JP7572691B1 - Combustion System - Google Patents

Abstract

[Problem] To provide a combustion system capable of improving combustion efficiency in a combustion system that directly burns solid fuel. [Solution] The combustion system includes at least a compressor 4b that produces pressurized air, a combustor 1 that generates high-temperature pressurized combustion gas by directly burning solid fuel, and a primary heat exchanger 6 that heats the pressurized air, the combustor 1 includes a rotating cylinder member 1a and a support member 1b that supports the rotating cylinder member, and the combustion system supplies air pressurized by the compressor 4b and heated by the primary heat exchanger 6 to the combustor 1 as combustion air. [Selected Figure] Figure 1

Description

The present invention relates to a combustion system.

Conventionally, various combustion systems have been proposed to obtain heat. In such combustion systems, technology has been proposed for burning solid fuel formed into pellets or chips. However, when burning solid fuel formed into pellets or chips, it has been difficult to ensure that the solid fuel is burned reliably.

As a combustion system for burning such solid fuel, for example, as described in Patent Document 1, a technology has been proposed in which an inner cylinder and an outer cylinder are provided to perform primary and secondary combustion.
The combustion system of Patent Document 1 is equipped with a cylinder having a double structure of an outer cylinder and an inner cylinder, a nozzle connected to an opening of the cylinder, a supply path for supplying solid fuel to the internal space of the inner cylinder, and a ventilation port for supplying air to the internal space of the inner cylinder and the internal space of the nozzle, and is configured so that first the solid fuel is supplied to the inner cylinder to perform primary combustion, and then the gas and residue generated by the primary combustion are rotated and moved to the nozzle to perform secondary combustion in the nozzle. Furthermore, the rotation of the cylinder increases the combustion efficiency.

Patent No. 5097674

However, in the combustion system described in Patent Document 1, the temperature of the combustion air supplied from the blower was low, so the supply of combustion air caused the temperature of the internal space of the inner cylinder to drop, resulting in poor combustion efficiency. When the fuel combustion efficiency deteriorates and incomplete combustion occurs, tar (a viscous organic liquid that does not become gas components such as hydrogen, carbon monoxide, and methane during the thermal decomposition of organic substances) is generated, and the combustion gas containing this tar blows through the combustion system, causing so-called tar troubles such as clogged filters, which interferes with the continuous operation of the combustion system.

Furthermore, in the combustion system described in Patent Document 1, ash and the like are produced by burning solid fuel. Therefore, when the combustion gas produced by this combustion system is used to generate electricity, the ash and the like contained in the combustion gas may adhere to and accumulate on the generator, etc., potentially reducing the power generation efficiency.
To prevent adverse effects on generators, etc., it is possible to install a bag filter downstream of the nozzle, but in order to prevent a decline in the functionality of the bag filter, it would be necessary to perform regular maintenance on the bag filter, which would interfere with the continuous operation of the combustion system.

In the combustion system described in Patent Document 1, it is possible to improve the combustion efficiency by preheating the combustion air before supplying it to the internal space of the inner cylinder. However, since the combustion system described in Patent Document 1 increases the combustion efficiency by rotating the cylinder, if preheated combustion air is supplied to the cylinder, the mechanisms for rotating the cylinder, such as bearings and motors, may also be burned out by heat, which may hinder continuous operation.

The present invention has been proposed in consideration of these problems, and aims to provide a combustion system that directly burns solid fuel and is capable of improving combustion efficiency, reducing the adverse effects of ash and tar produced by burning solid fuel, and reducing the adverse effects of high heat on the mechanism for rotating the cylinder.

In order to achieve the above object, the present invention has the following features.
[1] A compressor that produces pressurized air; and
a combustor that generates high-temperature pressurized combustion gases by direct combustion of a solid fuel;
a primary heat exchanger for heating the compressed air;
A combustion system comprising at least
The combustor includes:
A rotating cylinder member;
a support member for supporting the rotating cylinder member,
Air compressed by the compressor and heated by the primary heat exchanger is supplied to the combustor as combustion air.

[2] The combustor comprises:
an outlet for the hot pressurized combustion gas produced in the combustor;
an ejector through which the combustion air passes,
The ejector is provided at the outlet,
The combustion air passes through the ejector, thereby drawing in the high-temperature pressurized combustion gas.

[3] The combustor comprises:
A secondary heat exchanger for heating the combustion air,
The compressor is driven by the combustion air heated by the secondary heat exchanger.

[4] The support member is
a rotating member that enables the rotating cylinder member to rotate in a circumferential direction;
An air passage through which the combustion air passes,
The rotating member is isolated from the air passage.

[5] Provide a heat insulating material at least in the portion of the air supply path that faces the rotating member.

According to the above feature [1], the air supplied to the combustor is pressurized by the compressor and heated by the primary heat exchanger, which improves the combustion efficiency of solid fuel.

According to the above feature [2], an ejector is provided at the exit of the combustion chamber, so that the high-temperature pressurized combustion gas generated in the combustor can be effectively supplied to the downstream side.

According to the above feature [3], the compressor is driven by the combustion air heated by the secondary heat exchanger, so that the equipment downstream of the secondary heat exchanger is less susceptible to adverse effects from ash, tar, etc.

According to the above feature [4], the rotating member is isolated from the flow path through which the combustion air passes, so that the adverse effects of heat on the rotating member can be reduced.

According to the above feature [5], heat insulation is provided at least in the portion of the flow path through which the combustion air passes that faces the rotating member, so that the adverse effects of heat on the rotating member can be further reduced.

The present invention provides a combustion system that directly burns solid fuel, which is capable of improving combustion efficiency, reducing the adverse effects of ash and tar produced by burning solid fuel, and reducing the adverse effects of high heat on the mechanism for rotating the cylinder.

1 is a block diagram showing a configuration of a combustion system according to a first embodiment of the present invention. 1 is a block diagram showing a configuration of a combustor according to a first embodiment of the present invention. FIG. 1 is a cross-sectional view of a combustor according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view of the pipe frame according to the first embodiment of the present invention. 4 is a cross-sectional view taken along line AA of FIG. 3 in the cylindrical body of the rotating cylindrical member according to the first embodiment of the present invention. FIG. 2 is a flowchart showing a solid fuel combustion method according to the first and second embodiments of the present invention. FIG. 5 is a block diagram showing a configuration of a combustion system according to a second embodiment of the present invention. FIG. 5 is a block diagram showing a configuration of a combustor according to a second embodiment of the present invention. FIG. 11 is a diagram showing a configuration of an ejector according to a second embodiment of the present invention. FIG. 11 is a block diagram showing a configuration of a combustion system according to a third embodiment of the present invention. FIG. 11 is a block diagram showing a configuration of a combustor according to a third embodiment of the present invention. FIG. 5 is a cross-sectional view of a combustor according to a third embodiment of the present invention. 13 is a cross-sectional view of the cylindrical body of the rotating cylindrical member according to the third embodiment of the present invention taken along line CC in FIG. 12. FIG. 14 is a cross-sectional view of the pipe frame according to the third embodiment of the present invention taken along line D-D in FIG. 13. FIG. 14 is a cross-sectional view of the pipe frame according to the third embodiment of the present invention taken along line E-E of FIG. 13. FIG. 11 is a flowchart showing a solid fuel combustion method according to a third embodiment of the present invention. FIG. 11 is a block diagram showing a modified example of the configuration of the combustion system according to the embodiment of the present invention. FIG. 4 is a cross-sectional view of a modified example of the combustor according to the embodiment of the present invention. FIG. 4 is a cross-sectional view showing a modified example of the combustor according to the first embodiment of the present invention. 20 is a cross-sectional view taken along line BB in FIG. 19 of the cylindrical body of the rotating cylindrical member according to the first embodiment of the present invention. FIG. 4 is a cross-sectional view showing a modified example of the pipe frame according to the first embodiment of the present invention. FIG. 11 is a cross-sectional view showing a modified example of the combustor according to the second embodiment of the present invention.

The following describes an embodiment of the present invention, but the present invention is not limited to the following embodiment as long as it does not go against the spirit of the present invention. The fuel used in the combustion system of the present invention is organic matter (biomass fuel) such as grass, livestock manure, food waste, and sewage sludge, and is a solid combustion material in the form of pellets, chips, granules, fibers, powder, etc.

Biomass in chip, granular, fibrous or powder form refers to, for example, finely divided solid matter of grass or wood materials such as cut and crushed grass, wood chips or sawdust, or solid matter that is originally granular or powdery and has fluidity, such as rice husks. It also includes the above finely divided solids that have been appropriately pelletized to give them fluidity, and organic waste such as waste mushroom culture medium generated in mushroom cultivation and food waste that has been dried into a powder form. In other words, it is sufficient to use biomass that is formed smaller than the required size and can be automatically transported using a fixed-volume supply conveyor, which will be described later.

1. First Embodiment 1.1. Overall Configuration Hereinafter, the overall configuration of a combustion system according to a first embodiment will be described with reference to FIGS.
As shown in FIG. 1 , the combustion system according to the first embodiment of the present invention comprises a combustor 1, a fuel hopper 2, a bag filter 3, a gas turbine 4, a turbine generator 5, a primary heat exchanger 6, and a chimney 7.

1.1.1. Combustor 1

As shown in Figs. 2 and 3, the combustor 1 according to the first embodiment is composed of a rotating cylinder member 1a, a support member 1b, a fuel supply member 1c, and a combustion chamber 1d.
The rotating cylinder member 1a is
a cylindrical body 101 having a front end which is an opening and a rear end which is a closed portion, and having a dual structure of an outer cylinder 102 and an inner cylinder 103 which are coaxially rotatable;
An elongated tube 104 attached to the rear end of the tube 101 and communicating with the inner tube 103;
A nozzle 105 having a refractory layer 106 on its inner surface, the nozzle 105 being connected to the outer cylinder 102 of the cylinder at an opening;
a ventilation port 108 formed in the blocking portion, which supplies air to an internal space of the nozzle 105 through a gap between the inner cylinder 103 and the outer cylinder 102 as a ventilation path 107;
A plurality of pipe frames 109 are provided on the wall surface of the inner cylinder 103, the pipe frames 109 communicate with the ventilation passages 107, and extend in the axial direction.
a plurality of small-diameter air outlets 110 formed on the inner cylinder 103 space side of the pipe frame 109 for blowing out a portion of the air flowing through the ventilation passage 107 into the internal space of the inner cylinder 103;
The opening area between the outer cylinder 102 and the inner cylinder 103 at the opening is equal to or larger than the opening area of the air outlet 110 .

5, the air outlet 110 of the pipe frame 109 is oriented in a direction inclined from the central axis of the rotating cylinder member 1a. With this configuration, the combustion air can be efficiently agitated, and the combustion efficiency of the solid fuel can be improved.
In the first embodiment, as shown in FIG. 5, the number of pipe frames 109 is four, but this is not limited to four and may be, for example, six, eight, or ten.

The support member 1b is
a support 111 that rotatably supports the rotating cylinder member 1a via a bearing 112 at the position of the tube body 104 by tilting the rotating cylinder member 1a so that the nozzle 105 faces upward;
a motor 113 provided on the support 111 for rotating the rotating cylinder member 1a in a circumferential direction;
The combustion air inlet 114 is provided on the support 111, and the combustion air inlet 114 takes in outside air. The air inlet 115 sends the taken-in air to the ventilation opening 108.
The bearing 112 and the motor 113 are isolated from the air supply path 115,
A heat insulating material 120 is provided in the air supply path 115 at a portion facing the bearing 112 and the motor 113 .

The rotating cylinder member 1a is preferably inclined by about 1 to 10 degrees when rotating so that the solid fuel does not reach the combustion chamber 1d before combustion, but it can also be horizontal without being inclined.

The fuel supply member 1c is
a supply passage 116 having an end port slidably abutting against a rear end port of the tube body 104 and supplying solid fuel to an internal space of the inner cylinder 103;
a screw conveyor 117 disposed within the tube 104 and the feed channel 116;
A motor 118 for rotating the screw conveyor 117 on the supply path 116 side;
A valve 119 that blocks communication between the space on the supply path 116 side and the atmosphere;
It is equipped with:

There are no limitations on the configuration of the valve 119 as long as it can block communication between the space on the supply path 116 side and the atmosphere, and it may be configured as, for example, a rotary valve, a knife gate valve, or a double damper.

The inner cylinder 103 of the combustor 1 may house a number of pulverizing members for pulverizing the solid fuel. The pulverizing members are made primarily of alumina oxide and are formed into granules with an outer diameter of 4 to 8 mm.

The combustor 1 also includes a combustion chamber 1d, and as partially shown in FIG. 3, a nozzle 105 of the rotating cylinder member 1a is positioned inside the combustion chamber 1d.
Although not shown, a wall for allowing ash to settle by gravity may be provided between the nozzle 105 and the outlet of the combustion chamber 1d to prevent ash generated by the combustion of the solid fuel from reaching the outlet of the combustion chamber 1d. Also, the combustion chamber 1d may be cylindrical and the nozzle 105 of the rotating cylinder member 1a may be connected from the tangential direction to rotate the high-temperature pressurized combustion gas containing ash within the combustion chamber 1d, causing the ash to settle by centrifugal force.

The combustor 1 also has an ignition burner (not shown). The ignition burner is, for example, a burner that burns LP gas, and is provided so that the tip of the burner nozzle faces the inside of the inner cylinder 103, allowing the solid fuel to be ignited. After the solid fuel is ignited, the supply of fuel to the ignition burner can be stopped, and only the blowing function of the compressor 4b can be used. This blowing function allows combustion air to be appropriately supplied to the inner cylinder 103 using the principle of a blower, improving the combustion efficiency of the solid fuel.

1.1.2. Fuel hopper 2
The fuel hopper 2 is configured as a funnel-shaped fuel tank for storing solid fuel to be supplied to the combustor 1. The lower end opening of the fuel tank is connected to a valve 119 of a fuel supply member 1c in the combustor 1.

1.1.3. Bag filter 3
The bag filter 3 is for removing ash and debris generated by the combustion of solid fuel in the combustor 1, and is usually a cyclone filter. Although the cyclone filter cannot remove very small ash particles of less than 1 micron, the particles that this filter cannot remove are sufficiently small to minimize problems of adhesion, erosion, and corrosion to the gas turbine 4 located downstream.

1.1.4. Gas turbine 4
The gas turbine 4 includes a turbine 4a and a compressor 4b, and the turbine 4a is driven by the high-temperature pressurized combustion gas generated in the combustor 1, and the compressor 4b is driven through a shaft to pressurize the air introduced as the combustion air to the combustor 1. Specifically, the high-temperature pressurized combustion gas that has passed through the bag filter 3 enters the turbine 4a of the gas turbine 4 and hits the blades of the turbine 4a to drive the turbine 4a, which drives the compressor 4b through the shaft, and the compressor 4b takes in air and discharges the compressed air. The high-temperature pressurized combustion gas that has flowed into the turbine 4a is discharged toward the turbine generator 5.

1.1.5. Turbine generator 5
The turbine generator 5 includes a turbine 5a and a generator 5b, and the turbine 5a is driven by the high-temperature pressurized combustion gas that has passed through the turbine 4a, and the generator 5b is driven through the shaft. A well-known generator may be used as the generator 5b. The high-temperature pressurized combustion gas that has flowed into the turbine 5a is discharged toward the primary heat exchanger 6.

1.1.6. Primary heat exchanger 6
The primary heat exchanger 6 has a flow path 6b through which compressed air discharged from a compressor 4b of the gas turbine 4 passes, and a flow path 6a through which high-temperature pressurized combustion gas discharged from a turbine 5a of the turbine generator 5 passes. Due to this structure, the compressed air discharged from the compressor 4b of the gas turbine 4 is mixed with the high-temperature compressed air discharged from the turbine 5a of the turbine generator 5. The compressed air is heated by the compressed combustion gas, and the heated compressed air is discharged to the combustor 1. In this way, the combustor 1 can use the preheated compressed air as combustion air. Therefore, the combustion efficiency can be improved. Furthermore, the high-temperature pressurized combustion gas that has passed through the flow passage 6a is discharged toward the chimney 7.

1.1.7. Chimney 7
The chimney 7 has a bag filter portion that effectively separates ash and the like contained in the high-temperature pressurized combustion gas discharged from the primary heat exchanger 6, and the high-temperature pressurized combustion gas that has passed through the bag filter portion is discharged into the atmosphere from the chimney 7. Since the high-temperature pressurized combustion gas is discharged into the atmosphere in the chimney 7 after passing through the bag filter portion, the possibility of air pollution can be reduced.

1.2 Solid Fuel Combustion Method Hereinafter, a solid fuel combustion method according to a first embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 6, the combustion method includes a fuel supply process S1, a combustion process S2, a dust collection process S3, a compressed air generation process S4, a power generation process S5, a primary heat exchange process S6, and an exhaust process S7.

1.2.1. Fuel supply process S1
The fuel supply step S1 is a step of supplying the solid fuel in the fuel hopper 2 to the inner cylinder 103 of the rotating cylinder member 1a in the combustor 1. First, the solid fuel in the fuel hopper 2 is supplied to the inner cylinder 103 of the rotating cylinder member 1a in the combustor 1 through the valve The solid fuel is supplied to the supply path 116 via the motor 118 and the screw conveyor 117 rotates. The solid fuel supplied to the supply path 116 is then conveyed by the screw conveyor 117 through the pipe. The fuel passes through the body 104 and is supplied to the internal space of the inner cylinder 103. Next, the motor 113 is driven to rotate the rotary cylinder member 1a. The solid fuel is tumblingly crushed by this rotation. Since a pulverizing member is accommodated in the inner cylinder 103 of the rotating cylinder member 1a, the solid fuel supplied to the inner space of the inner cylinder 103 collides with the pulverizing member as the inner cylinder 103 rotates. It is repeatedly crushed into fine pieces. Here, since the nozzle 105 of the cylindrical body 101 is inclined upward with respect to the horizontal plane, the crushing member housed in the internal space of the inner cylinder 103 will not fly out even when the cylindrical body 101 rotates.

1.2.2. Combustion process S2
The combustion step S2 is a step of combusting the solid fuel in the inner cylinder 103. In the fuel supply step S1, the solid fuel pulverized by the rotation of the rotary cylinder member 1a and the pulverizing member is ignited by an ignition burner (not shown). When the solid fuel is ignited, it starts to burn. When the solid fuel is ignited by the ignition burner, the rotation of the rotating cylinder member 1a may be stopped by stopping the driving of the motor 113. At this time, the solid fuel is Since the fuel is finely pulverized by the rotation of the cylindrical member 1a and the pulverizing member, gasification by direct combustion is rapidly performed. In addition, since the fuel is finely pulverized, residue or unburned remains are hardly generated, and the fuel supplied to the inner cylinder 103 is easily gasified. Most of the solid fuel is burned in the inner cylinder 103, generating gas, which floats to the nozzle 105.
In addition, until the combustion system is started and high-temperature pressurized combustion gas is stably supplied to the inner cylinder 103, the combustion air passing through the pipe frame 109 of the rotating cylinder member 1a becomes unstable. Therefore, for example, a blower or the like may be provided to forcibly supply combustion air.

1.2.3. Dust collection process S3
The dust collecting step S3 is a step for removing ash and debris contained in the high-temperature pressurized combustion gas generated in the combustion step S2. The high-temperature pressurized combustion gas generated in the combustion step S2 passes through a flow path a. The high-temperature pressurized combustion gas passes through the bag filter 3 and is supplied to the bag filter 3. The bag filter 3 removes ash, debris, and the like contained in the high-temperature pressurized combustion gas, and the high-temperature pressurized combustion gas is discharged into a flow path b.

1.2.4. Compressed air generation process S4
The compressed air generation step S4 is a step of generating compressed air using the high-temperature pressurized combustion gas that has been through the dust collection step S3. The high-temperature pressurized combustion gas that has passed through the bag filter 3 enters the turbine 4a of the gas turbine 4 and hits the blades of the turbine 4a to drive the turbine 4a. When the turbine 4a is driven, the compressor 4b is driven through the shaft, and the compressor 4b takes in air and discharges the compressed air through a flow path f toward the primary heat exchanger 6. The high-temperature pressurized combustion gas that has flowed into the turbine 4a is discharged through a flow path c toward the turbine generator 5.

1.2.5. Power generation process S5
The power generation step S5 is a step of generating electricity using the high-temperature pressurized combustion gas discharged from the turbine 4a through the flow path c in the compressed air generation step S4. The high-temperature pressurized combustion gas passing through the flow path c drives the turbine 5a of the turbine generator 5, which then drives the generator 5b through the shaft. The high-temperature pressurized combustion gas that has flowed into the turbine 5a is discharged toward the primary heat exchanger 6 through the flow path d.

1.2.6. Primary heat exchange step S6
The primary heat exchange step S6 is a step of transferring heat from the high-temperature compressed combustion gas that has been subjected to the power generation step S5 to the compressed air generated in the compressed air generation step S4. Compressed air discharged from the compressor 4b of the gas turbine 4 through a flow path f is heated by high-temperature compressed combustion gas discharged from the turbine 5a of the turbine generator 5 through a flow path d, which passes through the flow path 6a. The heated compressed air is discharged through a flow path g toward the combustor 1. The high-temperature compressed combustion gas passing through the flow path 6a is discharged through a flow path e. .

The heated compressed air discharged toward the combustor 1 through the primary heat exchange process S6 is used as combustion air in the combustion process S2. As shown in FIG. 3, the heated compressed air is taken in as heated air a0 from the combustion air inlet 114 of the support member 1b in the combustor 1, passes through the air supply path 115, and is supplied to the ventilation port 108. The heated air a0 supplied to the ventilation port 108 is supplied to the internal space of the nozzle 105 as secondary heated air a2 via the ventilation path 107, which is the gap between the inner cylinder 103 and the outer cylinder 102, and the heated air a0 taken into the pipe frame 109 from the intake port 127 shown in FIG. 4 and 5 is supplied to the internal space of the inner cylinder 103 as primary heated air a1. The heat of the heated air a0 passing through the air supply path 115 is intended to be transmitted to the rotating components such as the bearings 112 and the motor 113. However, since heat insulation material 120 is provided at least in the part of the air supply path 115 that faces the rotating components, the rotating components will not burn even if they are operated for a long time.

The pulverized solid fuel is partially combusted by the primary heated air a1 supplied to the internal space of the inner cylinder 103 via the pipe frame 109, and the heat generated raises the temperature inside the inner cylinder 103 to approximately 200-600°C, causing the volatile components contained in the solid fuel to pyrolyze and gasify. Because the solid fuel is pulverized by the rotation of the rotating cylinder member 1a and the pulverizing member, the volatile components are easily pyrolyzed and gasification is carried out quickly. However, because the amount of air supplied is not large, the internal space of the inner cylinder 103 is maintained in a low-oxygen state, and the solid fuel does not burn violently with a flame.

The opening area between the outer cylinder 102 and the inner cylinder 103 at the opening is equal to or larger than the opening area of the blowing port 110, and the amount of air taken in from the ventilation port 108 that is supplied to the internal space of the nozzle 105 is equal to or larger than the amount of air supplied to the internal space of the inner cylinder 103. Therefore, the combustion temperature in the nozzle 105 is higher than the combustion temperature in the inner cylinder 103. In other words, the nozzle 105 plays the role of secondary combustion, which burns at a high temperature. The gas and residue that floats in the nozzle 105 are burned at a high temperature and turned to ash. Since there is little residue or unburned remains, complete combustion occurs and little tar is produced. Since the ash is turned to ash reliably, the ash is quickly discharged from the nozzle 105.

The gas and residue float to the nozzle 105, where they are mixed with the large amount of air supplied through the ventilation passage 107 and completely combusted, with the combustion gas and ash being discharged directly from the nozzle 105. The internal space of the nozzle 105 becomes hot, at approximately 900 to 1200°C, but the ash is quickly discharged from the nozzle 105 before it melts, and clinker is unlikely to be formed.

1.2.7. Exhaust step S7
The exhaust step S7 is a step of discharging the high-temperature pressurized combustion gas that has passed through the primary heat exchange step S6 from a chimney 7 to the atmosphere. The chimney 7 has a bag filter portion that suitably separates ash contained in the high-temperature pressurized combustion gas discharged from the primary heat exchanger 6 through a flow path e, and the high-temperature pressurized combustion gas that has passed through the bag filter portion is discharged from the chimney 7 to the atmosphere.

1.3. Effects The combustion device of the first embodiment has the configuration as described above in detail, and therefore can provide a combustion system that can reduce the adverse effects on the gas turbine 4 and other components caused by ash, tar, and the like generated by burning solid fuel, improve the combustion efficiency by supplying preheated pressurized air to the combustor 1, and reduce the adverse effects on rotating members such as the bearings 112 and the motor 113 caused by the preheated pressurized air.

2. Second embodiment 2.1. Overall configuration Hereinafter, the overall configuration of a combustion system according to a second embodiment will be described with reference to FIGS.
As shown in FIG. 7 , the combustion system according to the second embodiment of the present invention comprises a combustor 1, a fuel hopper 2, a bag filter 3, a gas turbine 4, a turbine generator 5, a primary heat exchanger 6, and a chimney 7.
8 and 9, the second embodiment differs from the first embodiment in that an ejector 1e is provided at the outlet of the combustion chamber 1d in the combustor 1, and that heated compressed air that has passed through the primary heat exchanger 6 is supplied not only to the combustion air inlet 114 of the support member 1b in the combustor 1, but also to the ejector 1e. Other configurations are the same as those in the first embodiment, and therefore will not be described.

2.1.1. Ejector 1e
The ejector 1e takes in high-temperature combustion gas in the combustion chamber 1d of the combustor 1 without relying on mechanical drive such as a pump. As shown in Fig. 9, the ejector 1e has a tapered nozzle 122 through which the heated compressed air that has passed through the primary heat exchanger 6 passes and whose cross section becomes smaller toward the downstream side, a suction port 121 that draws in the high-temperature combustion gas in the combustion chamber 1d, and a mixing section that mixes the heated compressed air with the high-temperature combustion gas.

2.2 Solid Fuel Combustion Method Hereinafter, a solid fuel combustion method according to a second embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 6, the method of burning solid fuel includes a fuel supply process S1, a combustion process S2, a dust collection process S3, a compressed air generation process S4, a power generation process S5, a primary heat exchange process S6, and an exhaust process S7.
The solid fuel combustion method in the second embodiment differs from the solid fuel combustion method in the first embodiment mainly in the combustion step S2 after the primary heat exchange step S6, and therefore the other steps will not be described.

2.2.1. Combustion process S2
The combustion step S2 is the same as that of the first embodiment in that it is a step of burning the solid fuel in the inner cylinder 103. In the second embodiment, an ejector 1e is attached to the outlet portion of the combustion chamber 1d. Therefore, the high-temperature combustion gas generated in the nozzle 105 is efficiently transported downstream. Specifically, when the heated compressed air that has passed through the primary heat exchanger 6 passes through the tapered nozzle 122, it is ejected into the ejector 104. The pressure inside the combustion chamber 1e drops, so that the high-temperature combustion gas in the combustion chamber 1d is sucked in through the suction port 121. The sucked-in high-temperature combustion gas is mixed with the heated compressed air in the mixing section, and is discharged downstream. is transported to.

2.3 Effects Since the combustion device of the second embodiment has the configuration described above in detail, in addition to the effects achieved by the first embodiment, the ejector 1e can more efficiently supply the high-temperature pressurized combustion gas in the combustion chamber 1d to the downstream side.

3. Third embodiment 3.1. Overall configuration The overall configuration of a combustion system according to a third embodiment will be described below with reference to FIGS.
As shown in FIG. 10, the combustion system according to the third embodiment of the present invention comprises a combustor 1, a fuel hopper 2, a gas turbine 4, a turbine generator 5, a primary heat exchanger 6, and a chimney 7.
As shown in Figs. 10 and 11 , the third embodiment differs from the first embodiment mainly in that a secondary heat exchanger 1f is provided in the combustor 1, that a bag filter 3 is not provided, that high-temperature combustion gas discharged from a combustion chamber 1d is supplied to a primary heat exchanger 6, and that heated compressed air discharged from a turbine 5a of a turbine generator 5 is supplied to the combustor 1 as heated air a0 without passing through the primary heat exchanger 6.
Since the configuration of the second embodiment is almost the same as that of the first embodiment except for the configuration of the combustor 1, a description thereof will be omitted.

3.1.1. Combustor 1

As shown in Fig. 11, the combustor 1 according to the third embodiment is composed of a rotating cylinder member 1a, a support member 1b, a fuel supply member 1c, a combustion chamber 1d, and a secondary heat exchanger 1f. The following mainly describes the configuration different from the first embodiment.
As shown in FIGS. 12 to 15, the rotating cylinder member 1a has the following features:
a ventilation port 108 formed in the closed portion and configured to supply air to an internal space of the support member 1b through a gap between the inner cylinder 103 and the outer cylinder 102 as a ventilation passage 107;
A plurality of second pipe frames 123 are provided on the wall surface of the inner cylinder 103, communicate with the ventilation passage 107, and extend in the axial direction;
a plurality of small-diameter air outlets 124 formed on the outer cylinder 102 side of the second pipe frame 123 and for blowing out the secondary heated air a3 that has received heat from the internal space of the inner cylinder 103 into the ventilation passage 107;
It further comprises:

In the third embodiment, as shown in FIG. 13, the number of second pipe frames 123 is four, but this is not limited to four and can be, for example, six, eight, or ten.

The support member 1b is
an air supply path 126 provided in the support 111, which has an air supply port 125 for sending out the secondary heated air a3 to the outside and sends the heated air a0 taken in from the ventilation port 108 to the air supply port 125;
It further comprises:

In addition, in the combustor 1, the ventilation passage 107 of the rotating cylinder member 1a and the air supply passage 126 of the second pipe frame 123 and the support member 1b form the flow path that receives heat in the secondary heat exchanger 1f.

3.2 Solid Fuel Combustion Method Hereinafter, a solid fuel combustion method according to a third embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 16, the method of burning solid fuel includes a fuel supply process S11, a combustion process S12, a secondary heat exchange process S13, a compressed air generation process S14, a power generation process S15, a primary heat exchange process S16, and an exhaust process S17.
In the solid fuel combustion method according to the third embodiment, the fuel supplying step S11 is the same as the fuel supplying step S1 in the first embodiment, and therefore a description thereof will be omitted.

3.2.1. Combustion step S12
The combustion step S12 is the same as that of the first embodiment in that it is a step of combusting the solid fuel in the inner cylinder 103. The third embodiment differs from the first embodiment in that, as shown in Figures 10 to 12, the high-temperature pressurized combustion gas generated by the combustor 1 is discharged from the flow path F toward the primary heat exchanger 6 and is utilized in the secondary heat exchanger 1f.

3.2.2. Secondary heat exchange step S13
The secondary heat exchange process S13 is a process in which the heat generated in the inner cylinder 103 in the combustion process S12 is given to the heated air a0 passing through the second pipe frame 123 of the rotating cylinder member 1a in the combustor 1, etc.
As shown in FIGS. 11, 12 and 15, the heated air a0 in the second pipe frame 123 of the rotating cylinder member 1a is heated by the high-temperature pressurized combustion gas generated in the inner cylinder 103, and the heated air is discharged as secondary heated air a3 from the blowing port 124 to the ventilation passage 107 of the rotating cylinder member 1a. The secondary heated air a3 then passes through the air supply passage 126 and the air supply port 125 of the support member 1b. Then, the mixture is discharged into flow path A.
In addition, after starting up the combustion system, until the high-temperature pressurized combustion gas is stably supplied to the inner cylinder 103, the air passing through the second pipe frame 123 of the rotating cylinder member 1a becomes unstable. To prevent this, a blower or the like may be provided to forcibly send air into the second pipe frame 123 .

3.2.3. Compressed air generation process S14
The compressed air generating step S14 is a step of generating pressurized air using the secondary heated air a3 that has been through the secondary heat exchange step S13. The secondary heated air a3 that has been through the secondary heat exchange step S13 enters the turbine 4a of the gas turbine 4, and when it hits the blades of the turbine 4a to drive the turbine 4a, the compressor 4b is driven through the shaft, and the compressor 4b takes in air and discharges the compressed air through flow path D. The secondary heated air a3 that has flowed into the turbine 4a is discharged through flow path B.

3.2.4. Power generation process S15
The power generation step S15 is a step of generating electricity using the secondary heated air a3 discharged from the turbine 4a through the flow path B in the compressed air generation step S14. The secondary heated air a3 passing through the flow path B drives the turbine 5a of the turbine generator 5, and drives the generator 5b through the shaft. The secondary heated air a3 flowing into the turbine 5a is discharged toward the combustor 1 through the flow paths C and E.

3.2.5. Primary heat exchange step S16
The primary heat exchange step S16 is a step of transferring heat from the high-temperature compressed combustion gas discharged from the combustion chamber 1d through the flow path F to the compressed air generated in the compressed air generation step S14. In the gas turbine 4, compressed air discharged from the compressor 4b of the gas turbine 4 through a flow path D is heated in a flow path 6b by high-temperature compressed combustion gas discharged from the combustion chamber 1d through a flow path F, and the heated The compressed air is discharged to the combustor 1 through a flow path E. The high-temperature compressed combustion gas that has passed through the flow path 6a is discharged through a flow path G.

The heated compressed air discharged to the combustor 1 through the primary heat exchange process S16 is used in the combustion process S12, but this is the same as in the first embodiment, so a detailed explanation will be omitted.

3.2.6. Exhaust step S17
The exhaust step S7 is a step of discharging the high-temperature pressurized combustion gas discharged from flow path G through the primary heat exchange step S16 into the atmosphere from the chimney 7. The chimney 7 has a bag filter portion that suitably separates ash contained in the high-temperature pressurized combustion gas discharged from the primary heat exchanger 6 through flow path G, and the high-temperature pressurized combustion gas that has passed through the bag filter portion is discharged from the chimney 7 into the atmosphere.

3.3 Effects The combustion device of the third embodiment has the configuration described above in detail, and therefore in addition to the effects achieved by the first embodiment, the secondary heat exchanger 1f can effectively prevent ash, tar, and the like contained in the high-temperature pressurized combustion gas from adhering to the gas turbine 4 and the turbine generator 5 located downstream. As a result, it is possible to extend the life of the entire combustion system.

In the above embodiment, the combustion system is configured to generate electricity using the turbine generator 5, but it is not limited to the configuration for generating electricity. It is also possible to construct a hot water supply system that generates hot water, a temperature control system that generates hot air, a sterilization system that performs sterilization at high temperature, etc. This allows the combustion system of the present invention to be used in a wide range of applications.

In addition, in the above embodiment, a configuration was adopted in which separate turbines were used for the turbine 4a to drive the compressor 4b and the turbine 5a to drive the generator 5b, but this configuration is not limited thereto, and it is also possible to adopt a configuration in which the compressor 4b and the generator are driven by a single turbine 4a, as shown in FIG. 17. This simplifies the structure of the entire combustion system.

In addition, in the above embodiment, the supply path 116 is configured to abut against the rear end opening of the tube body 104, but as shown in FIG. 18, it is also possible to configure the supply path 116 to communicate with the internal space of the inner tube 103. This eliminates the connection points that existed in the path through which the solid fuel passes, making it possible to avoid the risk of solid fuel accumulating at the connection points and disrupting the supply of solid fuel.

In the above embodiment, the primary heat exchanger 6 has a flow path 6b through which the compressed air discharged from the compressor 4b of the gas turbine 4 passes, and a flow path 6a through which the high-temperature pressurized combustion gas discharged from the turbine 5a of the turbine generator 5 passes, and a configuration is adopted in which they can exchange heat with each other, but this is not limited to the above, and a configuration in which heat is added to the compressed air discharged from the compressor 4b of the gas turbine 4 by another heat source may also be used. Examples of other heat sources include steam, hot water, or hot air generated in another system.

In the first embodiment, the gap between the inner tube 103 and the outer tube 102 is used as the ventilation passage 107. However, as shown in FIG. 19 and FIG. 20, the gap between the inner tube 103 and the outer tube 102 may be filled with a more flexible insulating material 128 than the inner tube 103 made of a fire-resistant material such as SiC (silicon carbide). When this configuration is adopted, it is preferable that the heated air a0 introduced into the pipe frame 109 is introduced from the base of the pipe frame 109, and the secondary heated air a2 toward the nozzle 105 is discharged from the tip of the pipe frame 109, as shown in FIG. 21. By filling the gap between the inner tube 103 and the outer tube 102 with the flexible insulating material 128, the insulating material 128 functions as a buffer material, and the risk of the inner tube 103 being damaged by vibrations caused by the rotation of the rotating tube member 1a can be reduced.

In the second embodiment, an ejector 1e is provided at the outlet of the combustion chamber 1d in the combustor 1. However, as shown in FIG. 22, an outlet (suction port 121) may be provided in the support member 1b of the combustor 1, and the ejector 1e may be provided at the outlet. In this case, the high-temperature pressurized combustion gas a4 passes through the support member 1b and reaches the suction port 121. This allows the combustor 1 to be made more compact.

In the third embodiment, a bag filter 3 is not provided downstream of the combustor 1 and upstream of the gas turbine 4, but a bag filter 3 may be provided to supply cleaner secondary heated air a3 and improve the life of the combustion system.

In addition, in the third embodiment, an ejector is not provided at the outlet of the combustion chamber 1d, but an ejector may be provided in order to more efficiently supply high-temperature pressurized combustion gas.

Furthermore, in the third embodiment, the secondary heated air a3 that flows into the turbine 5a is discharged toward the combustor 1 through flow paths C and E, but the secondary heated air a3 that flows into the turbine 5a may be discharged from the chimney 7 via flow path 6a in the primary heat exchanger 6 or via flow path G. Also, it may be possible to switch between discharging the secondary heated air a3 that flows into the turbine 5a toward the combustor 1 through flow path C or discharging it from the chimney 7 via the primary heat exchanger 6.

1: Combustor 1a: Rotating cylinder member 1b: Support member 1c: Fuel supply member 1d: Combustion chamber 1e: Ejector 1f: Secondary heat exchanger 2: Fuel hopper 3: Bag filter 4: Gas turbine 4a: Turbine 4b: Compressor 5: Turbine generator 5a: Turbine 5b: Generator 6: Primary heat exchanger 6a: Flow path 6b: Flow path 7: Chimney 101: Cylinder body 102: Outer cylinder 103: Inner cylinder 104: Tube body 105: Nozzle 106: Fireproof layer 107: Ventilation path 108: Ventilation port 109: Pipe frame 110: Air outlet 111: Support body 112: Bearing 113: Motor 114: Combustion air inlet 115: Air supply path 116: Supply path 117: Screw conveyor 118: Motor 119 : Valve 120 : Heat insulating material 121 : Suction port 122 : Nozzle 123 : Second pipe frame 124 : Air outlet 125 : Air supply port 126 : Air supply path 127 : Air intake 128 : Heat insulating material

Claims (4)

A compressor that produces pressurized air;
a combustor that generates high-temperature pressurized combustion gases by direct combustion of a solid fuel;
a primary heat exchanger for heating the compressed air;
A combustion system comprising at least
The combustor includes:
A rotating cylinder member;
a support member for supporting the rotating cylinder member;
an outlet for the hot pressurized combustion gas produced in the combustor;
An ejector,
Air compressed by the compressor and heated by the primary heat exchanger is supplied to the combustor as combustion air;
The ejector is provided at the outlet,
The combustion system according to claim 1, wherein the combustion air passes through the ejector, thereby drawing in the high-temperature pressurized combustion gas. A compressor that produces pressurized air;
a combustor that generates high-temperature pressurized combustion gases by direct combustion of a solid fuel;
a primary heat exchanger for heating the compressed air;
A combustion system comprising at least
The combustor includes:
A rotating cylinder member;
a support member for supporting the rotating cylinder member;
a secondary heat exchanger for heating the combustion air;
Air compressed by the compressor and heated by the primary heat exchanger is supplied to the combustor as the combustion air;
a combustion system, characterized in that the compressor is driven by the combustion air heated by the secondary heat exchanger. The support member is
a rotating member that enables the rotating cylinder member to rotate in a circumferential direction;
An air passage through which the combustion air passes,
3. The combustion system of claim 1 or 2, wherein the rotating member is isolated from the air inflection passage. The combustion system according to claim 3 , wherein a heat insulating material is provided at least in a portion of the air supply passage that faces the rotating member.