A high pressure powder burner device

Abstract

The utility model discloses a high pressure powder combustor device, including combustor body, the combustor body end portion is equipped with combustion pipe, and is provided with bidirectional cooling structure on the combustion pipe, be provided with first liquid cooling coil on bidirectional cooling structure, and first liquid cooling coil's one side is equipped with second liquid cooling coil, second liquid cooling coil one end is equipped with water inlet pipe B, and its other end is equipped with drain pipe B, first liquid cooling coil one end is equipped with water inlet pipe A, and first liquid cooling coil other end is equipped with drain pipe A. The high pressure powder combustor device, the medium of reverse flow can form the sustained temperature difference gradient in the coil, avoid the heat exchange attenuation problem of the big temperature difference of the entrance end, the small temperature difference of the export end when single flow, make the medium can more fully absorb the heat of combustion pipe, avoid the combustion pipe because of the outer wall long -term high temperature, the pipe wall oxidation thinning of easy appearance, and along with the generation of the case of thermal crack, improve the service life of equipment.

Description

Technical Field

[0001] This utility model relates to the field of burners, specifically a high-pressure powder burner device. Background Technology

[0002] High-pressure pulverized coal burners (hereinafter referred to as "high-pressure pulverized coal burners") are thermal energy devices that enhance the dispersion, mixing and combustion of pulverized coal through high-pressure air supply. Their core objective is to achieve efficient and stable combustion of pulverized coal while reducing pollutant emissions. They are widely used in industrial boilers, heating furnaces, rotary kilns and other thermal energy demand scenarios.

[0003] When in use, the ignition system is activated when the uniform air-coal mixture reaches the burner outlet: if it is electric spark ignition, the high-voltage electric spark (voltage 10-20kV) directly ignites the air-coal mixture; if it is "heavy oil / natural gas ignition" (applicable to low volatile coal powder), the heavy oil / natural gas is ignited first to form a high-temperature torch (temperature above 1000℃), and then the air-coal mixture is ignited.

[0004] Regarding patents for high-pressure pulverized coal burners, a search revealed a pulverized coal burner with anti-slagging publication number CN213146547U, comprising a pulverized coal burner mounting frame. A rotating wheel bracket is fixedly connected to the inner side of one end of the mounting frame, a rotating support wheel is rotatably connected to the outer side of one end of the rotating wheel bracket, an annular track is rotatably connected to the outer side of one end of the rotating support wheel, an annular toothed plate is fixedly connected to the outer side of one end of the annular track, and a pulverized coal burner combustion chamber is fixedly connected to the inner wall of one end of the annular toothed plate. Although the above-mentioned device can be connected to the rotating shaft, high-pressure gas pipe, and high-pressure gas pump, and can achieve the function of preventing slagging, during the use of the burner, the combustion tube at its end is prone to oxidation and thinning due to long-term high temperature on the outer wall, accompanied by the generation of thermal cracks, forcing shutdown and replacement, thus reducing the service life of the equipment. Utility Model Content

[0005] The purpose of this invention is to provide a high-pressure powder burner device to solve the problems mentioned in the background art.

[0006] To achieve the above objectives, a high-pressure powder burner device is provided, comprising a burner body, a combustion tube installed at the end of the burner body, and a bidirectional cooling structure provided on the combustion tube. A first liquid cooling coil is provided on the bidirectional cooling structure, and a second liquid cooling coil is installed on one side of the first liquid cooling coil. One end of the second liquid cooling coil is provided with a water inlet pipe B, and the other end is provided with a drain pipe B. One end of the first liquid cooling coil is provided with a water inlet pipe A, and the other end is provided with a drain pipe A.

[0007] Furthermore, the first liquid cooling coil and the second liquid cooling coil have a spiral structure, and the first liquid cooling coil and the second liquid cooling coil are linearly distributed.

[0008] Furthermore, the media inside the first liquid cooling coil and the second liquid cooling coil flow in opposite directions, and both the first liquid cooling coil and the second liquid cooling coil have rectangular cross-sections.

[0009] Furthermore, the combustion tube is provided with an installation plate on its outer side, and a docking seat is screwed onto the installation plate. A radiation shielding plate is provided on the outer side of the docking seat, and the radiation shielding plate has a dovetail-shaped cross-section.

[0010] Furthermore, an injection port is fixedly provided at the end of the combustion tube, and a guide groove is provided on the inner circumference of the injection port.

[0011] Furthermore, the guide channel is spiral-shaped and has a depth of 0.2–0.5 cm, while the injection port is cylindrical and its diameter is larger than that of the combustion tube.

[0012] Compared with the prior art, the beneficial effects of this utility model are: 1. This solution utilizes a bidirectional cooling structure where both the first and second liquid cooling coils are spirally and tightly wrapped around the outer circumference of the combustion tube. This maximizes the contact area between the cooling medium and the high-temperature outer wall of the combustion tube, allowing heat to be rapidly transferred through the tube wall to the medium inside the coil. Simultaneously, the internal media of the first and second liquid cooling coils flow in opposite directions, forming counter-convective heat exchange. The opposing flow of the media creates a continuous temperature gradient within the coil, avoiding the heat exchange attenuation problem of a large temperature difference at the inlet and a small temperature difference at the outlet when flowing in a single direction. This allows the medium to more fully absorb the heat from the combustion tube, preventing the combustion tube from easily oxidizing and thinning due to long-term high temperatures on the outer wall, which can lead to thermal cracking and improve the service life of the equipment. 2. This scheme uses a guide channel to cause the high-pressure air-coal mixture to generate spiral motion when it is ejected, forming a strong turbulent flow field, which significantly increases the contact area between the coal powder particles and the air, accelerates the combustion of volatile matter and fixed carbon, and improves combustion efficiency; 3. This solution uses a radiation shielding plate with a dovetail-shaped cross-section on the outside of the docking seat. Compared with ordinary flat plate structures, its dovetail-shaped design can increase the space between the plate and the outer wall of the combustion tube, forming an air insulation layer. This reduces the direct radiation of high temperature from the combustion tube to surrounding equipment, and prevents surrounding components from aging or being damaged due to long-term exposure to high temperature radiation. Attached Figure Description

[0013] Figure 1 This is a front view schematic diagram of the structure of this utility model; Figure 2 This is a cross-sectional view of the bidirectional cooling structure of this utility model; Figure 3 This is a bottom view of the structure of this utility model; Figure 4 This is a rear view of the structure of this utility model; Figure 5 This is a schematic diagram of the bidirectional cooling structure and combustion tube structure of this utility model; Figure 6 This is a schematic diagram of the bidirectional cooling structure of this utility model.

[0014] The following are the labels in the diagram: 1. Burner body; 2. Mounting plate; 3. Radiation shield; 31. Connecting seat; 4. Injector nozzle; 41. Flow guide groove; 5. Two-way cooling structure; 51. First liquid cooling coil; 511. Water inlet pipe A; 512. Drain pipe A; 52. Second liquid cooling coil; 521. Water inlet pipe B; 522. Drain pipe B; 6. Combustion tube. Detailed Implementation

[0015] Please see Figure 1-6 This utility model provides a high-pressure powder burner device, including a burner body 1, a combustion tube 6 installed at the end of the burner body 1, and a bidirectional cooling structure 5 provided on the combustion tube 6. A first liquid cooling coil 51 is provided on the bidirectional cooling structure 5, and a second liquid cooling coil 52 is installed on one side of the first liquid cooling coil 51. One end of the second liquid cooling coil 52 is provided with a water inlet pipe B521, and the other end is provided with a drain pipe B522. One end of the first liquid cooling coil 51 is provided with a water inlet pipe A511, and the other end is provided with a drain pipe A512.

[0016] Working principle: When high-pressure pulverized coal is ignited and burned inside the combustion tube 6 and then ejected, a bidirectional cooling structure 5 is provided on the outside of the combustion tube 6. The bidirectional cooling structure 5 is mainly composed of a first liquid cooling coil 51 and a second liquid cooling coil 52. The first liquid cooling coil 51 and the second liquid cooling coil 52 are spirally wrapped around the outer circumference of the combustion tube 6, and the medium inside the first liquid cooling coil 51 and the second liquid cooling coil 52 flows in opposite directions. This allows for water cooling of the high-temperature combustion tube 6, preventing the tube wall from easily oxidizing and thinning due to long-term high temperature, and avoiding the occurrence of thermal cracks. This improves the service life of the equipment.

[0017] In a preferred embodiment, the first liquid cooling coil 51 and the second liquid cooling coil 52 have a spiral structure and are linearly distributed.

[0018] The media inside the first liquid cooling coil 51 and the second liquid cooling coil 52 flow in opposite directions, and the cross-sections of the first liquid cooling coil 51 and the second liquid cooling coil 52 are both rectangular.

[0019] like Figure 1-5As shown: The first liquid cooling coil 51 and the second liquid cooling coil 52 of the bidirectional cooling structure 5 are both tightly wrapped around the outer circumference of the combustion tube 6 in a spiral shape, maximizing the contact area between the cooling medium and the high-temperature outer wall of the combustion tube 6, allowing heat to be quickly transferred to the medium inside the coil through the tube wall; at the same time, the internal media of the first liquid cooling coil 51 and the second liquid cooling coil 52 flow in opposite directions, forming counter-convective heat exchange. The media flowing in opposite directions will form a continuous temperature gradient in the coil, avoiding the heat exchange attenuation problem of large temperature difference at the inlet end and small temperature difference at the outlet end when flowing in a single direction, so that the medium can absorb the heat of the combustion tube 6 more fully. For example, when the medium in the first liquid cooling coil 51 absorbs heat from the low temperature end and rises in temperature, the low temperature medium in the second liquid cooling coil 52 can simultaneously fill the gap and absorb heat in the high temperature region, significantly improving the heat exchange efficiency per unit time, quickly controlling the temperature of the combustion tube 6 within a safe range, and avoiding overheating of the tube wall due to the high temperature of 1200-1600℃ generated by the ignition and combustion of pulverized coal; To balance the circumferential temperature of the combustion tube 6 and avoid localized thermal stress damage, the spiral design of the bidirectional cooling structure 5 itself achieves full-coverage cooling of the circumference of the combustion tube 6. The superimposed reverse medium flow of the first liquid cooling coil 51 and the second liquid cooling coil 52 can further offset the temperature gradient when cooling a single coil. For example, when the medium in the first liquid cooling coil 51 flows from one end of the combustion tube 6 to the other, the temperature will gradually increase with heat absorption, which may lead to a decrease in the cooling capacity of the corresponding area at the outlet of the coil. At this time, the low-temperature medium flowing in the reverse direction in the second liquid cooling coil 52 can supplement the cooling of this weak area, ultimately making the temperature of each point on the outer circumference of the combustion tube 6 more uniform, avoiding damage such as thermal deformation and cracking caused by excessive local temperature difference, and extending the service life of the combustion tube 6. The bidirectional cooling structure 5 consists of two independent circuits, namely the first liquid cooling coil 51 and the second liquid cooling coil 52, instead of a single cooling channel. On the one hand, if one set of coils, such as the first liquid cooling coil 51, temporarily fails due to medium blockage or pipeline leakage, the other set of coils, the second liquid cooling coil 52, can still maintain basic cooling of the combustion tube 6, preventing the combustion tube 6 from overheating momentarily due to cooling interruption. On the other hand, the independent control characteristics of the two coils allow for separate adjustment of the medium flow rate and pressure of the two sets of coils, and can flexibly adjust the cooling intensity according to the real-time temperature changes of the combustion tube 6. For example, when the coal pulverized combustion load increases, the medium flow rate of the two sets of coils can be increased simultaneously. Compared with the single-coil, one-size-fits-all cooling method, this is more suitable for the dynamic heat load changes of the combustion tube 6 and improves the overall operational stability of the cooling system. The combustion tube 6 needs to withstand the high temperature and flame erosion of pulverized coal ignition and combustion for a long time. If the temperature continues to exceed the material's tolerance limit, high-temperature oxidation is likely to occur, and oxide scale will form on the tube wall, resulting in a reduction in thickness. The bidirectional cooling structure 5 can stably control the tube wall temperature of the combustion tube 6 within the material's safe tolerance range through efficient and uniform cooling, reducing the corrosion of the tube wall metal by high temperature. The reverse heat exchange between the first liquid cooling coil 51 and the second liquid cooling coil 52 can avoid a sudden rise in local tube wall temperature, inhibit oxidation and creep, ensure the structural integrity of the combustion tube 6, and ensure the sealing of the pulverized coal combustion and ejection process. The bidirectional cooling structure 5, through its spiral full-coverage and reverse convection design, not only solves the problem of efficient cooling of the combustion tube 6, but also takes into account temperature uniformity, operational reliability and energy saving. It is a key auxiliary structure that ensures stable ignition and combustion of high-pressure pulverized coal in the combustion tube 6 and safe ejection.

[0020] As a preferred embodiment, the outer side of the combustion tube 6 is also provided with a mounting plate 2, and a docking seat 31 is screwed onto the mounting plate 2. A radiation shielding plate 3 is provided on the outer side of the docking seat 31, and the cross-section of the radiation shielding plate 3 is dovetail-shaped.

[0021] like Figure 1 As shown: The mounting plate 2 on the outside of the combustion tube 6 provides a stable installation reference for the docking seat 31, ensuring that the docking seat 31 is accurately positioned and firmly fixed when installed by screw connection. At the same time, the dovetail-shaped radiation shielding plate 3 on the outside of the docking seat 31, compared with the ordinary flat plate structure, can increase the space between the dovetail and the outer wall of the combustion tube 6, forming an air insulation layer, reducing the direct radiation transfer of high temperature from the combustion tube 6 to the surrounding equipment, and avoiding the performance aging or damage of the surrounding components due to long-term exposure to high temperature radiation. On the other hand, the two sloping sides of the dovetail shape can more comprehensively cover the circumferential outer wall of the combustion tube 6, further blocking the heat loss to the outside, reducing heat loss and improving the thermal efficiency of the entire combustion system. Moreover, this cross-sectional shape can also enhance the structural strength of the radiation shielding plate 3 itself, preventing it from deforming in high temperature environment and ensuring the long-term stable radiation shielding effect.

[0022] In a preferred embodiment, an injection port 4 is fixedly provided at the end of the combustion pipe 6, and a guide groove 41 is provided on the inner circumference of the injection port 4.

[0023] The guide channel 41 is spiral-shaped and has a depth of 0.2 to 0.5 cm. Meanwhile, the injection port 4 is cylindrical and its diameter is larger than that of the combustion tube 6.

[0024] like Figure 1As shown: The guide channel 41 causes the high-pressure air-coal mixture to generate a spiral motion when it is ejected, forming a strong turbulent flow field, which significantly increases the contact area between the coal powder particles and the air, accelerates the release of volatile matter and the combustion of fixed carbon, and improves combustion efficiency; the streamlined design of the guide channel 41 optimizes the airflow path, reduces the frictional resistance of the inner wall of the injection port 4, and the spiral airflow forms a central low-pressure zone at the outlet of the combustion tube 6, which entrains high-temperature flue gas and returns it to the combustion front, maintaining a stable ignition source and preventing flame detachment or flameout, which is especially suitable for the stable combustion of low-volatile coal powder; the guide channel 41 guides the airflow to diffuse evenly, avoids the formation of local high-temperature zones, reduces the risk of coking on the inner wall of the combustion tube 6, and extends the service life of the equipment.

Claims

1. A high-pressure powder burner device, comprising a burner body (1), characterized in that: The burner body (1) is equipped with a combustion tube (6) at one end, and a bidirectional cooling structure (5) is provided on the combustion tube (6). A first liquid cooling coil (51) is provided on the bidirectional cooling structure (5), and a second liquid cooling coil (52) is installed on one side of the first liquid cooling coil (51). One end of the second liquid cooling coil (52) is provided with a water inlet pipe B (521), and the other end is provided with a drain pipe B (522). One end of the first liquid cooling coil (51) is provided with a water inlet pipe A (511), and the other end of the first liquid cooling coil (51) is provided with a drain pipe A (512).

2. The high-pressure powder burner device according to claim 1, characterized in that: The first liquid cooling coil (51) and the second liquid cooling coil (52) are spiral structures, and the first liquid cooling coil (51) and the second liquid cooling coil (52) are linearly distributed.

3. The high-pressure powder burner device according to claim 1, characterized in that: The media inside the first liquid cooling coil (51) and the second liquid cooling coil (52) flow in opposite directions, and the cross-sections of the first liquid cooling coil (51) and the second liquid cooling coil (52) are both rectangular.

4. The high-pressure powder burner device according to claim 1, characterized in that: The combustion tube (6) is also provided with an installation plate (2) on the outside, and a docking seat (31) is screwed on the installation plate (2). A radiation shielding plate (3) is provided on the outside of the docking seat (31), and the cross section of the radiation shielding plate (3) is dovetail shaped.

5. A high-pressure powder burner device according to claim 4, characterized in that: The combustion tube (6) is fixedly provided with an injection port (4) at its end, and a guide groove (41) is provided on the inner circumference of the injection port (4).

6. A high-pressure powder burner device according to claim 5, characterized in that: The guide groove (41) is spiral-shaped and the depth of the guide groove (41) is 0.2 to 0.5 cm. Meanwhile, the injection port (4) is cylindrical and the diameter of the injection port (4) is larger than the diameter of the combustion tube (6).

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