Multistage variable-diameter reverse-direction-reversing shaftless blade stirring type jet flow aerator and jet flow aeration method

Abstract

This invention discloses a multi-stage variable-diameter, counter-rotating, shaftless, blade-driven agitator jet aerator, comprising an inlet nozzle connected to a mixing chamber, a variable-diameter air intake unit connected to the bottom of the mixing chamber, an integrated sealing shell connected to the end of the mixing chamber away from the inlet nozzle, a turbine nozzle connected to the end of the integrated sealing shell away from the mixing chamber, and nested primary and secondary rotating sleeves connected inside the integrated sealing shell. A large impeller is connected to the inner wall of the primary rotating sleeve, and a small impeller is connected to the inner wall of the secondary rotating sleeve. This invention can not only effectively reduce the operating costs of water treatment facilities, but also further improve the efficiency of wastewater reuse and effluent quality, playing a crucial role in promoting technological upgrading and low-carbon emissions in the entire water treatment industry and wastewater treatment sector.

Description

Technical Field

[0001] This invention belongs to the technical field of wastewater treatment equipment, specifically relating to a multi-stage variable diameter, counter-rotating shaftless blade stirring jet aerator, and also to a jet aeration method for the jet aerator. Background Technology

[0002] In the field of wastewater treatment, air-supply jet aerators are an indispensable and important piece of equipment that can efficiently achieve thorough mixing of gas and liquid phases, increase the dissolved oxygen content in the treated wastewater, activate the metabolic activity of aerobic microorganisms, degrade various pollutants in water bodies, and improve the overall effect of wastewater treatment. They have outstanding engineering application value.

[0003] Air-supply jet aeration utilizes the kinetic energy of high-speed fluid to eject, pulverize, and mix air, creating gas-liquid turbulence to achieve efficient oxygen transfer and powerful mixing with wastewater within the tank. A high-pressure water pump pressurizes the wastewater-activated sludge mixture, while a blower introduces external air through an intake pipe, allowing for precise airflow control. Inside the aerator, the airflow and liquid flow violently mix, blend, and collide within the mixing chamber, resulting in a continuous and chaotic two-phase flow. Tiny bubbles are continuously generated, broken, and diffused in the wastewater. The intense turbulent vortex dynamically compresses and tears these bubbles, refining their size. Finally, the jet is ejected through the end nozzle, forming a high-speed jet stream. This jet propels the surrounding water into a large-scale circulation flow, increasing the renewal frequency of the turbulent boundary layer and the circulation energy within the tank. This makes it a preferred technology for treating high-concentration wastewater in deep tanks.

[0004] However, under current technological conditions, most wastewater treatment plants generally adopt methods such as increasing air supply pressure, adding aeration equipment, and extending operating time to improve the mass transfer efficiency and oxygenation effect of jet aerators, thereby achieving better oxygen transfer efficiency and hydrodynamic characteristics. However, all of these methods increase the overall energy consumption of the jet aerator, directly leading to a sharp increase in the economic cost, power consumption, and resistance loss of wastewater treatment. Therefore, developing a new type of jet aerator that combines low aeration energy consumption, high oxygenation efficiency, and excellent gas-liquid mixing has become a key technical problem urgently needing to be solved in the field of water pollution control. Summary of the Invention

[0005] The purpose of this invention is to provide a multi-stage variable diameter, counter-rotating shaftless blade stirring jet aerator, which solves the problem of low oxygen transfer rate in existing air-supplying jet aerators.

[0006] Another objective of this invention is to provide a jet aeration method for a multi-stage variable diameter, counter-rotating shaftless blade stirring jet aerator.

[0007] The technical solution adopted in this invention is: a multi-stage variable diameter counter-rotating shaftless blade stirring jet aerator, including an inlet spray pipe, a mixing chamber connected to the inlet spray pipe, a variable diameter air intake unit connected to the bottom of the mixing chamber, an integral sealing shell connected to the end of the mixing chamber away from the inlet spray pipe, a turbine nozzle connected to the end of the integral sealing shell away from the mixing chamber, and a first-stage rotating sleeve and a second-stage rotating sleeve nested inside the integral sealing shell, a large thrust impeller connected to the inner wall of the first-stage rotating sleeve, and a small thrust impeller connected to the inner wall of the second-stage rotating sleeve.

[0008] The invention is further characterized in that,

[0009] One end of the water inlet nozzle is configured as a convergent nozzle, which is located within the mixing chamber.

[0010] The variable diameter intake unit includes a main intake pipe. Along its length, the main intake pipe is connected to a large-diameter branch pipe, a medium-diameter branch pipe, and a small-diameter branch pipe. The large-diameter branch pipe is located near the converging nozzle of the water inlet spray pipe. The large-diameter branch pipe, the medium-diameter branch pipe, and the small-diameter branch pipe are all connected to the bottom of the mixing chamber. The angles between the pipe body of the large-diameter branch pipe, the medium-diameter branch pipe, and the small-diameter branch pipe extending into the mixing chamber and the axis of the mixing chamber are 45°, 60°, and 90°, respectively.

[0011] The ends of the large-diameter branch pipe, the medium-diameter branch pipe, and the small-diameter branch pipe that extend into the mixing chamber are respectively connected to the first swirling nozzle, the second swirling nozzle, and the third swirling nozzle.

[0012] A first thrust ball bearing and a first radial bearing, a second radial bearing and a second thrust ball bearing are connected between the outer wall of the first-stage rotating sleeve and the integrated sealing housing. The first thrust ball bearing and the first radial bearing are located near the mixing chamber, while the second radial bearing and the second thrust ball bearing are located near the second-stage rotating sleeve. A third radial bearing and a fourth radial bearing are respectively fitted onto both ends of the outer wall of the second-stage rotating sleeve. The third radial bearing is located near the first-stage rotating sleeve, and the fourth radial bearing is located near the turbine nozzle. A convex retaining ring is fitted onto the end of the second-stage rotating sleeve near the turbine nozzle, and the convex retaining ring contacts the fourth radial bearing.

[0013] The integrated sealing housing has a variable diameter structure. Three small gears are evenly connected around the variable diameter section of the integrated sealing housing. The first-stage rotating sleeve is located in the larger diameter section of the integrated sealing housing, and the second-stage rotating sleeve is located in the smaller diameter section of the integrated sealing housing. The end of the second-stage rotating sleeve is fitted with an outer wall gear, and the inner wall of the first-stage rotating sleeve is connected with an inner wall gear. The three small gears are matched with the outer wall gear and the inner wall gear.

[0014] There are three large thrust impellers, which are evenly arranged along the length of the first-stage rotating sleeve. All three large thrust impellers are connected to the inner wall of the first-stage rotating sleeve, and each large thrust impeller is equipped with five thrust blades.

[0015] Five small impellers are set up, and the five small impellers are evenly arranged along the length of the secondary rotating sleeve. All five small impellers are connected to the inner wall of the secondary rotating sleeve. Each small impeller is set with five propulsion blades. The propulsion blades of the small impellers are installed at opposite angles to the propulsion blades of the large impellers.

[0016] The turbine nozzle includes a turbine housing, an annular slide rail, and fastening bolts. One end of the turbine housing is connected to an integrated sealing housing via a flange. On the edge of the turbine housing away from the integrated sealing housing, several protrusions with central openings are evenly arranged circumferentially. A turbine is installed inside the turbine housing, with a through hole in the center. Bolt holes corresponding to the protrusions are evenly arranged circumferentially along the edge of the turbine. Countersunk bolt holes are evenly arranged circumferentially inside the annular slide rail. Fastening bolts are passed through the countersunk bolt holes and bolt holes to lock with the protrusions. Several rollers are installed in the slide rail, and each roller is connected to a connecting plate by screws. The connecting plate is connected to an annular plate by slide rail bolts. Several arc-shaped blocks are evenly connected circumferentially along the annular plate, and each arc-shaped block is connected to a claw-shaped baffle.

[0017] Another technical solution adopted in this invention is a jet aeration method for a multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator, which is implemented according to the following steps:

[0018] Step 1: Connect the inlet end of the water inlet nozzle to an external water pump using a high-pressure hose to introduce high-pressure water flow. The high-speed jet formed by the high-pressure water flow enters the mixing chamber axially.

[0019] Step 2: The blower pumps external air into the main intake pipe, and the gas is introduced into the mixing chamber through the large-diameter branch pipe, medium-diameter branch pipe and small-diameter branch pipe to mix with the high-pressure water flow.

[0020] Step 3: The gas-liquid mixture in the mixing chamber enters the integrated sealed housing and impacts the large impeller in the first-stage rotating sleeve and the small impeller in the second-stage rotating sleeve.

[0021] Step 4: The fully agitated and mixed fluid enters the turbine nozzle and is ejected.

[0022] The beneficial effects of this invention are as follows:

[0023] 1. By combining the main air intake pipe, three variable diameter air intake branches and three types of split-type swirling inclined channel nozzles, along with the super shearing effect generated by multiple sets of shaftless blades, large bubbles can be refined to the micro-nano level, effectively increasing the gas-liquid contact area and bubble residence time, thereby significantly improving the oxygen dissolution rate and mass transfer efficiency in wastewater.

[0024] 2. Multiple sets of shaftless blades eliminate the need for sealing and lubrication maintenance of the central shaft and support structure, avoiding the risk of the central shaft obstructing fluid flow and forming a low-speed vortex zone; at the same time, shaftless blades can reduce end vortices by optimizing the curved surface shape, thereby reducing energy consumption and making the stress distribution on the blades more uniform, thus extending fatigue life.

[0025] 3. The turbine nozzle separates the gas-liquid-solid multiphase mixed flow into a central jet and a circumferential circulation, which can form a three-dimensional, large-scale strong turbulent flow field in the aerobic aeration tank, completely eliminating the dead corners and blind spots existing in traditional aeration methods, and ensuring that the sludge in the tank always remains in a uniform suspended state.

[0026] 4. The overall modular design uses high-strength flanges and multiple sealing methods at the connection points. Key transmission components are encapsulated in an integrated sealed shell. The fully enclosed design prevents foreign objects from entering, is corrosion-resistant and has low wear, has a compact layout and occupies little space, has no weak connection points, has strong resistance to deformation, and has low daily maintenance costs.

[0027] 5. This air-supply jet aerator integrates repeated gas-liquid impact, mixing, cutting and propulsion, and complex extended spraying functions, which not only ensures good oxygenation and mass transfer capacity and in-tank circulation and stirring effect, but also provides a superior biological metabolic environment for the sewage treatment process, thus accelerating the technological iteration of sewage treatment. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of the overall structure of the present invention;

[0029] Figure 2 This is a cross-sectional view of the overall structure of the present invention;

[0030] Figure 3a This is a schematic diagram of the structure of the first swirling nozzle in this invention;

[0031] Figure 3b This is a schematic diagram of the structure of the first swirling nozzle in this invention;

[0032] Figure 3c This is a schematic diagram of the structure of the first swirling nozzle in this invention;

[0033] Figure 4 for Figure 1 Enlarged view of point A in the middle;

[0034] Figure 5 for Figure 1Enlarged view of point B in the middle;

[0035] Figure 6 for Figure 1 Enlarged view of point C in the middle;

[0036] Figure 7 This is an exploded axial view of the turbine nozzle in this invention;

[0037] Figure 8 This is a half-sectional view of the integrated sealing housing in this invention;

[0038] Figure 9 This is a schematic diagram of the axial section of the first-stage rotating sleeve in this invention;

[0039] Figure 10 This is a perspective view of the axial structure of the secondary rotating sleeve in this invention.

[0040] In the diagram: 1. Inlet nozzle, 2. Mixing chamber, 3. Large thrust impeller, 4. Small thrust impeller, 5. Main air inlet pipe, 6. Large-diameter branch pipe, 61. First swirl nozzle, 7. Medium-diameter branch pipe, 71. Second swirl nozzle, 8. Small-diameter branch pipe, 81. Third swirl nozzle, 9. Integrated sealing housing, 10. First-stage rotating sleeve, 11. Second-stage rotating sleeve, 12. First thrust ball bearing, 13. First radial bearing, 1 4. Second radial bearing; 15. Second thrust ball bearing; 16. Pinion; 17. Third radial bearing; 18. Fourth radial bearing; 19. Convex retaining ring; 20. Turbine housing; 21. Protrusion; 22. Turbine; 23. Bolt hole; 24. Annular slide rail; 25. Fastening bolt; 26. Connecting plate; 27. Claw-shaped retaining wing; 28. Ring plate; 29. ​​Slide rail bolt; 30. Inner wall gear; 31. Outer wall gear. Detailed Implementation

[0041] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments.

[0042] Multi-stage variable diameter, counter-rotating, shaftless blade agitator jet aerator, such as Figure 1-2As shown, it includes an inlet nozzle 1, which is connected to a mixing chamber 2. A variable diameter air intake unit is connected to the bottom of the mixing chamber 2. An integral sealing housing 9 is connected to the end of the mixing chamber 2 away from the inlet nozzle 1. A turbine nozzle is connected to the end of the integral sealing housing 9 away from the mixing chamber 2. A first-stage rotating sleeve 10 and a second-stage rotating sleeve 11 are nested inside the integral sealing housing 9. A large thrust impeller 3 is connected to the inner wall of the first-stage rotating sleeve 10, and a small thrust impeller 4 is connected to the inner wall of the second-stage rotating sleeve 11. The inlet end of the water inlet nozzle 1 is connected to an external water pump via a high-pressure hose to introduce high-pressure water flow. The middle part of the mixing chamber 2 is a circular pipe of equal diameter, and the end is a conical tapered variable diameter pipe. The cross-sectional area shrinkage can significantly increase the velocity of the multiphase mixture in a short distance, effectively converting pressure energy into kinetic energy and reducing energy loss. External air enters the mixing chamber 2 through the variable diameter air inlet unit and mixes with the high-pressure water flow. The gas-liquid mixture impacts the large thrust impeller 3 in the first-stage rotating sleeve 10 and the small thrust impeller 4 in the second-stage rotating sleeve 11, and is finally ejected by the turbine nozzle.

[0043] Example 1

[0044] One end of the water inlet nozzle 1 is configured as a converging nozzle, which is located inside the mixing chamber 2. The end of the water inlet nozzle 1 is configured as a converging nozzle, with a constricted cross-section, allowing the water flow to enter the mixing chamber 2 rapidly and with high impact.

[0045] Example 2

[0046] The variable diameter intake unit includes a main intake pipe 5. Along its length, the main intake pipe 5 is connected to a large-diameter branch pipe 6, a medium-diameter branch pipe 7, and a small-diameter branch pipe 8. The large-diameter branch pipe 6 is positioned near the converging nozzle of the water inlet spray pipe 1. The large-diameter branch pipe 6, medium-diameter branch pipe 7, and small-diameter branch pipe 8 are all connected to the bottom of the mixing chamber 2. The angles between the pipe bodies of the large-diameter branch pipe 6, medium-diameter branch pipe 7, and small-diameter branch pipe 8 extending into the mixing chamber 2 and the axis of the mixing chamber 2 are 45°, 60°, and 90°, respectively. When gas flows through the main intake pipe 5, the diameter of the main intake pipe remains constant, i.e., a constant diameter design. The gas velocity gradually decreases along the flow direction. The multi-stage variable diameter intake design, from coarse to fine, reduces the cross-sectional area of ​​the pipe as the gas flow rate decreases, helping to maintain the gas velocity within the main pipe within a relatively constant and optimal range. The reduced pipe diameter significantly decreases the pressure drop loss at the front end of the main air inlet pipe 5, maintaining the air inlet pressure at a higher and more balanced level. The gas is distributed more evenly among the branch pipes, and the uniform air inlet distribution is the basis for ensuring consistent mixing effect throughout the aeration zone. The variable pipe diameter design ensures that each branch pipe injection point from the front end of the main pipe to the end can provide relatively consistent and effective gas injection energy. The turbulent shear field, bubble distribution, and oxygen mass transfer efficiency in the aeration tank are more uniform and efficient, avoiding the problems of insufficient or excessive aeration in certain areas. This stepped multi-stream air inlet method fundamentally improves the gas-liquid uniformity in the primary mixing stage, laying the foundation for subsequent deep shearing and refinement.

[0047] Example 3

[0048] like Figures 3a-3c As shown, the ends of the large-diameter branch pipe 6, medium-diameter branch pipe 7, and small-diameter branch pipe 8 that extend into the mixing chamber 2 are respectively connected to a first swirling nozzle 61, a second swirling nozzle 71, and a third swirling nozzle 81. The first swirling nozzle 61 includes four nozzle groups, with adjacent nozzle groups arranged perpendicularly to each other. Each nozzle group has four parallel strip-shaped nozzles. The second swirling nozzle 71 includes three nozzle groups, which are arranged at an angle to each other. Each nozzle group has four parallel strip-shaped nozzles. The third swirling nozzle 81 includes parallel and intersecting strip-shaped nozzles. The gas introduced by the small-diameter branch pipe 8 supplements the mixing blind zone and avoids the air blockage phenomenon caused by concentrated airflow. The slit swirling nozzle structures of each level of air intake branch pipe are different, guiding the gas to form multiple swirling streams that collide with the main water flow at different angles, increasing the turbulent mixing intensity. The design of different pipe diameters for air intake can achieve the consistency requirements of parameters such as flow rate, velocity, and pressure.

[0049] Example 4

[0050] like Figure 4-6As shown, a first thrust ball bearing 12 and a first radial bearing 13, a second radial bearing 14 and a second thrust ball bearing 15 are connected between the outer wall of the first-stage rotating sleeve 10 and the integral sealed housing 9. The first thrust ball bearing 12 and the first radial bearing 13 are located near the mixing chamber 2, and the second radial bearing 14 and the second thrust ball bearing 15 are located near the second-stage rotating sleeve 11. A third radial bearing 17 and a fourth radial bearing 18 are respectively sleeved at both ends of the outer wall of the second-stage rotating sleeve 11. The third radial bearing 17 is located near the first-stage rotating sleeve 10, and the fourth radial bearing 18 is located near the turbine nozzle. A convex retaining ring 19 is sleeved at the end of the second-stage rotating sleeve 11 near the turbine nozzle, and the convex retaining ring 19 contacts the fourth radial bearing 18. The first thrust ball bearing 12, the second thrust ball bearing 15, the first radial bearing 13, and the second radial bearing 14 respectively bear the axial force of the liquid flow impacting the first-stage rotating sleeve 10 and the radial force generated by the high-speed rotation of the sleeve; the third radial bearing 17 and the fourth radial bearing 18 are used to support the rapid rotation of the second-stage rotating sleeve 11. The convex retaining ring 19 axially positions the fourth radial bearing 18. The inner ring of the fourth radial bearing 18 is axially fixed by the convex retaining ring 19 through bolts to fasten the flange of the turbine housing 20, and the outer ring is axially fixed by the right end face of the integrated sealing housing 9 to prevent axial movement during operation.

[0051] Example 5

[0052] like Figure 8-10 As shown, the integrated sealing housing 9 has a variable diameter structure. Three small gears 16 are evenly connected along the circumference of the variable diameter section of the integrated sealing housing 9. The first-stage rotating sleeve 10 is located in the larger diameter section of the integrated sealing housing 9, and the second-stage rotating sleeve 11 is located in the smaller diameter section of the integrated sealing housing 9. An outer wall gear 31 is sleeved on the end of the second-stage rotating sleeve 11, and an inner wall gear 30 is connected to the inner wall of the first-stage rotating sleeve 10. The three small gears 16 are matched with the outer wall gear 31 and the inner wall gear 30. The inner wall gear 30 of the first-stage rotating sleeve 10 and the outer wall gear 31 of the second-stage rotating sleeve 11 mesh synchronously and precisely with three small gears 16 fixed in the integrated sealed housing 9 and circumferentially distributed at 120°, forming a planetary gear structure. The simultaneous meshing of multiple teeth shares the torque, improving the load-bearing capacity and transmission efficiency of the structure. When the first-stage rotating sleeve 10 rotates due to the impact of the gas-liquid two-phase flow, the torque is reversed and changed in speed through the small gears 16. The inner wall gear 30 drives the small gears 16 to rotate in the opposite direction, and the small gears 16 drive the outer wall gears 31 to rotate synchronously, driving the second-stage rotating sleeve 11 to rotate at a higher speed, thereby making the first-stage rotating sleeve 10 and the second-stage rotating sleeve 11 rotate in opposite directions.

[0053] The left flange of the integrated sealing housing 9 is aligned with the right flange of the mixing chamber 2 of the initial gas-liquid two-phase impact module. A rubber sealing ring is embedded between the flange faces, and pre-tightened bolts are symmetrically tightened to ensure uniform force distribution, preventing warping or deformation and exhibiting high rigidity and fatigue resistance. This prevents connection failure due to loosening, achieving dual sealing protection through a combination of metal hard seal and rubber soft seal. The secondary rotating sleeve 11 with an outer wall gear 31 on the left end is coaxially nested inside the primary rotating sleeve 10 with an inner wall gear 30 machined on the right end. The primary rotating sleeve 10 and the flange connection of the mixing chamber 2 form multiple barriers through multiple layers of sealing rubber rings, which can gradually reduce the pressure gradient, reduce the load on the single-stage seal, avoid single-point failure, reduce leakage risk, and extend service life. The secondary rotating sleeve 11 and the primary rotating sleeve 10 also adopt a multiple sealing structure to increase the leakage path length, slow down the medium penetration rate, form an internal sealing barrier, and eliminate gas-liquid leakage, enabling the aeration equipment to adapt to the complex and harsh working conditions of sewage treatment.

[0054] Example 6

[0055] There are three large thrust impellers 3, which are evenly arranged along the length of the first-stage rotating sleeve 10. All three large thrust impellers 3 are connected to the inner wall of the first-stage rotating sleeve 10, and each large thrust impeller 3 is equipped with five thrust blades.

[0056] Five small thrust impellers 4 are evenly arranged along the length of the secondary rotating sleeve 11. Each small thrust impeller 4 is connected to the inner wall of the secondary rotating sleeve 11. Each small thrust impeller 4 has five thrust blades, and the installation angle of the thrust blades of the small thrust impeller 4 is opposite to that of the thrust blades of the large thrust impeller 3. When the fluid flows along the curved surface of the blades, it generates a continuous impact on the thrust blades, forming a strong axial thrust, which is then converted into the rotational motion of the sleeve, continuously pushing the fluid forward. When the large thrust impeller 3 is impacted by the water flow and drives the primary rotating sleeve 10 to rotate, the torque is reversed and accelerated via the pinion 16, driving the outer wall gear 31 to drive the secondary rotating sleeve 11 to rotate in the opposite direction at a higher speed. At this time, the small thrust impellers 4 push out the gas-liquid mixture at high speed and prevent fluid backflow. Furthermore, the opposing inclination angles of the impeller blades in the large and small impellers (3 and 4) generate different axial and radial composite multiphase flows, promoting continuous up-and-down tumbling and circulation of the gas, liquid, and solid phases. The installation angle can also be adjusted according to specific stirring requirements and mixing characteristics. This shaftless impeller blade design completely eliminates the problem of blockage caused by fibers or hair entangled on the main shaft during rotation, giving it a significant advantage when treating sludge containing a large amount of ribbon-like material or highly viscous sludge. Simultaneously, due to the absence of a central main shaft, the shaftless impeller blades can more fully utilize the stirring space to achieve a wider range of cutting and mixing. During rotation, the gas-liquid contact interface is larger, creating a more uniform turbulent stirring effect throughout the jet aerator, avoiding the dead zones of gas-liquid mixing that may exist near the central shaft position with impeller blades. For activated sludge containing large-particle bacterial flocs, the shaftless impeller blades facilitate smoother shearing and crushing, avoiding obstruction by the main shaft and allowing smooth passage through the two-stage rotating sleeve mixing zone, ensuring the continuity and stability of oxygenation and mass transfer. The large velocity gradient within the narrow gap generates strong shear stress on the bubble surface, initially breaking large bubbles into smaller ones. The vortex formed by the reverse rotation further tears the bubbles, causing their diameter to continuously shrink. The high-speed bubbles continuously collide with each other, effectively preventing bubble coalescence. Ultimately, this achieves the micro-refinement of bubbles from millimeters to micrometers or even nanometers. The gas-liquid contact surface area increases exponentially, and the oxygen molecule mass transfer rate and dissolution efficiency are significantly improved, effectively solving the pain point of low mass transfer efficiency in traditional aerator structures.

[0057] Example 7

[0058] like Figure 7As shown, the turbine nozzle includes a turbine housing 20, 21, protrusions, a turbine 22, 23, bolt holes, an annular slide rail 24, fastening bolts 25, a connecting plate 26, claw-shaped baffles 27, annular plate 28, and slide rail bolts 29. One end of the turbine housing 20 is connected to the integrated sealing housing 9 via a flange. Several protrusions 21 with central openings are evenly arranged circumferentially along the edge of the turbine housing 20 away from the integrated sealing housing 9. A turbine 22 is installed inside the turbine housing 20. The center of the turbine 22 is configured as a through hole, and the edge of the turbine 22 is evenly provided with protrusions that correspond to the central openings. The annular slide rail 24 has corresponding bolt holes 21 and 23. Countersunk bolt holes are evenly distributed around its circumference. Fastening bolts 25 pass through these countersunk bolt holes, bolt holes 23, and the centrally located protrusion 21 to lock the turbine 22 to the turbine housing 20. Several rollers are installed within the slide rail 24, each connected to a connecting plate 26 by screws. The connecting plate 26 is then fastened. A ring plate 28 is connected to the connecting plate 26 by slide rail bolts 29. Several arc-shaped blocks are evenly connected around the ring plate 28, each connected to a claw-shaped baffle 27. The track allows for circumferential rotation within the annular slide rail 24. The arc-shaped blocks and the grooved claw-shaped baffles 27 are locked together by bolts. The angle between the grooved claw-shaped baffles 27 and the arc-shaped blocks can be adjusted to accommodate different circumferential scattering patterns under various operating conditions. The turbine nozzle is fastened to the right end outlet of the integrated sealed housing 9 via a flange connection. The gas-liquid mixture, after being fully cut, chopped, and refined, finally enters the circumferential claw-shaped baffle turbine scattering nozzle. The fluid first impacts the guide channel on the turbine 22. The angle and shape of the guide channel precisely control the direction of the gas-liquid-solid multiphase flow entering the turbine 22, ensuring that the fluid enters the turbine 22 at the optimal angle and that the mixture acts uniformly on the turbine 22 blades. The special shape of the guide vanes also accelerates the gas-liquid-solid flow mixture. When the fluid passes through the guide vanes, the channel between the vanes gradually reduces the flow area of ​​the multiphase flow. According to the principles of fluid mechanics, the multiphase flow velocity will increase accordingly, converting part of the fluid's pressure energy into rotational kinetic energy, which can provide greater power to the turbine 22, increase the output power of the turbine 22, and form a strong swirling flow. The powerful swirling flow drives the circumferentially distributed claw-shaped baffles 27 to rotate. During the rotation, the claw-shaped baffles 27 will have a strong disturbance effect on the multiphase flow, causing the fluid to generate a complex turbulent state, increasing the contact area of ​​the gas, liquid and solid phases, breaking the stability of the phase interface and constantly renewing it, accelerating the mass transfer and mixing speed. The rotating baffles also enable solid particles to be better suspended and dispersed in the sewage, preventing particle agglomeration and improving the mixing effect between oxygen-enriched gas, sewage flow and sludge particles.In the gas-liquid mixed jet, the turbulence generated by the claw-shaped baffles 27 promotes more uniform dispersion of bubbles in the mixture, improves the diffusion consistency of the refined bubble group, avoids local hypoxia or hyperxia, and achieves more precise and balanced mixing of dissolved oxygen and matter. This ensures a relatively balanced dissolved oxygen concentration throughout the aeration treatment area, which is beneficial for aerobic microorganisms to carry out metabolic decomposition activities in a stable environment. Furthermore, the circumferentially arranged claw-shaped baffles 27 effectively control the jet direction and distribution of the multiphase flow. By adjusting the airfoil shape and angle, the gas-liquid-solid mixed flow is jetted according to the expected direction and pattern. The resulting annular diffusion flow range can generate a strong churning effect on the water body, ensuring thorough mixing of organic matter, microorganisms, and nutrients in the wastewater. This helps increase the contact probability between microorganisms and organic matter, accelerates the biochemical reaction rate, and thus improves the overall wastewater treatment effect. The circumferentially arranged claw-shaped baffles 27 can suppress the relative movement between phases through the generated turbulence and shear force, reducing phase separation and gas-liquid stratification. The circumferentially arranged claw-shaped baffles 27 diffuser nozzles generate additional energy input to the multiphase flow during rotation, giving the gas-liquid-solid three phases a greater initial velocity during injection. This increases the spray range and coverage, creating a strong hydraulic circulation in the treatment tank. This ensures sufficient residence time for the wastewater, avoiding dead zones and short-circuiting issues, and eliminating the performance problems of traditional aeration equipment such as "near-field concentration saturation and insufficient far-field aeration." The core fluid in the central section, not propelled by centrifugal force, is channeled through a pre-reserved opening in the center of the turbine 22 to create a high-energy, highly penetrating jet. This jet breaks the stagnant state of the deep water in the axial direction of the aerator, preventing activated sludge from accumulating at the bottom of the tank and maintaining sludge activity and fluidity.

[0059] Example 8

[0060] The jet aeration method of a multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator is implemented according to the following steps:

[0061] Step 1: The inlet end of the water inlet nozzle 1 is connected to an external water pump using a high-pressure hose to introduce high-pressure water flow. The high-speed jet formed by the high-pressure water flow enters the mixing chamber 2 axially.

[0062] Step 2: The blower pumps external air into the main intake pipe 5. The gas is then introduced into the mixing chamber 2 through the large-diameter branch pipe 6, the medium-diameter branch pipe 7, and the small-diameter branch pipe 8 to mix with the high-pressure water flow.

[0063] Step 3: The gas-liquid mixture in the mixing chamber 2 enters the integrated sealed housing 9 and impacts the large impeller 3 in the first-stage rotating sleeve 10 and the small impeller 4 in the second-stage rotating sleeve 11.

[0064] Step 4: The fully agitated and mixed fluid enters the turbine nozzle and is ejected.

[0065] The working principle of the multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator of the present invention is as follows:

[0066] The water pump is turned on to inject high-pressure water into the inlet nozzle 1. When the high-pressure water flows through the converging inlet nozzle, its cross-sectional area decreases and its velocity increases significantly. The resulting high-speed jet enters the mixing chamber 2 axially. At the same time, the blower pumps external air into the main air intake pipe 5. The gas passes through the three-stage variable-diameter air intake branch pipes to ensure the consistency of flow velocity and pressure. Each air intake branch pipe outlet has a segmented narrow-slit swirling nozzle with a specific extension angle, generating multiple streams of swirling air intake kinetic energy. These ordered swirling streams collide and disperse with the main water intake stream at multiple gradients, completing the initial mixing of the gas and liquid phases. The gas-liquid mixture enters the integrated sealed housing 9 and impacts the first-stage large thrust impeller 3 at the front end of the first-stage rotating sleeve 10. The liquid flow impact force is converted into the rotational torque of the cylinder, driving the first-stage rotating sleeve 10 to rotate. This torque is transmitted and reversed by three small gears 16 symmetrically distributed at 120° circumference. Due to the difference in transmission ratio between the inner wall gear 30 and the outer wall gear 31, the second-stage rotating sleeve 11 is driven to rotate in the opposite direction at a higher speed. When the two-stage sleeves rotate at high speed in opposite directions, the large velocity gradient within the narrow annular gap generates strong shearing and tearing effects, effectively breaking large bubbles into micro-nano-sized microbubble clusters and significantly increasing the gas-liquid contact surface area. Due to their opposing tilt angles, the thrust blades of the multi-stage large thrust impeller 3 and small thrust impeller 4 generate significant axial thrust during the stirring and shearing process, continuously forcing the multiphase fluid to move axially, preventing fluid backflow and localized accumulation and blockage within the pipe, and ensuring smooth shearing and mixing of the mixture. The thoroughly agitated and mixed fluid enters the turbine nozzle. The liquid flow first impacts the turbine 22, converting some of its pressure and kinetic energy into rotational mechanical energy. This drives the circumferentially distributed claw-shaped baffles 27 to rotate at high speed around the axis. The rotating claw-shaped baffles 27 generate a strong centrifugal force, which disperses and stirs along the tangential direction, forming a more extensive annular diffusion layer. The central jet maintains a strong flow velocity and forms a penetrating disturbance cycle in the far field of the jet through the central opening of the turbine 22. This composite diffusion mode, combining circumferential scattering and core jet, induces oxygen to be distributed more widely and evenly in the wastewater, significantly increasing the contact area between the gas and liquid phases. This means that the rate at which oxygen and other substances are transferred from the gas phase to the liquid phase is faster, significantly improving the mass transfer efficiency during aeration. This allows more oxygen to dissolve into the water, meeting the oxygen requirements of microorganisms in the biological treatment process. Circumferential scattering causes the gas to form more dispersed small bubbles in the wastewater. The rising path of these small bubbles is more tortuous, which prolongs the residence time of the gas in the liquid compared to a single core jet. This causes turbulence and mixing in the liquid over a larger area, continuously breaking the phase separation and stratification phenomenon in multiphase mixed flow, and allowing the three phases to mix thoroughly. This composite jet mode can more effectively transfer jet energy to the wastewater, making full use of energy in the gas-liquid mixing and mass transfer process, reducing energy consumption and waste, lowering the energy consumption and cost of the aeration process, ensuring the water quality balance in the entire aeration treatment area, and improving wastewater treatment efficiency and water quality stability.

[0067] The multi-stage variable diameter, counter-rotating shaftless blade stirring jet aerator of this invention can not only effectively reduce the operating cost of water treatment facilities, but also further improve the efficiency of wastewater reuse and the quality of effluent. It plays a vital role in promoting the technological upgrading and low-carbon emission of the entire water treatment industry and wastewater treatment sector.

Claims

1. A multi-stage variable-diameter counter-rotating shaftless blade agitated jet aerator, characterized in that, Includes an inlet nozzle (1), which is connected to a mixing chamber (2). The bottom of the mixing chamber (2) is connected to a variable diameter air intake unit. An integral sealing shell (9) is connected to the end of the mixing chamber (2) away from the inlet nozzle (1). A turbine nozzle is connected to the end of the integral sealing shell (9) away from the mixing chamber (2). The interior of the integral sealing shell (9) is connected to a first-stage rotating sleeve (10) and a second-stage rotating sleeve (11) nested together. A large thrust impeller (3) is connected to the inner wall of the first-stage rotating sleeve (10), and a small thrust impeller (4) is connected to the inner wall of the second-stage rotating sleeve (11). The variable diameter air intake unit includes a main air intake pipe (5). The main air intake pipe (5) is connected to a large diameter branch pipe (6), a medium diameter branch pipe (7), and a small diameter branch pipe (8) along its length. The large diameter branch pipe (6) is located near the converging nozzle of the water inlet spray pipe (1). The large diameter branch pipe (6), the medium diameter branch pipe (7), and the small diameter branch pipe (8) are all connected to the bottom of the mixing chamber (2). The angles between the pipe body of the large diameter branch pipe (6), the medium diameter branch pipe (7), and the small diameter branch pipe (8) extending into the mixing chamber (2) and the axis of the mixing chamber (2) are 45°, 60°, and 90°, respectively. The ends of the large-diameter branch pipe (6), medium-diameter branch pipe (7) and small-diameter branch pipe (8) that extend into the mixing chamber (2) are respectively connected to the first swirling nozzle (61), the second swirling nozzle (71) and the third swirling nozzle (81). The turbine nozzle includes a turbine housing (20), an annular slide rail (24), and fastening bolts (25). One end of the turbine housing (20) is connected to the integrated sealing housing (9) via a flange. A number of protrusions (21) with central openings are evenly arranged along the circumference of the edge of the turbine housing (20) away from the integrated sealing housing (9). A turbine (22) is provided inside the turbine housing (20). The center of the turbine (22) is configured as a through hole. The edge of the turbine (22) is evenly provided with protrusions (21) corresponding to each other along its circumference. The bolt holes (23) are evenly provided in the annular slide rail (24) along its circumference. The bolt holes (23) are locked to the protrusion (21) by fastening bolts (25) passing through the countersunk bolt holes. Several rollers are provided in the slide rail (24). Each roller is connected to a connecting plate (26) by screws. The connecting plate (26) is connected to a ring plate (28) by slide rail bolts (29). Several arc-shaped blocks are evenly connected to the ring plate (28) along its circumference. Each arc-shaped block is connected to a claw-shaped baffle (27).

2. The multi-stage variable-diameter hetero-directional reverse turning shaftless blade-agitating jet aerator according to claim 1, characterized in that, One end of the water inlet nozzle (1) is configured as a converging nozzle, and the converging nozzle of the water inlet nozzle (1) is located in the mixing chamber (2).

3. The multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator according to claim 1, characterized in that, The outer wall of the first-stage rotating sleeve (10) is connected to the integral sealed housing (9) by a first thrust ball bearing (12), a first radial bearing (13), a second radial bearing (14), and a second thrust ball bearing (15). The first thrust ball bearing (12) and the first radial bearing (13) are located near the mixing chamber (2), and the second radial bearing (14) and the second thrust ball bearing (15) are located near the second-stage rotating sleeve (11). The outer ends of the second-stage rotating sleeve (11) are respectively fitted with a third radial bearing (17) and a fourth radial bearing (18). The third radial bearing (17) is located near the first-stage rotating sleeve (10), and the fourth radial bearing (18) is located near the turbine nozzle. The end of the second-stage rotating sleeve (11) near the turbine nozzle is fitted with a convex retaining ring (19), which contacts the fourth radial bearing (18).

4. The multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator according to claim 3, characterized in that, The integrated sealing housing (9) has a variable diameter structure. Three small gears (16) are evenly connected around the variable diameter section of the integrated sealing housing (9). The first-stage rotating sleeve (10) is located in the larger diameter section of the integrated sealing housing (9), and the second-stage rotating sleeve (11) is located in the smaller diameter section of the integrated sealing housing (9). An outer wall gear (31) is sleeved on the end of the second-stage rotating sleeve (11), and an inner wall gear (30) is connected to the inner wall of the first-stage rotating sleeve (10). The three small gears (16) are matched with the outer wall gear (31) and the inner wall gear (30).

5. The multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator according to claim 1, characterized in that, The large thrust impeller (3) is configured as three, and the three large thrust impellers (3) are evenly arranged along the length direction of the first-stage rotating sleeve (10). The three large thrust impellers (3) are all connected to the inner wall of the first-stage rotating sleeve (10), and each large thrust impeller (3) is configured as five thrust blades.

6. The multi-stage variable diameter, counter-rotating, shaftless blade stirring jet aerator according to claim 1, characterized in that, The five small impellers (4) are arranged evenly along the length of the secondary rotating sleeve (11). The five small impellers (4) are all connected to the inner wall of the secondary rotating sleeve (11). Each small impeller (4) is equipped with five impeller blades. The installation angle of the impeller blades of the small impellers (4) is opposite to that of the impeller blades of the large impeller (3).

7. The jet aeration method of the multi-stage variable diameter counter-rotating shaftless blade stirring jet aerator according to any one of claims 1-6, characterized in that, The specific steps are as follows: Step 1: The inlet end of the water inlet nozzle (1) is connected to an external water pump using a high-pressure hose to introduce high-pressure water flow. The high-speed jet formed by the high-pressure water flow enters the mixing chamber (2) axially. Step 2: The blower pumps external air into the main intake pipe (5), and the gas is introduced into the mixing chamber (2) through the large-diameter branch pipe (6), the medium-diameter branch pipe (7) and the small-diameter branch pipe (8) to mix with the high-pressure water flow; Step 3: The gas-liquid mixture in the mixing chamber (2) enters the integrated sealed housing (9) and impacts the large impeller (3) in the first-stage rotating sleeve (10) and the small impeller (4) in the second-stage rotating sleeve (11). Step 4: The fully agitated and mixed fluid enters the turbine nozzle and is ejected.

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