A control method for a heat-controlled temperature-controlled fully premixed multi-stage jet gas burner

Abstract

The present invention belongs to the technical field of biomass gasification and its gas burner control. It discloses a control method for a heat-controlled, temperature-controlled, fully premixed, multi-stage ejector gas burner. The method generates high-temperature air by introducing the high-temperature flue gas generated by combustion into a heat storage high-temperature air generator. After the high-temperature air is used to quickly ignite and stabilize the gasifier and gas burner, the medium- and high-temperature heat pipes are activated. The liquid filling in the evaporation end of the medium- and high-temperature heat pipes absorbs heat and evaporates, then reaches the condensation end and releases heat to heat the crude gas, raising the temperature to above 300°C. Based on the temperature and flow signals fed back by subsequent heat-consuming equipment, including boilers and hot blast furnaces, the actual operating load of the gasifier and gas burner is intelligently monitored and controlled. The present invention uses a heat storage method to increase the hydrogen content in the gas, thereby improving combustion performance. A two-stage or even multi-stage ejection method is used to ensure that the ejected air in the first-stage ejector has a high flow rate, thereby increasing pressure, enhancing mixing, and stabilizing combustion.

Description

Technical Field

[0001] The present invention belongs to the technical field of biomass gasification and gas burner control, and in particular relates to a control method for a heat-controlled temperature-controlled full-premixed multi-stage injection gas burner. Background Art

[0002] The largest heat loss factor affecting boiler thermal efficiency is exhaust loss, and the primary factors influencing exhaust heat loss are exhaust volume and temperature. The primary parameter influencing exhaust volume is the excess air coefficient during combustion. Biomass direct combustion utilizes gas-solid heterogeneous contact, which requires a high excess air supply for adequate combustion. The ideal excess air coefficient is generally between 1.4 and 1.6. However, in practice, depending on the level of automation, it is not uncommon for the excess air coefficient during heterogeneous gas-solid combustion to exceed 2 or even 3. This increase in excess air coefficient significantly increases exhaust volume, leading to a significant increase in boiler exhaust heat loss and a sharp drop in boiler thermal efficiency. Research has shown that, beyond the optimal excess air coefficient, every 0.1 increase in the excess air coefficient results in a decrease in boiler thermal efficiency of approximately 1.3%. This is one of the key reasons why traditional chain-type boilers are being phased out due to their low thermal efficiency (as low as around 60%). The parameters that affect the exhaust gas temperature can be summarized as heat transfer efficiency, and the most important factor affecting the heat transfer efficiency is the heat transfer coefficient. Compared with coal, although the ash content in biomass fuel is much lower than that of coal (only about 1 / 6), the content of alkali metals such as K and Na is much higher than that of coal. The melting points of alkali metals and their compounds are relatively low. When burned or gasified, they easily evaporate upward and enter the gas phase. After cooling, they solidify on the downstream heat exchanger wall to form a layer of hard ash that is difficult to clean (unlike the ash in coal-fired boilers). The thick ash layer with high thermal resistance will seriously reduce the heat transfer efficiency of the heat exchanger heating surface, resulting in a serious decrease in heat transfer, a significant increase in exhaust gas temperature and a serious decrease in boiler thermal efficiency.

[0003] The utilization of biomass fuel gasification into fuel gas can solve the above problems to a great extent, especially when using updraft gasifier and directly burning the fuel gas for heating without cooling and purification. The reasons are:

[0004] (1) After the gasification process changes the fuel from solid to gas, its combustion mode also changes from gas-solid heterogeneous combustion to homogeneous combustion, which is not only easier to burn out, but also easier to achieve automatic control of combustion. At the same time, the excess air coefficient can be maintained below 1.2 through automatic control, thereby greatly reducing flue gas emissions, reducing exhaust losses, and improving thermal efficiency.

[0005] (2) Studies have shown that compared to the direct combustion of biomass, fluidized bed gasification and downdraft gasification can control 60-80% of alkali metals in the gasifier so that they do not enter the gas phase, while updraft gasification can control more than 99% of alkali metals in the furnace so that they do not enter the gas phase. Because the gas produced by updraft gasification must flow upward through the oxidation zone, reduction zone, distillation zone and drying zone before leaving the gasifier, the gas temperature drops significantly during this flow process. The alkali metals that evaporate into the gas phase due to the high temperature in the oxidation zone will condense into a solid state again and be blocked and filtered by the material layer and retained in the furnace. Therefore, compared to direct combustion of biomass or other types of gasification, the gas produced by the updraft gasification process suppresses the possibility of ash accumulation on the downstream heat exchange surface of the boiler to the greatest extent after combustion, thereby being able to always maintain a high heat exchange efficiency.

[0006] However, updraft gasification also has obvious shortcomings, which are specifically reflected in:

[0007] (1) The tar content in the gas is much higher than that in the fluidized bed and downdraft types. Once the tar condenses, it will adhere to the fan blades, valves, connecting pipe walls and other parts. On the one hand, it will corrode downstream equipment, and on the other hand, it will also cause serious blockage.

[0008] (2) Compared with the gas temperature of up to 800℃ in the gasification process of downdraft and fluidized bed, the temperature of gasified gas produced by updraft gasifier is usually not higher than 200℃, so its combustion reaction speed is much lower than the former two. When air gasification (rather than oxygen-enriched gasification) is used, the calorific value of gasified gas produced is also relatively low. In particular, the raw gas produced during the startup phase of the gasifier contains a large amount of water vapor from the fuel, which condenses into a large number of fine white mist droplets when cooled, and the combustion performance is very poor. The combination of the above many unfavorable factors leads to the gas produced by updraft gasifier often having problems such as ignition difficulty and poor combustion stability. Therefore, the startup process of updraft biomass gasifier often takes a long time, and it is normal for it to fail to ignite successfully for a long time. This not only leads to a large amount of fuel waste, but also seriously affects the normal use of gasifier users, thereby greatly limiting the use of updraft gasifier. This situation becomes more serious when the capacity of the gasifier is large.

[0009] In addition, various gasification utilizations also have difficulties to be overcome compared to direct combustion. For example, except for pressurized gasifiers, the gasified gas produced by other types of gasifiers needs to be pressurized before it can be used in the downstream burner. However, in order to avoid the problems of corrosion, blockage, etc. that may be caused by the rich tar in the gas, conventional boosting equipment such as booster fans and other equipment require that the gas must first undergo dust removal, tar removal and other purification steps, and these steps usually require the gas to be cooled. Obviously, the purification and cooling of the gas will inevitably lead to a sharp increase in system complexity and a significant decrease in energy utilization efficiency. In fact, if it is not in demanding occasions such as gas turbines and gas internal combustion engines, but in direct heating occasions, the purification and cooling process of the gas is actually not necessary. At this time, there are two technical paths to increase the gas pressure:

[0010] (1) The positive pressure required for gas combustion is maintained in the upper free space of the updraft gasifier by relying on the pressure provided by the gasification air blower. However, since the feeding process is also carried out at the top, a sealed feeding device must be used at this time. The sealed feeding process means that only intermittent feeding can be used, and this pressure-raising method is also prone to gas leakage.

[0011] (2) Use other non-traditional blower methods (such as induced or injected) to increase the pressure of the generated gas to avoid problems such as blade corrosion and blockage caused by tar condensation and adhesion. At the same time, maintain the free space area above the gasifier in a slightly negative pressure state, so that continuous feeding can be achieved without causing gas leakage. Because the negative pressure is relatively small at this time, the resistance of the fuel itself in the feed pipe is sufficient to prevent a large amount of air from leaking in. The gas is directly burned without cooling and purification, so even if a small amount of air leaks in due to the negative pressure in the furnace, it will be quickly burned not far downstream, so that there will be no accumulation and explosion and other safety problems.

[0012] However, existing fully premixed jet burners also have significant drawbacks. First, they are difficult to adjust the burner's load. As the load decreases, the jet gas velocity also decreases, making it difficult to effectively boost pressure and maintain a negative pressure above the gasifier. Furthermore, the mixing of gas and air deteriorates, leading to incomplete combustion and even flameout.

[0013] In summary, the problems that need to be solved in the combustion of updraft gasification gas can be summarized as follows: ignition is very difficult in the startup phase; it is difficult to increase the pressure of unpurified gas. If the induced pressure increase method is used, it is difficult for the burner to change the load, which can easily cause incomplete combustion and flameout.

[0014] In addition, the use of two-stage air injection can achieve air staging during the combustion process, thereby effectively reducing NOx emissions. Therefore, it is urgent to design a gas burner that uses two-stage air injection.

[0015] Through the above analysis, the problems and defects of the existing technology are as follows: in the existing updraft gasification gas combustion scheme, ignition is very difficult during the startup phase; and it is difficult to increase the pressure of unpurified gas. If an induced pressure increase method is used, it is difficult to change the load of the burner, which can easily cause problems such as incomplete combustion and flameout. Summary of the Invention

[0016] To overcome the problems existing in the related art, the embodiments disclosed in the present invention provide a control method for a heat-controlled temperature-controlled fully premixed multi-stage jet gas burner, and more particularly, relate to a method for quickly starting and stably burning a biomass gasifier and a control method for a heat-controlled temperature-controlled fully premixed multi-stage jet gas burner. The technical solution is as follows:

[0017] The present invention is implemented as follows: a control method for a heat-controlled temperature-controlled fully premixed double-injection gas burner, the method comprising the following steps:

[0018] S1, introducing the high-temperature flue gas generated by combustion into a regenerative high-temperature air generator to generate high-temperature air;

[0019] S2: After the high-temperature air ignition is successful, the gasifier is quickly ignited and started. The generated gas is quickly ignited and stably burned under the support of the high-temperature air. After that, the medium- and high-temperature heat pipes are started. The liquid in the evaporation end of the medium- and high-temperature heat pipes absorbs the heat of the flame and evaporates. After reaching the condensation end, it releases heat to heat the raw gas, raising the temperature to a temperature that can maintain stable combustion (usually above 300°C).

[0020] Using external natural gas as a heat source and utilizing regenerative heat exchange technology to generate high-temperature air above 500°C as ignition air for the gasifier enables rapid and even startup of the gasifier. Simultaneously, the high-temperature air, acting as both induced and combustion-supporting air, also enables rapid ignition and stable combustion of the low-calorific-value, low-quality gas generated during the initial startup phase of the gasifier. (Note that if the external natural gas heat source is removed during the initial startup phase without taking other stabilizing measures such as preheating the air or preheating the gasified gas, the combustion of the gasified gas will remain unstable and could extinguish again at any time.) The heat released by the combustion of the gasified gas is then released at the evaporation end 2 of the medium- and high-temperature heat pipe. The working fluid at the evaporation end absorbs the heat and evaporates into steam, which then flows to the condensation end 11 of the heat pipe, releasing heat to heat the low-temperature (100-200°C) gasified gas from the gasifier, raising its temperature to above 300°C. This allows for continued stable combustion even after the external natural gas heat source is removed. The high-temperature working medium vapor in the medium- and high-temperature heat pipe condenses into liquid after releasing heat at the condensation end 11. The liquid working medium returns to the evaporation end 2 under the action of the liquid absorption core in the pipe or its own gravity to start the next heat absorption and heat release cycle.

[0021] S3, based on the temperature and flow signals fed back from subsequent heat-using equipment including boilers and hot blast stoves, intelligently monitors and controls the actual operating load of the gasifier and gas burner.

[0022] The load status is determined and provided by the heat user based on various sensor signals. The present invention uses this data to perform related automatic control operations. How the heat user determines and provides this data is not covered by this patent.

[0023] In step S1 , a clean gaseous fuel with a high calorific value, such as natural gas, is burned as fuel.

[0024] In step S1, the air generator continuously generates high-temperature air with a temperature exceeding 500°C.

[0025] In step S1, high-temperature air flows to the bottom of the gasifier as gasification air, and realizes rapid and uniform ignition on the entire cross-section of the oxidation zone of the gasifier at the initial startup. The high-temperature air is also introduced into the central nozzle or annular seam of the induced burner through a pipeline as induced / combustion-supporting air to realize rapid and stable combustion of the gas.

[0026] In step S2, the startup process of the medium and high temperature heat pipe is as follows: the high temperature flame and flue gas generated by the combustion of the gasification gas release heat when flowing through the evaporation end of the medium and high temperature heat pipe, so that the working medium at the evaporation end absorbs heat and evaporates from liquid to vapor, and flows to the condensation end of the heat pipe; then it is cooled by the gasification gas with a lower temperature and releases heat, and the low-temperature gasification gas between 100-200°C is heated to above 300°C; the working medium in the medium and high temperature heat pipe releases heat at the condensation end and condenses from vapor to liquid, and the liquid working medium returns to the evaporation end under the action of the liquid absorption core in the pipe or its own gravity to start the next heat absorption and heat release cycle.

[0027] In step S2, after the condensing end of the medium and high temperature heat pipe heats the raw fuel gas to a temperature above the stable combustion temperature, both the induced air and the gasified air can be switched to the common air preheater.

[0028] In step S2, when the combustion is stable, the heat storage high-temperature air generating device heated by natural gas or other fuels stops running and the valves on the corresponding pipelines are closed at the same time; the valve and blower on the ordinary air preheater located at the tail end of the boiler or hot blast furnace are opened, and the 200°C hot air generated by the ordinary air preheater enters the center or annular nozzle of the ejector, completing the process of boosting the ejection gas pressure and assisting combustion.

[0029] In step S3, at least two stages of air injection are adopted, and each stage of air injection adopts central nozzle injection or annular gap injection, and the air flow rate in the central nozzle of the ejector is above 40m / s.

[0030] In step S3, the automatic control process during the normal operation phase includes:

[0031] Step 1: Periodically collect the temperature, pressure, and flow data of the terminal heat user and estimate the actual load rate required by the terminal heat user according to the calibration formula;

[0032] Step 2: Estimate the actual air volume currently required by the heat exchange equipment and heat generation equipment and the total amount of flue gas emissions based on the estimated load rate of the terminal heat user;

[0033] Step 3: Determine whether the estimated load rate is zero. If so, immediately stop the blower, vibration motor, and feeding motor in the heat generating equipment, immediately close all solenoid valves 1-3, delay the slag discharge motor and induced draft fan for a period of time before stopping them, and return to step 1.

[0034] Step 4: If the estimated load rate is not zero, periodically collect data from the pilot burner outlet temperature sensor and determine whether flameout has occurred. If not, return to the data collection step. If so, activate the electronic ignition and return to the data collection step.

[0035] Step 5: If the estimated load rate is not zero, then determine whether the current power of the heat generation and heat exchange equipment's blower and induced draft fan, feeding, vibration, and slag discharge equipment and load-related motors matches the estimated load rate. If not, adjust the power of the relevant motors proportionally according to the estimated load rate to match the estimated load rate.

[0036] Step 6. If the current power of the load-related motor matches the estimated load rate, fully open solenoid valve 1 and calculate the opening of solenoid valve 2 that makes the air flow rate in the first-stage ejector tube within the set range under the current estimated load rate; determine whether the required opening of solenoid valve 2 is greater than zero. If so, fully open solenoid valve 1, adjust solenoid valve 2 according to the calculated opening and return to step 1; if not, fully open solenoid valve 1, close solenoid valve 2, and return to step 1.

[0037] Combining all the above technical solutions, the advantages and positive effects of the present invention are as follows:

[0038] 1. The high-temperature air generated by the heat storage high-temperature air generator of the present invention is divided into two parts. One part is used as the ignition air of the gasifier, and the other part is introduced into the central nozzle of the induced burner through a pipeline, that is, it can be used as induced air. At this time, the induced air is also combustion-supporting air, and also plays the role of high-temperature combustion. The high-temperature condition can improve the problem of ignition difficulty in the initial stage of the gasifier startup; the heat storage method is used to heat water vapor to generate high-temperature water vapor for the gasification process, increase the hydrogen content in the fuel gas, and improve the combustion performance during the startup process.

[0039] 2. The present invention adopts a two-stage or even multi-stage ejection method, combined with the heating effect of the high-temperature heat pipe, which can at least ensure that the ejected air in the first-stage ejector still has a very high flow rate when the load changes, thereby still being able to efficiently play the role of pressurization, enhanced mixing and stable combustion.

[0040] 3. The present invention adopts intelligent monitoring and control methods to achieve combustion stability regulation during load changes; by controlling the valve to reduce the ejection air flow in one stage of the ejector, the air flow (i.e., flow velocity) in the other stage of the ejector increases accordingly, thereby continuing to ensure its ejection performance; the ejection has two main functions: the first function is to increase the pressure of the gas and form a negative pressure above the gasifier to avoid gas leakage; the second function is to ensure that the gas and air are fully mixed after the ejection to ensure complete combustion.

[0041] Compared with the traditional ignition system, the core innovations of the present invention are as follows:

[0042] 1. During the ignition and startup phase, the regenerative ignition and stable combustion system enables ultra-fast and uniform ignition of the updraft gasifier, solving the problems of difficult startup and long startup cycles in traditional updraft gasifiers.

[0043] 2. During normal operation, the high-temperature heat pipe stable combustion system realizes the continuous and stable combustion of the low-calorific value gas in the gasifier, solving the problem that traditional updraft gasifiers are prone to flameout during normal operation due to the low calorific value and low temperature of the gas. The above two points are combined to achieve rapid ignition and continuous and stable combustion of traditional updraft gasifiers.

[0044] 3. During normal operation, when loads fluctuate, the burner's multi-stage injection design and the medium- and high-temperature heat pipes' heating and combustion-stabilizing effect on the gas resolve the load regulation challenges of conventional injection-type gas burners. Furthermore, injection-type combustion inherently boosts gas pressure, eliminating the need for traditional gas booster fans and overcoming the challenges of prior tar removal and fly ash purification required during the boosting process. BRIEF DESCRIPTION OF THE DRAWINGS

[0045] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure;

[0046] Figure 1 This is a flow chart of a control method for a heat-controlled temperature-controlled, fully premixed, multi-stage jet gas burner provided by an embodiment of the present invention;

[0047] Figure 2 This is a structural diagram of a heat-controlled temperature-controlled, fully premixed, multi-stage jet gas burner provided by an embodiment of the present invention;

[0048] Figure 3 This is a schematic diagram of the automatic control principle during the normal operation phase provided by an embodiment of the present invention;

[0049] Figure 4 This is a graph showing the temperature variation of gasification gas in different ignition modes during the ignition startup phase of an updraft gasifier provided by an embodiment of the present invention;

[0050] In the figure: 1. Combustion diffusion zone of the second-stage ejector; 2. Evaporation end of medium and high temperature heat pipe; 3. Refractory insulation material; 4. Mixing zone of the second-stage ejector; 5. Ejection zone of the second-stage ejector; 6. Second-stage ejector; 7. Mixing zone of the first-stage ejector; 8. Ejection zone of the first-stage ejector; 9. First-stage ejector; 10. Air flow regulating valve; 11. Condensation end of medium and high temperature heat pipe; 12. Flange; 13. Regenerative high temperature air generator; 14. Ordinary air preheater; 15. Temperature sensor; 16. Electronic lighter. DETAILED DESCRIPTION

[0051] To make the above-mentioned objects, features, and advantages of the present invention more readily apparent, specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. The following description sets forth numerous specific details to facilitate a full understanding of the present invention. However, the present invention can be implemented in many other ways than those described herein, and those skilled in the art may make similar modifications without departing from the scope of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0052] The innovation of the present invention is:

[0053] (1) During the ignition startup phase, the regenerative ignition and stable combustion system enables ultra-fast and uniform ignition of the updraft gasifier, solving the problems of difficult startup and long startup cycles in traditional updraft gasifiers.

[0054] (2) During the normal operation phase, the high-temperature heat pipe stable combustion system realizes the continuous and stable combustion of the low calorific value gas in the gasifier, solving the problem that the traditional updraft gasifier is prone to flameout during the normal operation phase due to the low calorific value and low temperature of the gas. The above two points are combined to achieve the rapid ignition and continuous and stable combustion of the traditional updraft gasifier.

[0055] (3) During normal operation, when the load changes, the burner's multi-stage injection design and the medium- and high-temperature heat pipes' heating and stabilizing effect on the gas solve the problem of difficult load regulation in conventional injection-type gas burners. Moreover, the injection-type combustion itself can achieve gas pressure boosting without the need for a traditional gas booster fan, overcoming the problem of tar removal and fly ash purification required before the gas booster fan pressure boosting process.

[0056] (4) This design can achieve stable combustion of gas under the premise of using a high material layer thickness to efficiently retain alkali metals and alkaline earth metals, and completely solve the most difficult to overcome coking problem on the downstream heating surface during the biomass heat utilization process.

[0057] Principle Explanation: Conventional updraft gasifiers can achieve stable combustion by increasing the gas temperature by reducing the thickness of the fuel bed. However, a high fuel bed thickness is crucial for controlling the alkali and alkaline earth metals in the biomass. This is because the filtration and cooling effects of the fuel bed condense most of the alkali and alkaline earth metals that volatilize into the fuel gas into solids. These solids are then retained within the fuel bed through the filtration effect of the fuel bed, effectively eliminating the most difficult problem of coking on the downstream heating surfaces during biomass thermal utilization. Therefore, in conventional gasifiers, controlling the alkali and alkaline earth metal content in the fuel gas to suppress coking and increasing the fuel temperature to ensure combustion stability are mutually exclusive. In other words, increasing the fuel bed thickness compromises combustion stability, while reducing the bed thickness compromises efficient control of the alkali and alkaline earth metals in the fuel gas, making coking unavoidable. Achieving uniform and rapid ignition in the gasifier is essential for rapid startup and stable combustion in the gas burner. Uneven ignition in the gasifier can also lead to ignition difficulties in the gas burner. Therefore, the present invention does not simply rely on a specially designed gas burner to solve the problem of ignition startup and stable combustion, but relies on the organic combination of "rapid and uniform ignition of the gasifier part" and "stable combustion of the specially designed burner part" to solve the industry problem of rapid startup and stable combustion of updraft gasifiers.

[0058] Examples, such as Figure 1 As shown, the control method of the heat-controlled temperature-controlled full-premixed multi-stage jet gas burner provided in the embodiment of the present invention includes the following steps:

[0059] S1, introducing the high-temperature flue gas generated by combustion into a regenerative high-temperature air generator to generate high-temperature air;

[0060] S2: After the high-temperature air ignition is successful, the gasifier is quickly ignited and started. The generated gas is quickly ignited and stably burned under the support of the high-temperature air. Then, the medium- and high-temperature heat pipes are started. The liquid in the evaporation end of the medium- and high-temperature heat pipes absorbs heat and evaporates. After reaching the condensation end, it releases heat to heat the raw gas, raising the temperature to a temperature that can maintain stable combustion (usually above 300°C).

[0061] S3, based on the temperature and flow signals fed back from subsequent heat-using equipment including boilers and hot blast stoves, intelligently monitors and controls the actual operating load of the gasifier and gas burner.

[0062] Preferably, the control method of the heat-controlled temperature-controlled fully premixed multi-stage jet gas burner provided in the embodiment of the present invention specifically includes:

[0063] (1) How to use the startup process:

[0064] Using natural gas as fuel, high-temperature flue gas generated after combustion is introduced into the heat storage type high-temperature air generator 14 with honeycomb ceramics or ceramic balls as heat storage bodies, which can continuously generate high-temperature air with a temperature exceeding 500°C. Part of the high-temperature air flows to the bottom of the gasifier as gasification air, which can achieve very uniform ignition on the entire cross-section of the oxidation zone of the gasifier at the initial start-up. "Note: The ignition temperature of biomass solid fuel is about 400°C, and the higher the temperature, the better the effect. Conventional gasifier ignition includes hot flue gas ignition or diesel ignition on the grate. However, when the cross-section of the gasifier is large, the ignition speed of the above ignition methods is too slow, and it is even easy for local areas to fail to ignite (the reason why the hot flue gas ignition speed is slow or even fails to ignite in local areas is that the oxygen content in the flue gas is too low, and diesel ignition causes local areas to fail to ignite). The reason why the diesel ignition method itself does not ignite in the entire large cross section is that it is difficult to ignite evenly across the entire cross section. Once the gasifier cross section does not ignite, the gasification air will directly penetrate the material layer and enter the upper part of the gasifier. This may increase the risk of explosion. On the other hand, it may also cause the calorific value of the gas to decrease, resulting in excessive air in the burner and difficulty in ignition. However, using high-temperature hot air over 500°C or even higher to ignite the gasifier does not have this hidden danger at all, because the grate holes of the grate are relatively evenly distributed, and the high-temperature air can quickly burn the fuel near the hole when it passes through the grate hole at any position. Ignition, and the higher the air temperature, the better the effect, which is much better than the hot flue gas ignition method. In addition, it is difficult for conventional air preheating methods to produce such high-temperature air (usually only around 300°C at most), while the heat storage method can obtain preheated air with a temperature of more than 1000°C. In other words, the hot air that can be produced by conventional air heating methods cannot play a role in rapid and uniform ignition. In addition, one of the measures to improve the combustion performance of the induced burner is to mix a certain amount of high-temperature water vapor into the gasified air so that enough hydrogen is produced in the fuel gas, but conventional water vapor generators are also difficult to produce high-temperature water vapor. Water vapor with a temperature of 500°C or even above 1000°C can be generated, thereby preventing the air generated due to failure to ignite in some local areas from directly entering the upper space of the gasifier and mixing with the gas, which in turn causes a decrease in the calorific value of the gas, and leads to difficulty in ignition. This is also one of the important reasons for the difficulty in ignition in the initial stage of the gasifier startup; the other part of the high-temperature air can be used as induced air. Explanation: The high-temperature air generated by the heat storage high-temperature air generator is divided into two parts, one part is used as the ignition air of the gasifier, and the other part is introduced into the induced air tube through a pipeline, which can be used as induced air. At this time, the induced air is also combustion-supporting air. It also plays the role of high-temperature combustion. The high-temperature condition can further improve the problem of difficult ignition in the initial stage of the gasifier startup; the heat storage method is used to heat water vapor to generate high-temperature water vapor for the gasification process, increase the hydrogen content in the gas, and improve the combustion performance.

[0065] (2) How to use the combustion stabilization process:

[0066] After a period of successful high-temperature air ignition, the medium- and high-temperature heat pipes start operating. The heat pipe consists of two sections: the evaporator end 2 and the condenser end 11. To start operating, the evaporator end 2 must first be heated so that the working fluid inside can evaporate and enter the condenser end 11, releasing heat to heat the gas. Therefore, if the burner itself is not ignited, the heat pipe will not function. Normal operation begins. At this point, the liquid in the evaporator end 2 of the medium- and high-temperature heat pipe absorbs heat, evaporates, and then reaches the condenser end 11, releasing heat to heat the crude gas, raising its temperature to over 300°C. This means that stable combustion requires ignition. After ignition, the flame temperature of the burning gas exceeds 1300°C. Furthermore, the gas temperature is already above 100°C before heating. Simply recovering a small portion of the heat released by the evaporator end 2 of the heat pipe is sufficient to heat the gas to over 300°C. This effectively improves the combustion stability of the low-calorific-value crude gas. Both the induced air and the vaporized air can then be switched to the standard air preheater 14. Note: When combustion stabilizes, the natural gas-heated regenerative high-temperature air generator 13 ceases operation, and the valves on the corresponding pipelines are closed. The valves and blower on the conventional air preheater 14 (located at the rear of the boiler or hot blast furnace) are opened. Hot air at approximately 200°C generated by the conventional air preheater 14 then enters the ejector tube, completing the ejector gas pressure boosting and combustion-supporting process.

[0067] (3) Combustion stability adjustment during load changes

[0068] Adopt multi-stage air injection mode, each stage of the injection air can be injected by the central nozzle or the annular gap. When the load of the burner drops to a certain level, the injection air flow rate in the injection pipe will also decrease. This means that intelligent monitoring and control are the key elements of the automatic control. Figure 3As shown in Figure 1, the actual operating load of the gasifier and its gas burners is adjusted based on temperature and flow signals fed back by subsequent heat-consuming equipment, such as boilers and hot blast furnaces. If the air pressure drops below a certain level, the ejection capacity decreases, making it insufficient to raise the gas pressure and causing the pressure in the gasifier's upper chamber to drop to negative pressure. In this case, the ejection air flow rate in one stage of the ejector can be reduced by controlling the valve, which in turn increases the air flow rate (and therefore velocity) in the other stage, thereby maintaining ejection performance. Ejection has two main functions: first, to raise the gas pressure and create a negative pressure above the gasifier, preventing gas leakage; second, to ensure thorough mixing of the gas and air after ejection, ensuring complete combustion. Both of these functions require a high air velocity within the ejector's central nozzle, typically designed to exceed 40 m / s. When the heat load of heat-consuming equipment, such as boilers, decreases, the air velocity within the central nozzle inevitably decreases, resulting in a poor ejection effect and making it difficult to achieve both pressure increase and thorough mixing. If two or even multiple stages of ejection are used, at least the ejected air velocity in the first ejector can be maintained at a high level, thus maintaining the desired effect of pressurization and enhanced mixing. Preliminary experimental results indicate that when the ejected air velocity is 20 m / s, the content of incomplete combustion products, CO, in the flue gas can increase by more than 50%, or even several times, compared to an ejected air velocity of 40 m / s, and the gas pressurization effect is reduced by 50-80%. At this point, it is no longer possible to maintain a negative pressure above the gasifier. Of course, these test data will vary significantly depending on the specific structure and dimensions of the burner.

[0069] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described or recorded in detail in a certain embodiment, reference can be made to the relevant description of other embodiments.

[0070] The information interaction, execution process, etc. between the above-mentioned devices / units are based on the same concept as the embodiment of the method of the present invention. Their specific functions and technical effects can be found in the method embodiment part and will not be repeated here.

[0071] Those skilled in the art can clearly understand that, for the convenience and brevity of description, only the division of the above-mentioned functional units and modules is used as an example for illustration. In actual applications, the above-mentioned functions can be distributed and completed by different functional units and modules as needed, that is, the internal structure of the device can be divided into different functional units or modules to complete all or part of the functions described above. The functional units and modules in the embodiment can be integrated into one processing unit, or each unit can exist physically alone, or two or more units can be integrated into one unit. The above-mentioned integrated unit can be implemented in the form of hardware or in the form of software functional units. In addition, the specific names of the functional units and modules are only for the convenience of distinguishing each other, and are not used to limit the scope of protection of the present invention. The specific working process of the units and modules in the above-mentioned system can refer to the corresponding process in the aforementioned method embodiment.

[0072] According to an embodiment of the present application, the present invention also provides a computer device, which includes: at least one processor, a memory, and a computer program stored in the memory and executable on the at least one processor, wherein the processor implements the steps of any of the above-mentioned method embodiments when executing the computer program.

[0073] An embodiment of the present invention further provides a computer-readable storage medium, wherein the computer-readable storage medium stores a computer program. When the computer program is executed by a processor, the steps in the above-mentioned method embodiments can be implemented.

[0074] An embodiment of the present invention also provides an information data processing terminal, which is used to provide a user input interface to implement the steps in the above-mentioned method embodiments when executed on an electronic device. The information data processing terminal is not limited to mobile phones, computers, and switches.

[0075] An embodiment of the present invention further provides a server, which is used to provide a user input interface to implement the steps in the above method embodiments when executed on an electronic device.

[0076] An embodiment of the present invention further provides a computer program product. When the computer program product is run on an electronic device, the electronic device can implement the steps in the above-mentioned method embodiments when executing the computer program product.

[0077] If the integrated unit is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the present application implements all or part of the processes in the above-mentioned embodiment method by instructing the relevant hardware through a computer program. The computer program can be stored in a computer-readable storage medium. When the computer program is executed by a processor, it can implement the steps of each of the above-mentioned method embodiments. The computer program includes computer program code, which can be in source code form, object code form, executable file or some intermediate form. The computer-readable medium can at least include: any entity or device that can carry the computer program code to the camera / terminal device, recording medium, computer memory, read-only memory (ROM), random access memory (RAM), electrical carrier signal, telecommunication signal and software distribution medium. For example, a USB flash drive, a mobile hard disk, a magnetic disk or an optical disk.

[0078] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described or recorded in detail in a certain embodiment, reference can be made to the relevant description of other embodiments.

[0079] In order to further demonstrate the positive effects of the above embodiment, the present invention conducts the following experiments based on the above technical solution.

[0080] (1) Description of relevant equipment:

[0081] (1) End heat users: equipment that uses steam, hot water, or hot air;

[0082] (2) Heat exchange equipment: boiler, hot air furnace or other heat exchanger;

[0083] (3) Heat-generating equipment; gasifier and its induced burner;

[0084] (4) Injection burner; the ejector tube shall consist of at least two stages, namely the first stage ejector tube and the second stage ejector tube, and may adopt central ejection or annular slot ejection;

[0085] (5) Solenoid valve 1: The first-stage ejector tube ejects air inlet solenoid valve, with adjustable opening size;

[0086] (6) Solenoid valve 2: The solenoid valve for the air inlet of the second-stage ejector tube can be adjusted in opening size;

[0087] (7) Solenoid valve 3: Solenoid valve for the gasification air inlet of the gasifier, with adjustable opening size;

[0088] (8) On-off valve: A valve that is manually fully closed or fully opened, with no adjustment of the opening size. There are 4 valves in total.

[0089] (2) Ignition start-up phase

[0090] Here are the steps:

[0091] (1) Press the start switch or receive the start signal;

[0092] (2) Switch valves 1 and 3 are closed, and switch valves 2 and 4 are open. Solenoid valves 1, 2, and 3 are fully open;

[0093] (3) Start the induced draft fan of heat exchange equipment such as boilers and hot air furnaces;

[0094] (4) Start the ignition system induced draft fan;

[0095] (5) The blower of the heat-generating equipment is started;

[0096] (6) Ignition and combustion of external heat sources such as natural gas;

[0097] (7) The electronic igniter 16 at the outlet of the ignition burner continues to ignite, and determines whether the ignition process is successful based on the temperature data from the burner outlet temperature sensor 15. If it is not successful, the ignition continues.

[0098] (8) The blower of the heat generating equipment blows the cold air in the environment into the heat storage type high temperature air ignition and stable combustion system through the switch valve 2. The high temperature air above 500℃ generated by heat exchange is divided into the following three parts:

[0099] 1) The first part of high-temperature air enters the gasifier through the solenoid valve 3, achieving a uniform and rapid ignition process of the gasifier;

[0100] 2) The second part of high-temperature air enters the first-stage ejector pipe through the switch valve 4 and the solenoid valve 1 in sequence, and is ignited by the electronic igniter 16 to eject the gasified gas and stabilize its combustion;

[0101] 3) The third part of high-temperature air enters the second-stage ejector tube through the switch valve 4 and the electromagnetic valve 2 in sequence, and is ignited by the electronic igniter 16 to eject the gasified gas and stabilize its combustion.

[0102] (9) After a period of normal and stable combustion, the system determines that the ignition is successful. The medium and high temperature heat pipes are started by the high temperature flue gas in the induced burner and then gradually transition to the normal operation stage.

[0103] The detailed process for starting a medium- and high-temperature heat pipe is as follows: The high-temperature flame and flue gas generated by the combustion of the vaporized gas release heat to the evaporator end 2 of the medium- and high-temperature heat pipe. This causes the working medium at the evaporator end to absorb heat and evaporate from liquid to vapor. This vapor then flows to the condenser end 11 of the heat pipe, where it is then cooled by the cooler vaporized gas and releases heat, heating the low-temperature vaporized gas (between 100-200°C) to above 300°C. After releasing heat at the condenser end 11, the working medium in the medium- and high-temperature heat pipe condenses from vapor to liquid. The liquid working medium then returns to the evaporator end 2 through the pipe's wick or gravity, undergoing the next heat absorption and release cycle.

[0104] (10) When the external heat source such as natural gas goes out, the ignition system draft fan stops running after a delay of a period of time.

[0105] (11) All the switch valves 1, 3, and 4 are opened, and the switch valve 2 is closed.

[0106] (12) The blower of the heat generating equipment blows the cold air in the environment into the ordinary air preheater through the switch valve 1. The hot air of about 200℃ generated by the heat exchange of the ordinary air preheater passes through the switch valve 3 and finally goes to the following three parts:

[0107] 1) The first part of hot air enters the gasifier through the switch valve 4 and the solenoid valve 3 in sequence, providing the gasification air required for the normal operation of the gasifier;

[0108] 2) The second part of hot air enters the first-stage ejector pipe through the solenoid valve 1 to eject the gasifier gas and stabilize the combustion;

[0109] 3) The third part of hot air enters the second-stage ejector pipe through the solenoid valve 2 to eject the gas from the gasifier and stabilize the combustion;

[0110] At this point, the regenerative high-temperature air ignition and combustion stabilization system completed its startup phase and stopped operating, entering the normal operation phase.

[0111] Note: After the external heat source such as natural gas completes the ignition and stabilization tasks in the startup phase and is extinguished, the low calorific value of the gasified gas is sufficient to continue to maintain stable combustion with the help of the normal working medium and high temperature heat pipes heating the gasified gas and the ordinary air preheater heating the induced air.

[0112] (3) Normal operation stage

[0113] Automatic control during normal operation Figure 3 Based on various thermal measuring instruments such as thermocouples, pressure gauges, and flow meters, the temperature, pressure, and flow rate of the terminal heat users are periodically collected, and the load rate actually required by the terminal heat users is estimated based on a pre-calibrated load estimation formula.

[0114] Based on the estimated actual load rate currently required by the terminal heat user, the total air volume, gasification air volume, and total flue gas emissions currently actually required by the heat exchange equipment and heat generation equipment are estimated.

[0115] 1. When the estimated load rate is zero:

[0116] That is, the terminal heat user stops using heat, and the heat generating equipment and heat exchange equipment should also stop running. The specific steps are as follows:

[0117] (1) The supply of gasification and induced air in the heat generating equipment needs to be stopped immediately, that is, the blower in the heat generating equipment needs to be stopped immediately;

[0118] (2) Solenoid valves 1, 2, and 3 are all closed immediately to prevent any air from entering;

[0119] (3) The vibration motor and feeding motor in the heat generating equipment stop running immediately;

[0120] (4) The slag discharge motor in the heat generating equipment is delayed for a period of time before stopping;

[0121] (5) The induced draft fan in the heat exchange equipment is delayed for a period of time before stopping.

[0122] 2. When the estimated load rate is not zero:

[0123] (1) The blower and slag discharge motor in the heat-generating equipment proportionally adjust the output power or speed according to the estimated load rate through energy-saving methods such as frequency conversion;

[0124] (2) The vibration motor in the heat generating equipment adjusts the vibration frequency accordingly based on the estimated load rate;

[0125] (3) The opening of the solenoid valve 1 in the heat generating equipment is immediately adjusted to the maximum in order to minimize the air flow resistance loss;

[0126] (4) The opening of the solenoid valve 3 in the heat generating equipment is adjusted according to the estimated load rate;

[0127] (5) The opening degree of the solenoid valve 2 in the heat generating device is determined by the air flow rate in the first-stage ejector pipe, so as to at least ensure that the air flow rate in the first-stage ejector pipe is higher than the minimum value of the set reasonable range;

[0128] (6) If the load rate is too low, even if the electromagnetic valve 2 is completely closed, it is not enough to ensure that the air flow rate in the first-stage ejector tube is higher than the minimum value of the set reasonable range. In this case, no other adjustment action will be performed after the electromagnetic valve 2 is closed;

[0129] (7) The induced draft fan in the heat exchange equipment proportionally adjusts the output power according to the estimated load rate through energy-saving methods such as frequency conversion;

[0130] (8) Determine whether flameout has occurred based on the temperature data from the burner outlet temperature sensor 15, and based on this, determine whether the electronic ignition device 16 needs to be started again.

[0131] Notice:

[0132] (1) Because the inner diameters of the first and second stage ejector tubes are designed according to the rated heat load of the heat generating equipment, the heat generating equipment will not operate at overload, but only at reduced load. Therefore, when the electromagnetic valves at the inlet of the first and second stage ejector tubes are fully open, the air flow rate in the ejector tubes can only be lower than the lowest value of the set reasonable range, and will not be higher than the highest value of the set reasonable range. When the air flow rate in the ejector tube is lower than the lowest value of the set reasonable range, the ejection air's ability to pressurize the gasified gas, its ability to force mixing of the ejection air and the gasified gas, and its ability to pump negative pressure from the upper space of the gasifier will be significantly weakened;

[0133] (2) If the heat generating equipment is operated at a reduced load within a certain range, it is only necessary to fully open the inlet solenoid valve of the first-stage ejector pipe and adjust the opening of the inlet solenoid valve of the second-stage ejector pipe to control the ejection air flow rate in the first-stage ejector pipe and ensure that the ejection air flow rate therein is higher than the minimum value of the set reasonable range;

[0134] (3) If the load of the heat generating equipment is too low, even if the inlet solenoid valve of the first-stage ejector pipe is fully opened and the inlet solenoid valve of the second-stage ejector pipe is fully closed, so that all the ejected air is ejected through the first-stage ejector pipe, it is still not enough to ensure that the ejected air flow rate in the first-stage ejector pipe is within the set reasonable range. In this case, the control strategy is to simply open the inlet solenoid valve of the first-stage ejector pipe and close the inlet solenoid valve of the second-stage ejector pipe. In other words, it is no longer mandatory that the ejected air flow rate in the first-stage ejector pipe must be within the set reasonable range.

[0135] (4) When the boiler is in use, the start, stop, and load regulation of its water supply pump are all controlled by its own control system and have nothing to do with this control system.

[0136] (IV) Introduction to the experimental test platform: The inner diameter of the gasifier is 600mm and the height is 1500mm. Eight flame-viewing mirrors with a diameter of 35mm are evenly installed around the oxidation zone of the gasifier to observe the ignition of the gasifier. A set of K-type thermocouples are installed before and after the condensation section of the heat pipe at the outlet of the gasification gas above the gasifier and at the outlet of the induced burner, a total of 3 sets of thermocouples, which are used to detect the temperature of the gasification gas before and after being heated by the heat pipe and the temperature of the combustion flame. The experimental results are shown in Table 1 and Figure 4 shown.

[0137] Table 1 Experimental test comparison between regenerative high temperature air ignition and stable combustion system and traditional ignition system

[0138]

[0139] ① When the medium and high temperature heat pipe is not started, the temperature before and after the condensation section of the heat pipe is the same; ② This refers to the gasification gas temperature after the medium and high temperature heat pipe.

[0140] From Table 1 and Figure 4 The following results can be seen:

[0141] (1) When using the traditional hot flue gas and diesel fuel ignition start-up methods, the total startup time exceeds 30 minutes. However, when using the heat storage high-temperature air ignition and stable combustion system, the total ignition start-up time does not exceed 6 minutes. Moreover, after the gasification gas is generated, the burner ignition time is less than 1 minute, and the actual ignition time is only a few seconds, which is almost instantaneous.

[0142] (2) When using the traditional hot flue gas ignition and diesel ignition two gasification furnace startup methods, during multiple experimental tests, after the burner successfully ignited for the first time, the burner would flame out 8-15 times. However, after the heat storage high-temperature air ignition and stable combustion system was used, it was quickly ignited successfully within 6 minutes, and no flameout occurred again.

[0143] (3) When the traditional diesel ignition above the grate is used for startup, the gasification gas temperature is lower than 100℃ for a long time in the initial stage of the ignition startup; when the traditional hot flue gas ignition is used for startup, the gasification gas temperature hovers around 100℃ for a long time in the initial stage. In comparison, the heat storage high-temperature air ignition and stable combustion system is only lower than 100℃ within 3 minutes, and then quickly heats up to around 150℃ before the heat pipe condensation section within 6 minutes, and even rises to above 300℃ after the medium and high temperature heat pipe is started.

[0144] (4) During the ignition startup phase, the data of “number of visible open flames in the oxidation zone / total number of fire-viewing mirrors” showed that both the hot flue gas ignition and the regenerative high-temperature air ignition systems could achieve uniform ignition, while the diesel ignition method above the grate had two cases where no open flames were seen, indicating that the ignition in some local areas of the gasifier was unsuccessful.

[0145] (5) During the ignition startup phase, when the regenerative high-temperature air generation system is not shut down, the burner flame temperature is 500°C higher than that of the two traditional gasifier startup methods of hot flue gas ignition and diesel ignition. When the regenerative high-temperature air generation system is not shut down and the medium and high-temperature heat pipe is started, the burner flame temperature is still more than 100°C higher.

[0146] Note that when using diesel ignition above the grate, the first 10 minutes or so of the ignition startup phase primarily involve using diesel ignition materials or soaked materials directly burning above the grate to ignite the biomass pellet fuel. Once the biomass pellet fuel begins to burn vigorously, additional fuel is added to ignite the fire. Only then will the gasification phase truly begin, producing gasified gas. In comparison, when using other ignition startup methods, the fuel is first filled, then the gasification phase is directly entered. When using hot flue gas ignition, hot flue gas is first used to heat the bottom of the thick fuel layer above the grate to ignite it. After a period of heating, the high-temperature flue gas is replaced with room-temperature air as the gasification air. Furthermore, during the ignition startup phase, in both diesel ignition above the grate and hot flue gas ignition, due to the lack of other heat sources, only room-temperature air can be used as the combustion air.

[0147] Experiments have shown that when the temperature of the gas produced by the updraft gasifier is lower than 100°C, the gas cannot be ignited at all when using room temperature air for combustion. Moreover, the gas temperature remains below 100°C for a long time. Figure 2 When the gas temperature is higher than 100°C, the gas may be ignited intermittently when it is ignited with room temperature air, but the flame is unstable and can easily go out, especially when the air volume is adjusted. The flame may go out at any time. There are three reasons why the gas stays below 100°C for a long time and is difficult to ignite:

[0148] (1) At the initial stage of ignition startup, after the gasification process in the updraft gasifier officially begins, the gasification air and combustion air used in traditional utilization methods are often both room temperature air. During the long period of time when the fuel above the material layer begins to be heated, the evaporation process of the water in the fuel absorbs a large amount of heat. During the constant-rate drying stage of the fuel, the temperature of the material layer is difficult to exceed 100°C, and the temperature of the gasified gas leaving the material layer is also difficult to exceed 100°C. Of course, the large amount of water vapor generated in this stage also causes a significant decrease in the calorific value of the gas.

[0149] (2) The fuel in the local area above the grate of the gasifier often fails to be successfully ignited due to uneven ignition. At this time, the cold air passing through this area will directly penetrate the material layer and then mix with the gasification gas from other areas above the grate. This situation will not only reduce the temperature of the gasification gas, but also reduce its calorific value, making it more difficult to ignite. Referring to the direct observation data of "Number of visible open flames in the oxidation zone / Total number of fire-viewing mirrors" in Table 1, it can be seen that when the diesel ignition method above the grate is used, no open flames can be observed at 2 observation points out of a total of 8 direct observation points, indicating that the area has not been successfully ignited. Obviously, as the diameter of the gasifier increases, this situation will only become more serious.

[0150] In comparison, when using a regenerative high-temperature air ignition and combustion stabilization system, both the gasification and combustion-supporting air are high-temperature air exceeding 500°C. Figure 2 It can be seen that the temperature of the gas generated in the gasifier quickly exceeds 100°C within a few minutes, and under the combustion-supporting effect of the 500°C induced air, rapid ignition and start-up and intense and stable combustion are achieved.

[0151] The above description is only a preferred specific implementation method of the present invention, but the scope of protection of the present invention is not limited thereto. Any modifications, equivalent substitutions and improvements made by any technician familiar with this technical field within the technical scope disclosed by the present invention and within the spirit and principles of the present invention should be covered by the scope of protection of the present invention.

Claims

1. A control method for a heat-controlled temperature-controlled fully premixed multi-stage jet gas burner, characterized in that: The method comprises the following steps: S1, introducing the high-temperature flue gas generated by combustion into a regenerative high-temperature air generator to generate high-temperature air; In S2, high-temperature air is used to achieve rapid start-up and stable combustion of the gasifier in the initial ignition startup phase. The liquid in the evaporation end of the medium- and high-temperature heat pipe absorbs heat and evaporates, then reaches the condensation end and releases heat to heat the crude gas, raising the temperature to a level above that which can maintain stable combustion. S3, based on the temperature and flow signals fed back from subsequent heat-consuming equipment including boilers and hot blast stoves, intelligently monitors and controls the actual operating load of the gasifier and gas burner; In step S1, high-temperature air flows to the bottom of the gasifier as gasification air, achieving rapid and uniform ignition across the entire oxidation zone of the gasifier during the initial startup. The high-temperature air is also introduced through a pipeline into the central nozzle or annular seam of the induced burner as induced / combustion-supporting air to achieve rapid and stable combustion of the gas. In step S2, the startup process of the medium and high temperature heat pipe is as follows: The high-temperature flame and flue gas generated by the combustion of the gasified gas release heat when flowing through the evaporation end of the medium- and high-temperature heat pipe, causing the working medium at the evaporation end to absorb heat and evaporate from liquid to vapor, flowing to the condensation end of the heat pipe. It is then cooled by the lower-temperature gasified gas and releases heat, heating the low-temperature gasified gas between 100 and 200°C to above 300°C. The working medium in the medium- and high-temperature heat pipe releases heat at the condensation end and condenses from vapor to liquid. The liquid working medium returns to the evaporation end through the liquid wick in the pipe or under the action of its own gravity to start the next heat absorption and heat release cycle. In step S2, when combustion stabilizes, the regenerative high-temperature air generator heated by natural gas stops operating and the valves on the corresponding pipelines are closed. The valve and blower on the common air preheater located at the rear of the boiler or hot blast furnace are opened, and the 200°C hot air generated by the common air preheater enters the center or annular nozzle of the ejector, completing the process of injector gas pressure boosting and combustion support. In step S3, at least two stages of air injection are adopted, and each stage of air injection adopts central nozzle injection or annular gap injection.

2. The control method of the heat-controlled temperature-controlled full premixed multi-stage jet gas burner according to claim 1 is characterized in that: In step S1 , clean gaseous energy including natural gas is burned as fuel.

3. The control method of the heat-controlled temperature-controlled full premixed multi-stage jet gas burner according to claim 1 is characterized in that: In step S1, the air generator continuously generates high-temperature air with a temperature exceeding 500°C.

4. The control method of the heat-controlled temperature-controlled full premixed multi-stage jet gas burner according to claim 1 is characterized in that: In step S2, after the condensing end of the medium and high temperature heat pipe heats the raw fuel gas to a temperature above the stable combustion temperature, both the induced air and the gasified air can be switched to the common air preheater.

5. The control method of the heat-controlled temperature-controlled full premixed multi-stage jet gas burner according to claim 1 is characterized in that: The air flow rate in the central nozzle of the ejector is above 40m / s.

6. The control method of the heat-controlled temperature-controlled full premixed multi-stage jet gas burner according to claim 1 is characterized in that: In step S3, the automatic control process during the normal operation phase includes: Step 1: Periodically collect the temperature, pressure, and flow data of the terminal heat user and estimate the actual load rate required by the terminal heat user according to the calibration formula; Step 2: Estimate the actual air volume currently required by the heat exchange equipment and heat generation equipment and the total amount of flue gas emissions based on the estimated load rate of the terminal heat user; Step 3: Determine whether the estimated load rate is zero. If so, immediately stop the blower, vibration motor, and feeding motor in the heat generating equipment, immediately close all solenoid valves 1-3, delay the slag discharge motor and induced draft fan for a period of time before stopping them, and return to step 1. Step 4: If the estimated load rate is not zero, periodically collect data from the pilot burner outlet temperature sensor and determine whether flameout has occurred. If not, return to the data collection step. If so, activate the electronic ignition and return to the data collection step. Step 5: If the estimated load rate is not zero, then determine whether the current power of the heat generation and heat exchange equipment's blower and induced draft fan, feeding, vibration, and slag discharge equipment and load-related motors matches the estimated load rate. If not, adjust the power of the relevant motors proportionally according to the estimated load rate to match the estimated load rate. Step 6. If the current power of the load-related motor matches the estimated load rate, fully open solenoid valve 1 and calculate the opening of solenoid valve 2 that makes the air flow rate in the first-stage ejector tube within the set range under the current estimated load rate; determine whether the required opening of solenoid valve 2 is greater than zero. If so, fully open solenoid valve 1, adjust solenoid valve 2 according to the calculated opening and return to step 1; if not, fully open solenoid valve 1, close solenoid valve 2, and return to step 1.

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