-furnace temperature of the pressurized fluidized furnace becomes higher than a predetermined temperature. A control method is provided.

(Function and effect)
A first step of maintaining the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace at a predetermined temperature, and a second step of maintaining the discharge amount of the combustion air discharged from the compressor of the supercharger at a predetermined flow rate. Since it has, it can be set as the pressurized flow furnace system which has the high heat recovery rate of combustion exhaust gas. Further, in the first procedure, there is provided a third step of increasing the discharge amount of the combustion air discharged from the compressor of the supercharger when the in-furnace temperature of the pressurized flow furnace becomes higher than a predetermined temperature. Therefore, it is possible to provide a pressurized flow furnace system that is excellent in safety and that suppresses an abnormal increase in the furnace temperature.

  A pressurized fluidized furnace system is proposed in which the utilization rate of combustion exhaust gas discharged from a pressurized fluidized furnace is increased, and a supercharger that supplies combustion air to the pressurized fluidized furnace can be driven stably.

It is explanatory drawing of the pressurized flow furnace system of 1st Embodiment. It is the elements on larger scale of FIG. It is the elements on larger scale of FIG. It is the elements on larger scale of FIG. It is explanatory drawing of the pressurized flow furnace system of 2nd Embodiment. It is the elements on larger scale of FIG. It is the elements on larger scale of FIG. It is the elements on larger scale of FIG.

  Hereinafter, a first embodiment of the present invention will be described in detail with reference to the accompanying drawings. In addition, in order to make an understanding easy, although it showed and demonstrated the direction for convenience, the structure is not limited by these.

<First Embodiment>
A pressurized flow furnace system 1 according to the first embodiment is shown in FIG. This system performs heat exchange between a storage device 10 for storing an object to be processed containing organic matter such as sewage sludge and municipal waste, a pressurized flow furnace 20 for incinerating the object to be processed, and combustion exhaust gas and combustion air. An air preheater 40 to be performed, a dust collector 50 that collects combustion ash, dust, and the like in the combustion exhaust gas, a turbine 61 that is rotated by the combustion exhaust gas, and a pressure fluidizing furnace 20 that rotates with the rotation of the turbine 61. A supercharger 60 having a compressor 62 for supplying combustion air to the interior and a flue gas treatment tower 80 for discharging combustion exhaust gas to the outside are provided.
A first waste heat boiler 100 that generates steam is provided in parallel with the gas preheater 40 between the pressurized fluidized furnace 20 and the dust collector 50, and the supercharger 60 and the flue gas treatment tower 80 are provided. A second waste heat boiler 110 that generates steam is provided therebetween.

(Storage device)
The storage device 10 stores an object to be processed such as sewage sludge that has been dehydrated to a moisture content of about 65 to 85% by mass.

As shown in FIGS. 1 and 2, a fixed amount feeder 11 that supplies a predetermined amount of an object to be processed to the pressurized fluidized furnace 20 is disposed at the lower part of the storage device 10. At the bottom of the quantitative feeder 11, a charging pump 12 that pumps the workpiece to the pressurized fluidized furnace 20 is disposed. As the input pump 12, a single screw pump, a piston pump or the like can be used.
A pipe for connecting the charging pump 12 and the pressurized fluidized furnace 20 may be provided with a workpiece heating apparatus 13C for heating the workpiece. At least one of steam discharged from the first waste heat boiler, the second waste heat boiler, or the power generation device 120 is supplied to the workpiece heating device 13C to heat the workpiece. As the workpiece heating device 13C, a double tube heat exchanger, a plate heat exchanger, or the like can be applied.

(Pressurized flow furnace)
The lower part of the pressurized fluidized furnace 20 is filled with solid particles such as sand having a predetermined particle diameter to be a fluidized medium. The pressurized fluidized furnace 20 maintains the fluidized state of a fluidized bed (sand layer) made of solid particles by the supplied combustion air, while the object to be treated supplied from the outside, city gas, heavy oil supplied as needed. Auxiliary fuel such as is burned.

As shown in FIGS. 1 and 2, the pressurized fluidized furnace 20 is provided with an auxiliary fuel combustion device 21 for heating the sand layer at the lower part of the side wall on one side, and at a position near the upper side of the auxiliary fuel combustion device 21. Is provided with a starter burner 22 for heating the sand layer at the start. Further, a water gun (not shown) for cooling the combustion exhaust gas is disposed at the upper part of the pressurized fluidized furnace 20, and when the temperature of the combustion exhaust gas rises to a predetermined temperature or higher, the cooling water is sprayed into the furnace. . The timing of spraying the cooling water from the water gun into the furnace is preferably performed before or after the fifth step described later or simultaneously with the fifth step.

A combustion air supply pipe 24 for supplying combustion air to the inside of the pressurized fluidized furnace 20 is disposed at the lower part of the side wall on the other side of the pressurized fluidized furnace 20, and the upper side wall having a reduced diameter is treated. A discharge port 90 </ b> A is formed through which exhaust gas and water vapor generated by the combustion of an object, auxiliary fuel, etc. are discharged to the outside.
A temperature sensor (first temperature sensor) 20 </ b> A is installed on the side wall of the pressurized fluidized furnace 20 in order to measure the temperature inside the pressurized fluidized furnace 20. In the present specification, exhaust gas and water vapor are collectively referred to as combustion exhaust gas.

(Air preheater)
The combustion exhaust gas discharged from the pressurized fluidized furnace 20 is supplied to the air preheater 40 installed at the rear stage of the pressurized fluidized furnace 20 through the pipe 90. In the air preheater 40, in order to increase the temperature of the combustion air supplied to the pressurized fluidized furnace 20, heat exchange between the combustion exhaust gas and the combustion air is performed indirectly. In addition, as the air preheater 40, it is desirable to use a shell and tube heat exchanger.

  As shown in FIGS. 1 and 3, the air preheater 40 has a supply port 90 </ b> B for supplying combustion exhaust gas having a pressure of 100 to 200 kPa discharged from the pressurized fluidized furnace 20 and a temperature of about 850 ° C. An exhaust port 91 </ b> A for discharging combustion air having a temperature of about 130 to 650 ° C. to the outside of the machine is formed in the upper part of the side wall formed. The combustion exhaust gas supply port 90 </ b> B is connected to the discharge port 90 </ b> A of the pressurized fluidized furnace 20 through the pipe 90, and the combustion air exhaust port 91 </ b> A is provided in the pressurized fluidized furnace 20 through the pipe 91. It is connected to the rear part of the combustion air supply pipe 24.

  A discharge port 92A for discharging combustion exhaust gas having a pressure of about 100 to 200 kPa and a temperature of about 200 to 700 ° C. is formed in the lower portion of the side wall on the other side of the air preheater 40. Is formed with a supply port 95B for supplying combustion air having a pressure of about 100 to 200 kPa and a temperature of about 10 to 140 ° C.

(First waste heat boiler)
The first waste heat boiler 100 is arranged in parallel with the air preheater 40 at the subsequent stage of the pressurized fluidized furnace 20, and in order to effectively utilize the combustion exhaust gas discharged from the pressurized fluidized furnace 20, the pressurized fluidized furnace 20. It is the apparatus which raises the temperature of the water supplied to the 1st waste heat boiler 100 with the combustion exhaust gas supplied from and makes it water vapor | steam. In addition, the installation position of the 1st waste heat boiler 100 is not limited in parallel with the air preheater 40, If it is between the pressurized fluidized furnace 20 and the supercharger 60, it will be in series with the air preheater 40. May be installed. In addition, although a well-known waste heat boiler can be used for the 1st waste heat boiler 100, it is preferable to employ | adopt a water pipe boiler especially.
As shown in FIGS. 1 and 3, the first waste heat boiler 100 is supplied with a combustion exhaust gas having a pressure of about 100 to 200 kPa discharged from the pressurized fluidized furnace 20 and a temperature of about 850 ° C. in the upper part thereof. A port 90C is formed, and a plurality of discharge ports 101A for discharging water vapor to the outside of the apparatus are formed in the upper part of the side wall. The combustion exhaust gas supply port 90C is connected to the discharge port 90A of the pressurized fluidized furnace 20 via a pipe 90, and the pipe 90 extends to the supply port 90C of the first waste heat boiler 100 at an intermediate portion. It has a branch pipe.

  A discharge port 92C for discharging combustion exhaust gas to the outside of the machine is formed in the lower part of the side wall on the other side of the first waste heat boiler 100, and water supplied from outside through the pump 81C is supplied to the lower part of the side wall in the machine. A supply port 101 </ b> C is formed to be supplied.

Above the first waste heat boiler 100, a steam drum 102 for storing water vapor generated by the first waste heat boiler 100 is disposed.
A plurality of supply ports 101B for supplying water vapor into the apparatus are formed in the lower part of the steam drum 102, and a discharge port 103A for discharging the stored water vapor to the outside of the apparatus is formed in the upper part. The steam supply port 101 </ b> B is connected to the discharge port 101 </ b> A of the first waste heat boiler 100 via the pipe 101.

Below the first waste heat boiler 100, a steam header 104 for removing moisture contained in the water vapor stored in the steam drum 102 is disposed.
On one side of the upper surface of the steam header 104, a supply port 103B for supplying the steam stored in the steam drum 102 into the machine, and a supply port 103C for supplying the steam discharged from the second waste heat boiler 110 described later into the machine. On the other side, a discharge port 105A for discharging the steam from which moisture has been removed to the outside of the machine is formed. The steam supply port 103B is connected to the discharge port 103A of the steam drum 102 via the pipe 103, and the supply port 103C is connected to the discharge port 110A of the second waste heat boiler 110 via the pipe 112. ing.

A power generation device 120 that generates power using steam is installed behind the steam header 104. As the power generation device 120, a steam turbine, a power generation device that rotates the screw rotor to generate power by the supplied steam, a heating medium that circulates in the device using the steam is evaporated, and a Rankine that drives the turbine by the evaporated heat medium A power generation device using a cycle can be employed.
A supply port 105 </ b> B for supplying steam is formed on one side of the upper surface of the power generation apparatus 120, and a discharge port 105 </ b> C for discharging the steam circulated in the first waste heat boiler 100 is formed on the other side. The supply port 105B for supplying steam is connected to the discharge port 105A of the steam header 104 via the pipe 105, and the steam discharged from the discharge port 105C of the power generator 120 is a heat exchanger for preventing white smoke. 70.

(Dust collector)
The combustion exhaust gas discharged from the air preheater 40 and the first waste heat boiler 100 is supplied to the dust collector 50 after joining. In the dust collector 50, impurities such as incinerated ash, dust, and fluidized sand in the combustion exhaust gas are removed. As the dust collector 50, a known dust collector such as a ceramic bag filter or a cyclone can be used, and a ceramic bag filter is particularly preferable.

  As shown in FIGS. 1 and 3, the dust collector 50 has a combustion at a pressure of 100 to 200 kPa and a temperature of 200 to 700 ° C. discharged from the air preheater 40 and the first waste heat boiler 100 at the lower part of one side wall. A supply port 92B for supplying exhaust gas into the machine is formed, and a discharge port 93A for discharging the combustion exhaust gas from which impurities and the like have been removed is formed at the upper part. The combustion exhaust gas supply port 92B is connected to the combustion exhaust gas discharge port 92A of the air preheater 40 and the combustion exhaust gas discharge port 92C of the first waste heat boiler 100 via the pipe 92, and the discharge port 92A. , 92C are provided with flow rate regulators 92G and 92H each composed of a damper or the like.

  In the dust collector 50, in order to remove impurities and the like mixed in the combustion exhaust gas, a ceramic bag filter or the like is provided between the supply port 92B formed in the lower portion and the discharge port 93A formed in the upper portion in the vertical direction. A filter (not shown) to be selected is built in. Impurities and the like in the combustion exhaust gas removed by the filter are temporarily stored at the bottom in the dust collector 50 and then periodically discharged to the outside.

(Supercharger)
The supercharger 60 is arranged at the rear stage of the dust collector 50, the turbine 61 rotated by the combustion exhaust gas discharged from the dust collector 50, the shaft 63 that transmits the rotation of the turbine 61 to the compressor 62, and the shaft 63 And a compressor 62 that rotates to generate combustion air as the turbine 61 is transmitted through the compressor.

  As shown in FIGS. 1 and 3, the supercharger 60 has a supply port for supplying combustion exhaust gas having a pressure of 100 to 200 kPa and a temperature of 200 to 650 ° C. discharged from the dust collector 50 into the lower part of the turbine 61. 93E is formed, and a discharge port 97E for discharging combustion exhaust gas to the outside of the machine is formed at the side of the turbine 61. The combustion exhaust gas supply port 93E is connected to the exhaust port 93A of the dust collector 50 via a pipe 93, and a temperature sensor (a second sensor) for measuring the temperature of the supplied combustion exhaust gas is provided near the supply port 93E. A temperature sensor 93F is arranged.

A supply port 67E for supplying air into the machine is formed at the side of the compressor 62 of the supercharger 60. Combustion air having a pressure of 150 to 200 kPa and a temperature of about 15 to 150 ° C. is outside the machine at the upper part of the compressor 62. A discharge port 94E is formed to discharge the gas.
The air supply port 67E is connected to the starter blower 65 through pipes 67, 66, and the combustion air discharge port 94E is connected to the supply port 95B of the air preheater 40 through the pipes 94, 96, 95 and the pipe. 94 and 96 are connected to and controlled by the rear part of the starter burner 22 of the pressurized fluidized furnace 20.

(Starting blower)
The starter blower 65 is a device that supplies combustion air to the starter burner 22 when the pressurized fluidized furnace system 1 is started. Further, the starter blower 65 reduces the combustion exhaust gas supplied to the turbine 61 of the supercharger 60 and the combustion air discharged from the compressor 62 due to the interruption of the supply of the object to be processed from the storage device 10. In such a case, it also has a function of forcibly supplying outside air to the compressor 62.

  The storage device 10 is connected to a pipe 16 via a pipe 15 in order to deodorize the odor gas generated from the object to be processed by burning it in the pressurized fluidized furnace 20. In addition, a flow meter 95G that measures the amount of combustion air discharged from the compressor 62 of the supercharger 60 is provided.

(Second waste heat boiler)
The second waste heat boiler 110 is arranged at the rear stage of the supercharger 60, and in order to effectively use the combustion exhaust gas discharged from the supercharger 60, the second waste heat boiler 110 is discharged by the combustion exhaust gas supplied from the supercharger 60. This is a device that raises the temperature of the water supplied to the heat boiler 110 to produce water vapor.

  As shown in FIGS. 1 and 4, the second waste heat boiler 110 has a supply port 97 </ b> B for supplying combustion exhaust gas having a temperature of 200 to 550 ° C. discharged from the supercharger 60 into the side wall on one side wall. An exhaust port 98A for discharging the combustion exhaust gas to the outside of the machine is provided on the other side wall. In addition, a supply port 110B for supplying water supplied from the outside via the pump 81C into the machine and a discharge port 110A for discharging the water vapor generated in the second waste heat boiler 110 to the outside are provided in the upper part. It has been. In addition, an ash discharge device 110C including, for example, a valve or the like for discharging dust and the like accumulated inside is provided at the lower portion. In addition, although a well-known boiler can be employ | adopted for the 2nd waste heat boiler 110, a water pipe boiler is suitable.

  The combustion exhaust gas supply port 97 </ b> B is connected to a discharge port 97 </ b> E of the supercharger 60 through a pipe 97. Further, the pipe 93 and the pipe 97 are connected by a pipe 114, and the pipe 114 is provided with a flow rate regulator (second flow rate regulator) 114D for adjusting the flow rate of the combustion exhaust gas supplied to the supercharger 60. .

(Heat exchanger for white smoke prevention)
The white smoke prevention heat exchanger 70 is an apparatus that indirectly exchanges heat between the water vapor supplied from the power generation device 120 and the white smoke prevention air supplied from the white smoke prevention fan 65A. A shell and tube heat exchanger or a plate heat exchanger can be used as the white smoke prevention heat exchanger 70.

As shown in FIGS. 1 and 4, the white smoke prevention heat exchanger 70 has white smoke at a pressure of 3 to 10 kPa and a temperature of about 10 to 40 ° C. discharged from the white smoke prevention fan 65 </ b> A on one side wall. A supply port 70A for supplying prevention air into the apparatus is formed, and a supply port 70B for supplying water vapor discharged from the second waste heat boiler 110 into the apparatus is formed at the bottom.
The other side wall is formed with a discharge port 70C for discharging white smoke prevention air, which has been raised to a temperature of about 70 to 95 ° C. by heat exchange, to the outside, and the upper portion discharges water vapor to the outside. A discharge port 70D is formed.

(Smoke exhaust treatment tower)
The flue gas treatment tower 80 is a device that prevents the impurities contained in the combustion exhaust gas from being discharged to the outside, and a chimney 87 is disposed on the upper part of the flue gas treatment tower 80. In addition, although the chimney 87 is installed in the upper part of the flue gas processing tower 80, you may install independently from a flue gas processing tower, without being limited to this.

  As shown in FIGS. 1 and 4, the flue gas treatment tower 80 has a supply port 98 </ b> B for supplying combustion exhaust gas discharged from the second waste heat boiler 110 into the machine at the lower part of the side wall on one side. A supply port 99 </ b> B that supplies white smoke prevention air discharged from the white smoke prevention heat exchanger 70 to the chimney 87 is formed in the lower portion of the side wall on one side of the chimney 87. The combustion exhaust gas supply port 98 </ b> B is connected to a discharge port 98 </ b> A formed on the side wall of the second waste heat boiler 110 via a pipe 98, and the white smoke prevention air supply port 99 </ b> B is connected via a pipe 99. It is connected to an outlet 70 </ b> C formed on the side wall of the white smoke prevention heat exchanger 70.

  A spray pipe 84 for spraying water supplied from the outside into the apparatus is disposed on the upper side wall on the other side of the flue gas treatment tower 80, and the intermediate part and the lower part are respectively connected via a circulation pump 83. A spray pipe 85 for spraying caustic soda water containing caustic soda stored at the bottom of the smoke treatment tower 80 into the apparatus is disposed.

  Caustic soda water stored in the flue gas treatment tower 80 is supplied from a caustic soda tank via a caustic soda pump, and is always maintained at an appropriate amount. Moreover, the heat utilization apparatus which collect | recovers and reuses the thermal energy which has the waste_water | drain of the temperature 50-80 degreeC discharged | emitted from the flue gas processing tower 80 can be provided. Binary power generation (not shown) or the like can be used as the heat utilization device.

  The combustion exhaust gas supplied to the flue gas treatment tower 80 is mixed with white smoke prevention air after impurities and the like are removed, and is discharged from the chimney 87 to the outside.

(Control of combustion exhaust gas)
In order to maintain the steady operation of the pressurized fluidized furnace system 1, a predetermined amount of combustion exhaust gas discharged from the pressurized fluidized furnace 20 is supplied to the turbine 61 of the supercharger 60, and is rotated as the turbine 61 rotates. It is necessary to supply a predetermined amount of combustion air discharged from the moving compressor 62 to the pressurized fluidized furnace 20.

  First, as a first step, according to the measured value of the first temperature sensor 20A disposed on the side wall of the pressurized fluidized furnace 20 in order to maintain the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace 20 at a predetermined temperature. Then, the flow rate adjuster 92G disposed in the vicinity of the discharge port 92A of the air preheater 40 is driven to adjust the supply amount of the combustion exhaust gas supplied to the air preheater 40.

When the measured value of the first temperature sensor 20A is lower than a predetermined temperature (650 to 900 ° C.), the flow regulator (first flow regulator) 92G is driven in the opening direction and supplied to the air preheater 40. The amount of combustion exhaust gas supplied is increased, the amount of heat supplied to the air preheater 40 is increased, and the temperature of the combustion air is increased. As a result, the combustion air whose temperature has been raised is supplied to the pressurized fluidized furnace 20, so that the temperature of the pressurized fluidized furnace 20 rises, and the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace 20 can be increased. it can.
On the other hand, when the measured value of the first temperature sensor 20A is higher than a predetermined temperature (650 to 900 ° C.), the air flow preheater 40 is driven by driving the flow rate regulator (first flow rate regulator) 92G in the closing direction. The amount of combustion exhaust gas supplied to is reduced, the amount of heat supplied to the air preheater is reduced, and the temperature of the combustion air is lowered. As a result, the combustion air whose temperature has been lowered is supplied to the pressurized fluidized furnace 20, so that the temperature of the pressurized fluidized furnace 20 is lowered and the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace 20 is lowered. it can.
In the first step, the flow rate regulator (first flow rate regulator) 92G of the air preheater 40 is driven to adjust the supply amount of the combustion exhaust gas supplied to the air preheater 40. It is also possible to adjust the supply amount of the combustion exhaust gas supplied to the air preheater 40 by driving the flow rate adjuster 92H disposed in the vicinity of the discharge port 92C of the first waste heat boiler 100.

  Next, as a second step, in order to maintain the discharge amount of the combustion air discharged from the compressor 62 of the supercharger 60 at a predetermined flow rate, it is arranged in a pipe 95 connecting the supercharger 60 and the air preheater 40. The pump 81C is driven according to the measured value of the flow meter 95G, and the supply amount of water supplied to the first waste heat boiler 100 is adjusted.

When the measured value of the flow meter 95G is lower than a predetermined set value calculated based on the auxiliary fuel supply amount and the workpiece supply amount, the rotational speed of the pump 81C is decreased and / or the flow control valve 81E is opened. Is adjusted in the closing direction to reduce the amount of water supplied to the first waste heat boiler 100, thereby increasing the temperature of the combustion exhaust gas discharged from the first waste heat boiler 100. As a result, the combustion exhaust gas whose temperature has risen is supplied to the turbine 61 of the supercharger 60, so that the rotational speed of the turbine 61 increases and the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates. The amount of combustion air discharged from the air increases.
On the other hand, when the measured value of the flow meter 95G is higher than a predetermined set value, the first waste heat boiler 100 is adjusted by increasing the rotational speed of the pump 81C and / or adjusting the opening of the flow control valve 81E in the opening direction. The supply amount of the water supplied to is increased, and the temperature of the combustion air discharged from the first waste heat boiler 100 is lowered. As a result, the combustion air whose temperature has been reduced is supplied to the turbine 61 of the supercharger 60, so that the rotational speed of the turbine 61 is reduced and the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates rotates. The amount of exhausted combustion air is reduced.

  Further, instead of the second step, as a third step, in order to maintain the discharge amount of the combustion air discharged from the compressor 62 of the supercharger 60 at a predetermined discharge amount, the supercharger 60 and the air preheater 40 are provided. In accordance with the measurement value of the flow meter 95G arranged in the pipe 95 to be connected, the flow regulator 114D arranged in the pipe 114 is driven, and the second waste heat is passed through the pipe 114 without going through the supercharger 60. The supply amount of the combustion exhaust gas supplied to the boiler 110 can also be adjusted.

When the measured value of the flow meter 95G is lower than a predetermined set value, the flow rate regulator 114D is driven to reduce the supply amount of the combustion exhaust gas that flows through the pipe 114 and is supplied to the second waste heat boiler 110. Accordingly, since a large amount of combustion exhaust gas is supplied to the turbine 61 of the supercharger 60, the rotational speed of the turbine 61 is increased and discharged from the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates. The amount of combustion air discharged increases.
On the other hand, when the measured value of the flow meter 95G is lower than a predetermined set value, the flow rate regulator 114D is driven to increase the supply amount of the combustion exhaust gas that flows through the pipe 114 and is supplied to the second waste heat boiler 110. . Thereby, since a small amount of combustion exhaust gas is supplied to the turbine 61 of the supercharger 60, the rotational speed of the turbine 61 is reduced and discharged from the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates. The amount of discharged combustion air is reduced.

Further, in place of the second step, the third step, or as the fourth step, in order to maintain the discharge amount of the combustion air discharged from the compressor 62 of the supercharger 60 at a predetermined flow rate, the supply port of the supercharger 60 The water supplied to the first waste heat boiler 100 is adjusted by adjusting the rotational speed of the pump 81C and / or the opening of the flow control valve 81E according to the measured value of the second temperature sensor 93F disposed in the vicinity of 93E. It is also possible to adjust the supply amount.
Note that the first step to the fourth step do not need to specify the control order and are preferably performed simultaneously.

When the measured value of the second temperature sensor 93F is lower than a predetermined set value (250 to 650 ° C.), the rotational speed of the pump 81C is decreased and / or the opening degree of the flow control valve 81E is adjusted in the closing direction. The amount of water supplied to the waste heat boiler 100 is decreased, and the temperature of the combustion exhaust gas discharged from the first waste heat boiler 100 is increased. As a result, the combustion exhaust gas whose temperature has risen is supplied to the turbine 61 of the supercharger 60, so that the rotational speed of the turbine 61 increases and the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates. The amount of combustion air discharged from the air increases.
On the other hand, when the measured value of the second temperature sensor 93F is higher than a predetermined set value (250 to 650 ° C.), the rotational speed of the pump 81C is increased or the opening degree of the flow control valve 81E is adjusted in the opening direction. The amount of water supplied to the first waste heat boiler 100 is increased, and the temperature of the combustion air discharged from the first waste heat boiler 100 is lowered. As a result, the combustion exhaust gas whose temperature has been lowered is supplied to the turbine 61 of the supercharger 60, so that the rotational speed of the turbine 61 is reduced and the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates rotates. The amount of exhausted combustion air is reduced.

  Next, as a fifth step, the measured value of the flow meter 95G disposed in the pipe 95 connecting the supercharger 60 and the air preheater 40 in order to maintain the in-furnace temperature of the pressurized flow furnace 20 at a predetermined temperature. Accordingly, the pump 81C is driven to adjust the amount of combustion air supplied to the pressurized fluidized furnace 20 via the supercharger 60. The fifth step is performed when the furnace temperature still does not decrease to a predetermined temperature (650 to 900 ° C.) even if the amount of combustion exhaust gas supplied to the air preheater 40 is decreased to the minimum amount in the first step. .

In the fifth step, in order to lower the furnace temperature, a second set value having a flow rate higher than the set value calculated based on the auxiliary fuel supply amount and the workpiece supply amount in the second step is set, and the flow meter If the measured value of 95G is lower than the second set value, the first waste heat is reduced by reducing the rotational speed of the pump 81C and / or adjusting the opening of the flow control valve 81E in the closing direction, as in the second step. The supply amount of water supplied to the boiler 100 is decreased, and the temperature of the combustion exhaust gas discharged from the first waste heat boiler 100 is increased. As a result, the combustion exhaust gas whose temperature has risen is supplied to the turbine 61 of the supercharger 60, so that the rotational speed of the turbine 61 increases and the compressor 62 of the supercharger 60 that rotates as the turbine 61 rotates. The amount of combustion air discharged from the furnace increases, and the furnace temperature can be lowered. Further, the third step and the fourth step may be replaced with the second step, and the second step, the third step and the fourth step may be performed in combination with the second step.
In a pressurized fluidized furnace system that discharges combustion air from combustion exhaust gas, it is possible to increase the amount of combustion air without requiring additional power, so normal pressure incineration that controls the amount of combustion air with a fluid blower Compared with the furnace, the fifth step works effectively.

  In order to efficiently reduce the in-furnace temperature of the pressurized fluidized furnace 20, the rotational speed of the charging pump 12 is reduced as a sixth step before or after the fifth step or simultaneously with the fifth step, or the object to be processed It is also possible to adjust the flow rate adjusting valve 13E installed in the supply pipe in the closing direction to reduce the supply amount of the object to be processed supplied to the pressurized fluidized furnace. The sixth step is preferably performed after the fifth step because it leads to a reduction in the amount of heat recovered in the waste heat boiler.

  Next, a second embodiment of the present invention will be described in detail with reference to the accompanying drawings. In addition, the same code | symbol is attached | subjected about the same apparatus and member, and the overlapping description is abbreviate | omitted.

Second Embodiment
A pressurized fluidized furnace system 1 of the second embodiment is shown in FIG. It differs from the first embodiment in that two superchargers are installed in parallel. These superchargers are referred to as a first supercharger 60A and a second supercharger 60B, respectively. Further, an ejector 71 is provided so that the compressed air generated by the second supercharger 60B can be used as white smoke prevention air.

The outline is as follows. The pressurized fluidized furnace system 1 of 2nd Embodiment is the storage apparatus 10 which stores the to-be-processed object containing the organic substance, the pressurized fluidized furnace 20 which incinerates a to-be-processed object, and heat exchange of combustion exhaust gas and combustion air. The preheater 40 for performing the above, the dust collector 50 for removing dust and the like in the combustion exhaust gas, the turbine 61A rotated by the combustion exhaust gas, and rotating with the rotation of the turbine 61A, the combustion air to the pressurized fluidized furnace 20 The first supercharger 60A having a compressor 62A for supplying the combustion gas, the turbine 61B rotated by the combustion exhaust gas, and rotating with the rotation of the turbine 61B to supply the combustion air to the white smoke prevention heat exchanger 70 And a second supercharger 60B in which a compressor 62B is mounted, and a flue gas treatment tower 80 for discharging combustion exhaust gas to the outside.
A first waste heat boiler 100 that generates steam is provided in parallel with the gas preheater 40 between the pressurized fluidized furnace 20 and the dust collector 50, and the supercharger 60 and the flue gas treatment tower 80 are provided. A second waste heat boiler 110 that generates steam is provided therebetween.

(First turbocharger)
60 A of 1st superchargers are arrange | positioned in the back | latter stage of the dust collector 50, The turbine 61A rotated by the combustion exhaust gas discharged | emitted from the dust collector 50, The axis | shaft 63A which transmits rotation of the turbine 61A to the compressor 62A, This is a device provided with a compressor 62A that rotates with the rotation of the turbine 61A transmitted through the shaft 63A to generate combustion air.

  As shown in FIGS. 5 and 7, the first supercharger 60 </ b> A is supplied with combustion exhaust gas having a pressure of about 100 to 200 kPa and a temperature of 200 to 650 ° C. discharged from the dust collector 50 in the lower part of the turbine 61 </ b> A. A supply port 93B is formed, and a discharge port 97A for discharging combustion exhaust gas to the outside of the machine is formed at the side of the turbine 61A. Further, the combustion exhaust gas supply port 93 </ b> B is connected to the discharge port 93 </ b> A of the dust collector 50 through the pipe 93. In addition, by adjusting the flow regulator 93D installed in the branch pipe of the pipe 93, which will be described later, from the dust collector 50 to the turbine 61A of the first supercharger 60A that supplies the combustion air necessary for the pressurized fluidized furnace 20. 50 to 90% of the exhaust gas discharged is supplied. As the flow regulator 93D, a flow regulating damper, a flow regulating valve, or the like can be used. The flow rate regulator 93D is controlled based on measurement values detected by a measurement unit (not shown) that measures the flow rate and pressure of the compressed air supplied from the first supercharger 60A. Specifically, the combustion exhaust gas supplied to the first supercharger 60A is controlled so that the measured value becomes a predetermined value.

A supply port 67B for supplying air into the apparatus is formed at the side of the compressor 62A of the first supercharger 60A, and combustion air having a pressure of 50 to 200 kPa and a temperature of 15 to 200 ° C. is formed above the compressor 62. A discharge port 94A for discharging to the outside is formed.
The air supply port 67B is connected to the starter blower 65 via pipes 67, 66, and the combustion air discharge port 94A is connected to the supply port 95B of the air preheater 40 via the pipes 94, 96, 95. 94 and 96 are connected to and controlled by the rear part of the starter burner 22 of the pressurized fluidized furnace 20.

(Second turbocharger)
The second supercharger 60B is arranged in parallel with the first supercharger 60A at the subsequent stage of the dust collector 50, and the turbine 61B rotated by the combustion exhaust gas discharged from the dust collector 50, and the rotation of the turbine 61B Is a device that includes a shaft 63B that transmits the air to the compressor 62B, and a compressor 62B that rotates with the rotation of the turbine 61B transmitted through the shaft 63B to generate white smoke prevention air.

As shown in FIGS. 5 and 7, combustion exhaust gas having a pressure of 100 to 200 kPa discharged from the dust collector 50 and a temperature of 250 to 650 ° C. is supplied to the second supercharger 60 </ b> B in the lower part of the turbine 61 </ b> B. A supply port 93C is formed, and a discharge port 97C for discharging combustion exhaust gas to the outside of the machine is formed at the side of the turbine 61B.
The combustion exhaust gas supply port 93C is connected to the discharge port 93A of the dust collector 50 via a pipe 93, and the pipe 93 has a branch pipe extending to the supply port 93C of the second supercharger 60B at an intermediate portion. ing. Further, the branch pipe of the pipe 93 and the branch pipe of the pipe 97 are connected by the pipe 111, and the pipe 111 is provided with a flow rate regulator 111D for adjusting the flow rate of the combustion exhaust gas supplied to the second supercharger 60B. Yes. 10-50% of the combustion exhaust gas discharged from the dust collector 50 is supplied to the second supercharger 60B by the flow rate regulator 111D. As the flow regulator 111D, a flow regulating damper, a flow regulating valve, or the like can be used. This flow regulator 111D is controlled based on the measured value detected by the measurement means (not shown) which measures the flow volume and pressure of the compressed air supplied from the 2nd supercharger 60B. Specifically, the combustion exhaust gas supplied to the second supercharger 60B is controlled so that the measured value becomes a predetermined value.

On the side of the compressor 62B of the second supercharger 60B, a supply port 67C for sucking air into the machine is formed, and at the top of the compressor 62B is for white smoke prevention at a pressure of 80 to 150 kPa and a temperature of 70 to 120 ° C. A discharge port 94C for discharging air to the outside of the machine is formed.
Air is supplied to the air supply port 67C via the pipe 72, and the white smoke prevention air discharge port 94C is supplied to the white smoke prevention heat exchanger 70 via the pipe 74, the ejector 71, and the pipe 73. 70A. The white smoke prevention heat exchanger 70 has a supply port 70A for supplying white smoke prevention air into the machine on one side wall, and a supply port for supplying steam discharged from the power generator 120 into the machine at the bottom. 70B is formed. The other side wall is provided with a discharge port 70C for discharging white smoke prevention air, which has been raised to a temperature of 70 to 95 ° C. by heat exchange, to the outside, and a discharge port for discharging water vapor to the outside. An outlet 70D is formed.
The steam supplied to the heat exchanger for preventing white smoke is not limited to the steam discharged from the power generator 120, but may be discharged from the first waste heat boiler or the second waste heat boiler, or steam. It may be supplied via the header 110.

(Second waste heat boiler)
The second waste heat boiler 110 is arranged at the subsequent stage of the first supercharger 60A, the second supercharger, and 60B. The combustion exhaust gas discharged from the first supercharger 60 </ b> A and the second supercharger 60 </ b> B is supplied to the second waste heat boiler 110 via the pipe 97.

(Control of combustion exhaust gas)
In order to maintain the steady operation of the pressurized fluidized furnace system 1, a predetermined amount of combustion exhaust gas discharged from the pressurized fluidized furnace 20 is supplied to the turbine 61A of the first supercharger 60A, and the turbine 61A is rotated. Therefore, it is necessary to supply a predetermined amount of the combustion air discharged from the rotating compressor 62A to the pressurized fluidized furnace 20.

  First, as a first step, according to the measured value of the first temperature sensor 20A disposed on the side wall of the pressurized fluidized furnace 20 in order to maintain the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace 20 at a predetermined temperature. Then, the flow rate adjuster 92G disposed in the vicinity of the discharge port 92A of the air preheater 40 is driven to adjust the supply amount of the combustion exhaust gas supplied to the air preheater 40. In the first step, the flow rate adjuster 92G of the air preheater 40 is driven to adjust the supply amount of the combustion exhaust gas supplied to the air preheater 40. It is also possible to adjust the supply amount of the combustion exhaust gas supplied to the air preheater 40 by driving the flow rate adjuster 92H disposed in the vicinity of the discharge port 92C.

  Next, as a second step, the first supercharger 60A and the air preheater 40 are connected in order to maintain the discharge amount of the combustion air discharged from the compressor 62A of the first supercharger 60A at a predetermined discharge amount. The water supplied to the first waste heat boiler 100 by reducing the rotational speed of the pump 81C and / or adjusting the opening of the flow control valve 81E according to the measured value of the flow meter 95G arranged in the pipe 95 Adjust the supply amount.

  Further, instead of the second step, the first supercharger 60A and the air are used as a third step in order to maintain the discharge amount of the combustion air discharged from the compressor 62A of the first supercharger 60A at a predetermined discharge amount. According to the measured value of the flow meter 95G arranged in the pipe 95 connecting the preheater 40, the flow regulator 93D arranged in the branch pipe of the pipe 93 is driven without passing through the first supercharger 60A. The supply amount of the combustion exhaust gas supplied to the second supercharger 60B via the branch pipe of the pipe 93 can also be adjusted.

  Furthermore, in order to maintain the discharge amount of the combustion air discharged from the compressor 62A of the first supercharger 60A at a predetermined discharge amount as a fourth step instead of the second step and the third step, According to the measured value of the 2nd temperature sensor 93F arrange | positioned in the vicinity of the supply port 93E of 60 A of feeders, the rotation speed of the pump 81C is reduced and / or the opening degree of the flow control valve 81E is adjusted, and 1st waste The supply amount of water supplied to the heat boiler 100 can also be adjusted. Although the description is omitted to avoid duplication, the fifth and sixth steps described above can be used together with the first to fourth steps.

  In the second embodiment, the compressed air generated by the second supercharger 60B is used as a drive source for the ejector 71, and the air volume is increased to prevent white smoke without installing a white smoke prevention fan. It becomes possible to obtain working air. As a result, not only efficient heat recovery of the combustion exhaust gas but also power consumption of the entire facility can be reduced, and more energy-saving combustion facility can be provided.

DESCRIPTION OF SYMBOLS 1 Pressurized flow furnace system 10 Storage apparatus 12 Input pump 13E Flow regulator 20 Pressurized flow furnace 40 Air preheater
DESCRIPTION OF SYMBOLS 50 Dust collector 60 Supercharger 61 Turbine 62 Compressor 70 White smoke prevention heat exchanger 80 Smoke treatment tower 81C Pump 81E Flow control valve 87 Chimney 92G Flow controller 92H Flow controller 100 First waste heat boiler (waste heat boiler)
110 Second waste heat boiler 114D Flow regulator 120 Power generator

Claims (8)

A pressurized fluidizing furnace for combusting a workpiece, a turbine that is rotated by combustion exhaust gas discharged from the pressurized fluidizing furnace, and a turbocharger that is internally rotated with a rotation of the turbine; Between the pressurized fluidized furnace and the supercharger, waste heat generating steam and an air preheater that exchanges heat between the combustion exhaust gas discharged from the pressurized fluidized furnace and the combustion air supplied to the pressurized fluidized furnace. In a pressurized flow furnace system with boilers installed side by side,
A first step of maintaining the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace at a predetermined temperature;
A second step of maintaining the discharge amount of the combustion air discharged from the compressor of the supercharger at a predetermined flow rate;
In the first step, a third step of increasing the amount of combustion air discharged from the compressor of the supercharger when the furnace temperature of the pressurized fluidized furnace becomes higher than a predetermined temperature. A control method for a pressurized fluidized furnace system, characterized in that   The said 1st process WHEREIN: The 4th process of reducing the supply amount of the to-be-processed object to a pressurization fluidized furnace when the furnace temperature of the said pressurization fluidized furnace becomes higher than predetermined temperature is provided. A control method of a pressurized fluidized furnace system according to 1.   The method for controlling a pressurized fluidized furnace system according to claim 2, wherein the fourth step is performed after the third step.   The pressurized fluidized furnace according to any one of claims 1 to 3, wherein the first step is performed by changing a ratio between a combustion exhaust gas amount supplied to the air preheater and a combustion exhaust gas amount supplied to the waste heat boiler. How to control the system.   The said 2nd process is performed by the increase / decrease in the amount of boiler water supplied to a waste-heat boiler, or the opening / closing of the flow regulator provided in the vicinity of the supply port of a supercharger. Control method of pressurized fluidized furnace system.   4. The method according to claim 1, wherein the third step is performed by increasing or decreasing the amount of boiler water supplied to the waste heat boiler, or by opening and closing a flow rate regulator provided in the vicinity of a supply port of the supercharger. Control method of pressurized fluidized furnace system.   4. The pressurized flow according to claim 2, wherein the fourth step is performed by decelerating the number of rotations of a charging pump that conveys the object to be processed, or by opening and closing a flow rate adjusting valve installed in a pipe that supplies the object to be processed. Control method for furnace system. A pressurized fluidizing furnace for combusting a workpiece, a turbine that is rotated by combustion exhaust gas discharged from the pressurized fluidizing furnace, and a turbocharger that is internally rotated with a rotation of the turbine; Between the pressurized fluidized furnace and the supercharger, waste heat generating steam and an air preheater that exchanges heat between the combustion exhaust gas discharged from the pressurized fluidized furnace and the combustion air supplied to the pressurized fluidized furnace. In a pressurized flow furnace system with boilers installed side by side,
A first step of maintaining the temperature of the combustion exhaust gas discharged from the pressurized fluidized furnace at a predetermined temperature;
A second step of maintaining the discharge amount of the combustion air discharged from the compressor of the supercharger at a predetermined flow rate;
In the first step, a third step of increasing the discharge amount of combustion air discharged from the compressor of the supercharger when the in-furnace temperature of the pressurized fluidized furnace becomes higher than a predetermined temperature. Pressurized flow furnace system with control method to perform.

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