An acoustic wave soot blower with positive pressure anti-blocking function

Abstract

This invention relates to the field of soot blowing equipment technology, and discloses a sonic soot blower with positive pressure anti-clogging function, comprising a sound source assembly, a flange assembly, and a sound wave transmission assembly connected in sequence; the sound wave transmission assembly includes a horn body, a partition cylinder, and a shell, all coaxially sleeved and having gap spaces; the shell is cylindrical and located on the outermost layer, with one end fixedly connected to one side of the flange assembly; the partition cylinder is an arc-shaped conical cylinder located between the horn body and the shell, including an air inlet end and an air outlet end, the air inlet end being fixedly connected to one side of the flange assembly, and the air outlet end being fixedly connected to the shell at the other end near the shell; the horn body includes a small end and a large end, the small end being fixedly connected to one side of the flange assembly; the flange assembly is provided with several through holes aligned with the air inlet end of the partition cylinder to form swirling air pressure; the formed closed space and swirling space effectively prevent suspended matter from entering the dead corner of the shell and causing accumulation and blockage, thereby improving sound generation efficiency.

Description

Technical Field

[0001] This invention relates to the field of soot blowing equipment technology, and specifically to an acoustic soot blower with positive pressure anti-clogging function. Background Technology

[0002] During boiler operation, severe ash and slag buildup on heating surfaces such as water-cooled walls, superheaters, economizers, preheaters, and flues is a long-standing and difficult-to-solve problem. This not only weakens heat transfer on the boiler's heating surfaces, reducing thermal efficiency, but also, in severe cases, can lead to unexpected shutdowns and significant economic losses. Currently, most boilers are equipped with steam sootblowers, compressed air sootblowers, and steel ball sootblowers. However, these traditional sootblowers suffer from drawbacks in operation and performance, including limited blowing range, blind spots, high energy consumption, high maintenance costs, and inconvenient operation, resulting in low utilization rates and frequent disuse. Therefore, low-frequency acoustic soot removal technology for boilers (i.e., acoustic sootblowers) has emerged. Acoustic sootblowers emit sound waves through a specific horn-shaped sound-emitting structure, which are then directed into the enclosed space to be cleaned, allowing them to perform their cleaning function. This technology has been widely applied and has achieved good results.

[0003] However, during the operation of acoustic sootblowers, due to the high ambient temperature and the high frequency of the sound waves emitted by the sound-emitting cavity, the noise generated is large. The horn body structure is simple and fragile, and the emitted sound pressure level is low and unstable. Therefore, it is necessary to perform heat insulation and sound insulation treatment on acoustic sootblowers, and at the same time protect the horn body. The common practice is to add a shell to the outside of the horn body of the acoustic sootblower's sound transmission duct. There is a gap space between the shell and the horn body. In this case, because the air source pressure of the acoustic sootblower is low during operation, while the internal pressure of the boiler reactor is high, a negative pressure is created, which causes floating debris to enter the interior of the acoustic sootblower and cause blockage, affecting the soot blowing efficiency.

[0004] Based on the above problems, the conventional approach is to increase the air pressure inside the horn's internal cavity and add a glass wool insulation layer between the shell and the horn body. This provides some insulation and can also solve the blockage problem. However, glass wool releases harmful gases when heated to high temperatures, endangering the health of on-site personnel. Other high-temperature resistant and heat-insulating materials are expensive. In addition, increasing the gap in existing acoustic soot blowers and adding complex structures or sealing devices, such as adding ash valves or other pipeline structures, expands the space prone to blockage, increasing the likelihood of blockage. Once the equipment structure malfunctions, it can cause blockage again, making maintenance difficult and the complex structure unfavorable for later repairs. Summary of the Invention

[0005] The present invention aims to provide an acoustic soot blower with positive pressure anti-clogging function to solve the technical problem that existing acoustic soot blowers cannot completely solve the problem of abnormal sound production caused by the accumulation of dust particles in the dead corners inside the shell.

[0006] The basic solution provided by this invention is as follows: a sonic soot blower with positive pressure anti-clogging function, comprising a sound source assembly, a flange assembly, and a sound wave conduction assembly connected in sequence; the sound wave conduction assembly includes a horn body, a partition cylinder, and a shell, all coaxially sleeved and having gap spaces; the shell is cylindrical, located on the outermost layer, with one end fixedly connected to one side of the flange assembly; the partition cylinder is an arc-shaped conical cylinder, located between the horn body and the shell, including an air inlet end and an air outlet end, the air inlet end being fixedly connected to one side of the flange assembly, and the air outlet end being fixedly connected to the other end of the shell; the horn body includes a small end and a large end, the small end being fixedly connected to one side of the flange assembly, and the large end having a gap space with the other end of the shell; the flange assembly is provided with several through holes; the several through holes are aligned with the gap space between the horn body and the partition cylinder; it also includes a gas compressor and a gas conduit assembly; the gas compressor is connected to the several through holes through the gas conduit assembly, and is used to send gas through the several through holes into the gap space between the horn body and the partition cylinder to form a swirling air pressure.

[0007] The working principle and advantages of this invention are as follows: The sound source component transmits suitable sound waves from the small end to the large end of the horn body of the sound wave conduction component, blowing them into the space to be cleaned for cleaning. Simultaneously, the outer shell of the sound wave conduction component provides structural protection for the horn body. The partition cylinder of the sound wave conduction component divides the gap between the outer shell and the horn body into a closed space between the outer shell and the partition cylinder, and a swirling space between the partition cylinder and the horn body. The closed space prevents suspended matter caused by the gap between the horn body and the shell from adhering and accumulating in the dead corners of the shell, affecting the normal sound output of the horn body. This isolates the dead corners between the shell and the horn body from the adhesion and accumulation of suspended matter, improving the cleaning effect and working efficiency of the sonic sootblower. A gas compressor, through a gas conduit assembly, sends gas from the through-hole into the swirling space, achieving a circumferential flow within the swirling space, blowing away suspended matter that has entered the gap between the horn body and the shell, preventing the suspended matter from accumulating and adhering to the horn body, thus avoiding affecting its sonic sootblowing effect.

[0008] Compared to existing technologies, which often involve completely sealing off easily clogged spaces, this solution breaks with conventional thinking. Instead of using conventional physical or mechanical sealing methods, it retains the open design of easily clogged spaces. This opening utilizes swirling airflow to achieve dust removal, which not only completely isolates ash return and prevents the accumulation of debris in dead corners of the casing, but also simultaneously uses swirling airflow to achieve dust removal and heat dissipation. This balances the problem of debris accumulation in dead corners with improved dust removal efficiency, maintaining high-efficiency self-cleaning capability and improving soot blowing efficiency. It features a simple structure, environmentally friendly anti-clogging method, and strong dust removal capability.

[0009] Furthermore, several vibrators are fixedly connected to the outer side of the partition cylinder facing the outer shell.

[0010] Beneficial effects: The vibrator drives the partition cylinder to vibrate regularly, which can break up large particles that have entered the gap between the horn body and the shell, preventing them from accumulating and adhering to the partition cylinder and the outside of the horn body. Combined with the swirl, it improves the dust removal efficiency.

[0011] Furthermore, the plurality of vibrators are circumferentially distributed on the outer surface of the partition cylinder and close to the small end of the horn body.

[0012] Beneficial effects: Tests have shown that the impact of evenly distributed vibrations around the circumference and the smaller end near the speaker body on the sound efficiency of the sonic soot blower decreases as the vibration frequency increases within a certain range.

[0013] Furthermore, the number of the plurality of vibrators is three; along the horizontal axis, the distance between the plurality of vibrators and the small end of the horn body is controlled within the range of 1 / 4 to 1 / 3 of the length of the partition cylinder.

[0014] Beneficial effects: Tests have shown that this range of quantity and spacing results in high dust removal efficiency and improved sound production efficiency, while other quantities and spacings are less efficient.

[0015] Furthermore, along the horizontal axis, the length of the outer shell is less than the length of the horn body but greater than the length of the partition tube.

[0016] Beneficial effects: The length of the outer shell is less than the length of the horn body, which makes it convenient to use this length difference to install and fix the sonic soot blower on the device that needs to be cleaned; the length of the outer shell is greater than the length of the inner cylinder, which makes it convenient to install the partition cylinder onto the outer shell.

[0017] Furthermore, the length of the partition tube is controlled within the range of two-thirds to three-quarters of the length of the horn body.

[0018] Beneficial effects: This size setting can control the gap between the outer shell and the partition cylinder, as well as the gap between the partition cylinder and the horn body, within a certain proportional range, so that the ash blowing effect is maintained in a high-efficiency manner.

[0019] Furthermore, the diameter difference between the outer shell and the large end of the horn body is less than the diameter difference between the air inlet end of the partition cylinder and the small end of the horn body, with the difference controlled within the range of 4-5 times.

[0020] Beneficial effects: This size setting allows the gas to flow in an arc-shaped swirling pattern from the inlet to the outlet, which concentrates more at the outlet, effectively improving the soot blowing capacity and reducing the possibility of suspended matter entering the cavity.

[0021] Furthermore, the flange assembly includes a first flange installed at the small end of the horn body, a second flange installed at one end of the outer shell, and a third flange installed at the air inlet end of the partition cylinder.

[0022] Beneficial effects: Improves the firmness of the fixed connection between the speaker body, the partition cylinder and the outer shell.

[0023] Furthermore, the first flange and the second flange have the same structure; the diameter of the third flange is smaller than that of the first flange and the second flange.

[0024] Beneficial effects: The first and second flanges have the same structure, which increases the airflow path through the through hole, makes the through hole structure design more reasonable, enhances the circulation effect, and improves the soot blowing efficiency.

[0025] Furthermore, the sound source assembly includes a sound-generating device and a bent pipe connected between the sound-generating device and the flange assembly; one end of the bent pipe is coaxial with the sound-generating device; the other end of the bent pipe is coaxial with both the flange assembly and the sound wave transmission assembly.

[0026] Beneficial effect: Improves the quality of sound waves entering the speaker body. Attached Figure Description

[0027] Figure 1 This is a front view of an acoustic soot blower with positive pressure anti-clogging function provided in an embodiment of the present invention.

[0028] Figure 2 for Figure 1 AA cross-section view.

[0029] Figure 3 for Figure 1 BB cross-section.

[0030] Figure 4 This is a schematic diagram of the structure of the oscillator provided in an embodiment of the present invention.

[0031] Figure 5 This is a cross-sectional view of the through hole provided in an embodiment of the present invention.

[0032] Figure 6 The left view shows an acoustic soot blower with positive pressure anti-clogging function provided in an embodiment of the present invention.

[0033] Figure 7 This is a simulation diagram of the swirling space provided in an embodiment of the present invention.

[0034] Figure 8 This is a schematic diagram of the assembly of the acoustic wave conduction component provided in an embodiment of the present invention. Detailed Implementation

[0035] The following detailed explanation illustrates the specific implementation methods:

[0036] The markings in the accompanying drawings include: sound source assembly 1, sound generating device 11, bent pipe 12, flange assembly 2, first flange 21, second flange 22, third flange 23, first bolt assembly 24, second bolt assembly 25, third bolt assembly 26, sound wave transmission assembly 3, horn body 31, partition cylinder 32, outer shell 33, front end shell 331, rear end shell 332, through hole 4, straight hole section 41, bent hole section 42, oblique hole section 43, gas compressor 5, gas conduit assembly 6, branch conduit 61, enclosed space 7, swirling space 8, vibrator 9.

[0037] The basic implementation examples are as follows: Figure 1 As shown: A sonic soot blower with positive pressure anti-clogging function includes a sound source assembly 1, a flange assembly 2 and a sound wave transmission assembly 3 connected in sequence.

[0038] like Figure 1 and Figure 2 As shown, the sound wave transmission assembly 3 includes a horn body 31, a partition cylinder 32, and a shell 33, all coaxially fitted and having gaps between them; the shell 33 is cylindrical, located on the outermost layer, and one end is fixedly connected to one side of the flange assembly 2; the horn body 31 includes a small end and a large end, and according to the structure of a typical horn body 31, the larger opening is the large end, and the smaller opening is the small end, such as... Figure 2 As shown, the left side is the small end and the right side is the large end. The above is only for illustrating the difference between the large end and the small end, and does not limit the left and right sides. The small end is fixedly connected to one side of the flange assembly 2, and the large end faces the space to be cleaned. The sound source assembly 1 is connected to the speaker body 31. The sound wave is transmitted from the sound source assembly 1 to the speaker body 31, guided from the small end to the large end, and then transmitted from the large end to the space to be cleaned for cleaning.

[0039] The partition cylinder 32 is an arc-shaped conical cylinder located between the horn body 31 and the outer shell 33. It includes an air inlet end and an air outlet end. The air inlet end is fixedly connected to one side of the flange assembly 2. The diameter of the air inlet end is larger than the diameter of the small end of the horn body 31 and smaller than the diameter of the outer shell 33. There is a diameter difference between the outer shell 33 and the air inlet end of the partition cylinder 32, and a diameter difference between the air inlet end of the partition cylinder 32 and the small end of the horn body 31. Setting the two diameter differences within a reasonable range forms an effective gap space. In this embodiment, the diameter of the outer shell 33 is 419 mm, the diameter of the air inlet end of the partition cylinder 32 is 200 mm, and the diameter of the small end of the horn body 31 is 120 mm. With this size setting, the volume of the gap space formed is within a suitable range. The air outlet is fixedly connected to the outer shell 33 at the other end near the outer shell 33. The diameter of the air outlet is equal to the diameter of the outer shell 33 and larger than the diameter of the large end of the horn body 31. This diameter difference makes the air outlet of the partition cylinder 32 not connected to the horn body 31 near the large end, forming an opening to ensure that the gas flows from the air inlet to the air outlet and blows away the suspended matter from the opening. For better description, this connection is defined to divide the outer shell 33 into the front shell 331 and the rear shell 332. The difference between the diameter of the air outlet end and the diameter of the outer shell 33 and the large end diameter of the horn body 31 is controlled within the range of 20-30mm. This ensures the protective function of the outer shell 33 on the horn body 31 and the sound wave enhancement function, while minimizing the gap space volume between the outer shell 33 and the horn body 31 and reducing the possibility of dust return. In this embodiment, the large end diameter of the horn body 31 is 399mm, and the difference between it and the diameter of the outer shell 33 is 20mm. After testing, this diameter difference matches the diameter difference between the outer shell 33, the air inlet diameter of the partition cylinder 32, and the small end diameter of the horn body 31. This can reasonably divide the gap space between the outer shell 33 and the horn body 31, balancing the avoidance of dead corner accumulation and dust removal efficiency.

[0040] In summary, the connection methods described above, such as Figure 2 As shown, the partition cylinder 32 divides the gap space between the horn body 31 and the outer shell 33 into a closed space 7 and a swirling space 8. The closed space 7 is the space enclosed by the rear shell 332, the partition cylinder 32, and the flange assembly 2 between the outer shell 33 and the partition cylinder 32, and is used to isolate suspended matter flowing back from the large end of the horn body 31. The swirling space 8 is the open space formed by the rear shell 332, the partition cylinder 32, the flange assembly 2 between the partition cylinder 32 and the horn body 31, and the horn body 31. The opening is caused by the diameter difference between the outer shell 33 and the large end of the horn body 31. The opening faces the large end of the horn body 31, ensuring that gas is sent from the inlet end of the partition cylinder 32 into the swirling space 8 and then flows to the outlet end. At the opening, air pressure is used to remove ash, and the flow of gas in the swirling space 8 can dissipate heat from the horn body 31, achieving the effects of ash removal and heat dissipation, improving gas utilization efficiency, protecting the environment and reducing consumption, and lowering costs.

[0041] The volume of the enclosed space 7 is smaller than that of the swirling space 8. This arrangement is to balance the enclosed space 7 in solving the problem of dead corner accumulation and the swirling gas in achieving effective cleaning. Otherwise, if the enclosed space 7 is too large, the swirling space 8 will be small, resulting in a small air flow rate at the opening per unit time, which will not achieve high-efficiency dust removal. Therefore, it is necessary to control it within a reasonable space ratio range. In order to achieve the above purpose, the structural dimensions can be limited in the following way.

[0042] Specifically, along the horizontal axis, the length of the outer shell 33 is less than the length of the horn body 31 but greater than the length of the partition cylinder 32. The length difference between the outer shell 33 and the horn body 31 is controlled within the range of 15-20mm, which facilitates the installation of a fixing plate at the length difference and improves the connection firmness of the acoustic soot blower in the space or equipment to be cleaned. The length difference between the outer shell 33 and the partition cylinder 32 is adapted to the length of the partition cylinder 32, the horn body 31 and the size of the fixing plate, which is beneficial for gas guidance and assembly.

[0043] Specifically, the length of the partition cylinder 32 is controlled within two-thirds to three-quarters of the length of the horn body 31. In this embodiment, the length of the outer shell 33 is 745mm, the length of the horn body 31 is 760mm, and the length of the partition cylinder 32 is 570mm. This length setting is compatible with the diameter settings of the outer shell 33, the partition cylinder 32, and the horn body 31 in this embodiment, which can obtain a reasonable volume of the closed space 7 and the swirling space 8. The closed space 7 volume is minimized while ensuring that the closed space 7 can isolate the dead corner between the shell and the horn body 31 from the adhesion and accumulation of suspended matter. The swirling space 8 volume is maximized while ensuring that the swirling soot blowing efficiency remains high.

[0044] Specifically, the diameter difference between the outer shell 33 and the air inlet end of the partition cylinder 32 is controlled to be 2-2.5 times the diameter difference between the air inlet end of the partition cylinder 32 and the small end of the horn body 31, which can match other structural dimensions and control the volume ratio of the enclosed space 7 and the swirling space 8 within a reasonable range.

[0045] Specifically, the diameter difference between the outer shell 33 and the large end of the horn body 31 is less than the diameter difference between the air inlet end of the partition cylinder 32 and the small end of the horn body 31. The difference is controlled at 4-5 times. In this embodiment, the difference is 4 times. This size setting allows the gas to flow in an arc-shaped converging vortex from the air inlet to the air outlet, which is more concentrated at the outlet, effectively improving the blowing ability and reducing the possibility of suspended matter entering the cavity.

[0046] like Figure 1 , Figure 2 and Figure 4As shown, several vibrators 9 are fixedly connected to the outer surface of the partition cylinder 32 facing the outer shell 33. In this embodiment, they are welded together. The vibrators 9 drive the partition cylinder 32 to vibrate regularly, which can break up large particles that have entered the gap between the horn body 31 and the shell, preventing them from accumulating and adhering to the outside of the partition cylinder 32 and the horn body 31. Combined with the swirling flow, this improves the dust removal efficiency. The partition cylinder 32 has a low static friction coefficient, which is beneficial for breaking up suspended matter when it clumps together and for the sliding of particulate materials.

[0047] To select a suitable vibrator 9, tests were conducted. Vibrators 9 with different power and frequency were installed at different positions on the partition cylinder to test their effect on the sound emission efficiency of the acoustic sootblower (testing the sound emission decibels (dB) at the large end of the horn body 31). The front end refers to the position on the partition cylinder near the small end of the horn body. See Tables 1, 2, and 3 for details.

[0048] Table 1. Effect of a 60W vibrator on sound generation efficiency

[0049]

[0050] Table 2. Effect of a 100W vibrator on sound generation efficiency.

[0051]

[0052] Table 3. Effect of different numbers of vibrators with a power of 100W on sound generation efficiency

[0053]

[0054] Tables 1 and 2 show that, regardless of whether the power of the vibrator 9 is 60W or 100W, if the number of vibrators 9 remains constant but their positions change, the decibel level of the sound output increases from low to high and then decreases again as the vibration frequency increases within a certain range. Furthermore, the sound output efficiency is higher when the vibrator 9 is installed at the front end (near the small end of the speaker body 31). This indicates that when the vibrator 9 is installed at the front end, it has little impact on the sound output efficiency and can keep the sound output efficiency at a high level.

[0055] Therefore, the plurality of vibrators 9 are evenly distributed circumferentially on the outer surface of the partition cylinder 32 and close to the small end of the horn body 31. Along the horizontal axis, the distance between the plurality of vibrators 9 and the small end of the horn body 31 is controlled within the range of 1 / 4 to 1 / 3 of the length of the partition cylinder 32. In this embodiment, along the horizontal axis, the distance between the plurality of vibrators 9 and the small end of the horn body 31 is 1 / 4 of the length of the partition cylinder 32, and the quantity is 3. Model: HS-8SH-4528, resonant frequency 28KHz, power 100W, static capacitance 5600±10% (pF), resonant impedance ≤20 (Ω), and external dimensions 45x52mm in diameter. The height and insulation resistance are ≥100MΩ. This size selection is compatible with the other structural dimensions in this embodiment, which ensures the vibration and dust removal function of the vibrator 9 while reducing the negative impact on the sound generation efficiency.

[0056] like Figure 3 and Figure 5 As shown, the flange assembly 2 has several through holes 4 evenly distributed around its circumference. These through holes 4 are aligned with the gap space between the horn body 31 and the partition cylinder 32, i.e., the swirling space 8. Each through hole 4 includes a straight section 41, a bent section 42, and an inclined section 43. Air enters through the straight section 41 and exits through the inclined section 43. The inlet cross-section is circular, and the outlet cross-section is elliptical. The diameter of the circular section is smaller than the major axis of the elliptical section, which is beneficial for forming a swirling flow. The inclination angle of the inclined section 43 is controlled within the range of 20-25 degrees. In this embodiment, the inclination angle is 22 degrees. The diameter of the straight section 41 is 25 mm, and there are 4 through holes. This limitation allows for the gas to circulate within a relatively small range of air pressure, maintaining high efficiency to blow away suspended matter. If dust accumulates around the through holes, the frequency of swirling airflow can be increased to further reduce the impact of suspended particles entering the cavity.

[0057] like Figure 1 , Figure 6 and Figure 7 As shown, the acoustic soot blower also includes a gas compressor 5 and a gas conduit assembly 6; the gas compressor 5 is connected to several through holes 4 via the gas conduit assembly 6, and is used to send gas through the several through holes 4 into the gap space between the horn body 31 and the partition cylinder 32 to form a swirling air pressure. The gas conduit assembly 6 has multiple branch conduits 61 that are adapted to the several through holes 4 one by one, such as... Figure 6 As shown in the diagram, there are two branch conduits 61, but the number of branch conduits 61 is not limited and is set according to the actual number of through holes 4. In this embodiment, the gas is dry compressed air after steam-water separation. The dry compressed air after steam-water separation increases the dryness of the gas input to the vortex anti-clogging chamber, reducing the probability of moisture and ash mixing and forming deposits again inside the chamber. Before the suspended matter accumulates and forms clumps, this part is blown out, improving the soot blowing effect. During operation, there is a negative pressure in the space to be cleaned, but due to blockage caused by accumulation, the pressure difference between the gap space and the space to be cleaned is changed, resulting in a constant pressure in the gap space. The gas compressor 5 controls the gas supply and demand. As long as the gas is supplied, the pressure inside the chamber is greater than that outside the chamber. The gas source pressure is 0.3-0.6 MPa. At 0.5 MPa, the vortex space is spirally purged, i.e., positive pressure.

[0058] The sound source assembly 1 includes a sound generating device 11 and a bent tube 12 connected between the sound generating device 11 and the flange assembly 2; one end of the bent tube 12 is coaxial with the sound generating device 11; the other end of the bent tube 12 is coaxial with the flange assembly 2 and the sound wave conduction assembly 3, thereby improving the quality of the sound waves entering the speaker body 31.

[0059] To improve the strength of fixed connections, such as Figure 8 As shown, in this embodiment, the flange assembly 2 includes a first flange 21 installed at the small end of the horn body 31, a second flange 22 installed at one end of the outer casing 33, and a third flange 23 installed at the air inlet end of the partition cylinder 32. The first flange 21 and the second flange 22 have the same structure; the diameter of the third flange 23 is smaller than that of the first flange 21 and the second flange 22. The purpose of this arrangement is to make the outer casing 33 and the horn body 31 more firmly installed, and at the same time to increase the thickness of the flange assembly 2. The through hole 4 passes through the first flange and the second flange, and has a longer guide groove, which is conducive to the formation of a more effective gas swirl.

[0060] The first flange 21 and the second flange 22 are fixedly connected near the outer ring by a first bolt group 24. In this embodiment, the first bolt group 24 is an M30x80 high-strength bolt. The third flange 23 is fixedly connected to both the first flange 21 and the second flange 22 by a second bolt group 25. In this embodiment, the second bolt group 25 is an M10x60 high-strength bolt. The outer shell 33 and the partition cylinder 32 are fixedly connected by a third bolt group 26. In this embodiment, the third bolt group 26 is an M20x30 high-strength bolt, achieving a stable connection for the entire acoustic component. Sealing rings are provided at both the second bolt group 25 and the third bolt group 26 to improve the sealing performance of the sealed space and prevent ash from entering the cavity and accumulating through the bolts.

[0061] In practical use, the entire acoustic sootblower is installed in the space to be cleaned in a conventional manner. The specific installation method is well known to those skilled in the art, and this invention does not limit the installation method. The large end of the horn body 31 faces the enclosed space 7 that needs to be cleaned, such as an SCR denitrification reactor. When the reactor is running, it needs to be cleaned. The sound waves are guided from the small end of the horn body 31 to the large end and enter the reactor to achieve cleaning. The pressure in the waiting space of the reactor is greater than the pressure in the acoustic sootblower cavity, forming a negative pressure that allows some suspended dust to enter the gap space between the horn body 31 and the shell. The partition cylinder 32 of this invention forms a sealed space and a swirling space 8. When suspended dust approaches the acoustic sootblower, the swirling space 8 is at the opening. With airflow and within a certain air pressure range, it can effectively isolate suspended matter outside the acoustic soot blower. Even if suspended dust may enter from the opening of the swirling space 8, the sealed space can effectively isolate it, preventing suspended dust from entering the dead corner of the shell and accumulating. At the same time, in the swirling space 8, with the vibration of the vibrator 9 and the continuous swirling disturbance, it will be blown out again from the opening with the swirling flow, realizing positive pressure blowing of dust, preventing suspended matter from accumulating and adhering to the horn body 31 and affecting its acoustic soot blowing effect, thus improving the soot blowing efficiency of the acoustic soot blower.

[0062] To achieve effective swirl, the air pressure range is 0.3-0.5 MPa, and the air intake time can be set to 1 minute and the interval time to 2 minutes. If the unit produces a high-frequency sharp sound during operation, it is judged that the dust accumulation is serious. The purging frequency of compressed gas is increased by shortening the equal interval time and increasing the set time. The equal interval time and the set time are shortened and increased by half.

[0063] Compared with existing technologies, when using the sonic sootblower with positive pressure anti-clogging function of this invention, the horn body is in the closed space of the boiler. The air medium connected to the horn body through the curved pipe is subjected to the pressure of sound energy to blow away the flue gas and suspended matter in the boiler. At the same time, due to the formation of the closed space and swirling space, ash accumulation and blockage between the horn body and the shell are avoided, which improves the sootblowing effect and working efficiency of the sonic sootblower. It can effectively avoid abnormal sounding caused by ash accumulation and agglomeration inside the sonic sootblower, resulting in wasted sound energy. It solves the problems of serious ash accumulation on the boiler heat exchange surface, reduced boiler efficiency, and increased flue gas temperature. Compared with traditional sonic sootblowers, the sootblowing efficiency is greatly improved.

[0064] The above descriptions are merely embodiments of the present invention. Commonly known structures and characteristics of the solutions are not described in detail here. Those skilled in the art are aware of all common technical knowledge in the field prior to the application date or priority date, are aware of all existing technologies in that field, and have the ability to apply conventional experimental methods prior to that date. Those skilled in the art can, under the guidance of this application, improve and implement this solution in combination with their own capabilities. Some typical known structures or methods should not be obstacles for those skilled in the art to implement this application. It should be noted that those skilled in the art can make several modifications and improvements without departing from the structure of the present invention. These should also be considered within the scope of protection of the present invention, and will not affect the effectiveness of the implementation of the present invention or the practicality of the patent.

Claims

1. A sonic soot blower with positive pressure anti-clogging function, characterized in that, The system includes a sound source assembly, a flange assembly, and a sound wave conduction assembly connected in sequence. The sound wave conduction assembly includes a coaxially sleeved horn body, a partition cylinder, and a shell, with gaps between the horn body and the partition cylinder, and between the partition cylinder and the shell. The shell is cylindrical and located on the outermost layer, with one end fixedly connected to one side of the flange assembly. The partition cylinder is an arc-shaped conical cylinder located between the horn body and the shell, including an inlet end and an outlet end. The inlet end is fixedly connected to one side of the flange assembly, and the outlet end is fixedly connected to the shell at the other end near the shell. The horn body includes a small end and a large end, with the small end fixedly connected to one side of the flange assembly. The flange assembly has several through holes aligned with the inlet end of the partition cylinder. The system also includes a gas compressor and a gas conduit assembly. The gas compressor is connected to the several through holes through the gas conduit assembly to deliver gas through the through holes into the gap space between the horn body and the partition cylinder to form a swirling air pressure. The flange assembly has several through holes evenly distributed around its circumference; these through holes are aligned with the gap space between the horn body and the partition cylinder, i.e., the swirling space; the through holes include straight hole sections, curved hole sections, and inclined hole sections, with air entering from the straight hole section and exiting from the inclined hole section. The air inlet end has a circular cross-section, and the air outlet end has an elliptical cross-section. The diameter of the circle is smaller than the major axis of the ellipse, which is conducive to the formation of swirling flow.

2. The acoustic wave sootblower with positive pressure anti-blocking function according to claim 1, characterized in that, Several vibrators are fixedly connected to the outer side of the partition cylinder facing the outer shell.

3. The acoustic wave sootblower with positive pressure anti-blocking function according to claim 2, characterized in that, The plurality of vibrators are evenly distributed circumferentially on the outer surface of the partition cylinder and close to the small end of the horn body.

4. The acoustic wave sootblower with positive pressure anti-blocking function according to claim 3, characterized in that, The number of vibrators is three; along the horizontal axis, the distance between the vibrators and the small end of the horn body is controlled within 1 / 4 to 1 / 3 of the length of the partition cylinder.

5. The acoustic wave sootblower with positive pressure anti-blocking function according to claim 1, characterized in that, Along the horizontal axis, the length of the outer shell is less than the length of the horn body but greater than the length of the partition tube.

6. The acoustic wave sootblower with positive pressure anti-blocking function according to claim 1, characterized in that, The length of the partition tube is controlled within the range of two-thirds to three-quarters of the length of the horn body.

7. The acoustic wave sootblower with positive pressure anti-blocking function according to claim 1, characterized in that, The diameter difference between the outer shell and the large end of the horn body is less than the diameter difference between the air inlet end of the partition cylinder and the small end of the horn body. The diameter difference between the air inlet end of the partition cylinder and the small end of the horn body is controlled within the range of 4-5 times the diameter difference between the outer shell and the large end of the horn body.

8. The acoustic wave descaler with positive pressure anti-blocking function according to claim 1, characterized in that, The flange assembly includes a first flange installed at the small end of the horn body, a second flange installed at one end of the outer shell, and a third flange installed at the air inlet end of the partition cylinder.

9. The acoustic wave descaler with positive pressure anti-blocking function according to claim 8, characterized in that, The first flange and the second flange have the same structure; the diameter of the third flange is smaller than that of the first flange and the second flange.

10. A sonic soot blower with positive pressure anti-clogging function according to claim 1, characterized in that, The sound source assembly includes a sound-generating device and a bent tube connected between the sound-generating device and the flange assembly; one end of the bent tube is coaxial with the sound-generating device; the other end of the bent tube is coaxial with both the flange assembly and the sound wave transmission assembly.

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