Oxy-combustion heating system and pipe diameter design method thereof

Abstract

The application provides an oxygen-enriched combustion heating system and a pipe diameter design method thereof, and relates to the technical field of heating furnace combustion. The system comprises a heating furnace, a mixing pipeline and an ignition head. The input end of the mixing pipeline is connected with the oxygen-enriched air, the output end of the mixing pipeline is communicated with the input end of the ignition head, the output end of the ignition head penetrates through the furnace wall of the heating furnace and is communicated with the inside of the heating furnace, the mixing pipeline comprises a straight pipe part and a variable diameter part, the variable diameter part is located between the two straight pipe parts and is communicated with the two straight pipe parts, the variable diameter part comprises a variable small part, a thin pipe part and a variable large part in sequence along the gas flow direction, the variable small part gradually decreases in diameter along the gas flow direction, the thin pipe part and the variable small part have the same diameter at the smallest end, one end of the thin pipe part away from the variable small part is communicated with the variable large part, the variable large part gradually increases in diameter, the middle part of the thin pipe part is communicated with a gas supply pipeline, and the combustible gas is filled in the gas supply pipeline. The system can uniformly mix the oxygen-enriched air and the combustible gas, so that the combustion efficiency and quality can be improved.

Description

Technical Field

[0001] This invention relates to the field of combustion technology for heating furnaces, and in particular to an oxygen-enriched combustion heating system and its pipe diameter design method. Background Technology

[0002] With the continuous rise in energy prices and increasingly stringent environmental laws and regulations, researching, finding, and upgrading efficient combustion technologies for heating furnaces in large steel rolling enterprises to reduce energy consumption and costs while also reducing emissions of pollutants such as nitrogen oxides and sulfur oxides is a long-term research challenge.

[0003] In related technologies, oxygen-enriched combustion is used to reduce the supply of high-calorific-value fuels to the heating furnace, thereby reducing coke oven gas consumption. This method involves introducing oxygen into the combustion air ducts of the heating furnace, achieving an oxygen concentration of 22%-29% in the combustion air, thus realizing oxygen-enriched combustion throughout the furnace. Oxygen-enriched combustion can significantly increase the concentrations of CO2 and H2O in the flue gas within the heating furnace, increasing the radiation coefficient of the flue gas by more than 15% compared to conventional air combustion, and improving the overall heat exchange efficiency of the heating furnace.

[0004] However, the combustible gas and oxygen-enriched air are still prone to uneven mixing at the ignition point, resulting in relatively low combustion efficiency and quality. Summary of the Invention

[0005] This invention provides an oxygen-enriched combustion heating system and its pipe diameter design method. The oxygen-enriched combustion heating system can uniformly mix oxygen-enriched air and combustible gas in advance, improving combustion efficiency and quality. The technical solution of this invention is as follows:

[0006] In a first aspect, the present invention provides an oxygen-enriched combustion heating system, including a heating furnace, a mixing pipe, and an ignition head;

[0007] The mixing pipe has an inlet end that is supplied with oxygen-enriched air and an outlet end that is connected to the inlet end of the ignition head. The outlet end of the ignition head passes through the furnace wall of the heating furnace and is connected to the interior of the heating furnace. The mixing pipe includes a straight pipe section and a variable diameter section. The variable diameter section is located between two straight pipe sections and is connected to both of them. The variable diameter section includes a decreasing section, a thin pipe section, and a increasing section in sequence along the gas flow direction. The diameter of the decreasing section gradually decreases along the gas flow direction. The thin pipe section, which is straight, is connected to the smallest diameter end of the decreasing section and has the same diameter as the smallest diameter end of the decreasing section. The end of the thin pipe section away from the decreasing section is connected to the increasing section. The diameter of the increasing section gradually increases. A gas supply pipe is connected to the middle of the thin pipe section, and combustible gas is supplied through the gas supply pipe.

[0008] Preferably, the oxygen-enriched air is pumped into the mixing pipe by a first constant flow pump, and the combustible gas is pumped into the gas supply pipe by a second constant flow pump.

[0009] Preferably, the ignition head includes a heat insulation plate, a heat insulation chamber, and a nozzle;

[0010] The heat insulation chamber is cylindrical, and the heat insulation plate is installed at one end of the heat insulation chamber that is connected to the mixing pipe. The heat insulation plate has multiple vent holes, and the nozzle is installed at the end of the heat insulation chamber away from the heat insulation plate.

[0011] Preferably, an expansion joint is installed around the vent hole, the expansion joint facing the heat insulation chamber, and a baffle is installed at the end of the expansion joint away from the vent hole, the size of the baffle being larger than the size of the vent hole.

[0012] Preferably, the baffle is a curved surface protruding towards the nozzle, and the edge of the baffle is wrapped with rubber.

[0013] Preferably, there are multiple nozzles, and the output orifice diameter of each nozzle is 2~4mm.

[0014] Preferably, an oxygen-enriched combustion heating system further includes a water-cooled layer, which is installed outside the heating furnace. The nozzle passes through the water-cooled layer and the furnace wall of the heating furnace in sequence, and the water-cooled layer is filled with water.

[0015] Preferably, an oxygen-enriched combustion heating system further includes a heat exchanger, wherein water in the water-cooled layer flows into a first pipe of the heat exchanger, and exhaust gas from the heating furnace is introduced into a second pipe of the heat exchanger, and the first pipe is connected to a pneumatic power device.

[0016] In a second aspect, the present invention provides a pipe diameter design method for an oxygen-enriched combustion heating system. Based on the oxygen-enriched combustion heating system described in the first aspect, the pipe diameter design method includes:

[0017] The mixing ratio of the combustible gas and the oxygen concentration of the oxygen-enriched air is determined according to the type of combustible gas and the oxygen concentration of the oxygen-enriched air, and the ratio of the first flow rate upstream of the capillary section and the second flow rate of the gas supply pipe is determined according to the mixing ratio.

[0018] The target flow rate at the output end of the ignition head is determined based on the mixing ratio; wherein, the target flow rate is the speed at which the ignition head outputs a stable flame.

[0019] The third flow rate of the mixed gas is determined based on the target flow rate and the output orifice area of ​​the ignition head output end;

[0020] The first flow rate and the second flow rate are determined based on the ratio of the first flow rate to the second flow rate and the third flow rate;

[0021] The diameter of the thin tube and the diameter of the gas supply pipe are determined based on the first flow rate, the second flow rate, and the preset pressure difference.

[0022] Preferably, determining the diameter of the thin tube and the diameter of the gas supply pipe based on the first flow rate, the second flow rate, and the preset pressure difference includes:

[0023] The flow velocity difference between the capillary tube and the gas supply pipe is determined based on the preset pressure difference;

[0024] Make the diameters of the thin tube and the gas supply pipe equal, and determine the diameters of the thin tube and the gas supply pipe based on the first flow rate, the second flow rate, and the velocity difference.

[0025] Compared with the prior art, the present invention has at least the following beneficial effects:

[0026] In this embodiment, when the oxygen-enriched air is transported to the reducing section in the mixing pipe, the reducing section becomes narrower. Under the premise that the flow rate in the mixing pipe remains constant, the flow velocity of the oxygen-enriched air inside the reducing section increases, which in turn leads to a decrease in pressure in the narrow section. This increases the pressure difference between the narrow section and the gas supply pipe. The extremely high pressure difference causes the combustible gas in the gas supply pipe to be torn apart and dispersed in the oxygen-enriched air after entering the narrow section. This achieves uniform dispersion of the combustible gas in the oxygen-enriched air. The fully mixed and uniform combustible gas can achieve stable and high-quality combustion, thereby improving combustion efficiency and quality. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 This is a top view schematic diagram of an oxygen-enriched combustion heating system provided in an embodiment of the present invention;

[0029] Figure 2 This is a partial structural schematic diagram of an oxygen-enriched combustion heating system provided in an embodiment of the present invention.

[0030] In the picture:

[0031] 1-Direct Management Department;

[0032] 2- Variable diameter section;

[0033] 21-Minimum part;

[0034] 22-Thin tubular section;

[0035] 23- Becomes larger;

[0036] 3-Heating furnace;

[0037] 4-Ignition head;

[0038] 41-Insulation board;

[0039] 42-Insulated compartment;

[0040] 43-Baffle;

[0041] 44 - Telescopic component;

[0042] 45- Nozzle;

[0043] 5-Gas supply pipeline;

[0044] 6-Water cooling layer;

[0045] 7-Heat exchanger. Detailed Implementation

[0046] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are some embodiments of the present invention, but not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0047] like Figures 1 to 2 As shown, this embodiment provides an oxygen-enriched combustion heating system, including a heating furnace 3, a mixing pipe, and an ignition head 4;

[0048] The mixing pipe has oxygen-enriched air introduced at its inlet and an outlet connected to the inlet of the ignition head 4. The outlet of the ignition head 4 passes through the furnace wall of the heating furnace 3 and is connected to the interior of the heating furnace 3. The mixing pipe includes a straight pipe section 1 and a variable diameter section 2. The variable diameter section 2 is located between two straight pipe sections 1 and is connected to both of them. The variable diameter section 2 includes a decreasing section 21, a thin pipe section 22, and a increasing section 23 in sequence along the gas flow direction. The diameter of the decreasing section 21 gradually decreases along the gas flow direction. The thin pipe section 22, which is straight, is connected to the smallest diameter end of the decreasing section 21 and has the same diameter as the smallest diameter end of the decreasing section 21. The end of the thin pipe section 22 away from the decreasing section 21 is connected to the increasing section 23. The diameter of the increasing section 23 gradually increases. A gas supply pipe 5 is connected to the middle of the thin pipe section 22, and combustible gas is introduced into the gas supply pipe 5.

[0049] In this embodiment, to improve the utilization rate of oxygen-enriched air and increase the combustion quality of combustible gas, the oxygen-enriched air and combustible gas are thoroughly mixed through the variable diameter section 2 of the mixing pipe before ignition and combustion. Specifically, when the oxygen-enriched air moves to the variable diameter section 2 in the mixing pipe, the variable diameter section 2 becomes narrower. Under the premise that the flow rate in the mixing pipe remains constant, the flow velocity of the oxygen-enriched air inside the narrow tube section 22 increases to match the flow rate of the straight tube section 1, thereby causing the pressure in the narrow tube section 22 to decrease. The flow velocity of combustible gas in the gas supply pipe 5 connected to the narrow tube section 22 is relatively slow. This is because controlling the sustainable combustion of combustible gas requires controlling the ratio of combustible gas to oxygen-enriched air. The air-fuel ratio is mostly 10-40, which means that the flow rate and velocity of oxygen-enriched air need to be tens of times that of combustible gas. Therefore, the setting of the narrow tube section 22 further increases the pressure difference between the narrow tube section 22 and the gas supply pipe 5. The extremely high pressure difference causes the combustible gas in the gas supply pipe 5 to be torn apart and dispersed in the oxygen-enriched air after entering the thin tube section 22. The extremely high pressure difference achieves uniform dispersion of the combustible gas in the oxygen-enriched air. The fully mixed and uniform combustible gas can achieve stable and high-quality combustion. It will not cause incomplete combustion due to insufficient oxygen-enriched air around the combustible gas, nor will it cause combustion interruption due to excessive distance between the dispersed combustible gases.

[0050] In some embodiments of the present invention, the oxygen-enriched air is pumped into the mixing pipe by a first constant flow pump, and the combustible gas is pumped into the gas supply pipe 5 by a second constant flow pump.

[0051] In this embodiment, the first constant flow pump and the second constant flow pump can control the flow rate, thereby controlling the gas volume ratio after the oxygen-enriched air and combustible gas are mixed. A reasonable gas volume ratio can prevent combustion interruption due to excessive distance between the dispersed combustible gases after the combustible gas is evenly dispersed, and can also prevent incomplete combustion due to excessively low oxygen-enriched air content.

[0052] In some embodiments of the present invention, the ignition head 4 includes a heat insulation plate 41, a heat insulation chamber 42, and a nozzle 45;

[0053] The heat insulation chamber 42 is cylindrical. The heat insulation plate 41 is installed at one end of the heat insulation chamber 42 that is connected to the mixing pipe. The heat insulation plate 41 has multiple vent holes. The nozzle 45 is installed at the end of the heat insulation chamber 42 that is away from the heat insulation plate 41.

[0054] In this embodiment, since the ignition head 4 ignites a mixed gas, if the combustion gets out of control, the combustion will spread inward to the mixing pipe. The chain reaction caused by combustion in a confined space is very likely to cause an explosion. Therefore, an explosion-proof design is required. Specifically, the ignition head 4 is designed to include a heat insulation plate 41, a heat insulation chamber 42, and a nozzle 45. The heat insulation plate 41 is made of heat insulation material and can isolate heat from the outside of the mixing pipe. The vent holes on the heat insulation plate 41 allow the mixed gas to enter the heat insulation chamber 42. The heat insulation chamber 42 has a buffering effect. The mixed gas has a low thermal conductivity, and the design of the heat insulation chamber 42 can further insulate the gas in the mixing pipe.

[0055] In some embodiments of the present invention, a telescopic member 44 is installed around the vent hole, the telescopic member 44 faces the heat insulation chamber 42, and a baffle 43 is installed at the end of the telescopic member 44 away from the vent hole, the size of the baffle 43 being larger than the size of the vent hole.

[0056] In this embodiment, when the mixed gas is being output normally, it can enter the insulation chamber 42 through the vent and then be output by the nozzle 45. An ignition needle can be installed at the nozzle 45 to ignite the mixed gas. In the event of an accidental explosion, an explosion will first occur inside the insulation chamber 42. The small-scale explosion inside the insulation chamber 42 can generate high pressure, and the high-pressure baffle 43 will block the vent to prevent further transfer of heat and open flame.

[0057] In this embodiment, the telescopic member 44 can be a spring or a telescopic sleeve.

[0058] Understandably, the baffle 43 enables the mixed gas to form small-scale turbulence as it passes through, further increasing the mixing degree of the combustible gas and oxygen-enriched air. Furthermore, the telescopic member 44 is preferably a spring, whose vibration under the impact of the airflow further agitates the mixed gas, further increasing the mixing degree of the combustible gas and oxygen-enriched air.

[0059] In some embodiments of the present invention, the baffle 43 is a curved surface protruding toward the nozzle 45, and the edge of the baffle 43 is wrapped with rubber.

[0060] In this embodiment, the baffle 43 can be made of ceramic, and the wrapped rubber can block the transmission of gas.

[0061] In some embodiments of the present invention, there are multiple nozzles 45, and the output orifice diameter of each nozzle 45 is 2~4mm.

[0062] In this embodiment, the mixed gas is ejected through multiple nozzles 45. The output orifice diameter of the nozzles 45 is relatively small, ranging from 2 to 4 mm. This smaller output orifice diameter results in a faster flow rate, which helps prevent the flame from retreating inward and causing an explosion. Simultaneously, the numerous nozzles 45 provide sufficient flame, thereby providing adequate heat.

[0063] In some embodiments of the present invention, an oxygen-enriched combustion heating system further includes a water-cooled layer 6, which is installed outside the heating furnace 3. The nozzle 45 passes through the water-cooled layer 6 and the furnace wall of the heating furnace 3 in sequence, and the water-cooled layer 6 is filled with water.

[0064] In this embodiment, the water-cooling layer 6 can remove heat from the nozzle 45, reducing the risk of heat conduction into the interior and causing an explosion.

[0065] In this embodiment, the nozzle 45 can be conical. The conical shape can increase the contact area between the nozzle 45 and the water-cooling layer 6 while ensuring that the nozzle 45 has a small output aperture, thereby increasing the cooling effect.

[0066] In some embodiments of the present invention, an oxygen-enriched combustion heating system further includes a heat exchanger 7, water in the water-cooled layer 6 flows into a first pipe of the heat exchanger 7, and exhaust gas from the heating furnace 3 is introduced into a second pipe of the heat exchanger 7, the first pipe being connected to a pneumatic power device.

[0067] In this embodiment, the water in the water-cooled layer 6, after being heated by the nozzle 45, has a certain amount of heat. After entering the heat exchanger 7, it vaporizes at the high temperature of the waste heat from the heating furnace 3 to generate water vapor. The water vapor can be used by a pneumatic power device such as a steam engine to generate electricity or be converted into other forms of energy for use.

[0068] This invention also provides a pipe diameter design method for an oxygen-enriched combustion heating system. Based on any of the above embodiments of an oxygen-enriched combustion heating system, the pipe diameter design method includes:

[0069] The mixing ratio of the combustible gas and the oxygen concentration of the oxygen-enriched air is determined according to the type of combustible gas and the oxygen concentration of the oxygen-enriched air, and the ratio of the first flow rate upstream of the capillary section 22 to the second flow rate of the gas supply pipe 5 is determined according to the mixing ratio.

[0070] The target flow rate at the output end of the ignition head 4 is determined based on the mixing ratio; wherein, the target flow rate is the speed at which the ignition head 4 outputs a stable flame.

[0071] The third flow rate of the mixed gas is determined based on the target flow rate and the output orifice area of ​​the ignition head 4.

[0072] The first flow rate and the second flow rate are determined based on the ratio of the first flow rate to the second flow rate and the third flow rate;

[0073] The diameter of the thin tube section 22 and the diameter of the gas supply pipe 5 are determined based on the first flow rate, the second flow rate, and the preset pressure difference.

[0074] In this embodiment, different types of combustible gases require different volumes of oxygen-enriched air for complete combustion. Therefore, the optimal volume ratio between the oxygen concentration of the oxygen-enriched air and the type of combustible gas can be determined, thereby determining the flow rate ratio. The ratio can be a single value or a range.

[0075] Specifically, the ratio of the first flow rate to the second flow rate is expressed by the formula: ;in, Q 1 represents the first flow rate. Q 2 represents the second flow rate. A This refers to the mixing ratio of the two.

[0076] To ensure a stable flame, the flow rate of the nozzle 45 of the ignition head 4 must not be too fast or too slow. Therefore, a reasonable gas flow rate, i.e., the target flow rate, needs to be set. The target flow rate can be determined by observing and recording the flow rate when the flame is about to retreat back to the nozzle 45 and the flow rate when the flame disappears away from the nozzle 45 through experiments. The target flow rate is determined by taking the middle value of the two extreme flow rates.

[0077] After obtaining the target flow velocity, the flow rate of the mixed gas, i.e., the third flow rate, can be determined by combining the sum of the output orifice diameters of all nozzles 45. The third flow rate can be calculated using the following formula:

[0078]

[0079] in, V For the target flow rate, Q 3 represents the third flow rate. n The number of nozzles is 45. a This represents the area of ​​the nozzle's output orifice (45).

[0080] After obtaining the third flow rate, the first and second flow rates can be obtained by combining the above proportional relationships.

[0081] That is, according to , able to obtain Q 1 and Q The value of 2.

[0082] The orifice diameters of the thin tube section 22 and the gas supply pipe 5 can be obtained based on the first flow rate and the second flow rate, combined with the preset pressure difference.

[0083] In some embodiments of the present invention, determining the diameter of the thin tube 22 and the diameter of the gas supply pipe 5 based on the first flow rate, the second flow rate, and the preset pressure difference includes:

[0084] The velocity difference between the thin tube section 22 and the gas supply pipe 5 is determined based on the preset pressure difference;

[0085] Make the diameters of the thin tube section 22 and the gas supply pipe 5 equal, and determine the diameters of the thin tube section 22 and the gas supply pipe 5 based on the first flow rate, the second flow rate and the velocity difference.

[0086] In this embodiment, the preset pressure difference is a high pressure that can fully disperse flammable gas, which can be obtained through experiments or data simulation.

[0087] After determining the preset pressure difference, the diameters of the capillary tube 22 and the gas supply pipe 5 are made the same. To ensure directional gas flow within the capillary tube 22 and to ensure that the combustible gas in the gas supply pipe 5 fully enters the capillary tube 22 for dispersion, the gas supply pipe 5 needs to be perpendicular to the capillary tube 22. Since the gas supply pipe 5 is perpendicular to the capillary tube 22, its diameter needs to be less than or equal to the diameter of the capillary tube 22. To maximize the pressure difference between the two, the flow velocity within the gas supply pipe 5 should be as slow as possible; therefore, its diameter should be as large as possible. In summary, the largest possible pipe diameter is selected, i.e., the diameters of the capillary tube 22 and the gas supply pipe 5 are the same.

[0088] After obtaining the preset pressure difference, the flow velocity difference can be calculated. The specific calculation formula is as follows:

[0089]

[0090]

[0091] in, P 1 represents the pressure inside the capillary tube. P 2 represents the pressure inside the gas supply pipeline. ρ 1 represents the density of the gas mixture inside the capillary tube. ρ 2 represents the density of oxygen-rich air. h Due to the height difference, horizontal pipes are used. h The value is 0, C is a constant that can be obtained through experiments, ΔP is the preset pressure difference, v1 and v2 are the flow velocities in the capillary section 22 and the air supply pipe 5, respectively, g is the acceleration due to gravity, and S is the cross-sectional area of ​​the pipe. The expression is as follows:

[0092]

[0093] After obtaining the cross-sectional area S, the diameters of the thin tube section 22 and the gas supply pipe 5 can be obtained using the formula for the area of ​​a circle.

[0094] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An oxycombustion heating system, characterized by, It comprises a heating furnace (3), a mixing pipeline and an ignition head (4); The input end of the mixing pipeline is connected with the oxygen-enriched air, the output end of the mixing pipeline is communicated with the input end of the ignition head (4), the output end of the ignition head (4) penetrates through the wall of the heating furnace (3) and is communicated with the inside of the heating furnace (3), the mixing pipeline comprises straight pipe sections (1) and a variable diameter section (2), the variable diameter section (2) is located between the two straight pipe sections (1) and is communicated with the two straight pipe sections (1), the variable diameter section (2) comprises a decreasing section (21), a thin pipe section (22) and an increasing section (23) in sequence along the gas flow direction, the decreasing section (21) gradually decreases in diameter along the gas flow direction, the thin pipe section (22) is communicated with the smallest diameter end of the decreasing section (21) and has the same diameter as the smallest diameter end of the decreasing section (21), one end of the thin pipe section (22) away from the decreasing section (21) is communicated with the increasing section (23), the increasing section (23) gradually increases in diameter, the middle of the thin pipe section (22) is communicated with a gas supply pipeline (5), the combustible gas is introduced into the gas supply pipeline (5); The ignition head (4) comprises an insulating plate (41), an insulating bin (42) and a spray head (45); The insulating bin (42) is in a cylindrical shape, the insulating bin (42) is installed with the insulating plate (41) at one end communicated with the mixing pipeline, a plurality of air permeable holes are formed in the insulating plate (41), the spray head (45) is installed at one end of the insulating bin (42) away from the insulating plate (41); The air permeable holes are installed with retractable members (44) around the air permeable holes, the retractable members (44) are towards the insulating bin (42), the retractable members (44) are installed with baffle plates (43) at one end away from the air permeable holes, the baffle plates (43) have a size larger than that of the air permeable holes; the baffle plates (43) are in a shape of a curved surface protruding towards the spray head (45), the edges of the baffle plates (43) are wrapped with rubber; When the mixed gas ignited by the ignition head (4) is normally output, the mixed gas enters the insulating bin (42) through the air permeable holes and is then output by the spray head (45); when an unexpected explosion occurs, the insulating bin (42) explodes and generates high pressure, the baffle plates (43) block the air permeable holes to prevent the further transmission of heat and open flame.

2. An oxycombustion heating system according to claim 1, wherein, The oxygen-enriched air is pumped into the mixing pipeline by a first constant flow pump, the combustible gas is pumped into the gas supply pipeline (5) by a second constant flow pump.

3. The oxy-combustion heating system of claim 1, wherein, The number of the spray heads (45) is multiple, the output aperture of each spray head (45) is 2-4 mm.

4. The oxy-combustion heating system of claim 1, wherein, It further comprises a water cooling layer (6), the water cooling layer (6) is installed outside the heating furnace (3), the spray head (45) penetrates through the water cooling layer (6) and the wall of the heating furnace (3) in sequence, the water cooling layer (6) is filled with water.

5. An oxycombustion heating system according to claim 4, wherein, It further comprises a heat exchanger (7), the water in the water cooling layer (6) flows into a first pipeline of the heat exchanger (7), the exhaust gas of the heating furnace (3) enters a second pipeline of the heat exchanger (7), the first pipeline is connected with a pneumatic device.

6. A method for designing a tube diameter of an oxygen-enriched combustion heating system, characterized by, The oxygen-enriched combustion heating system according to any one of claims 1-5, wherein the pipe diameter design method comprises: determining a mixing ratio of the combustible gas and the oxygen-enriched air according to the type of the combustible gas and the oxygen concentration of the oxygen-enriched air, and determining a ratio of a first flow rate upstream of the fine tube portion (22) to a second flow rate of the gas supply pipe (5) according to the mixing ratio; determining a target flow rate of an output end of the ignition head (4) according to the mixing ratio, wherein the target flow rate is a speed at which the ignition head (4) outputs a stable flame; determining a third flow rate of the mixed gas according to the target flow rate and an output hole area of the output end of the ignition head (4); determining the first flow rate and the second flow rate according to the ratio of the first flow rate to the second flow rate and the third flow rate; determining pipe diameters of the fine tube portion (22) and the gas supply pipe (5) according to the first flow rate, the second flow rate, and a preset pressure difference.

7. A method of designing a tube diameter of an oxygen-enriched combustion heating system according to claim 6, wherein The determining of the pipe diameters of the fine tube portion (22) and the gas supply pipe (5) according to the first flow rate, the second flow rate, and the preset pressure difference comprises: determining a flow rate difference of the fine tube portion (22) and the gas supply pipe (5) according to the preset pressure difference; equalizing the pipe diameters of the fine tube portion (22) and the gas supply pipe (5), and determining the pipe diameters of the fine tube portion (22) and the gas supply pipe (5) according to the first flow rate, the second flow rate, and the flow rate difference.

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