Double-inlet double-flow self-adapting fluidization booster and air inlet method

Abstract

The application provides a double-inlet double-flow self-adaptive fluidization booster and an air inlet method, and relates to the technical field of material conveying. The fluidization booster comprises a valve body, and has an exhaust passage, a first air inlet passage, a second air inlet passage, a feedback passage and a feedback cavity. The exhaust passage is used for being communicated with a container or a pipeline to be fluidized. The first air inlet passage is used for being connected with compressed air. The second air inlet passage is used for being connected with gasification air. The second air inlet passage is communicated with the exhaust passage. The feedback passage is communicated with the exhaust passage and the feedback cavity. A flow switching mechanism has a first flow passage and a second flow passage which are connected in parallel between the first air inlet passage and the exhaust passage. The first flow passage is always kept in a communication state. When the pressure in the feedback cavity is lower than a set threshold, the second flow passage is in a closed state. A feedback execution mechanism can drive the flow switching mechanism to open the second flow passage when the pressure in the feedback cavity reaches the set threshold, so that the switching between basic fluidization and reinforced fluidization is realized.

Description

Technical Field

[0001] This invention relates to the field of material conveying technology, and in particular to a fluidizing booster with dual air intake and dual flow rate adaptive and an air intake method. Background Technology

[0002] Pneumatic conveying systems are crucial equipment for material transport. Within these systems, the booster (also known in the industry as a fluidizer, arch breaker, or aeration plate device) is a core auxiliary component ensuring smooth material flow. It is typically embedded or flange-mounted at the bottom of the hopper, the inner wall of the silo pump, and at bends and diameter changes in the conveying pipeline—locations prone to clogging. Its working principle involves introducing pressurized fluidizing gas externally, which is then evenly sprayed into the material accumulation layer through the booster's diffusion structure. This creates an air film between powder particles, reducing the internal friction angle and bulk density, achieving material fluidization. This eliminates arching, bridging, wall adhesion, and localized blockages, improving conveying continuity and unloading smoothness.

[0003] Traditional boosters generally employ a fixed air inlet structure with a single air source, constant flow rate, and constant pressure. The mainstream configuration involves connecting to a system aeration fan, with a supply pressure typically ranging from 55 kPa to 100 kPa. The air duct is usually a single through-hole or a simple perforated plate structure. While these traditional boosters can achieve basic fluidization functions under stable operating conditions, they exhibit significant technical limitations under complex conditions, varying material levels, and varying back pressure. When the material level inside the container rises, the material compaction increases, or the back pressure in the conveying pipeline increases and local resistance rises, the internal pressure of the container rises accordingly. This causes the pressure difference between the externally supplied air source and the container's interior to decrease rapidly, and may even result in momentary pressure reversal. Under these conditions, the air intake of a traditional constant pressure booster decreases significantly, making it difficult for the gas to effectively penetrate the material layer. The fluidization gas velocity is insufficient, failing to disrupt the stable arch structure and adhesion layer. The fluidization effect drops sharply, easily leading to problems such as material blockage, material interruption, and conveying fluctuations. In severe cases, it can cause system shutdown, pipeline pressure buildup, and equipment overload.

[0004] Meanwhile, the lack of flow redundancy and adjustment mechanisms in single air intake channels makes it impossible to match the corresponding air intake volume according to internal pressure fluctuations. Under conditions of frequent pressure fluctuations, this can easily lead to inconsistent air intake, uneven fluidization zones, localized over-fluidization, or the coexistence of fluidization blind zones. For high-humidity and highly viscous powder materials, traditional boosters cannot achieve adaptive air replenishment and have insufficient arch-breaking capabilities. In addition, the existing structures of traditional boosters generally lack reliable anti-material backflow sealing mechanisms. When the pneumatic conveying system stops, depressurizes, or experiences a sudden pressure reversal, powdery materials can easily backflow into the air passages, causing pore blockage and dust accumulation. This necessitates frequent shutdowns for cleaning, significantly increasing maintenance costs and reducing system operational stability.

[0005] In summary, traditional boosters are insufficient to meet the requirements of high-reliability and high-adaptability pneumatic conveying systems, especially in scenarios involving large-capacity silo pumps, dense-phase conveying, and frequent changes in operating conditions. There is an urgent need for a fluidization booster that can adapt to pressure, is dual-path adjustable, and is anti-clogging and anti-backflow. Summary of the Invention

[0006] The purpose of this invention is to provide a dual-inlet, dual-flow adaptive fluidization booster and an air intake method to solve the technical problems of poor fluidization effect and poor air intake in existing fluidization boosters when the internal pressure of the container increases.

[0007] To achieve the above objectives, this invention proposes a dual-intake, dual-flow adaptive fluidization booster, wherein the fluidization booster comprises: The valve body has an exhaust channel, a first intake channel, a second intake channel, a feedback channel, and a feedback chamber; the exhaust channel is used to communicate with a fluidized container or pipeline, the first intake channel is used to receive compressed air, the second intake channel is used to receive vaporized air, the second intake channel is connected to the exhaust channel, and the feedback channel is connected to the exhaust channel and the feedback chamber. A flow switching mechanism is disposed in the valve body. The flow switching mechanism has a first flow channel and a second flow channel. The first flow channel and the second flow channel are connected in parallel between the first intake channel and the exhaust channel. The inner diameter of the first flow channel is smaller than the inner diameter of the second flow channel. The first flow channel is always kept in a connected state. When the pressure in the feedback chamber is lower than a set threshold, the second flow channel is in a closed state. A feedback actuator is disposed within the feedback chamber. The feedback actuator can drive the flow switching mechanism to open the second flow channel when the pressure in the feedback chamber reaches a set threshold.

[0008] This invention also proposes a dual-intake, dual-flow adaptive intake method, wherein the dual-intake, dual-flow adaptive intake method includes: The vaporized air is continuously introduced into the exhaust channel through the second intake channel to achieve basic fluidization; Compressed air is introduced into the exhaust passage through the first intake passage and the first flow passage; The pressure in the exhaust passage is transmitted to the feedback actuator via the feedback channel; When the pressure reaches a set threshold, the feedback actuator drives the flow switching mechanism to open the second flow channel. The inner diameter of the second flow channel is larger than that of the first flow channel. The compressed air enters the exhaust channel simultaneously through the first flow channel and the second flow channel to achieve enhanced fluidization.

[0009] Compared with the prior art, the present invention has the following features and advantages: The dual-inlet, dual-flow adaptive fluidization booster and intake method proposed in this invention can automatically adjust the intake flow rate of compressed air according to the pressure changes inside the container or pipeline to be fluidized, thereby achieving the switching between basic fluidization and enhanced fluidization.

[0010] The fluidization booster and intake method proposed in this invention, featuring dual intake and dual flow rate adaptive design, directly transmit pressure to the feedback actuator through a feedback channel within the valve body. This allows for automatic switching between the basic fluidization flow rate and the enhanced fluidization flow rate without the need for external sensors, controllers, or manual intervention. When the pressure reaches a threshold, the feedback actuator drives the flow switching mechanism to open the second flow channel, achieving adaptive control of on-demand air supply and improving the automation level and response speed of the fluidization booster. Attached Figure Description

[0011] The accompanying drawings described herein are for illustrative purposes only and are not intended to limit the scope of the invention in any way. Furthermore, the shapes and proportions of the components in the drawings are merely illustrative to aid in understanding the invention and do not specifically limit the shapes and proportions of the components. Those skilled in the art, guided by the teachings of this invention, can select various possible shapes and proportions to implement the invention according to specific circumstances.

[0012] Figure 1 This is a schematic diagram of the structure of the dual-intake, dual-flow adaptive fluidization booster proposed in this invention.

[0013] Explanation of reference numerals in the attached figures

[0014] 1. Valve body; 2. Valve cover; 3. Diaphragm assembly; 4. Main piston; 5. Piston connecting rod; 6. Positioning boss; 7. Check diaphragm; 8. Spring seat; 9. Spring cover; 10. First elastic reset element; 11. Second elastic reset element; 12. Flow regulating bolt; 13. First check valve; 14. First air intake channel; 15. Second air intake channel; 16. Exhaust channel; 17. Second flow channel; 18. First flow channel; 19. Feedback channel; 20. Main air intake chamber; 21. Upper chamber; 22. Lower chamber; 23. Exhaust chamber; 24. Feedback pressure regulating hole; 25. Upper working air port; 26. Lower working air port; 27. First sealing ring; 28. Second sealing ring. Detailed Implementation

[0015] The details of the present invention can be more clearly understood by referring to the accompanying drawings and the description of specific embodiments. However, the specific embodiments of the present invention described herein are for illustrative purposes only and should not be construed as limiting the invention in any way. Under the teachings of this invention, those skilled in the art can conceive of any possible modifications based on the invention, and these should all be considered to fall within the scope of the invention.

[0016] Reference Figure 1 The present invention provides a fluidization booster with dual intake and dual flow adaptive, including a valve body 1, a feedback actuator and a flow switching mechanism.

[0017] The valve body 1 is the main structure of the entire fluidization booster, and its interior has an exhaust channel 16, a first air inlet channel 14, a second air inlet channel 15, a feedback channel 19, and a feedback chamber. The exhaust channel 16 is used to connect to the container to be fluidized or a pipeline, delivering airflow to the inside of the fluidization container in real time; the first air inlet channel 14 is used to connect to an external compressed air source to provide high-pressure fluidization power; the second air inlet channel 15 is used to connect to the vaporized air of the vaporization air system to provide basic fluidization airflow; the second air inlet channel 15 is directly connected to the exhaust channel 16 to ensure that vaporized air can continuously enter the container to be fluidized; the feedback channel 19 connects the exhaust channel 16 and the feedback chamber, transmitting the pressure changes in the exhaust channel 16 to the feedback chamber in real time.

[0018] A flow switching mechanism is disposed within the valve body 1. The flow switching mechanism has a first flow channel 18 and a second flow channel 17. The first flow channel 18 and the second flow channel 17 are connected in parallel between the first intake channel 14 and the exhaust channel 16. The inner diameter of the first flow channel 18 is smaller than the inner diameter of the second flow channel 17. The first flow channel 18 is always kept in a connected state. When the pressure in the feedback chamber is lower than a set threshold, the second flow channel 17 is in a closed state. A feedback actuator is disposed within the feedback chamber. The feedback actuator can drive the flow switching mechanism to open the second flow channel 17 when the pressure in the feedback chamber reaches the set threshold.

[0019] The dual-intake, dual-flow adaptive fluidization booster proposed in this invention can automatically adjust the intake flow of compressed air according to the pressure change in the exhaust channel 16 (i.e., the pressure change inside the fluidized container or pipe), thereby achieving the switching between basic fluidization and enhanced fluidization.

[0020] The dual-inlet, dual-flow adaptive fluidization booster proposed in this invention transmits pressure directly to the feedback actuator through the feedback channel 19 within the valve body 1, automatically switching between the basic fluidization flow rate and the enhanced fluidization flow rate without the need for external sensors, controllers, or manual intervention. When the pressure reaches a threshold, the feedback actuator drives the flow switching mechanism to open the second flow channel 17, achieving adaptive control of on-demand air supply and improving the automation level and response speed of the fluidization booster.

[0021] The fluidization booster proposed in this invention features a dual-intake, dual-flow adaptive design, comprising a first intake channel 14 and a second intake channel 15. It can simultaneously receive compressed air and vaporized air, which have a significant pressure difference. Through a flow switching mechanism, the fluidized gas blown out from the exhaust channel 16 also exhibits a very large pressure difference range, enabling the fluidization booster to simultaneously possess both continuous, gentle fluidization and instantaneous, powerful impact characteristics. Furthermore, during normal fluidization operation, the booster uses low-pressure, high-flow-rate vaporized air and low-flow-rate compressed air to maintain fluidization; in case of blockage, it automatically switches to high-pressure, high-flow-rate compressed air for impact, achieving on-demand energy supply and significantly reducing average energy consumption.

[0022] The working principle of the dual-intake, dual-flow adaptive fluidization booster proposed in this invention is as follows: When the material inside the fluidized container or pipeline is transported smoothly and the pressure is normal, the aerated air generated by the external aeration air system enters the exhaust channel 16 directly through the second air inlet channel 15, and is then transported to the inside of the fluidized container or pipeline, providing continuous basic fluidization assistance to the material. External compressed air enters the valve body 1 through the first air inlet channel 14. Since the pressure in the feedback chamber is lower than the set threshold at this time, the feedback actuator does not operate, and the second flow channel 17 is in the closed state. The compressed air can only enter the exhaust channel 16 through the first flow channel 18 with a smaller inner diameter, and after merging with the aerated air, it enters the fluidized container together to achieve small-flow assisted fluidization.

[0023] When the pressure inside the fluidized container or pipeline rises sharply due to material accumulation, increased material level, or downstream obstruction, the pressure in the exhaust channel 16 also rises. The high-pressure gas in the exhaust channel 16 is rapidly transmitted to the feedback chamber via the feedback channel 19, causing the pressure inside the feedback chamber to rise above a set threshold. Under pressure, the feedback actuator displaces, driving the flow switching mechanism to open the second flow channel 17. Since the inner diameter of the second flow channel 17 is larger than that of the first flow channel 18, its flow capacity is significantly enhanced. At this time, compressed air simultaneously enters the exhaust channel 16 through both the first and second flow channels 18, and after merging with the vaporized air, it is injected into the fluidized container or pipeline with a larger flow rate and higher velocity. The large flow of compressed air forms a powerful jet within the fluidized container or pipeline, impacting and breaking down any arches or blockages formed by the material, restoring the material to a fluidized state. As the blockage is cleared, the pressure inside the fluidized container or pipeline gradually returns to normal, the pressure in the feedback chamber decreases, the feedback actuator resets, the second flow channel 17 automatically closes, and the exhaust channel 16 returns to its basic fluidized state.

[0024] As can be seen from the above process, the flow rate of the fluidized gas output from the exhaust channel 16 can be automatically and cyclically adjusted according to the pressure changes inside the container or pipe to be fluidized, without the need for external control signals or manual intervention, thus achieving adaptive adjustment of energy-saving gas supply during normal operation and powerful blockage breaking during blockage.

[0025] In an optional embodiment of the present invention, the second intake channel 15 and the exhaust channel 16 are coaxially arranged, and the end of the second intake channel 15 connected to the exhaust channel 16 is enlarged to form an exhaust chamber 23.

[0026] In an optional example of this implementation, the inner diameter of the exhaust passage 16 is larger than the inner diameter of the exhaust chamber 23.

[0027] In an optional embodiment of the present invention, the feedback actuator includes a diaphragm assembly 3 and a main piston 4. Both the diaphragm assembly 3 and the main piston 4 are disposed in the feedback chamber. The diaphragm assembly 3 divides the feedback chamber into an upper chamber 21 and a lower chamber 22 that are not interconnected. The feedback channel 19 is connected to the upper chamber 21. The lower chamber 22 has a lower working air port 26 for exhausting gas.

[0028] With the above structure, when the pressure in the upper chamber 21 is greater than the pressure in the lower chamber 22, the diaphragm assembly 3 is deformed and displaced towards the lower chamber 22 under the pressure in the upper chamber 21, thereby pushing the main piston 4 to move towards the lower chamber 22, and the gas in the lower chamber 22 is discharged from the lower working port 26.

[0029] In an optional example, the lower working air port 26 is connected to the external environment to ensure that the gas in the lower chamber 22 can be freely discharged without creating resistance to the movement of the main piston 4.

[0030] In an optional example of this embodiment, the feedback actuator further includes a first elastic reset member 10, a second elastic reset member 11, a piston rod 5, and a spring seat 8. The sum of the deformation threshold of the diaphragm assembly 3, the pre-compression elastic threshold of the first elastic reset member 10, and the pre-compression elastic threshold of the second elastic reset member 11 is the set threshold. When the feedback pressure exceeds the set threshold, the pressure overcomes the pre-compression elastic force of the first elastic reset member 10 and the second elastic reset member 11, pushing the diaphragm assembly 3 downward to deform and generate displacement.

[0031] The downward displacement of the diaphragm assembly 3 pushes the main piston 4, which is sealed to it, downward. The downward movement of the main piston 4 causes the piston rod 5, which is fixed to it, to move downward. The downward movement of the piston rod 5 pushes the spring seat 8, which is fixed to it, downward. During the downward movement, the spring seat 8 compresses the first elastic reset member 10.

[0032] By adjusting the position of the spring cover 9, and thus adjusting the spring force threshold of the first elastic reset member 10, different set thresholds can be changed.

[0033] In an alternative example, the top of the valve body 1 is fixedly connected to the valve cover 2 by fastening bolts, and a sealing fit is formed between the valve cover 2 and the valve body 1. The edge of the diaphragm assembly 3 is clamped and fixed between the valve body 1 and the valve cover 2.

[0034] In an optional example, the diaphragm assembly 3 is made of a multilayer rubber composite material, which has good elastic deformation capacity and pressure resistance, and can withstand frequent differential pressure fluctuations without fatigue damage.

[0035] In an optional example, the valve cover 2 is provided with an upper working air port 25 for venting and depressurizing the upper chamber 21, and can be connected to an external air source control device.

[0036] In one optional example of this embodiment, the main piston 4 has a cylindrical structure, and its outer peripheral wall is sealed to the inner wall of the valve body 1 through a first sealing ring 27.

[0037] The upper chamber 21 is located above the diaphragm assembly 3, and the lower chamber 22 is located below the main piston 4.

[0038] In an optional embodiment of the present invention, a valve cavity is further provided inside the valve body 1. One end of the valve cavity is connected to the lower chamber 22, and the other end is connected to the first air intake channel 14. The valve cavity extends through the exhaust channel 16 along its extension path, forming a cross-shaped channel structure. The flow switching mechanism includes a piston connecting rod 5, a spring seat 8, and a first elastic reset member 10.

[0039] Piston connecting rod 5 passes through the valve cavity. Piston connecting rod 5 has a slender rod-like structure, and its axial direction is consistent with the extension direction of the valve cavity. An annular gap is formed between the outer peripheral wall of piston connecting rod 5 and the inner peripheral wall of the valve cavity. This annular gap constitutes a common flow channel for the second flow channel 17 and the first flow channel 18. The cross-sectional area of ​​this annular gap is much larger than the cross-sectional area of ​​the first flow channel 18, enabling it to provide a large flow of compressed air when needed.

[0040] One end of the piston connecting rod 5 is fixedly connected to the main piston 4. Specifically, the end of the piston connecting rod 5 connected to the main piston 4 is provided with a radially protruding connecting seat. The outer diameter of the connecting seat is larger than the outer diameter of the piston connecting rod 5 body. The connecting seat is sealed to the inner wall of the valve body 1, and the seal is achieved by the second sealing ring 28. The setting of this connecting seat enhances the connection strength between the piston connecting rod 5 and the main piston 4, and ensures the sealing between the piston connecting rod 5 and the valve body 1 during axial movement, preventing gas leakage from the connection.

[0041] The other end of the piston connecting rod 5 extends out of the valve chamber and is fixedly connected to the spring seat 8, which is located in the first intake passage 14.

[0042] The outer diameter of the spring seat 8 is larger than the inner diameter of the port of the valve cavity facing the first air intake channel 14.

[0043] One end of the first elastic reset member 10 abuts against the upper surface of the spring seat 8, and the other end abuts against the spring cap 9, which is positioned on the inner wall of the valve body 1 corresponding to the first air intake channel 14. Under normal conditions, the first elastic reset member 10 is in a pre-compressed state, applying an upward elastic force to the spring seat 8 to ensure that the spring seat 8 and the valve cavity port maintain a sealed contact.

[0044] Under the pressure of the upper chamber 21, the main piston 4 drives the piston connecting rod 5 to move axially, thereby causing the spring seat 8 to engage with or disengage from the port of the valve chamber, so as to cut off or open the inlet connected to the annular interval and the first intake channel 14.

[0045] In an optional example of this embodiment, the end of the first intake channel 14 connected to the valve chamber is provided with an enlarged main intake chamber 20 so that the spring seat 8 and the first elastic reset member 10 have sufficient installation space.

[0046] In an optional example, a spring cap 9 is provided on the inner wall of the valve body 1 to limit and fix the first elastic reset member.

[0047] Furthermore, the pre-compression of the first elastic reset member 10 can be adjusted by adjusting the position of the spring cover 9, thereby adjusting the operating pressure threshold of the flow switching mechanism.

[0048] In an alternative example, the first elastic reset element 10 is a compression spring.

[0049] In an optional example of this embodiment, the spring seat 8 has a disc-shaped structure, and its outer diameter is larger than the inner diameter of the port of the valve cavity facing the first intake channel 14. When the spring seat 8 is in the initial position, the bottom surface of the spring seat 8 is tightly fitted with the sealing surface of the valve cavity port to form a sealing fit. At this time, the inlet of the second flow channel 17 is completely cut off, and compressed air cannot enter the exhaust channel 16 through the second flow channel 17.

[0050] Preferably, the sealing surfaces of the spring seat 8 and the valve body 1 are made of high-molecular wear-resistant materials, which form a tight fit to ensure that the sealing performance does not decrease during long-term use.

[0051] In an optional example of this embodiment, to ensure the stable reset of the main piston 4, a second elastic reset member 11 is also provided in the lower chamber 22. One end of the second elastic reset member 11 abuts against the bottom surface of the main piston 4, and the other end of the second elastic reset member 11 abuts against and is limited to the inner wall of the valve body 1. Under normal conditions, the second elastic reset member 11 is in a pre-compressed state, applying an upward elastic force to the main piston 4. The auxiliary diaphragm assembly 3 and the first elastic reset member 10 together realize the rapid reset of the main piston 4, piston connecting rod 5, and spring seat 8.

[0052] In an alternative example, the second elastic reset member 11 is also a compression spring, and the second elastic reset member 11 is sleeved outside the connecting seat.

[0053] In an optional embodiment, the piston connecting rod 5 has a radial through groove on its end face where it connects to the spring seat 8. This radial through groove extends radially along the piston connecting rod 5, and both ends of the radial through groove communicate with the annular gap (second flow channel 17), forming a radial passage for airflow. The spring seat 8 has an axial through hole that extends axially along the spring seat 8. One end of the axial through hole communicates with the radial through groove, and the other end communicates with the main intake chamber 20, and further with the first intake channel 14. The axial through hole and the radial through groove together constitute the first flow channel 18.

[0054] In an optional example, to facilitate adjustment of the flow rate in the first flow channel 18, a flow adjustment bolt 12 is provided on the spring seat 8, which is threaded into the axial through hole of the spring seat 8. A small flow inlet hole is formed on the body of the flow adjustment bolt 12, which constitutes part of the first flow channel 18. By rotating the flow adjustment bolt 12, the relative position of the small flow inlet hole and the axial through hole can be changed, thereby adjusting the effective cross-sectional area of ​​the first flow channel 18 and achieving precise control of the small flow rate. In practical applications, a suitable basic fluidizing gas volume can be set by adjusting the flow adjustment bolt 12 according to the characteristics of the material to be fluidized and the size of the fluidizing container.

[0055] In this invention, the inner diameter of the first flow channel 18 is much smaller than the inner diameter of the second flow channel 17. Furthermore, the first flow channel 18 remains continuously connected, meaning that regardless of pressure changes within the feedback chamber, compressed air can always enter the exhaust channel 16 from the first intake channel 14 through the first flow channel 18, providing basic auxiliary fluidizing airflow. When the pressure within the feedback chamber is lower than a set threshold, the spring seat 8, under the action of the first elastic reset member 10, seals against the valve chamber port, the second flow channel 17 is closed, and compressed air can only enter the exhaust channel 16 through the first flow channel 18.

[0056] In an optional example of this implementation, a check valve is provided in the second flow channel 17 to prevent gas backflow.

[0057] In an optional example, such as Figure 1 As shown, the piston connecting rod 5 has a radially protruding positioning boss 6, which is sealed and slides with the valve body 1. The positioning boss 6 has multiple guide holes, each of which is opened along the axis parallel to the piston connecting rod 5 and opens at the upper and lower ends of the positioning boss 6. A check diaphragm 7 is provided at the upper end of the positioning boss 6. The check diaphragm 7 has a one-way conduction structure, which only allows airflow from the annular interval to the exhaust channel 16, preventing the airflow in the exhaust channel 16 from flowing back into the second flow channel 17.

[0058] In this embodiment, a check diaphragm 7 is used as the check component. The check diaphragm 7 can be made of flexible rubber material, which can bend upward and open under the push of compressed air. When the pressure in the exhaust channel 16 is higher than the pressure in the second flow channel 17, the check diaphragm 7 tightly adheres to the upper end face of the positioning boss 6 under the action of the pressure difference, realizing a reliable check function. By setting the check diaphragm 7, the backflow of material or airflow in the fluidizing container into the flow switching mechanism is effectively prevented, protecting the normal operation of the device.

[0059] In an optional embodiment of the present invention, to prevent backflow of airflow in the fluidized container or pipeline, the exhaust channel 16 is connected to the fluidized container or pipeline via a first check valve 13. The first check valve 13 is located at the outlet of the exhaust channel 16, allowing airflow only from the exhaust channel 16 to the fluidized container or pipeline, preventing airflow, material, or dust in the fluidized container or pipeline from flowing back into the fluidization booster.

[0060] In one optional example of this implementation, the first check valve 13 adopts a spring-loaded one-way valve structure, which has the characteristics of fast response speed and good sealing performance.

[0061] In an optional example of this embodiment, to facilitate monitoring and adjustment of the pressure within the feedback chamber, a feedback pressure regulating hole 24 communicating with the external environment of the valve body 1 is provided on the feedback channel 19. A pressure gauge can be installed at the feedback pressure regulating hole 24 to monitor the pressure value in the upper chamber 21 in real time; or a feedback pressure regulating bolt can be installed, and the pressure in the upper chamber 21 can be adjusted by adjusting the position or opening of the feedback pressure regulating bolt, thereby adjusting the response characteristics and operating frequency of the flow switching mechanism. In practical applications, a suitable pressure threshold and response time can be set by adjusting the feedback pressure regulating bolt at the feedback pressure regulating hole 24 according to the requirements of the fluidization process.

[0062] In this invention, such as Figure 1 As shown, the main piston 4 can drive the piston connecting rod 5 to move axially under the pressure of the upper chamber 21, thereby causing the spring seat 8 to engage with or disengage from the port of the valve chamber, so as to cut off or open the inlet connected to the annular gap (second flow channel 17) and the first intake channel 14. Specifically, when the pressure in the upper chamber 21 reaches a set threshold, the pressure overcomes the elastic force of the first elastic reset member 10 and the second elastic reset member 11, pushing the diaphragm assembly 3 to deform downward. The diaphragm assembly 3 pushes the main piston 4 to move downward. The main piston 4 drives the piston connecting rod 5 to move downward. The piston connecting rod 5 pushes the spring seat 8 to move downward and compresses the first elastic reset member 10, causing the spring seat 8 to disengage from the sealing surface of the valve chamber port. The inlet of the second flow channel 17 is opened, and compressed air can enter the exhaust channel 16 in large quantities through the second flow channel 17. When the pressure in the upper chamber 21 drops below the set threshold, the elastic force of the first elastic reset member 10 and the second elastic reset member 11 pushes the spring seat 8, piston connecting rod 5, main piston 4 and diaphragm assembly 3 to reset, the spring seat 8 re-seales with the valve chamber port, and the inlet of the second flow channel 17 is closed.

[0063] This invention also proposes a dual-intake, dual-flow adaptive intake method, comprising: The vaporized air continuously enters the exhaust passage 16 through the second intake passage 15 to achieve basic fluidization; Compressed air is directed to enter the exhaust passage 16 through the first intake passage 14 and the first flow passage 18. The pressure of the exhaust passage 16 is transmitted to the feedback actuator through the feedback passage 19; When the pressure reaches the set threshold, the feedback actuator drives the flow switching mechanism to open the second flow channel 17. The inner diameter of the second flow channel 17 is larger than that of the first flow channel 18. Compressed air enters the exhaust channel 16 through both the first flow channel 18 and the second flow channel 17 to achieve enhanced fluidization.

[0064] The present invention also proposes a dual-intake, dual-flow adaptive intake method. When the pressure of the fluidized container or pipeline is normal, only vaporized air is supplied to the exhaust channel 16 through the second intake channel 15 and a small amount of compressed air is supplied through the first flow channel 18 to achieve basic fluidization. Only when the internal pressure of the exhaust channel 16 rises to a set threshold is the second flow channel 17 automatically activated for enhanced fluidization. This segmented air supply strategy avoids continuous high-flow consumption of compressed air and significantly reduces air source energy consumption while ensuring normal delivery.

[0065] Please refer to Figure 1 The following describes in detail the specific working process of the dual-intake dual-flow adaptive fluidization booster and intake method of the present invention, with reference to an embodiment.

[0066] (1) Basic fluidization stage (low flow rate mode): When the material transport in the fluidized container or pipeline is normal, the internal pressure of the container is at a normal low pressure state. At this time, the pressure fed back through the feedback channel 19 in the upper chamber 21 is low, the diaphragm assembly 3 has not undergone significant deformation, and is in its normal initial position. Under the elastic force of the first elastic reset member 10 and the second elastic reset member 11, the main piston 4, piston connecting rod 5, and spring seat 8 are also in their normal initial positions. The sealing surface of the spring seat 8 is tightly fitted with the valve body 1, and the inlet of the second flow channel 17 is completely closed.

[0067] In this state, the aerated air generated by the aerated air system enters the exhaust channel 16 through the second intake channel 15, and then enters the fluidization container or pipeline through the first check valve 13, providing basic fluidization assistance to the material and maintaining its fluidized state. At the same time, a small portion of compressed air enters the main intake chamber 20 through the first intake channel 14, passes through the small flow intake hole in the flow regulating bolt 12 on the spring seat 8, enters the first flow channel 18, then enters the second flow channel 17 through the radial groove, pushes open the check diaphragm 7 and enters the exhaust chamber 23, and finally enters the fluidization container or pipeline through the exhaust channel 16 and the first check valve 13, providing auxiliary fluidization airflow.

[0068] In the basic fluidization stage, vaporized air provides the main fluidizing gas volume, while compressed air supplied by the first flow channel 18 serves as the auxiliary gas volume. Together, they maintain the normal fluidization state of the material. Since the compressed air only enters through the first flow channel 18, the gas volume is relatively small, resulting in low energy consumption and achieving basic fluidization in an energy-saving mode.

[0069] (2) Enhanced fluidization stage (high flow rate mode): When the internal pressure of a fluidizing container or pipeline rises sharply due to material accumulation, excessively high material level, material arching, or poor downstream conveying, the pressure difference between the external constant pressure air source and the inside of the container decreases, resulting in poor intake of vaporized air and compressed air through the first flow channel 18, thus weakening the fluidization effect.

[0070] The increased pressure inside the fluidizing container or pipeline is fed back to the upper chamber 21 through the exhaust channel 16 and the feedback channel 19. As the pressure inside the container continues to rise, the pressure inside the upper chamber 21 rises accordingly, and this pressure acts on the upper surface of the diaphragm assembly 3. When the pressure inside the upper chamber 21 reaches a set threshold, this pressure overcomes the pre-compression elastic force of the first elastic reset member 10 and the second elastic reset member 11, pushing the diaphragm assembly 3 to deform downward and generate displacement.

[0071] The downward displacement of the diaphragm assembly 3 pushes the main piston 4, which is sealed to it, downward. The downward movement of the main piston 4 causes the piston rod 5, which is fixed to it, to move downward. The downward movement of the piston rod 5 pushes the spring seat 8, which is fixed to it, downward. During the downward movement, the spring seat 8 compresses the first elastic reset member 10. When the bottom surface of the spring seat 8 disengages from the sealing surface of the valve chamber port, the inlet of the second flow channel 17 is opened, and the main intake chamber 20 communicates with the exhaust chamber 23 through the second flow channel 17.

[0072] At this time, a large amount of compressed air enters the main intake chamber 20 through the first intake channel 14, and then pushes open the check diaphragm 7 through the second flow channel 17 (i.e., the annular gap between the outer peripheral wall of the piston connecting rod 5 and the inner peripheral wall of the valve chamber) to enter the exhaust chamber 23. It then enters the fluidizing container or pipeline through the exhaust channel 16 and the first check valve 13. Because the cross-sectional area of ​​the second flow channel 17 is much larger than that of the first flow channel 18, the flow rate of the compressed air increases significantly, forming a powerful jet airflow that quickly impacts and breaks up material arches or blockages, restoring the material to a fluidized state.

[0073] During the enhanced fluidization stage, compressed air simultaneously enters the exhaust channel 16 through the first flow channel 18 and the second flow channel 17, significantly increasing the total intake volume and enhancing the fluidization intensity. This effectively addresses abnormal conditions such as material accumulation and arching, ensuring the continuous and stable operation of the material conveying system.

[0074] (3) Automatic reset process: Once the material bridging or blockage is broken and eliminated, the internal pressure of the fluidizing container or pipeline quickly returns to its normal value. The pressure fed back through the feedback channel 19 in the upper chamber 21 decreases accordingly, reducing the pressure acting on the upper surface of the diaphragm assembly 3. At this time, the elastic force of the first elastic reset member 10 and the second elastic reset member 11 is greater than the pressure in the upper chamber 21. Under the action of its own elastic force and the elastic force of the second elastic reset member 11, the diaphragm assembly 3 resets upward, pushing the main piston 4 to move upward.

[0075] The upward movement of the main piston 4 causes the piston connecting rod 5 to move upward, and the upward movement of the piston connecting rod 5 pulls the spring seat 8 upward. Under the elastic force of the first elastic reset member 10, the spring seat 8 returns to its original position until the end face of the spring seat 8 is tightly fitted with the sealing surface of the valve cavity port again, and the inlet of the second flow channel 17 is closed again.

[0076] At this point, the fluidization booster automatically reverts to the low-flow mode of the basic fluidization stage, with only vaporized air and a small flow of compressed air supplied, achieving energy-saving operation. The entire switching process is fully automated, requiring no manual intervention, and achieves adaptive adjustment based on changes in the internal pressure of the fluidization vessel.

[0077] In this embodiment, to improve the durability and sealing performance of the booster, both the spring seat 8 and the valve body 1 are made of hard alloy material, which has high strength, high wear resistance, and good dimensional stability. The sealing surfaces of the spring seat 8 and the valve body 1 are made of high-molecular wear-resistant material, which has excellent wear resistance and sealing performance, can withstand frequent opening and closing actions without wear, and ensures that the sealing performance does not decrease during long-term use, forming a tight fit between the two.

[0078] The diaphragm assembly 3 is made of a multi-layer rubber composite material, which is composed of multiple layers of rubber materials with different properties. This composite material possesses both good elastic deformation capacity and sufficient strength and pressure resistance, enabling it to withstand frequent pressure fluctuations and repeated deformation cycles without fatigue damage. By employing a multi-layer composite structure, the service life of the diaphragm assembly 3 is effectively extended, and the reliability of the device is improved.

[0079] Through the above structural optimization, the dual-intake dual-flow adaptive fluidization booster of the present invention has good sealing performance, long service life and high reliability, and can operate stably for a long time in harsh industrial environments.

[0080] In summary, this invention achieves multiple technical benefits, including energy saving, rapid response, improved fluidization effect, automated and stable operation, and high reliability, through innovative technologies such as dual-intake dual-flow adaptive regulation, diaphragm pressure feedback, dual-flow channel design, and structural optimization. It provides reliable technical support for the efficient, stable, and economical operation of fluidized conveying systems.

[0081] The dual-inlet dual-flow adaptive fluidization booster and inlet method proposed in this invention are mainly applicable to pneumatic conveying systems for powdery materials such as fly ash, cement, slag powder, limestone powder, and chemical powder that are prone to arching, agglomeration, and pipe blockage.

[0082] The detailed explanations of the above embodiments are intended only to explain the present invention so as to facilitate a better understanding of the present invention. However, these descriptions should not be construed as limiting the present invention for any reason. In particular, the various features described in different embodiments can be arbitrarily combined with each other to form other embodiments. Unless there is an explicit description to the contrary, these features should be understood to be applicable to any embodiment, and not limited to the described embodiments.

Claims

1. A fluidization booster with dual intake and dual flow rate adaptive characteristics, characterized in that, The fluidization booster includes: The valve body has an exhaust channel, a first intake channel, a second intake channel, a feedback channel, and a feedback chamber; the exhaust channel is used to communicate with a fluidized container or pipeline, the first intake channel is used to receive compressed air, the second intake channel is used to receive vaporized air, the second intake channel is connected to the exhaust channel, and the feedback channel is connected to the exhaust channel and the feedback chamber. A flow switching mechanism is disposed in the valve body. The flow switching mechanism has a first flow channel and a second flow channel. The first flow channel and the second flow channel are connected in parallel between the first intake channel and the exhaust channel. The inner diameter of the first flow channel is smaller than the inner diameter of the second flow channel. The first flow channel is always kept in a connected state. When the pressure in the feedback chamber is lower than a set threshold, the second flow channel is in a closed state. A feedback actuator is disposed within the feedback chamber. The feedback actuator can drive the flow switching mechanism to open the second flow channel when the pressure in the feedback chamber reaches a set threshold.

2. The dual-intake, dual-flow adaptive fluidization booster as described in claim 1, characterized in that, The feedback actuator includes a main piston disposed within the feedback chamber, which also has a lower working air port for exhausting gas.

3. The dual-intake, dual-flow adaptive fluidization booster as described in claim 2, characterized in that, The feedback actuator further includes a diaphragm assembly disposed within the feedback chamber. The diaphragm assembly divides the feedback chamber into an upper chamber and a lower chamber that are not interconnected. The bottom surface of the diaphragm assembly is sealed to the top surface of the main piston, and the edge of the diaphragm assembly is sealed and fixed to the inner wall of the valve body.

4. The dual-intake, dual-flow adaptive fluidization booster as described in claim 3, characterized in that, The valve body also has a valve chamber, one end of which is connected to the lower chamber, and the other end of which is connected to the first air intake channel. The valve chamber extends through the exhaust channel along its extension path. The flow switching mechanism includes a piston rod, a spring seat, and a first elastic reset member. The piston rod passes through the valve cavity, and an annular gap is formed between the outer peripheral wall of the piston rod and the inner peripheral wall of the valve cavity. The annular gap constitutes a common flow channel for the second flow channel and the first flow channel. One end of the piston rod is connected to the main piston, and the other end of the piston rod extends out of the valve cavity and contacts the spring seat. The spring seat is located in the valve cavity, and the outer diameter of the spring seat is larger than the inner diameter of the port of the valve cavity facing the first air intake channel. One end of the first elastic reset member abuts against the spring seat, and the other end of the first elastic reset member abuts against and is limited to the spring cover at the lower end of the valve body. Under the pressure of the upper chamber, the main piston drives the piston rod to move axially, thereby causing the spring seat to fit against or disengage from the port of the valve cavity, so as to cut off or open the inlet connected to the first air intake channel by the annular gap.

5. The dual-intake, dual-flow adaptive fluidization booster as described in claim 4, characterized in that, A check valve is provided within the annular gap to prevent airflow from the exhaust channel from flowing back into the annular gap.

6. The dual-intake, dual-flow adaptive fluidization booster as described in claim 4, characterized in that, The piston connecting rod has a radial through groove on its end face connected to the spring seat. The radial through groove is connected to the annular spacer. The spring seat has an axial through hole. One end of the axial through hole is connected to the radial through groove, and the other end of the axial through hole is connected to the first air intake channel. The axial through hole and the radial through groove constitute the first flow channel.

7. The dual-intake, dual-flow adaptive fluidization booster as described in claim 4, characterized in that, The end of the piston connecting rod that connects to the main piston is provided with a radially protruding connecting seat, and the connecting seat is sealed to the valve body.

8. The dual-intake, dual-flow adaptive fluidization booster as described in claim 1, characterized in that, The exhaust channel is connected to the fluidized container or pipeline via a first check valve, which prevents the backflow of airflow in the fluidized container or pipeline.

9. The dual-intake, dual-flow adaptive fluidization booster as described in claim 1, characterized in that, The feedback channel is provided with a feedback pressure adjustment hole, which can adjust the feedback pressure fed back from the feedback channel to the feedback chamber.

10. The dual-intake, dual-flow adaptive fluidization booster as described in claim 1, characterized in that, The feedback channel has an exhaust port that communicates with the external environment of the valve body, and a pressure gauge or feedback pressure adjusting bolt is installed at the exhaust port.

11. A dual-intake, dual-flow adaptive intake method, characterized in that, The dual-intake, dual-flow adaptive intake method includes: This allows vaporized air to continuously enter the exhaust channel through the second intake channel, thus achieving basic fluidization; Compressed air is introduced into the exhaust passage through the first intake passage and the first flow passage; The pressure in the exhaust passage is transmitted to the feedback actuator via the feedback channel; When the pressure reaches a set threshold, the feedback actuator drives the flow switching mechanism to open the second flow channel. The inner diameter of the second flow channel is larger than that of the first flow channel. The compressed air enters the exhaust channel simultaneously through the first flow channel and the second flow channel to achieve enhanced fluidization.

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