CN209840096U - Low-concentration gas pulsation burner with flame stabilizing disc structure - Google Patents
Low-concentration gas pulsation burner with flame stabilizing disc structure Download PDFInfo
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- CN209840096U CN209840096U CN201920356003.7U CN201920356003U CN209840096U CN 209840096 U CN209840096 U CN 209840096U CN 201920356003 U CN201920356003 U CN 201920356003U CN 209840096 U CN209840096 U CN 209840096U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery
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Abstract
The utility model discloses a low-concentration gas pulsation burner with a flame stabilizing disc structure, which comprises a columnar gas shunting shell, wherein one side of the gas shunting shell is provided with five flame stabilizers which are distributed in an equidistant array along the axis of the gas shunting shell; the utility model adds the flame stabilizer structure, generates double reflux areas in the combustion chamber, enhances the flame stability during firing, widens the upper limit of the gas flow speed entering the combustor, can obtain a better speed field under the optimized design scheme, and enhances the flow uniformity and the combustion stability; meanwhile, a thickening structure is added in the scheme, and the problem that the concentration is too low to be continuously combusted is solved.
Description
Technical Field
The utility model belongs to the gas combustion field.
Background
Although coal resources in China are very rich, a considerable part of coal seams are in high-gas or gas outburst coal seams which are about 48 percent, the reserves of the gas resources in China are also very rich directly, most of gas extraction is more mixed with air and has a single form, the extraction quantity is suddenly high and suddenly low, so that most of low-concentration gas with the concentration of about 8 percent is extracted during the extraction process, the gas is 70 percent or more of the total extraction quantity, the concentration of the part of gas is low, the stable combustion of the part of gas is difficult to maintain by using a conventional combustion mode, the concentration is also in the concentration of gas explosion, if the gas cannot be reasonably utilized, the gas can only be exhausted into the atmosphere, otherwise, potential safety hazards are caused, and therefore, the large amount of gas with the concentration is generally discharged to the air after being extracted, which is reported in 2006, the reserves of 36 billion cubic meters of gas in China, the content of the natural gas is basically the storage amount of natural gas on land, and according to incomplete statistics, about 150 billion cubic meters of gas is required to be discharged in each year of coal mining in China, so that not only is serious potential energy waste caused, but also the environment is polluted.
It is well known that methane, the major component of gas, is a serious greenhouse gas, and its greenhouse effect and CO are2Compared with 24.6 times of the total carbon dioxide, the carbon dioxide has the capability of destroying the atmospheric ozone layer and is CO27 times of the total weight of the powder. Therefore, a great amount of low-concentration gas in mines is discharged to the air due to unavailable utilization every year, so that not only is the limited non-renewable fossil energy seriously wasted, but also the greenhouse effect and the environmental pollution are aggravated. The combustion heat value of the gas is 35000-39000 kJ/m3Meanwhile, the natural gas becomes greenhouse gas and plays a role of high-quality energy, and the natural gas is comparable to the conventional natural gas and can be used as a raw material in an energy chemical process.
However, the low-concentration gas has extremely low combustible components as the name implies, the heat generated in the combustion process is far less than the heat dissipation amount in the environment, the continuous combustion is very difficult, and therefore, the conventional combustion device cannot be adopted for combustion, and therefore, a special combustion mode and a corresponding burner are required to be adopted for the low-concentration gas with the concentration.
The pulsation combustion is a special combustion mode, and neither knocking nor normal combustion is performed but is interposed therebetween. The periodic pulse combustion can be generated by giving a certain condition excitation to ensure that the generated acoustic pulse and the thermal pulse generated in the combustion process achieve certain acoustic thermal coupling. The state parameters of pressure, temperature, heat release rate and the like which characterize the combustion characteristics in the combustion process are periodically changed along with time, so that the device has the advantages of high combustion efficiency, larger heat transfer coefficient, smaller pollution discharge and self-absorption pressurization, and the combustion of low-concentration gas can be effectively processed by utilizing the pulse combustion technology;
since the concentration of the gas source is not a constant value, the low-concentration gas that is forced into the combustion chamber from the main pipe may have a problem that the methane concentration is too low, and even in the case of pulsating gas supply to the combustion chamber, there is a problem that smooth ignition is not possible in the combustion chamber, or continuity of combustion is not maintained for a plurality of pulsation cycles.
Disclosure of Invention
The purpose of the invention is as follows: in order to overcome the deficiencies in the prior art, the utility model provides a lower concentration gas pulse combustor of steady flame dish structure in area that combustion stability is better.
The technical scheme is as follows: in order to achieve the purpose, the low-concentration gas pulsation burner with the flame stabilizing disc structure comprises a columnar gas distribution shell, wherein five flame stabilizers are arranged on one side of the gas distribution shell and are distributed in an equidistant array along the axis of the gas distribution shell;
each flame stabilizer is in a conical shell structure, the axis of the conical shell of each flame stabilizer is perpendicular to the axis of the gas diversion shell, a flame stabilizing conical cavity is arranged inside the conical shell of each flame stabilizer, and the thick end of the flame stabilizing conical cavity is communicated with the gas diversion cavity inside the gas diversion shell through at least seven uniformly distributed gas guide holes; the thin end of the flame stabilizing conical cavity is provided with a gas jet hole coaxially;
the gas burner is of a cylindrical structure, the inner cavity of the gas burner is a cylindrical combustion chamber, and a gas outlet of each flame stabilizer is coaxially communicated with a gas inlet end of the combustion chamber of the corresponding gas burner; one end of each combustion chamber, which is far away from the flame stabilizer, is connected with an exhaust straight pipe;
the end, far away from the flame stabilizer, of the gas diversion shell further comprises a low-concentration gas pulsation supply pipe, and the gas outlet end of the low-concentration gas pulsation supply pipe is communicated with a gas diversion cavity in the gas diversion shell.
Furthermore, an annular methane enrichment box body is integrally arranged on the outer side of the gas burner, and an annular pure methane pressure storage cavity is formed in the annular methane enrichment box body; an annular methane enrichment cavity layer is coaxially arranged between the pure methane pressure accumulation cavity and the combustion chamber; the pure methane pressure accumulation cavity is separated from the methane enrichment cavity layer by a first annular wall, and the methane enrichment cavity layer is separated from the combustion chamber by a second annular wall; a plurality of methane enrichment holes are uniformly distributed on two sides of the second annular wall along the axis in a circumferential array, and the methane enrichment holes are used for communicating the methane enrichment cavity layer with the combustion chamber; a plurality of first gas guide channels are distributed on the first ring wall in a circumferential array, the inner end of each first gas guide channel is communicated with the methane enrichment cavity layer, a rotary gas distribution ring body is further arranged in the pure methane pressure accumulation cavity and rotatably sleeved on the outer side of the first ring wall, an annular flange is integrally and coaxially arranged in the middle of an inner ring of the rotary gas distribution ring body, the outer end of each first gas guide channel is blocked by the inner wall of the annular flange, a plurality of second gas guide channels are distributed on the annular flange in a circumferential array, the outer end of each second gas guide channel is communicated with the pure methane pressure accumulation cavity, and the inner end of each second gas guide channel can synchronously rotate along with the annular flange to respectively align and communicate with the outer ends of the plurality of first gas guide channels; the pure methane pressurizing and supplying pipe is arranged, and the gas outlet end of the pure methane pressurizing and supplying pipe is communicated with the pure methane pressure storage cavity; the outer lane of rotatory distribution ring body is provided with the round tooth body, pure methane pressure storage chamber still fixed mounting has the motor, the synchronous connection has output gear on the output shaft of motor, output gear with round tooth body meshing connection on the rotatory distribution ring body.
Has the advantages that: the utility model adds the flame stabilizer structure, generates double reflux areas in the combustion chamber, enhances the flame stability during firing, widens the upper limit of the gas flow speed entering the combustor, can obtain a better speed field under the optimized design scheme, and enhances the flow uniformity and the combustion stability; meanwhile, a thickening structure is added in the scheme, and the problem that the concentration is too low to be continuously combusted is solved.
Drawings
FIG. 1 is a burner assembly with a flame holder;
FIG. 2 is a schematic view of a burner cut-away structure when a methane enrichment tank is not installed;
FIG. 3 is a CFD analysis velocity cloud chart of a burner assembly with a flame holder;
FIG. 4 is a CFD analysis local vector velocity cloud for a gas burner;
FIG. 5 is a schematic structural view of a burner with a methane enrichment tank;
FIG. 6 is a first perspective cross-sectional view of FIG. 4;
FIG. 7 is a second perspective cross-sectional view of FIG. 4;
FIG. 8 is a third perspective cross-sectional view of FIG. 4;
FIG. 9 is a schematic structural view of a rotary distribution ring body;
FIG. 10 is a graph of tailpipe temperature versus flow;
FIG. 11 is a graph of the temperature profiles of the tail pipes in the reference group at different flow rates;
FIG. 12 is a graph of the line of the tail pipe temperature for the optimized set of different flow rates.
Detailed Description
The present invention will be further described with reference to the accompanying drawings.
The low-concentration gas pulsation burner with the flame stabilizing disc structure as shown in fig. 1 to 9 comprises a cylindrical gas distribution shell 74, wherein five flame stabilizers 89 are arranged on one side of the gas distribution shell 74, and the five flame stabilizers 89 are distributed in an equidistant array along the axis of the gas distribution shell 74;
each flame stabilizer 89 is in a conical shell structure, the axis of the conical shell of each flame stabilizer 89 is perpendicular to the axis of the gas distribution shell 74, a flame stabilizing conical cavity 72 is arranged inside the conical shell of each flame stabilizer 89, and the thick end of the flame stabilizing conical cavity 72 is communicated with the gas distribution cavity 71 inside the gas distribution shell 74 through at least seven uniformly distributed gas guide holes 75; the thin end of the flame stabilizing conical cavity 72 is provided with a gas jet port 73 coaxially;
the gas burner comprises five gas burners 10, wherein the five gas burners 10 correspond to the five flame holders 89 coaxially, the gas burners 10 are of a cylindrical structure, the inner cavity of each gas burner 10 is a cylindrical combustion chamber 12, and the gas outlet 73 of each flame holder 89 is communicated with the gas inlet end of the corresponding combustion chamber 12 of the gas burner 10 coaxially; one end of each combustion chamber 12, which is far away from the flame stabilizer 89, is connected with an exhaust straight pipe 20;
the gas distributing shell 74 further comprises a low-concentration gas pulsation supply pipe 81 at one end far away from the flame holder 89, and the gas outlet end of the low-concentration gas pulsation supply pipe 81 is communicated with the gas distributing cavity 71 inside the gas distributing shell 74.
An annular methane enrichment tank body 18 is integrally arranged on the outer side of the gas burner 10, and an annular pure methane pressure accumulation cavity 2 is formed in the annular methane enrichment tank body 18; an annular methane enrichment cavity layer 7 is coaxially arranged between the pure methane pressure accumulation cavity 2 and the combustion chamber 12; the pure methane pressure accumulation cavity 2 and the methane enrichment cavity layer 7 are separated by a first annular wall 1, and the methane enrichment cavity layer 7 and the combustion chamber 12 are separated by a second annular wall 9; a plurality of methane enrichment holes 11 are uniformly distributed on two sides of the second annular wall 9 in a circumferential array along the axis, and the methane enrichment cavity layer 7 is communicated with the combustion chamber 12 through each methane enrichment hole 11; a plurality of first air guide channels 14 are distributed on the first annular wall 1 in a circumferential array, the inner ends of the first air guide channels 14 are communicated with the methane enrichment cavity layer 7, a rotary air distribution ring body 6 is further arranged in the pure methane pressure accumulation cavity 2, the rotary air distribution ring body 6 is rotatably sleeved on the outer side of the first annular wall 1, an annular flange 21 is integrally and coaxially arranged in the middle of an inner ring of the rotary air distribution ring body 6, the outer end of each first air guide channel 14 is plugged by the inner wall of the annular flange 21, a plurality of second air guide channels 17 are distributed on the annular flange 21 in a circumferential array, the outer ends of the second air guide channels 17 are communicated with the pure methane pressure accumulation cavity 2, and the inner ends of the second air guide channels 17 can synchronously rotate along with the annular flange 21 to be respectively aligned and communicated with the outer ends of the first air guide channels 14; the device also comprises a pure methane pressurizing and supplying pipe 8, wherein the gas outlet end of the pure methane pressurizing and supplying pipe 8 is communicated with the pure methane pressure storage cavity 2; each first gas guide channel 14 is internally provided with a one-way valve 13 for preventing gas from flowing backwards, and the one-way valve 13 can prevent the gas in the methane enrichment cavity layer 7 from flowing backwards to the pure methane pressure accumulation cavity 2 through the first gas guide channel 14; two bearings 16 are also symmetrically and rotatably arranged on two sides of the annular flange 21 of the inner ring of the rotary air distribution ring body 6; the outer lane of rotatory distribution ring body 6 is provided with round tooth body 25, pure methane pressure storage chamber 2 still fixed mounting has motor 5, synchronous connection has output gear 3 on the output shaft 4 of motor 5, output gear 3 with round tooth body 25 meshing connection on the rotatory distribution ring body 6, motor 5 passes through output gear 3 and drives rotatory distribution ring body 6 is rotatory along the axis.
Pulse combustion experiment of low-concentration gas
Principle of experiment
According to the flame holder structure provided by the embodiment, the uniformity of the actual flow rate is researched under the condition that the methane concentration of the gas is normal and an additional enrichment structure is not considered. When the flow rate of each burner is stable and the flow field is uniformly distributed, the temperature of the straight exhaust pipe 20 of each burner 10 can be stable after stable combustion. Considering that the temperature of the straight exhaust pipe 20 is too high during operation, the flow of the straight exhaust pipe 20 is not suitable for being directly measured by installing a flowmeter, but the temperature of the straight exhaust pipe 20 can be easily measured by a thermocouple, so that the flow condition is indirectly reflected by measuring the temperature of the straight exhaust pipe 20 instead of a direct measurement method, namely the correctness of the optimization design is checked through the temperature difference of the straight exhaust pipe 20 of each combustor.
In this experiment, two sets of burners were simultaneously started, one set was the case of the non-optimized, i.e., reference, set of burners (no flame stabilizer 89 added), and the other set was the optimized set of burners. The temperature of each straight exhaust pipe 20 is measured under 4 groups of different flow rates, and data are recorded after the experiment is finished;
the following table shows the inlet gas flow rate of 0.021m of the low-concentration gas pulsation feeding pipe 813Temperature condition of straight exhaust pipe of/s reference group and optimization group
The following table shows the temperature conditions of the straight exhaust pipes of the reference group and the optimized group of the low-concentration gas pulsation supply pipe 81 with the inlet flow of 0.024m3/s
The lower table shows the inlet flow of 0.031m through the concentration gas pulsation feeding pipe 813Temperature condition of straight exhaust pipe of/s reference group and optimization group
The following table shows the temperature conditions of the straight exhaust pipes of the reference group and the optimized group of the low-concentration gas pulsation supply pipe 81 with the inlet flow of 0.024m3/s
The lower table shows the inlet flow of 0.031m through the concentration gas pulsation feeding pipe 813Temperature condition of straight exhaust pipe of/s reference group and optimization group
The following table shows the inlet flow rate of 0.039m of the low-concentration gas pulsation feeding pipe 813Temperature condition of straight exhaust pipe of/s reference group and optimization group
The graph of the tail pipe temperature changing with the flow rate is drawn by taking the tail pipe number one of the optimization group as an example and is shown in fig. 10, and the average temperature line graphs of five tail pipes of the reference group and the optimization group under the condition of four flow rates are drawn and are shown in fig. 11 and 12. From the graph 10, we can draw two conclusions, and firstly, it can be seen that the tail pipe temperature is gradually changed after being sharply increased in a certain flow interval along with the increase of the air inlet flow, because the heat load is correspondingly increased when the flow is increased, and simultaneously, the pulse amplitude and the pulse strength in the combustor are strengthened, and the strengthening can inhibit the formation of a laminar boundary layer so as to generate a plurality of large and small vortexes on the wall surface of the laminar boundary layer, so that the transfer of momentum, heat and mass is enhanced. However, the heat exchange effect cannot be enhanced without limit due to the increase of the flow, the flow rate at the inlet of the heat exchanger is increased inevitably due to the increase of the flow, when the flow rate reaches the fire-removing limit speed, the fire-removing phenomenon occurs, and once the fire-removing combustion is carried out, the fire-removing combustion cannot be continued. This is directly reflected in a sharp drop in tailpipe temperature. On the basis of obtaining the relation between the flow and the tail pipe temperature, we can indirectly obtain a second conclusion that: the flow rate of each tail pipe of a group of combustors is different, and the temperature of the tail pipes is different; as can be seen from the average temperature line graphs of the tail pipes of the reference group and the optimized group shown in fig. 11 and 12, the temperature can be basically uniform, and the error range of each pipe is within 20 ℃, which is acceptable in engineering. Indirectly, the flow of each straight exhaust pipe 20 is basically uniform, and the flow field distribution is approximate. The analysis error is caused by the following reasons: as can be seen from the results of the outlet flow rate simulated in the third chapter, the size of the opening cannot guarantee that the flow rates of the tail pipes are absolutely equal, and the deviation in the flow rates still exists. Secondly, in the actual engineering transformation process, due to lack of working fineness, the deviation of the opening size is increased, and further the deviation of the flow is caused;
the structural rationality and the technical progress of the combustor are verified by adopting a CFD numerical simulation method:
numerical simulations under this grid were done using ANSYS fluent16.0, which was first examined to ensure that no negative values for grid area and volume existed, regardless of gravitational effects.
In the model, the flow process is set to be steady-state flow based on pressure, and since the flow condition of low-concentration gas is mainly concerned, the flow field distribution condition of the flow process in the combustor pipeline is calculated by adopting a multi-component model numerical value on the assumption that the flow is a mixed gas of CH4 and air.
Setting a model: an energy equation, a standard turbulence equation and a component transport equation;
material setting: the fluid is methane-air, and the solid wall surface is default aluminum;
setting boundary conditions: entry boundary conditions: a velocity inlet for setting the feeding velocity of the low-concentration gas pulsation feeding pipe 81 to 1.5 m/s; exit boundary conditions: the outlet of the exhaust straight pipe 20 is an atmospheric pressure outlet; turbulence index: turbulence intensity + hydraulic diameter;
temperature: 300K;
the components are as follows: 4.1% CH4, 19.64% O2, 2.82% CO2, 73.44% N2;
the solving method comprises the following steps: SIMPLE single precision, the gradient is based on a grid and adopts a least square method, the pressure adopts second-order windward, the momentum adopts first-order windward, the turbulent kinetic energy adopts first-order windward, and the turbulent dissipation rate adopts first-order windward;
residual monitoring: all parameters convergence accuracy is set to 0.001;
iteration step size: 1000, parts by weight;
initializing, wherein in the operation process, all indexes are converged to set precision in the step 324;
the burner combination overall velocity cloud picture obtained after the simulation is as the attached figure 3, the velocity cloud picture shows that a better velocity field can be obtained by adding the structural mode of the flame stabilizer 89, the attached figure 4 shows that the partial vector velocity cloud picture of the CFD analysis of the gas burner can show that a double-backflow area is generated in the combustion chamber 12, the partial velocity vector picture of the burner can obviously show that two nearly symmetrical backflow areas exist in the flow field, the generation of the symmetrical double-backflow area enhances the gas combustion, and the following processes and phenomena are newly added in the process: high-temperature flue gas is continuously generated along with the combustion, and is sucked to the root of the flame along with the backflow phenomenon, so that heat is transferred with newly-fed fuel gas. The heat source is additionally arranged at the root of the burner, which has important significance for the continuous combustion of the gas; particularly in the initial ignition period, the effect of the backflow area is more obvious; the high-temperature flue gas flows back to the root of the combustor from the beginning, the flow velocity of the high-temperature flue gas is increased, the returned flue gas is mixed with a medium in a main flow during the period, high-efficiency momentum transmission is carried out, and new and old fuel gases in a backflow area are promoted to be mutually exchanged and mixed, so that the temperature distribution in the combustion chamber is further more uniform; part of unburnt fuel gas which flows back to the root of the combustion chamber along with high-temperature flue gas can be reburnt together with new fuel gas at the root, and the device plays an important role in complete combustion of the gas. In summary, the combined effect of the recirculation zone is to provide a stable and complete combustion of the gas in the burner, promoting a uniform temperature and high thermal processing quality in the combustion chamber; the flame stability during ignition at each pulsation cycle is enhanced, and the upper limit of the gas flow rate into the burner 10 is widened;
the method, the process and the technical progress of enriching the methane in the combustion chamber are as follows:
the gas source comprises CH4、O2、N2、CO2Mixed gas of (2), wherein O2In a concentration of CH4The combustion reaction of (1):
CH in gas source4At concentrations above 4%, the combustion chamber 22 need not be CH fed4Thickening; at the moment, the pure methane pressurizing and supplying pipe 8 does not supply pure methane into the pure methane pressure storage cavity 2; at the moment, the one-way valve 13 can prevent the gas in the methane enrichment cavity layer 7 from flowing back to the pure methane pressure storage cavity 2 through the plurality of first gas guide channels 14; then working on a gas pumpContinuously supplying gas into the gas flow-dividing casing 74 in a form of a pulsation cycle by passing the gas through a low-concentration gas pulsation supply pipe 81; further, the gas in the gas flow-dividing chamber 71 is injected into the combustion chamber 12 in a pulsating cycle through the gas outlets 73 of the flame holders 89 by the continuous pulsating gas pressure in the gas flow-dividing chamber 71; after the gas in the combustion chamber 12 is ignited by the ignition device, continuous pulsating flame is formed in the combustion chamber 12, high-temperature tail gas generated by combustion in the combustion chamber 12 continuously passes through the exhaust straight pipes 20 and is ejected in the form of tail flame, and the tail flame ejected by each exhaust straight pipe 20 heats heat-using equipment; thereby realizing the utilization of the gas;
when CH is contained in the gas source4When the concentration is less than 4%, the gas is continuously supplied into the gas flow-dividing casing 74 in a form of a pulsation cycle through the low-concentration gas pulsation supply pipe 81 by the gas pump; further, the gas in the gas flow-dividing chamber 71 is injected into the combustion chamber 12 in a pulsating cycle through the gas outlets 73 of the flame holders 89 by the continuous pulsating gas pressure in the gas flow-dividing chamber 71; CH in the gas ejected through the gas ejection holes 73 of the flame holders 894Concentration less than 4%, failure to smoothly ignite in the combustion chamber 12 or failure to maintain continuity of combustion over multiple pulse cycles, requires CH for the combustion chamber 124Thickening; at this time, the pure methane pressurizing and supplying pipe 8 presses the pure methane into the pure methane pressure storage cavity 2, and the pure methane pressurizing and supplying pipe 8 continuously maintains the air pressure in the pure methane pressure storage cavity 2, and the air pressure in the pure methane pressure accumulation cavity 2 is always ensured to be larger than the air pressure in the combustion chamber 12, at the moment, the motor 5 is started, the motor 5 drives the rotary air distribution ring body 6 to rotate along the axis through the output gear 3, the annular flange 21 rotates synchronously with the rotary air distribution ring body 6, the inner ends of the second air guide channels 17 periodically rotate to the outer ends of the first air guide channels 14 in alignment and communication through the periodic rotation of the annular flange 21, so that the pure methane pressure storage cavity 2 and the methane enrichment cavity layer 7 are communicated with each other periodically, further, methane in the pure methane pressure accumulation cavity 2 periodically enriches the cavity layer 7 through the first gas guide channels 14.Pressure incidence pure CH4Further, pure CH is formed in the methane enriched cavity layer 74Pulsating the gas pressure and thereby methane enriching the CH in the cavity layer 74The pulsating gas pulsates and periodically presses pure CH into the combustion chamber 12 through a plurality of methane enrichment holes 114The rotating speed of the output gear 3 of the motor 5 is controlled to further control the rotating gas distribution ring body 6, so that the pure methane pressure accumulation cavity 2 and the methane enrichment cavity layer 7 are in periodic mutual communication period and pace consistent with the period and pace of the gas sprayed into the combustion chamber 12 by the flame stabilizer 89; further, the gas enrichment is carried out on each pulse combustion period in the combustion chamber 12, and the continuous pulse combustion of the combustion chamber 12 is ensured; high-temperature tail gas generated by combustion in the combustion chamber 12 is continuously ejected in the form of tail flames through the straight exhaust pipes 20, and the tail flames ejected from the straight exhaust pipes 20 heat the heat-consuming equipment; thereby realizing the utilization of the gas; meanwhile, the pure methane gas in the methane enrichment cavity layer 7 can absorb the heat generated after combustion in the combustion chamber 12 through the second annular wall 9, and then the preheated pure CH is sprayed into the combustion chamber 12 through the methane enrichment holes 114Thereby effectively improving the combustion efficiency in the combustion chamber 12.
The above description is only a preferred embodiment of the present invention, and it should be noted that: for those skilled in the art, without departing from the principle of the present invention, several improvements and modifications can be made, and these improvements and modifications should also be considered as the protection scope of the present invention.
Claims (2)
1. Take low concentration gas pulse combustor of steady flame dish structure, its characterized in that: the flame stabilizer comprises a columnar gas distribution shell (74), wherein five flame stabilizers (89) are arranged on one side of the gas distribution shell (74), and the five flame stabilizers (89) are distributed in an equidistant array along the axis of the gas distribution shell (74);
each flame holder (89) is of a conical shell structure, the axis of a conical shell of each flame holder (89) is vertical to the axis of the gas diversion shell (74), a flame holding conical cavity (72) is arranged inside the conical shell of each flame holder (89), and the thick end of the flame holding conical cavity (72) is communicated with the gas diversion cavity (71) inside the gas diversion shell (74) at least through seven uniformly distributed gas guide holes (75); the thin end of the flame stabilizing conical cavity (72) is provided with a gas jet hole (73) coaxially;
the gas burner is characterized by further comprising five gas burners (10), wherein five gas burners (10) correspond to five flame holders (89) coaxially respectively, the gas burners (10) are of cylindrical structures, the inner cavity of each gas burner (10) is a cylindrical combustion chamber (12), and a gas ejection port (73) of each flame holder (89) is communicated with a gas inlet end of the combustion chamber (12) of the corresponding gas burner (10) coaxially; one end of each combustion chamber (12) far away from the flame stabilizer (89) is connected with an exhaust straight pipe (20);
the gas reposition of redundant personnel casing (74) are kept away from the one end of steady flame ware (89) still includes low concentration gas pulsation feed pipe (81), the end intercommunication of giving vent to anger of low concentration gas pulsation feed pipe (81) the inside gas reposition of redundant personnel chamber (71) of gas reposition of redundant personnel casing (74).
2. The low-concentration gas pulsation burner with a flame stabilizing disc structure according to claim 1, wherein: an annular methane enrichment tank body (18) is integrally arranged on the outer side of the gas burner (10), and an annular pure methane pressure accumulation cavity (2) is formed in the annular methane enrichment tank body (18); an annular methane enrichment cavity layer (7) is coaxially arranged between the pure methane pressure accumulation cavity (2) and the combustion chamber (12); the pure methane pressure accumulation cavity (2) and the methane enrichment cavity layer (7) are separated by a first annular wall (1), and the methane enrichment cavity layer (7) and the combustion chamber (12) are separated by a second annular wall (9); a plurality of methane enrichment holes (11) are uniformly distributed on two sides of the second annular wall (9) along the axis in a circumferential array, and the methane enrichment holes (11) are used for communicating the methane enrichment cavity layer (7) with the combustion chamber (12); a plurality of first air guide channels (14) are distributed on the first annular wall (1) in a circumferential array, the inner end of each first air guide channel (14) is communicated with the methane enrichment cavity layer (7), the pure methane pressure accumulation cavity (2) is also internally provided with a rotary gas distribution ring body (6), the rotary gas distribution ring body (6) is rotatably sleeved on the outer side of the first ring wall (1), the middle part of the inner ring of the rotary air distribution ring body (6) is integrally provided with an annular flange (21) coaxially, the inner wall of the annular flange (21) blocks the outer end of each first air guide channel (14), a plurality of second air guide channels (17) are distributed on the annular flange (21) in a circumferential array, the outer end of each second air guide channel (17) is communicated with the pure methane pressure accumulation cavity (2), and the inner end of each second air guide channel (17) can synchronously rotate along with the annular flange (21) to respectively align and communicate with the outer ends of the plurality of first air guide channels (14); the device also comprises a pure methane pressurizing and supplying pipe (8), and the gas outlet end of the pure methane pressurizing and supplying pipe (8) is communicated with the pure methane pressure storage cavity (2); the outer lane of rotatory distribution ring body (6) is provided with round dentition body (25), pure methane pressure storage chamber (2) still fixed mounting have motor (5), synchronous connection has output gear (3) on output shaft (4) of motor (5), output gear (3) with round dentition body (25) meshing connection on the rotatory distribution ring body (6).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201920356003.7U CN209840096U (en) | 2019-03-20 | 2019-03-20 | Low-concentration gas pulsation burner with flame stabilizing disc structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920356003.7U CN209840096U (en) | 2019-03-20 | 2019-03-20 | Low-concentration gas pulsation burner with flame stabilizing disc structure |
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| CN201920356003.7U Expired - Fee Related CN209840096U (en) | 2019-03-20 | 2019-03-20 | Low-concentration gas pulsation burner with flame stabilizing disc structure |
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Granted publication date: 20191224 |