TWI299077B - Combustion method and system - Google Patents

Description

IX. INSTRUCTIONS: TECHNICAL FIELD OF THE INVENTION The present invention relates to a combustion method for a solid hydrocarbon fuel and a combustion system. t prior art 3 invention background

Solid fossil fuels (such as coal) are an important source of energy, especially for generating electricity. However, pollutants emitted from coal combustion are the main source of air pollution. Of the pollutants from coal combustion, nitrogen oxides (NOx) attract a lot of attention.

Two major sources of NOx are produced during combustion: fuel NOx and thermal NOx. Fuel NOx is NOx formed by the conversion of chemically bound nitrogen (fuel nitrogen) during combustion. Fuel nitrogen (or charcoal-N) is released by several complex combustion methods. The main starting product of combustion 15 is HCN or NH3. Then, the HCN is oxidized to NO or reduced to N2. If the oxidant or fuel is poor in the gas system, NO will be the main product of fuel nitrogen. If it is rich in fuel, HCN is reduced to N2 by CO or C (carbon) on the surface of coal. Thermal NOx refers to the formation of iN〇x from the high temperature oxidation reaction of atmospheric nitrogen. The formation of heat 20 NOx is an exponential function of temperature and a square root function of oxygen concentration. A lower combustion temperature or a lower oxygen concentration produces a lower N〇x. Therefore, the generation of thermal NOx can be controlled by controlling the reaction temperature or the oxygen concentration. However, lower combustion temperatures or lower oxygen concentrations result in insufficient combustion of the coal, i.e., a slow burning rate. The slow burning rate will cause the incomplete combustion of coal. 5 1299077 , v74 is no longer burned and the coal is prolonged burning.

Various techniques have been developed to reduce the release of cockroaches. These techniques reduce combustion temperatures or manipulate oxygen concentrations. The former is called “dilution-based combustion control technology”, and the latter is called “stoichiometric-based combustion control technology. The dilution-based combustion technology introduces inert gas (such as water or fuel gas). To reduce the peak temperature of the flame. The stoichiometric combustion technology consists of reducing the oxygen concentration in the flame region and producing a reduced atmosphere, thus reducing the enthalpy. Examples are low 1 〇 1 stage burners and 〇 s combustion, for example , over-fire-air and burner-out-of-service. These technologies generate fuel-rich zones (partial combustion zones) by providing air and/or fuel fractionation. And the subsequent rich air zone to complete the combustion method to control the production of ΝΟχ. Such low; 〇 之 burner can reduce the release of ΝΟχ to 每 65 to 〇 25 lbs per million 。 。. Another ΝΟχ control The technology is reburning the gas. This re-combustion technique reduces the release of ^^〇乂15 to 〇45 to 0.18 per million BTU.

However, such techniques for reducing defects are not appropriate. For example, it does not pay for the release of the U.S. Clean Air Act (less than 0.15 pounds per million BTU). In addition, in almost all low _ 燃烧 combustion technologies, the burning time needs to be significantly increased. Therefore, the size of the boiler needs to be increased by 20 to accommodate long burning times to allow the combustion of coal to be economically acceptable. As a result, almost all of the control technologies require significant capital investment and high operating costs. Recent studies have shown that the supply of high-temperature coal gas can significantly reduce the release of Ν0χ and the unburned carbon in fly ash. For combustion with high temperature gas, fuel 6

1299077 %4 π fiE 曰月曰,二> __—Supplement 虱 is rapidly devolatilized and reduced to nitrogen during devolatilization and combustion in the fuel-rich zone.

I SUMMARY OF THE INVENTION The present invention is based on the fact that the inventors have learned a number of problems related to the prior art, although the techniques used to reduce N0x in the prior art are based on Behring. However, devices based on such technologies generally do not achieve an optimal reduction. The reason is that these devices do not, or cannot quickly, shed operating parameters to accommodate the variability operation 10 conditions for optimal n 〇 X reduction. For example, when the quality or type of coal changes or when the amount of load changes, the device that knows the skill does not, or cannot quickly, recognize the change and adjust the operating parameters to accommodate the change. Therefore, the optimum 2Ν〇χ reduction cannot be achieved for the coal used. At the same time, the unburned carbon in the fly ash also increases. Another problem associated with the prior art is in the case of technologies involving the supply of hot gases to coal, which produce high combustion temperatures and the inability to adjust operating parameters. U Adapting to changing operating conditions can cause the flame front to become too close to the burner. The wall and/or the wall of the combustion chamber. Therefore, slag occurs on the walls of the burner and/or on the walls of the combustion chamber. For example, the inventors' experiments show that when the operation parameter is set for anthracite (with 7.36% volatiles) but using bituminous coal (with 17.22% volatiles), it will be overheated on the wall of the burner. The slag is generated and the combustion system is shut down. The present invention relates to a combustion process having low enthalpy release, low unburned, any styling, 5 automatic adaptation of fuel, and reduced slagging-or more advantages. This method of combustion can include a 7 1299077 17 correction date supplement

Empty*1/fuel stream injected into the burner creates a low pressure zone; directs the high temperature combustion gas machine from the combustion chamber to the low pressure zone of the combustor; mixes the high temperature combustion gas with the /main shot air/fuel stream Heating the injected air/fuel stream and causing the heated air/fuel stream to be injected from the burner into the combustion chamber, where the air/fuel stream is rapidly devolatilized and combusted within the flame; inductive combustion parameters; Based on the inductive combustion parameters, the combustion is controlled to achieve at least one of the desired reduction and the desired distance from the burner to the flame front. In a preferred embodiment, the combustion is controlled to maximize NOx reduction and no slag formation. It constitutes the “not allowed slag formation”, which cannot be determined in an abstract manner and depends on the design requirements of the specific combustion system. This decision can be made by those skilled in the art.

The invention also relates to a combustion system for a pulverized hydrocarbon fuel. The combustion system can include a combustor designed to receive an air/fuel stream; a combustion chamber coupled to the combustor to deliver high temperature combustion gases 15 to the combustor for heating the air/fuel stream, and receiving a heated air/fuel stream for combustion from a combustor; an inductor for inductive combustion parameters; and a controller for controlling combustion based on inductive combustion parameters to achieve desired reduction and combustion At least one of the desired distance from the device to the leading edge of the flame. In a preferred embodiment, the combustion is controlled to reduce the enthalpy to a maximum of 20 and no slag formation. In a preferred embodiment, the rate of air/fuel flow injected into the combustor is from 10 to 60 meters per second, more preferably from 15 to 50 meters per second. This rate can be designed to supply air/fuel flow under the unblocked supply line and to direct pressure below the combustion chamber to the interior of the burner. Injection section at the inlet of the burner 8 1299077 The product may be the fraction of the cross-sectional area of the burner, preferably 20% to 60%. The desired ratio of the two cross-sectional products is such that a specific amount of high temperature combustion gas flows back from the combustion chamber to the combustor. In another preferred embodiment, the air/fuel stream concentrates the air/fuel stream, i.e., has a low air to fuel ratio air/fuel flow. Preferably, the ratio of air to fuel solids in the concentrated stream is 八4 to 2.2 kg of air of eight kilograms of fuel, more preferably 0.7 to 1.8 kilograms of air per kilogram of fuel. this

Indicates only 8% to 25% of the stoichiometric amount of fuel for anthracite and bituminous coal. 10 There are several reasons for using a concentrated air/fuel flow system. First, the concentrated stream maintains a highly fuel-rich flame in the burner and combustion chamber, which significantly reduces NOx. Second, the concentrated stream can be heated using a relatively small amount of heat. Therefore, "Chen shrink flow can be quickly heated in a short distance. Third, the heated concentrated stream releases a large amount of volatile material during rapid heating. (Partial combustion will also occur during heating). The released volatile substances promote the ignition and combustion of the coal particles and reduce the unburned carbon in the fly ash. In addition, the rapid release of volatile materials (including the nitrogen of the combined fuel in a fuel-rich atmosphere) converts the nitrogen of the combined fuel into N2 rather than NOx. The concentrated air/fuel flow and the overall function of the designed fuel burner enable the implementation and maintenance of combustion in high temperature and reduced gas atmospheres, which contributes to ultra-low NOx release and low unburning in fly ash. Carbon. The air/fuel flow within the combustor can be a vortex flow or a direct current. Some typical burner structures are wall-type combustion, trans-combustion, tangent-linear combustion, and under-burning. The burner is preferably formulated at the same vertical height as the combustion chamber. 9 1299077 9氙4. ΠRevised Year 曰._ Supplementary to the other preferred embodiment of the invention, the combustion system may comprise a separation, tethering system for separating the air/fuel stream from the pulverizing system Into the rich, reduced air/fuel flow and the dilution air/fuel flow. The separation device is connected to the burner to supply the extended gas/fuel flow to the burner. The concentration of the concentrated flow [Η,: solids ratio It is lower than the air/fuel flow from the pulverization system. Typically, the ratio of air to fuel 2 in the air/fuel stream from the pulverization system can be from 1·25 to 4·〇 kg of air/1 kg. Fuel. The ratio of air to fuel solids in the concentrated air/fuel stream is preferably 〇 4 to 2.2 kg of empty milk / 1 kg of fuel, more preferably 7 7 to 18 kg of air, 8 kg of fuel The embodiment of the invention may comprise two or more air/fuel streams injected into the combustion chamber. Each of the air/fuel streams may be a concentrated air/fuel stream, It can have an air of 公斤.4 to 2.2 kg and an air of eight kilograms. The material is better than the space between 0 and 18 kilograms. The gas of eight kilograms of fuel, the ratio of air to fuel solids. In addition, each of these air/fuel streams may be a dilution air/fuel stream, which may have a larger empty milk than the concentrated air/fuel stream. Proportion of fuel. Each air/fuel stream may be heated as described above prior to injection into the combustion chamber, or may be unheated. For example, a preferred embodiment of the invention may include 2 〇 primary air that is concentrated and heated. a fuel stream, and a secondary air/fuel stream that is diluted and that may or may not be heated. Preferably, the primary air/fuel stream is injected into the combustion chamber first, and then the secondary air/fuel stream is injected. Complete combustion to the combustion chamber. The secondary air/fuel stream may contain sufficient oxygen to cause the total amount of oxygen supplied to the combustion chamber to constitute at least the chemistry required to completely burn the fuel.

1299077 Metering content. Preferably, the 'secondary air/fuel stream is supplied to a combustion chamber adjacent to the outlet for the combustion of the main stream. A typical secondary air and fuel stream contains about 3.5 to 8 kilograms of air for a 1 kilogram fuel system, which represents about 65 to the stoichiometric combustion of 5 burned air required to completely burn anthracite, bituminous coal and oil coke. 90%.

In this embodiment, an additional dilution air/fuel stream, such as the so-called "excessive combustion air", is injected into the combustion chamber. This additional dilution air/fuel stream can be heated or unheated. In certain embodiments, the additional dilution air/fuel stream contains sufficient oxygen to provide a total amount of oxygen supplied to the combustion chamber that is at least a stoichiometric amount that completely combusts the fuel. For another embodiment, a preferred embodiment of the invention may include two or more concentrated air/fuel streams that may or may not be heated, and each concentrated air/fuel stream may be followed by one or more A dilution air/fuel stream that can be heated or unheated. At least one of reducing the NOx and the distance from the burner to the flame front can be accomplished in several ways. For example, it may include controlling one or more of the following control parameters: a pressure in a low pressure zone within the combustor, at least one of a flow rate of the concentrated air/fuel stream and an air/fuel ratio, and a flow rate of the diluted air/fuel stream And at least one of the air/fuel ratio. Control of combustion can be achieved by controlling the pressure in the low pressure zone because the pressure in the low pressure zone affects the flow rate of the high temperature combustion gases from the combustion chamber to the low pressure zone within the combustor, thereby affecting the heating of the air/fuel stream. The pressure in the low pressure zone can be controlled by introducing a gas into the low pressure countercurrent zone. Preferably, this gas system is air (third air). When the amount of third air increases, low 11 1299077

The pressure in the nip is also increased, causing a decrease in the flow of high temperature combustion gases from the combustion chamber to the low pressure region. Therefore, the heating of the air/fuel stream is reduced, and the combustion temperature is reduced daily. The amount of third air also affects the air/fuel weight ratio of the air/fuel stream, which can also be used for combustion control. Combustion control can also be achieved by controlling the flow rate of the air/fuel stream and the air/fuel ratio that is injected into the burner because of the flow rate of the air/fuel stream and/or the concentration of the air and the air/fuel flow. Devolatilization and combustion. 10 The combustion control of the present invention may be based on - or a plurality of combustion parameters. Representative parameters can be the concentration of the operating temperature, pressure, and gas (such as 'deuterated carbon, carbon monoxide, oxygen, and nitrogen'). Preferably, the temperature is taken as a combustion parameter. Control can be achieved by inducing the value of the combustion parameters in the burner and/or combustion chamber, and by making the value of the money constant. Based on the difference between the sensed value and the predetermined value, the controller (such as a closed loop controller or a distributed control system) is adjusted—or multiple of the above discussed controls to reduce this difference. When the difference is reduced, the release is reduced, and/or the desired distance from the burner to the flame front is maintained at a low level. This automatic control allows the burner to be used in almost any type of fuel without changing the structure of the combustion system. 20 Here, turbulence, - the word means that the high-temperature combustion gas flows back from the combustion chamber to the combustion chamber. The flow of money (4) is in the opposite direction. Other terms used for the flow of the type are "reflow," and "recycle,". Countercurrent system: The pressure caused by the injection of air/fuel flow into the burner is reduced to 0 12

1299077 Here, the term "heating" means the heating of air/fuel flowing into the burner. The heating source is a countercurrent to the ambient temperature combustion gas. Heating can be carried out by mixing and heat radiation. In the case of a concentrated air/fuel stream, the temperature of the air/fuel stream is measured at a distance of 25 〇mm and 1950 mm from the outlet of the supply line for supplying the concentrated fuel stream to the burner, up to 700 〇c to 1200 〇C.

Here, the term "NOx" means an oxide of nitrogen, and includes a mixture of no, n〇2, no3, n2o, n2o3, n2o4, N304, and the like. The term "incorporating nitrogen" as used herein means nitrogen which is a constituent of a molecule composed of carbon and hydrogen and possibly oxygen. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing a preferred embodiment of the present invention for producing a concentrated fuel stream and performing heating in a burner and combusting in a combustion chamber. Figure 2 shows the flow pattern of the countercurrent and heating of the air/fuel stream. 15 Figures 3 and 4 show cross-sectional views of the burner of the embodiment shown in Figure 1. Figures 5 and 6 show cross-sectional representations of the apparatus of the present invention for supplying a concentrated fuel stream to a combustion chamber to produce a counter-current combustion gas countercurrently flowing back into the combustor and controlling the high temperature combustion gas to flow back into the combustor. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT The preferred embodiments of the invention described below are sometimes discussed in terms of coal combustion, and are an air-based gas assembly and an oxidant. The technique can be applied to any other powdered solid fuel and any other gaseous carrier. The invention is described by way of example only, but the description of the drawings is not intended to limit the scope of the invention. 13 1299077 96.4.17 Correction 卜巧充丨 Figures 1 to 4 show a preferred embodiment of a vortex burner in accordance with the present invention. Some embodiments of the burner are described in more detail in Figures 4 and 5. The present invention also encompasses a direct current burner in which a secondary flow or/and other flow system is supplied to the combustion chamber as a direct current. 5 Figure 1 shows a combustion system comprising a burner 3 and a combustion chamber 1 having a chamber. The combustion device of the present invention can be burned in it

Any device. Typical combustion devices include furnaces and boilers. The burner 3 is placed on the side wall or corner of the combustion apparatus 1 and supplies fuel solids and air from the source outside the combustion apparatus 1 to the combustion chamber 2 of the combustion apparatus 1. The fuel of Code 10 contains powdery hydrocarbon solids, examples of which are powdered coal or petroleum coke. In the illustrated embodiment, the fuel and air are used for the main air/fuel stream A and for pneumatically controlling the fuel and The secondary dilution air/fuel stream is supplied to the combustion system. For primary air/fuel stream A, air may be supplied in a stoichiometric ratio of less than one. The air for complete combustion of the fuel may be supplied to the combustion apparatus 1 as a secondary flow B (= Bl + I) and/or with excessive combustion air as shown in Figs. As shown in Figures 1 and 3 through 6, the burner 3 is comprised of a syringe 8, 16 for the primary concentrated air/fuel stream 31, a secondary flow injector 13, 19, and an automatic control unit 20. Preferably, the solid-gas separator 4 is placed in front of the injector 8 for the primary concentrated air/fuel stream 3! to divide the primary air/fuel stream A into a concentrated stream ai and a released fuel stream a2. The separator 4 is preferably a curved three-way separator, but should not be limited to a curved separator. The curved three-way separator 4 comprises a main inflow line 5, a curved line 6, a dilution feed line 14 2 "077, and a supply line for the main concentrated fuel Seven supply lines 8. Preferably, the winding angle 6 of the curved line 6 is 60. With 12 baht. between. The ratio of the inner radius of the line 8 for concentrating the air/fuel stream to the inner radius of the official line 7 for diluting the fuel stream is between 0.5 and 2.0. 5 The main air/fuel stream A from the comminution system (not shown) is self-contained

The inlet line 5 is supplied at a speed via the curved type road separator 4. The fuel powder can be concentrated at a bend outside the separator 4 by designing a separator 4 having a specific radius and a winding angle that matches the flow velocity of g. This divides the main stream A into a main concentrated stream (1) in the region outside the elbow and a dilute stream a2 in the region inside the elbow. The concentrated stream aHf is supplied to the combustor 3 via a supply line 8. The dilution stream a2 is supplied to the combustion apparatus 1 via the orifice 20 at a position close to the burner 3 via the supply line 7. The angle of the outlet direction of the separator 4 can be adjusted. The main stream A of the type contains about 1.25 to 4.0 kg of air for 1 kg of fuel solids, which means about 10 to 35% of the stoichiometric combustion 15 of the air required to completely burn the fuel. The flow rate and concentration of the concentrated stream &amplifier 1 or the dilution stream a can be placed in the sheet of the supply line 8 for the Han shrink stream a and the strip 7 for the dilution stream a2 Controlled by valves. In addition, some other configurations may be used by the rabbit 'I' to control the flow rate and concentration of the concentrated stream & The work/20 secondary flow system is from the secondary flow bellows 11 (Fig. 1). It is also known that the secondary flow system uses two-channel supply: the inner secondary flow channel and the outer secondary flow channel B2. The inner secondary flow channel 艮 includes a throttle valve 10 for the secondary flow of the 9 p flow between the throttling flows of the direct current flow, the air deflector 12, and the heat, 疋 ^ ^ ^ a person to flow out of the pipeline 13 . The outer secondary flow channel & includes an internode 1 15 1299077 for the DC secondary flow, a throttle valve 15 supplemented by the secondary flow of the vortex flow, an air deflector 18, and a secondary flow discharge line 19. If the elements are circular or cylindrical, the elements are placed centrally along the axis of the supply line 16 of the concentrated flow &!. It is supplied from the bellows 11, and thereafter, the secondary flow is divided into two streams by adjusting the throttle valves 9 and 510. In the meantime, the first stream bn is DC air, and the second stream

B12 is a swirling air generated by the axial air deflector 12. Adjusting the throttling valves 9 and 10 gives the desired vortex intensity. It is supplied from the bellows 11, and thereafter, the outer secondary stream B2 is divided into two streams by adjusting the throttle valves 14 and 15. Meanwhile, the first stream b21 is a direct current air, and the second stream b22 is a swirl flow generated by the axial air deflector 18 10 . Adjusting the throttle valves 14 and 15 can impart the desired vortex intensity. A typical secondary stream B contains about 3.5 to 8.0 kilograms of air for a kilogram of fuel, representing about 65 to 90% of the stoichiometric combustion air required for the complete combustion of anthracite, bituminous coal and oil coke. The vortex intensity is controlled by adjusting the throttle valves 9 and 10 and 14 and 15. Preferably, the number of vortices (as defined by J. M. Beer and N. A. Chigier, Robert E. Krieger Publishing Company, Inc., 1983) is from 0. 1 to 2.0. Preferably, the excess combustion air is supplied to the combustion apparatus 1 through the degree combustion air orifice 21 such that the entire combustion zone within the combustion apparatus 1 becomes rich in 20 fuel and more oxygen is supplied to assist in complete combustion of the fuel. The volume fraction of excessively combusted air may be between 0 and 30% of the total air required to be supplied to the combustion apparatus 1 for complete combustion of the fuel. In a preferred embodiment, the concentrated stream enters the combustor chamber 40 and forms a fuel rich region, wherein the stoichiometric ratio is between 0.08 and 0.25. High temperature 16

The countercurrent of 1299077 gas is introduced into the burner 3 from the combustion chamber 2 so that the concentrated stream is rapidly heated to devolatilize the volatile matter and the bound nitrogen. The combustion occurs sequentially between the fuel solid and the combustion air to produce a flame c2. The secondary flow and sometimes the excessive combustion air is injected into the combustion chamber 2 for complete combustion. The countercurrent system 5 is caused by relatively low pressure caused by injecting the concentrated flow center at a higher rate than the gas velocity in the combustion device 1.

Rapid heating of the concentrated fuel stream within the rich fuel zone Ci produces a volatile fuel zone. This significantly increases the flammability of the fuel stream. Therefore, the ignition is maintained and is completed in a short time and range. And the fuel can be burned at 10 high temperatures. Rapid heating and devolatilization combine with high temperature combustion under a reducing gas atmosphere to produce nitrogen. These identical combustion conditions also contribute to the combustion of the fuel particles, thus reducing the unburned carbon in the fly ash. When the fuel concentration is high or the air/fuel ratio is low, the ignition time will be shorter; the combustion temperature will be higher; and the flame front will be closer to the burner. When the flame front is too close to the mouth of the burner, for example, slagging can occur. This is particularly important when the fuel type is changed from a low-grade fuel having a low content of volatile matter, such as an 'anthracite coal, to a fuel having a high content of volatile matter, such as bituminous coal. In this case, the air/fuel ratio needs to be increased to avoid slagging. The present invention uses Inductive 22 to monitor changes in at least one parameter within burner 3 or combustion chamber 2. Representative parameters include temperature, pressure, and the amount of selected gas. The selected gas may be one or more of 〇2, CO, C02, N〇x, N2, and HC. The inductor can be placed in the burner 3 or in the combustion chamber 2, or in the region where the burner 3 and the combustion device 1 are in contact. For example, temperature sensing 17

The 1299077 can be placed at or near where slag formation may occur. The temperature signal is sent to the closed loop controller 23.

A typical controller can be a PID (proportional-integral-difference) controller or a dcs (distributed control system) controller. The signal is compared to a predetermined value. If the measured 5 temperature signal is greater than the predetermined value, meaning that the combustion temperature is too high or the flame front is closer to the burner than the desired distance, the controller sends an instruction to the servo 24, which changes the opening of the valve 25. Reduce the combustion temperature. In particular, the controller allows more third air T (either directly from the atmosphere or from a supply source) to enter the combustor 3. In addition, the third air dilutes the fuel stream and reduces the backflow of the combustion gases 10, increasing the distance between the burner 3 and the flame front. This control process continues automatically until the sensed temperature is the same or close enough to the desired value. Automatic control allows the combustion system to be applied to different fuel types and to reduce the release of helium. Preferably, the total amount of air supplied to the combustion device 1, that is, the main air A (=a! + aO, the secondary flow B (= Bi + BO, and the total air 15 in the third air T), is used Preferably, between 90 and 125% of the stoichiometric air required for complete combustion. Preferably, the air passing through the excessively combusted air orifices 21 is about 0 to 30% of the total air delivered to the combustion apparatus 1. The amount of excessively combusted air It can be controlled by adjusting the opening of the over-combustion air valve 26. Preferably, the second air enthalpy is controlled such that the flame front is tied between the burner 20 100 mm & 1400 mm. In some cases, when The slagging action also occurs when the flame front is closer to the burner than this preferred range. The amount of air supplied to the burner 3 and the aerodynamic configuration of the air are preferably used to establish a fuel rich region of the flame a. It is less than the stoichiometric ratio of 〇75. The air content in the concentrated stream is preferably less than 30% of the stoichiometric amount required to completely burn the solid fuel for the solidification of the year 12 1299077 96· 4· I7 More preferably, this content needs to be less than 20% of this stoichiometric amount.

The release of NOx and the unburned carbon in the fly ash are dependent on the stoichiometric ratio of the fuel-rich region (the enthalpy and the rich fuel flame region c2 and the rate of increase of the fuel-rich region q or the rate of temperature rise. For example, if When the main stream A is sent directly to the burner 3, the heat required to heat the stream to the ignition temperature is about twice or more than twice the heat required to heat the concentrated stream ajn. The ignition of the stream will be delayed and will not be fully combusted in the combustion system. At the same time, the release of N〇x will increase dramatically when the stoichiometric ratio is greater than 1.0. 10 In a preferred embodiment, the invention is Producing and maintaining a controlled rich fuel flame: concentrating the conventional main stream; then, using the countercurrent combustion gas in the combustor 3 to first heat the concentrated stream (the countercurrent is induced by its relatively high velocity concentrated fuel stream) The negative pressure is used to control the countercurrent. The highly concentrated fuel flow flame is preferably maintained by a countercurrent controlled by 15 to make the stoichiometric ratio sufficiently lower than the original primary air.

Gas value. Fuel injectors in burners typically have a circular cross section, a circular cross section (formed by a tubular member of the same center), or a square or rectangular cross section (e.g., a syringe in a 'tangentially fired boiler). These designs or configurations meet 20 for the second function of the present invention: supplying a fuel stream to the combustion unit and generating a counter-current gas back into the burner for heating the concentrated stream. Figures 5 and 6 show some representative designs for implementing these functions. However, the present invention encompasses all designs and configurations for supplying fuel and generating countercurrent flow of high temperature gas from the combustion unit. These designs can be used in wall-fired boilers, tangentially fired 19 1299077 steel furnaces, and below-burning furnaces. Figure 5 shows some fuel injectors without a third air inlet. It is noted that while certain embodiments of the present invention use third air to control the pressure in the low pressure countercurrent zone, other embodiments of the present invention also include a burner that does not use a third air. In the 5&Fig., the supply line 8 for the concentrated fuel stream is located in the line of the burner line 16. In the north map, the supply line 8 is located off the line of the burner line 16. In the first diagram, the supply line 8 surrounds the burner line 16

And configuration. In the 5th to 5g drawings, the supply line 8 is composed of two parts, a straight section and a concentric section, and in the burner line 16, it may be solid. When 10 third air is not used to control the pressure in the low pressure region within the combustor 3, the amount and/or amount of concentrated fuel stream flowing into the combustor can be controlled to adjust the pressure and/or adjustment within the combustor The heating in the burner 3 and the weight ratio of the fuel/air. Figure 6 shows some fuel injectors with a third air inlet. In Figure 6a, the second air inlet is located on the side wall of the combustor line 16. Preferably, the third air line 17 is located two thirds of the burner line 16 (from the fuel flow inlet). In Figure 6b, the third air inlet 17 is located on the front surface of the burner line 16 (here, the front is the inlet to the fuel stream). 2 The burner line 16 and the third air line 17 can be of any shape. The shape representing the bismuth is a cylindrical shape, a cubic shape, a 稜鏡 shape, a conical shape, an elliptical shape, and a truncated cone shape. In addition, all of the supply line 8 and the burner line 16 shown in Fig. 5 can be used as a fuel injector with a third air. The preferred shape is a cylindrical shape, a cubic shape, and a dome shape. There may be any number of supply lines and third air lines for the concentrated fuel stream. The third pipeline factory can be 20

1299077 is related to the burner centerline at any angle. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing a preferred embodiment of the present invention for producing a concentrated fuel stream and performing heating in a burner and combusting in a combustion chamber. Figure 2 shows the flow pattern of the countercurrent and heating of the air/fuel stream. Figures 3 and 4 show cross-sectional views of the burner of the embodiment shown in Figure 1.

Figures 5 and 6 show cross-sectional representations of the apparatus of the present invention for supplying a concentrated fuel stream to a combustion chamber, generating a high temperature combustion gas countercurrently back into the combustor, and controlling the high temperature combustion gas to flow back into the combustor. 10 [Main component symbol description] A...main air/fuel flow B...minor flow a...main concentrated air/fuel flow d2...diluted fuel flow B1...secondary Stream channel B2...outer secondary stream channel bn...苐one stream bi2....different two streams b2i...first stream b22... The second flow C1 ... rich fuel area C2 ·······flame 21 1299077

1...·..Combustion device 2...·.. chamber 3...·.. burner 4"··.. solid-gas separator 5...·.. main inlet line 6"" ...· .. Feeding line 8...·..Syringe 9..... Throttle valve 10.·....Throttle valve 11·..Secondary flow bellows 12......Air deflector 13.. ...secondary flow syringe 14··. throttle valve 15··. throttle valve 16··.injector 17·....second air line 18··....air deflector 19··.. secondary flow syringe 20... orifice 22

1299077 21.. .... Excessive combustion air orifice - 22 · · .... Sensor 23.. .... Closed loop controller - 24.. .... Servo machine Qin 25 · · · Valve 26.. .. .. Excessive combustion air valve i 30.. .... automatic control unit w 40.. .... burner chamber

twenty three

Claims (1)

1299077 10 15 20 X. Patent application scope: No. 95112987 Special money please (4) Request the patent scope to amend this revision date: 96 years 1 month 1 - Method for burning powdery cigarette fuel, the method includes: Making air/fuel flow Injection into the burner to create a low pressure zone; directing the south temperature combustion gas stream from the combustion chamber to the low pressure zone within the burner; mixing the high temperature combustion gas with the injected air/fuel stream to Injecting the air/fuel stream to heat, and injecting the heated air/fuel stream from the burner into the combustion chamber, during which the air/fuel stream is rapidly devolatilized and combusted in a flame having a high temperature; inductive combustion a parameter; and controlling combustion to achieve at least one of a desired NOx reduction and a desired distance from the burner to the flame front based on the inductive combustion parameter. 2. The method of claim 1 is Wherein the step of controlling combustion comprises controlling the pressure of the low pressure zone. 3. The method of claim 2, wherein the step of controlling the pressure in the low pressure zone comprises controlling a third air supplied to the low pressure zone to control the pressure of the low pressure zone. 4. The method of claim 3, wherein the supply line for supplying the third air is located two-thirds of the time before the inlet for the air/fuel stream is measured. 5. The method of claim 1, wherein the controlling the combustion step 24 1299077 comprises controlling a flow rate of the high temperature combustion gas from the combustion chamber to the low pressure region of the combustor. 10 15 The method of claim 1, wherein the controlling the combustion step comprises controlling at least one of a flow rate of the injected air/fuel stream and an air/fuel ratio. 7. The method of claim 1, wherein the air/fuel stream is a concentrated air/fuel stream. 8. The method of claim 7, wherein the concentrated stream has a weight ratio of air to fuel in the range of 0.4 to 2-2. 9. The method of claim 7, wherein the concentrated stream is heated to a temperature between 700 ° C and 1200 ° C measured at a distance of 250 mm and 1950 mm from the inlet of the burner for the high temperature gas. The temperature. 10. The method of claim 7, wherein the concentrated stream has a weight ratio of air to fuel in the range of 0.7 to 1.8. 11. The method of claim 7, wherein the concentrated flow is injected into the burner at a rate of 10 to 60 meters per second. 12. The method of claim 7, wherein the concentrated flow is injected into the burner at a rate of 15 to 50 meters per second. 13. The method of claim 1, wherein the cross-sectional area of the injected air/fuel stream to the inlet of the burner is a fraction of the cross-sectional area of the burner. 14. The method of claim 13, wherein the cross-sectional area of the injected air/fuel stream to the inlet of the combustor is less than 50% of the cross-sectional area of the combustor. 25 1299077 10 15 96. The application of the method of claim 1, wherein the fuel is at least one of coal and oil. 16. The method of claim 7, further comprising dividing the primary air/fuel stream into the concentrated air/fuel stream and the dilution air/fuel stream, and supplying the dilution stream to the combustion chamber. 17. The method of claim 16, wherein the controlling the combustion step comprises controlling the supply of the dilution stream to the combustion chamber. 18. The method of claim 16, wherein the step of dividing the primary air/fuel stream into the concentrated stream and the dilution stream is performed by a curved line. 19. The method of claim 18, wherein the winding line has a winding angle between 60° and 120°. 20. The method of claim 16, wherein the primary stream contains from 10% to 35% of the stoichiometric air. 21. The method of claim 1, wherein the combustion parameter comprises at least one of a pressure sensor, a temperature sensor, and a chemical sensor for sensing a gas content. 22. The method of claim 1, wherein the sensing step is performed by an inductor disposed within the burner or combustion chamber or embedded in a wall of the burner or combustion chamber. 23. The method of claim 1, further comprising injecting at least one additional air and fuel stream. 24. The method of claim 23, further comprising heating the at least one additional 26 1299077 Alum 月 曰 曰 曰 空气 空气 空气 空气 空气 空气 空气 之一 之一 之一 之一 之一 之一 26 26 26 26 26 26 26 26 26 26 26 26 . 25. The method of claim 23, wherein the at least one additional air and fuel stream is overburned m, the towel, the overburning air is supplied to the total air of the combustion chamber 〇 to 3〇%. 5. The method of claim 25, wherein the controlling the combustion step comprises controlling the supply of the excessively combusted air. 27. The method of claim 23, wherein the at least one additional air and fuel stream is intended to be a fuel stream. 28. The method of claim 27, further comprising supplying the secondary stream 10 to the combustion chamber adjacent the burner outlet for the H-th fuel stream. 29. The method of claim 27, wherein the step of controlling combustion comprises controlling the supply of the secondary stream. 30. The method of claim 27, wherein the secondary flow is directly 15 or one of the vortex flows. 31. The method of claim 3, wherein the step of dividing the quenching secondary stream into the inner secondary stream and the outer secondary stream. 32. The method of claim 31, wherein the vortex strength is between 〇.1 and 2.0. The method of claim 23, wherein the air/fuel stream is a first air/fuel stream, and wherein the at least one additional air and fuel stream is a second concentration Air and fuel flow. 34. The method of claim 33, wherein the second concentrated air/fuel stream is heated. The method of claim 1, wherein the step of controlling combustion comprises controlling combustion to maximize the reduction of enthalpy and does not allow for slag formation. 36. A combustion system for a pulverized hydrocarbon fuel, the apparatus comprising: 5 a burner designed to receive an air/fuel stream; - a combustion chamber coupled to the vessel for high temperature combustion gases Flowing to the combustion state to heat the air/fuel stream, and receiving the heated air/fuel stream for combustion from the combustor; a sensor for sensing combustion parameters; and 10 a controller, It controls combustion based on the inductive combustion parameters to achieve at least one of desired reduction and desired distance from the burner to the flame front. % 37_ The combustion system of claim 36, wherein the controller controls the pressure in the low pressure zone. The combustion system of claim 37, wherein the controller controls the third air supplied to the low pressure zone to control the pressure of the low pressure zone. 39. The combustion system of claim 36, wherein the controller controls a flow rate of the south temperature combustion gas from the combustion chamber to the 20 low pressure zone within the combustor. 40. The combustion system of claim 36, wherein the controller controls at least one of a flow rate of the injected air/fuel stream and an air/fuel ratio. - 41. The combustion system of claim 36, wherein the air/fuel 28 1299077 stream is a concentrated air/fuel stream. 42. The combustion system of claim 36, wherein the combustion parameter comprises at least one of a pressure sensor, a temperature sensor, and a chemical sensor for sensing a gas content. 5 10 15 43. The combustion system of claim 36, wherein the combustion chamber is injected into at least one additional air and fuel stream. 44. The combustion system of claim 43, wherein the at least one additional air and fuel stream is heated by an additional countercurrent flow from the high temperature combustion gases of the combustion chamber. 45. The combustion system of claim 43, wherein the at least one additional air and fuel stream is a secondary dilution air and fuel stream. 46. The combustion system of claim 43, wherein the air/fuel stream is a first concentrated air/fuel stream, and wherein the at least one additional air and fuel stream is a second concentrated air and Fuel flow. 47. The combustion system of claim 46, wherein the second concentrated air/fuel stream is heated. 48. The combustion system of claim 36, wherein the controller controls combustion to maximize NOx reduction and does not allow slagging. 29 1299077 9§·V7 Amendment Monthly Supplement VII. Designation of Representative Representatives: (1) The representative representative of the case is: (1). (2) A brief description of the component symbols of this representative figure: Α...main air/fuel flow Β···...secondary flow...second air1····..burning device 2 ...· .. chamber 3...·.. burner 11··.. secondary flow bellows 21.....excessive combustion air hole 26··.overburning air valve 8. If there is a chemical formula in this case, please disclose the chemical formula that best shows the characteristics of the invention: