Efficient deodorization and oil fume purification all-in-one machine

Abstract

The application relates to the technical field of oil fume aerosol purification, and discloses a high-efficiency oil fume purification all-in-one machine, which comprises a machine shell, a main air duct shell is arranged at the top of the machine shell, the main air duct shell is rotationally connected with a central main shaft through two upper and lower supports, the central main shaft is driven to rotate by a driving motor, a centrifugal turbine impeller and a spiral corrugated rotor are sequentially sleeved and fixedly connected to the outer wall of the central main shaft, the spiral corrugated rotor is located above the centrifugal turbine impeller, an acoustic stator ring is arranged around the periphery of the spiral corrugated rotor, and the acoustic stator ring is fixedly connected to the inner wall of the main air duct shell; an alternating gap is left between the outer circumferential surface of the spiral corrugated rotor and the inner side surface of the acoustic stator ring. Through high-frequency pneumatic coupling between the spiral corrugated rotor and a resonance microcavity, a high-energy ultrasonic standing wave field is established in the alternating gap, and high-efficiency deep deodorization is realized without the need of consumables such as activated carbon.

Description

Technical Field

[0001] This invention relates to the field of oil fume aerosol purification technology, specifically to an integrated oil fume purification machine with high efficiency deodorization. Background Technology

[0002] In the fields of commercial catering waste gas treatment and industrial high-viscosity aerosol purification, the efficient separation and degradation of gaseous volatile organic compounds and submicron-sized heavy oil droplets in multiphase mixed fluids has always been a highly challenging core problem at the intersection of multiphase fluid mechanics and environmental engineering.

[0003] Existing fume purification equipment, when dealing with complex multiphase flow fields, generally falls into a technological path dependence of over-reliance on physical interception and chemical adsorption consumables. This traditional treatment mode has a fundamental structural defect at the macroscopic fluid dynamics level. When a mixture of exhaust gas containing high concentrations of viscous oil and gaseous odor molecules is forcibly drawn through porous media (such as activated carbon filters, metal interwoven labyrinth plates, or electrostatic dust collection plates), submicron-sized oil particles will rapidly collide violently and irreversibly condense and adhere within these intricate micropores. As the equipment operates over time, these continuously accumulating and extremely viscous liquid deposits will cause severe pore blockage, leading to an exponential surge in the aerodynamic pressure drop within the system.

[0004] This unavoidable physical obstruction not only causes a sharp decrease in exhaust flow, but more critically, the trapped heavy oil layer will reverse and envelop the active surfaces responsible for adsorbing gaseous odor molecules. Free volatile organic compounds, having lost their effective adsorption boundary, can only penetrate the interception layer directly into the atmosphere as a gaseous co-flow, causing the deodorization efficiency to plummet within a very short operating cycle. To maintain even a minimum level of purification efficiency, users must shut down the machine extremely frequently and disassemble and replace these expensive and difficult-to-clean physical consumables.

[0005] Even though some high-end equipment attempts to introduce dynamic centrifugal separation mechanisms to use high-speed vortexes to eject liquid oil droplets, they are often limited by the simple macroscopic mechanical centrifugal force, and can only separate large-scale liquid particles. For gaseous odor substances closely accompanied by the airflow and ranging in size from the molecular to submicron scale, macroscopic mechanical inertial forces are powerless. These odor molecules move like ghosts through the macroscopic vortex and cannot be effectively forced to undergo phase transformation. Summary of the Invention

[0006] To address the shortcomings of existing technologies, this invention provides an integrated oil fume purification machine with high efficiency in deodorization, solving the problems of traditional purification equipment being extremely dependent on physical consumables, prone to viscous blockage, and having low efficiency in intercepting gaseous odor molecules.

[0007] To achieve the above objectives, the present invention provides the following technical solution: a high-efficiency deodorizing integrated fume purification machine, comprising a casing, a main air duct shell disposed on the top of the casing, the main air duct shell being rotatably connected to a central main shaft via upper and lower supports, the central main shaft being driven to rotate by a drive motor, a centrifugal turbine impeller and a spiral corrugated rotor being sequentially fitted and fixedly connected to the outer wall of the central main shaft, with the spiral corrugated rotor positioned above the centrifugal turbine impeller, and an acoustic stator ring being arranged around the spiral corrugated rotor and fixedly connected to the main air duct. An alternating gap is left between the outer circumferential surface of the spiral corrugated rotor and the inner surface of the acoustic stator ring on the inner wall of the casing. The centrifugal turbine impeller is used to push the multiphase mixed oil fume airflow upward into the alternating gap. Multiple resonant microcavities are opened on the inner surface of the acoustic stator ring. When the spiral corrugated rotor rotates at high speed, it periodically cuts off the airflow in the alternating gap to generate alternating aerodynamic pulses. The alternating aerodynamic pulses sweep the resonant microcavities and generate an acoustic standing wave field, which forces the gaseous odor molecules in the airflow to undergo acoustic wave aggregation in the acoustic standing wave field and physically transform into liquid dirt.

[0008] Preferably, the main air duct housing is a through exhaust channel, and the bottom of the housing has an air intake channel connected to the exhaust channel. A liquid collection guide groove is provided on the lower part of the inner wall of the main air duct housing, located radially outside the centrifugal turbine impeller, for collecting large oil particles thrown onto the inner wall by the centrifugal turbine impeller. The bottom of the liquid collection guide groove has an inclined structure and a main oil outlet is provided at the lowest point. A circular array of guide baffles is provided above the opening of the liquid collection guide groove. The guide baffles are inclined at an acute angle to the horizontal plane to physically shield the oil accumulated in the liquid collection guide groove and guide the airflow upward.

[0009] Preferably, the inner surface of the acoustic stator ring is further provided with acute-angle shear teeth. Multiple acute-angle shear teeth and multiple resonant microcavities are arranged alternately in an array along the circumferential direction of the acoustic stator ring. The multiphase mixed oil fume gas flow entering the alternating gap is mechanically sheared under the high-frequency geometric interference of the spiral corrugated rotor and the acute-angle shear teeth, and then transformed into submicron-level aerosols that enter the acoustic standing wave field.

[0010] Preferably, the integrated fume purification unit further includes a sewage discharge module, which includes a capillary drainage slit and an annular liquid collection manifold. The resonant microcavity is a blind-end cavity recessed towards the back of the acoustic stator ring. The capillary drainage slit radially penetrates the solid wall of the acoustic stator ring. The inlet of the capillary drainage slit is located at the lowest edge of the bottom wall of the resonant microcavity, and the outlet is connected to the annular liquid collection manifold fixedly mounted on the back of the acoustic stator ring.

[0011] Preferably, the bottom wall of the resonant microcavity is a solid structure with continuous main body, which is used to form an acoustic total reflection boundary. The entrance position of the capillary drainage slit is anchored at the acoustic displacement node of the acoustic standing wave field, so that the liquid contaminants generated by phase change in the resonant microcavity are driven by the centrifugal dynamic pressure generated by the high-speed swirling flow, and are forced into and flow through the capillary drainage slit in one direction, thereby achieving the separation and discharge of liquid contaminants without destroying the macroscopic acoustic rigidity of the microcavity.

[0012] Preferably, the bottom wall of the resonant microcavity is a smooth transition arc surface that is recessed towards the back of the acoustic stator ring. The smooth transition arc surface is used in the acoustic force field to geometrically focus the ultrasonic frequency band sound energy of total reflection into the internal space of the resonant microcavity to enhance the aggregation of sound waves. At the same time, it eliminates the right-angle vortex dead zone inside the resonant microcavity at the fluid dynamic level, and guides the liquid contaminants pushed by centrifugal dynamic pressure to slide and converge unimpeded along the curvature of the arc surface to the entrance of the capillary drainage slit.

[0013] Preferably, the sewage discharge module further includes a gravity liquid seal conduit, the upper end of which is connected to the annular liquid collection manifold and the main oil drain port, the pipe body extends downward and passes through the main air duct shell, and a U-shaped liquid seal section is provided on the pipe body path.

[0014] Preferably, the U-shaped liquid seal section contains a stationary liquid column, and the gravity hydrostatic pressure generated by the stationary liquid column is used to block the external atmospheric pressure, so that it forms a hydrostatic balance with the Bernoulli local low pressure generated when the fluid flows through the alternating gap, thereby forming a unidirectional fluid barrier to prevent external air from flowing back along the capillary drainage slit.

[0015] Preferably, when the liquid waste continuously collected in the annular collection manifold flows into the gravity liquid seal conduit, the additional gravitational potential energy of the newly added waste liquid breaks the original hydrostatic pressure balance and naturally pushes open the resident liquid column, so that the overflowing liquid waste is discharged unidirectionally into the waste oil collection device connected to the end of the gravity liquid seal conduit.

[0016] Preferably, the outer circumferential surface of the spiral corrugated rotor is provided with macroscopically axisymmetric multi-head spiral grooves. When the multi-head spiral grooves rotate with the central main shaft, they cooperate with the acoustic stator ring to form a high-frequency chopping interface. At the same time, they provide secondary axial flow boosting thrust for the pure airflow after phase change deodorization to overcome the system fluid pressure drop and discharge along the top of the main air duct shell. This invention provides a highly efficient integrated fume purification and deodorization machine. It has the following beneficial effects: 1. This invention establishes a high-energy ultrasonic standing wave field within an alternating gap through high-frequency aerodynamic coupling between a helical corrugated rotor and a resonant microcavity. This feature utilizes the acoustic agglomeration effect to force gaseous odor molecules to undergo a physical phase transition and polymerize into a liquid state, fundamentally solving the problem of traditional filtration technologies' inability to intercept molecular-level volatile organic compounds, achieving highly efficient deep odor removal without the need for consumables such as activated carbon. The alternating sharp-angle shear teeth on the inner side of the acoustic stator ring provide extremely high-frequency rigid boundary shear force for the fumes entering the core area. This structure, combined with sub-millimeter-level extrusion channels, can rapidly mechanically break down large-particle fume clusters into sub-micron-level aerosols, greatly increasing the microscopic surface area of ​​the multiphase fluid. This not only provides an ideal kinetic premise for subsequent acoustic phase transitions but also significantly improves the uniformity and thoroughness of the overall purification.

[0017] 2. This invention achieves energy-free directional drainage of liquid products by precisely positioning capillary drainage slits at the acoustic displacement nodes of the sound field within the resonant microcavity. This design ensures that the waste liquid generated during phase change can be discharged instantly in accordance with centrifugal pressure difference without causing acoustic energy escape or aerodynamic pressure drop fluctuations. Combined with the passive overflow mechanism of the gravity liquid seal conduit, the system constructs a fully static, maintenance-free drainage closed loop, avoiding the reliability risk of mechanical valves easily jamming in viscous environments.

[0018] 3. This invention utilizes multi-headed spiral grooves integrated on the surface of the spiral corrugated rotor to perform secondary axial flow pressurization on the airflow during high-speed rotation, achieving in-situ pressure compensation. This feature effectively counteracts the local aerodynamic resistance caused by the microscopic purification structure, ensuring that the fluid maintains sufficient axial dynamic pressure when passing through an extremely narrow acoustic zone. This aerodynamic compensation logic guarantees that the exhaust flow rate does not decrease while maintaining high-intensity purification, thus balancing purification depth and smoke extraction intensity.

[0019] 4. This invention completely eliminates easily saturated and clogged physical interception media by employing a physical purification path based on energy field conversion. The mechanical micro-oscillation characteristics of the high-energy sound field endow the core components with a natural self-cleaning function, effectively inhibiting the deposition of contaminants on the walls of the resonant microcavity and shear zone. This non-contact purification logic ensures that the acoustic resonant frequency and aerodynamic efficiency of the equipment remain constant under long-term, high-concentration, complex oil fume conditions, greatly extending the reliability of the equipment throughout its entire life cycle. Attached Figure Description

[0020] Figure 1 This is a perspective view of the present invention; Figure 2 This is a side sectional view of the housing in this invention; Figure 3 This is a schematic diagram of the internal structure of the main air duct shell in this invention; Figure 4 for Figure 3 Enlarged view of point A in the middle; Figure 5 This is a three-dimensional sectional view of the central main axis in this invention; Figure 6 This is a schematic diagram of the central spindle in this invention.

[0021] Among them, 1. Housing; 101. Air intake channel; 2. Main air duct housing; 201. Liquid collection guide groove; 202. Flow guide baffle; 3. Support; 4. Drive motor; 5. Central main shaft; 6. Centrifugal turbine impeller; 7. Spiral corrugated rotor; 701. Multi-head spiral groove; 8. Acoustic stator ring; 9. Resonance microcavity; 10. Acute angle shear teeth; 11. Capillary drainage slit; 12. Annular liquid collection manifold; 13. Gravity liquid seal conduit; 1301. U-shaped liquid seal section. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] Please see the appendix Figure 1 -Appendix Figure 6 This invention provides a highly efficient integrated fume purification machine for deodorization. It aims to achieve deep gas-liquid separation and gaseous odor degradation of multiphase oil fume airflow through a pneumatic-acoustic coupling mechanism, without the need for filter consumables. It includes a casing 1, with a main air duct casing 2 on the top. The main air duct casing 2 is rotatably connected to a central main shaft 5 via two upper and lower supports 3. The central main shaft 5 is driven to rotate by a drive motor 4. A centrifugal turbine impeller 6 and a spiral corrugated rotor 7 are sequentially fitted and fixedly connected to the outer wall of the central main shaft 5, with the spiral corrugated rotor 7 positioned above the centrifugal turbine impeller 6. An acoustic stator ring 8 surrounds the spiral corrugated rotor 7 and is fixedly connected to the inner wall of the main air duct casing 2. An alternating gap is left between the circumferential surface and the inner surface of the acoustic stator ring 8. The centrifugal turbine impeller 6 is used to push the multiphase mixed oil fume airflow upward into the alternating gap. Multiple resonant microcavities 9 are opened on the inner surface of the acoustic stator ring 8. When the spiral corrugated rotor 7 rotates at high speed, it periodically cuts off the airflow in the alternating gap to generate alternating aerodynamic pulses. The alternating aerodynamic pulses sweep the resonant microcavities 9 and generate an acoustic standing wave field, which forces the gaseous odor molecules in the airflow to undergo acoustic wave aggregation in the acoustic standing wave field and physically transform into liquid dirt.

[0024] In this embodiment, the main air duct housing 2 forms the outer contour and fluid envelope boundary of the entire unit, and defines a longitudinally penetrating exhaust channel inside. The bottom of the exhaust channel is defined as the intake port of the original oil fume airflow, and the top is defined as the exhaust port of the purified airflow. The main air duct housing 2 not only serves as a rigid constraint on fluid flow, but also bears the physical support function for the internal power components and acoustic units.

[0025] The drive motor 4 is securely mounted inside the main air duct housing 2. To ensure mechanical stability under high-speed rotation, the drive motor 4 is vertically anchored to the central axis of the main air duct housing 2 via a high-rigidity bracket 3. The power output end of the drive motor 4 is connected to a longitudinally extending central spindle 5 via a coupling or a one-piece molding process, transmitting rotational kinetic energy to the core working area.

[0026] The centrifugal turbine impeller 6 and the helical corrugated rotor 7 are coaxially fixed on the central main shaft 5 and rotate synchronously with the central main shaft 5. The centrifugal turbine impeller 6 is located on the air intake side near the bottom of the main air duct shell 2, and its blade geometry is constructed to generate a strong axial negative pressure suction force and a tangential swirling flow field.

[0027] The helical corrugated rotor 7 is located above the centrifugal turbine impeller 6, and its spatial position is in the central core area of ​​the exhaust duct. The outer circumferential surface of the helical corrugated rotor 7 exhibits a periodically undulating corrugated topological feature. Correspondingly, the acoustic stator ring 8 is rigidly fixed to the inner wall of the main air duct shell 2, and tightly surrounds the helical corrugated rotor 7 in a coaxial manner.

[0028] A very narrow annular gap, known as an alternating gap, is precisely defined between the outer circumferential surface of the helical corrugated rotor 7 and the inner surface of the acoustic stator ring 8. The radial width of this alternating gap is strictly controlled within a specific range at the millimeter level to ensure that an extremely high speed gradient and pressure pulsation can be formed between the rotating rotor boundary and the stationary stator boundary.

[0029] Multiple resonant microcavities 9 are machined on the inner surface of the acoustic stator ring 8, arranged in a circumferential array. When the drive motor 4 drives the central spindle 5 to rotate at high speed, the physical boundary of the outer edge of the helical corrugated rotor 7 sweeps across the opening of the resonant microcavities 9 at an extremely high linear velocity. This rotational motion generates alternating aerodynamic pulses with a constant fundamental frequency within the alternating gap, thereby inducing Helmholtz acoustic resonance in the resonant microcavities 9.

[0030] This power transmission architecture, based on the coaxial layout of the central main shaft 5, ensures that the lower centrifugal turbine impeller 6 can provide a stable pre-swirling flow field for the upper helical corrugated rotor 7 while performing high-flow-rate fluid suction and initial centrifugal capture. The precise spatial topological relationship between each rotating component and the stationary acoustic stator ring 8 forms the physical foundation for subsequent aeroacoustic coupling and phase change deodorization actions.

[0031] The overall power distribution logic of the machine aims to achieve the tiered utilization of fluid energy. The mechanical energy input by the drive motor 4 is converted into the initial kinetic energy and pressure potential energy of the fluid through the centrifugal turbine impeller 6, and then further converted into local high-frequency acoustic energy through the helical corrugated rotor 7. This evolution of energy form from macroscopic mechanical motion to microscopic acoustic energy field supports the unique technical path of the system to physically phase-change stripping odor molecules.

[0032] The main duct housing 2, drive motor 4, central spindle 5, and acoustic stator ring 8 are positioned using high-precision flanges or threaded structures, ensuring minimal coaxiality deviation between the spiral corrugated rotor 7 and the acoustic stator ring 8 during full-speed operation. This robust physical architecture fundamentally locks in the stability of the alternating pneumatic pulse excitation frequency, guaranteeing consistent odor removal performance even in extremely complex oil fume environments.

[0033] The main air duct housing 2 has a through exhaust channel inside. The bottom of the housing 1 has an air intake channel 101, which is connected to the exhaust channel. The lower part of the inner wall of the main air duct housing 2, and located on the radial outer side of the centrifugal turbine impeller 6, is provided with a liquid collection guide groove 201, which is used to collect large oil particles thrown to the inner wall by the centrifugal turbine impeller 6. The bottom of the liquid collection guide groove 201 has an inclined structure and the lowest point has a main oil outlet. Above the opening of the liquid collection guide groove 201, there is a circumferentially distributed baffle plate 202. The baffle plate 202 is inclined at an acute angle to the horizontal plane, which is used to physically shield the oil accumulated in the liquid collection guide groove 201 and guide the airflow upward.

[0034] The centrifugal turbine impeller 6 serves as the primary power element and inertial separation mechanism after the multiphase fluid enters the equipment. When the drive motor 4 drives the central main shaft 5 to rotate the centrifugal turbine impeller 6 at high speed, a strong axial negative pressure is generated at the intake at the bottom of the main air duct housing 2, which forces the original oil fume mixture containing large heavy oil droplets and gaseous odor molecules into the air.

[0035] The mixed airflow entering the main duct shell 2 is given extremely high tangential kinetic energy under the mechanical drive of the centrifugal turbine impeller 6, thus creating a high-speed rotating tangential vortex field in the lower region of the exhaust duct. Macroscopic oil particles with large mass inertia in the airflow undergo significant radial deflection under the action of extremely strong radial centrifugal force, eventually penetrating the gas phase and directly impacting the inner wall of the main duct shell 2.

[0036] The inner wall of the main air duct shell 2 is constructed as a physical interception and collection boundary for large oil particles. Liquid oil droplets impacting the wall surface, due to the fluid's viscosity and its wetting properties on the metal surface, form a continuously distributed liquid film and coalesce. As the liquid film accumulates, it is guided by gravity to flow longitudinally downwards along the wall surface, achieving pre-load reduction and separation before the mixed airflow enters the upper core acoustic treatment area.

[0037] On the lower inner wall of the main air duct casing 2, and in a spatial position radially outward of the centrifugal turbine impeller 6, a liquid-collecting guide channel 201 is provided, circumferentially distributed around the inner wall. The opening of the liquid-collecting guide channel 201 is open upward, used to collect and trap all liquid phase oil stains sliding down from the upper wall surface. The bottom of the liquid-collecting guide channel 201 has an inclined structure with a preset slope. This non-horizontal bottom topology ensures that highly viscous oil can flow in a directional manner under gravity.

[0038] The liquid collection guide trough 201 has a main oil drain port at its lowest point to discharge the collected macroscopic oil sludge into the flow channel environment. The main oil drain port is physically connected to the downstream sewage discharge module through an independent branch pipeline. As the centrifugal turbine impeller 6 generates a local high-pressure zone at its outer edge during rotation, this local pressure couples with the hydrostatic pressure of the fluid in the liquid collection guide trough 201, further enhancing the driving force for the high-viscosity oil to flow towards the main oil drain port.

[0039] To prevent the collected large oil particles from undergoing secondary failure in the complex turbulent environment, a circular array of guide baffles 202 is integrally installed above the opening of the liquid collection guide channel 201. Each guide baffle 202 is inclined at a specific acute angle to the horizontal plane, and its inclination direction is adapted to the swirling direction generated by the centrifugal turbine impeller 6.

[0040] The flow guide baffle 202 plays a dual role in fluid control. On the one hand, as a pneumatic flow guide element, the flow guide baffle 202 guides the originally chaotic rising airflow to conform to the inclined surface and transform it into a stable spiral rising airflow, reducing the energy loss of the airflow before entering the subsequent alternating gap; on the other hand, the flow guide baffle 202 forms a physical shield for the liquid collection guide trough 201 in space, effectively preventing the oil sludge accumulated in the trough from being splashed again or re-entrained into the gas phase flow field under the friction or suction of the high-speed rotating airflow.

[0041] The collaborative design of the liquid collection guide trough 201 and the flow guide baffle 202 ensures the system's interception efficiency and retention stability for macroscopic liquid pollutants. Through this purely physical inertial capture mechanism, the system completes the initial purification of large-sized particles in oil fumes without the aid of any porous filter media, thus physically avoiding the risk of the subsequent high-precision acoustic resonance microcavity 9 being directly filled with large-particle oil sludge.

[0042] Macroscopic oil sludge discharged from the main oil outlet ultimately flows into the unified sewage discharge system of the entire unit. This gravity- and centrifugal combined capture scheme complements the upper-level molecular-level deodorization scheme based on acoustic standing waves. The immediate removal of large oil particles not only ensures the unobstructed flow of internal channels but also provides a relatively clean aerosol environment for subsequent core aeroacoustic coupling actions, ensuring the long-term operational reliability of the entire unit under extreme heavy oil fume loads.

[0043] The inner surface of the acoustic stator ring 8 is also provided with acute-angle shear teeth 10. Multiple acute-angle shear teeth 10 and multiple resonant microcavities 9 are arranged alternately in an array along the circumference of the acoustic stator ring 8. The multiphase mixed oil fume gas flow entering the alternating gap is mechanically sheared under the high-frequency geometric interference of the spiral corrugated rotor 7 and the acute-angle shear teeth 10, and then transformed into submicron-level aerosols that enter the acoustic standing wave field.

[0044] The spiral corrugated rotor 7 and the acoustic stator ring 8 are spatially highly matched, and the tightly defined alternating gap between them forms a sub-millimeter to millimeter-level compression and shear flow channel. When the mixed gas flow containing aerosol-like oil droplets enters this region from the initial vortex field below, the fluid is forcibly accelerated in an extremely narrow radial space, establishing an extremely high velocity gradient and local Reynolds number, laying the dynamic foundation for subsequent microscopic separation.

[0045] Multiple sharp-angled shearing teeth 10 are protruding from the inner surface of the acoustic stator ring 8. These shearing teeth are evenly arranged circumferentially, with their tips pointing towards the central main shaft 5 and maintaining a very small gap with the outer edge of the helical corrugated rotor 7. When the helical corrugated rotor 7 passes over the stationary sharp-angled shearing teeth 10 at a speed of several thousand revolutions per minute, the macroscopic viscous oil fume agglomerates entering the alternating gap are subjected to intense and continuous rigid boundary shearing. This high-frequency mechanical tearing action forces the oil fume agglomerates to rapidly disintegrate, instantly transforming from micron-sized droplets into submicron-sized aerosols that are more prone to phase change.

[0046] The outer circumference of the helical corrugated rotor 7 is not a flat cylindrical surface, but rather exhibits a periodically undulating corrugated geometry. This corrugated structure, under high-speed rotation, generates a chopping effect on the continuous flow field within the alternating gap. Each corrugation peak, as it passes over the stator's inner wall, performs an instantaneous compression and release of the local fluid. This mechanical chopping effect converts the originally stable fluid kinetic energy into high-frequency alternating aerodynamic pulses, causing the total pressure and static pressure within the gap to exhibit violent periodic fluctuations.

[0047] The acute-angle shear teeth 10 and the resonant microcavities 9 are arranged alternately along the circumference of the acoustic stator ring 8. This alternating arrangement ensures a sequential processing of the fluid at the microscopic level: the mixed fluid is first mechanically fragmented by the acute-angle shear teeth 10, and then a high-frequency pneumatic pulse carrying kinetic energy immediately sweeps across the adjacent resonant microcavities 9. This compact topology eliminates kinetic energy loss between different processing stages, ensuring that the high-frequency pneumatic pulse can activate the acoustic resonance within the cavity with the highest energy density.

[0048] The rotational frequency of the helical corrugated rotor 7 achieves precise aerodynamic coupling with the geometric dimensions of the cavity array on the acoustic stator ring 8. By adjusting the number and rotational speed of the rotor's outer circumference corrugations, the fundamental frequency of the generated aerodynamic pulses is matched with the natural frequency of the resonant microcavity 9. Under this frequency-aligned condition, the alternating gap not only serves as a physical channel for fluid flow but also acts as a modulator for high-energy sound field excitation, efficiently pumping mechanical rotational energy into the microscopic acoustic energy level, providing the necessary excitation source for the subsequent acoustic aggregation of odor molecules.

[0049] At the outlet side of the alternating gap, the fluid is in a highly turbulent and high-frequency pulsating state. The corrugated geometry of the helical corrugated rotor 7 not only provides shearing force, but its periodic oblique structure also imparts an upward axial component force to the fluid. This aerodynamic feature ensures that the sheared and fragmented multiphase fluid can quickly pass through the acoustic action zone, preventing highly viscous substances from stagnating inside the narrow gap. Through this precisely designed mechanical shearing and aerodynamic chopping logic, the system achieves preliminary physical modification of the complex oil fume phase without the aid of any chemical additives.

[0050] The acoustic stator ring 8 is anchored to the inner wall of the main air duct shell 2 by a high-precision circumferential positioning device, locking the geometric symmetry of the alternating gap. The stability of this physical constraint directly determines the constancy of the shear frequency and chopping frequency, enabling the equipment to maintain a consistent acoustic excitation intensity when processing oil fumes of different concentrations, demonstrating the robustness of the aeroacoustic architecture under actual complex working conditions.

[0051] The acute-angle shear teeth 10 and the resonant microcavity 9 on the inner surface of the acoustic stator ring 8 typically employ a multi-layered axially stacked topology. This multi-layered design aims to create a "cascaded shearing" effect along the upward path of the fluid. As the oil fume gas flows upward axially, it passes through shear zones at different height levels in sequence, with each layer of acute-angle shear teeth 10 performing a high-frequency physical breakup of the aerosol clusters. This repetitive shearing mechanism ensures that even oil fume particles located at the center of the flow field or escaping due to turbulence can be thoroughly broken up during multiple passages through the alternating gaps.

[0052] When employing a multi-layered structure, adjacent layers of acute-angled shear teeth 10 can be arranged in a staggered displacement pattern (misaligned array) in the circumferential direction. This misaligned arrangement forcibly alters the linear trajectory of the fluid during its axial ascent, inducing strong radial pulsations. In this way, after the airflow is sheared by the first layer of shear teeth, the resulting micro-vortices immediately impact the windward surface of the second layer of toothed structure, thereby greatly improving the mechanical efficiency of mechanical shearing and the uniformity of acoustic excitation, and avoiding the penetration effect caused by incomplete fluid treatment in a single layer.

[0053] The number of layers of acute-angle shear teeth 10 is matched with the axial height of the helical corrugated rotor 7. During rotation, the corrugated topology of the helical corrugated rotor 7 simultaneously covers all tooth layers. This means that the system synchronously generates high-frequency aerodynamic pulses throughout the entire axially overlapping area. This multi-layered acoustic field distribution expands the effective treatment volume within the exhaust duct several times, significantly increasing the residence time of odor molecules in the ultrasonic standing wave field, thereby locking in a higher phase change conversion rate.

[0054] To meet the purification requirements of different power levels, the acoustic stator ring 8 can be constructed by axially stacking multiple standardized toothed ring modules. This modular, multi-layered design allows for flexible adjustment of the purification depth by increasing or decreasing the number of toothed ring layers. In conditions handling heavy commercial cooking fumes, increasing the number of acute-angle shear teeth 10 layers can significantly enhance the system's ability to degrade large organic molecules. Under light loads or domestic conditions, a single-layer or fewer-layer structure helps reduce motor drive resistance, achieving an optimal balance in energy efficiency.

[0055] Regardless of whether a single-layer or multi-layer arrangement is used, the geometric parameters of each layer of acute-angle shear teeth 10 maintain a high degree of consistency to ensure that the acoustic resonance frequency of the entire machine tends to be synchronized at different height positions. This precise constraint at the physical level constitutes the core technical support for the present invention to maintain a high deodorization rate even under complex frequency conversion conditions.

[0056] The integrated fume purification unit also includes a sewage discharge module, which includes a capillary drainage slit 11 and an annular liquid collection manifold 12. The resonant microcavity 9 is a blind-end cavity recessed towards the back of the acoustic stator ring 8. The capillary drainage slit 11 radially penetrates the solid wall of the acoustic stator ring 8. The inlet of the capillary drainage slit 11 is opened at the lowest edge of the bottom wall of the resonant microcavity 9, and the outlet is connected to the annular liquid collection manifold 12 fixedly covered on the back of the acoustic stator ring 8.

[0057] The bottom wall of the resonant microcavity 9 is a continuous solid structure used to form an acoustic total reflection boundary. The entrance position of the capillary drainage slit 11 is anchored at the acoustic displacement node of the acoustic standing wave field, so that the liquid contaminants generated by phase change in the resonant microcavity 9 are driven by the centrifugal dynamic pressure generated by the high-speed swirling flow, and are forced into and flow through the capillary drainage slit 11 in one direction, thereby achieving the separation and discharge of liquid contaminants without destroying the macroscopic acoustic rigidity of the microcavity.

[0058] Multiple resonant microcavities 9, located on the inner surface of the acoustic stator ring 8, are forced to oscillate violently within their internal air columns after receiving alternating aerodynamic pulses generated by the rotation of the helical corrugated rotor 7. Because the geometric volume and opening neck dimensions of the resonant microcavities 9 are acoustically impedance-tuned, they are excited to generate Helmholtz resonance at specific pulsating frequencies, thereby inducing a highly concentrated high-frequency acoustic energy field within the cavity and at its opening boundaries.

[0059] The sound field excited within the resonant microcavity 9 exhibits significant standing wave characteristics in its spatial distribution, with its oscillation frequency locked in the ultrasonic band. This standing wave field in the ultrasonic band possesses extremely large sound pressure gradients and sound displacement amplitudes, forcing free-state odor molecules, which are carried at high speed through the alternating gap by the airflow, to undergo intense micromechanical oscillations upon entering the standing wave-affected zone. Under the extremely high-frequency reciprocating displacement, the odor molecules, originally in a gas-phase diffuse state, collide frequently due to a sudden increase in kinetic energy, triggering a strong acoustic aggregation effect.

[0060] Through the acoustic agglomeration effect, diffusely distributed gaseous odor molecules physically condense with submicron-sized oil mist aerosols that have been fragmented by pre-stage mechanical shearing. This microscopic interaction forcibly disrupts the gaseous flow characteristics of odor substances, causing them to undergo a forced physical phase transition from a gaseous to a liquid state, ultimately dissolving and encapsulating them in the viscous liquid contaminants after condensation and polymerization. This process achieves highly efficient retention of volatile organic compounds from a purely physical perspective, solving the problem of traditional purification technologies' inability to intercept molecular-level pollutants.

[0061] This phase-change deodorization principle, based on aeroacoustic coupling, completely eliminates the physical dependence on filter consumables such as activated carbon or chemical catalysis. Because the deodorization process occurs within the microscopic dynamics of the fluid, the system avoids the technical defects of active site saturation or microscopic pore blockage. While performing its purification function, the high-energy sound field's high-frequency mechanical oscillation energy effectively suppresses static wall adhesion within the resonant microcavity, maintaining the geometric accuracy of the acoustic resonant chamber and ensuring the consistent purification efficiency of the entire unit during long-term operation.

[0062] By nonlinearly coupling the rotational speed of the helical corrugated rotor 7 with the geometric parameters of the resonant microcavity 9, the sound field intensity generated by the system can cover the entire particle size range from gaseous molecules to submicron droplets. This purely physical phase change deodorization path not only improves the thoroughness of odor degradation but also significantly reduces the aerodynamic pressure drop during system operation by reducing the physical interception layer in the fluid path, achieving a high energy efficiency fluid purification goal.

[0063] The bottom wall of the resonant microcavity 9 is a smooth transition arc surface that is recessed towards the back of the acoustic stator ring 8. In the acoustic field, the smooth transition arc surface is used to geometrically focus the ultrasonic frequency band sound energy of total reflection into the internal space of the resonant microcavity 9 to enhance the aggregation of sound waves. At the same time, at the fluid dynamic level, it eliminates the right-angle vortex dead zone inside the resonant microcavity 9 and guides the liquid dirt pushed by centrifugal dynamic pressure to slide and converge to the entrance of the capillary drainage slit 11 without hindrance, following the curvature of the arc surface.

[0064] The bottom wall of the resonant microcavity 9 is constructed as a smooth transition arc surface that is recessed towards the back of the acoustic stator ring 8. The geometric curvature of this arc surface is designed to further focus the sound field energy through sound wave reflection, ensuring that the maximum sound pressure level is locked in the central axis region of the resonant microcavity 9, thereby maximizing acoustic coverage of the passing airflow. At the same time, the smooth transition arc surface provides a fluid guiding surface without dead angles, ensuring that under the continuous centrifugal dynamic pressure within the alternating gap, the liquid contaminants generated by phase change can slide directionally towards the edge of the resonant microcavity 9 in accordance with the curvature of the arc surface.

[0065] The sewage discharge module also includes a gravity liquid seal conduit 13. The upper end of the gravity liquid seal conduit 13 is connected to the annular liquid collection manifold 12 and the main oil drain port, respectively. Its pipe body extends downward and passes through the main air duct shell 2, and a U-shaped liquid seal section 1301 is provided on the pipe body path.

[0066] The U-shaped liquid seal section 1301 contains a stationary liquid column. The gravity hydrostatic pressure generated by the stationary liquid column is used to block the external atmospheric pressure, so that it forms a hydrostatic balance with the Bernoulli local low pressure generated when the fluid flows through the alternating gap, thereby forming a unidirectional fluid barrier to prevent external air from flowing back into the capillary drainage slit 11.

[0067] When the liquid waste continuously collected in the annular collection manifold 12 flows into the gravity liquid seal conduit 13, the gravitational potential energy of the newly added waste liquid breaks the original hydrostatic pressure balance and naturally pushes open the stationary liquid column, so that the overflowing liquid waste is discharged unidirectionally into the waste oil collection device connected to the end of the gravity liquid seal conduit 13.

[0068] Phase-change liquid contaminants induced by the ultrasonic standing wave field continuously accumulate on the inner wall of the resonant microcavity 9. Driven by the extremely high centrifugal dynamic pressure generated by the rotation of the helical corrugated rotor 7, these highly viscous liquid products strictly conform to the geometric curvature of the smooth transition arc surface, and slide unimpeded directionally towards the edge region at the bottom of the resonant microcavity 9. This self-driven transport mechanism dominated by the aerodynamic pressure field ensures that the liquid components can be instantly removed from the core acoustic action area, physically preventing the accumulation of liquid from encroaching on the acoustic field resonant volume.

[0069] A capillary drainage slit 11 is radially penetrated through the solid wall of the acoustic stator ring 8. The inlet end of the capillary drainage slit 11 is precisely anchored to the lowest edge of the smooth transition arc surface. This spatial arrangement utilizes the inertia of fluid motion in a high-speed swirling flow field, allowing the contaminant squeezed to the edge of the cavity to flow smoothly into the slit channel. The radial length of the capillary drainage slit 11 completely penetrates the overall thickness of the acoustic stator ring 8, forming a microfluidic drainage path connecting the internal pneumatic processing space and the external static collection space.

[0070] The inlet position of the capillary slit 11 is precisely tuned to the acoustic displacement node of the standing wave field within the resonant microcavity 9 through rigorous tuning of its acoustic modal characteristics. At the acoustic displacement node, the gas particle velocity is extremely low, and the sound pressure amplitude is at its extreme value. This means that opening a venting channel at this location will not cause acoustic energy escape or drastic fluctuations in aerodynamic energy consumption. This design not only ensures that liquid contaminants smoothly penetrate the wall under continuous centrifugal force but also ensures that the acoustic quality factor of the resonant microcavity 9 does not significantly decrease due to physical openings, maintaining the efficient conversion capability of the standing wave energy field for odor molecules.

[0071] The annular liquid collection manifold 12, fixedly mounted on the back of the acoustic stator ring 8, provides a unified circumferential collection cavity for the waste liquid discharged from all resonant microcavities 9. The internal hollow cavity of the annular liquid collection manifold 12 is physically connected to the outlet end of each capillary drainage slit 11. When the liquid waste generated by phase change is pressed through the solid wall of the acoustic stator ring 8, it directly enters this fully enclosed liquid collection space, achieving physical isolation from the high-speed airflow field in the main air duct. This eliminates the technical risk of the separated liquid waste being secondary fragmented under high-speed turbulence and re-entrained into the exhaust channel.

[0072] The cross-sectional area of ​​the annular collection manifold 12 is non-uniformly distributed along the direction of gravity. This topology aims to guide the collected wastewater to gather at the bottom outlet of the manifold using its accumulated mass inertia. The aspect ratio of the capillary slit 11 is optimized, utilizing the surface tension of the liquid to form a natural gas barrier layer, further assisting the acoustic displacement nodes in locking the sound field. Through this integrated solution based on precise acoustic node positioning and microfluidic pressure relief, the system achieves efficient deodorization while constructing a self-cleaning liquid-phase drainage closed loop, ensuring the continuity and stability of the purification process.

[0073] The annular manifold 12 not only serves as a physical collector for waste liquid, but its outer shell structure also acts as a shield to aid in noise reduction, further suppressing the outward diffusion of specific frequency noise generated by the alternating gap. By topologically associating microscopic acoustic nodes with macroscopic discharge channels, this invention solves the technical problem in traditional purification devices where collected oil fumes and dirt are difficult to discharge in a timely and directional manner and easily interfere with the flow field, supporting maintenance-free operation of the entire unit under extremely high concentrations of oil fumes.

[0074] The outer circumferential surface of the spiral corrugated rotor 7 is provided with a macroscopically axially symmetrical multi-head spiral groove 701. When the multi-head spiral groove 701 rotates with the central main shaft 5, it works with the acoustic stator ring 8 to form a high-frequency chopping interface. At the same time, it provides secondary axial flow boosting thrust for the pure airflow after phase change deodorization to overcome the system fluid pressure drop and discharge along the top of the main air duct shell 2.

[0075] In addition to serving as the excitation source for high-frequency aerodynamic pulses, the helical corrugated rotor 7 also functions as an aerodynamic booster and pressure compensation unit on its outer circumferential surface. The outer circumferential surface of the helical corrugated rotor 7 is provided with axisymmetrically distributed multi-headed helical grooves 701. These grooves extend along the rotor's axial direction at a specific helical angle, and their geometry is constructed as a miniature propeller array. Under high-speed rotation, these grooves can significantly guide and propel the airflow passing through the alternating gap.

[0076] The depth and width of the multi-head spiral groove 701 have been optimized through flow field simulation to form a miniature axial flow booster channel together with the inner wall of the acoustic stator ring 8. When the airflow enters the alternating gap from the centrifugal turbine impeller 6 below, the fluid inevitably experiences severe local resistance loss due to the extremely narrow gap size. The spiral corrugated rotor 7, through the rotating multi-head spiral groove 701 on its surface, directly converts the mechanical energy of the drive motor 4 into the axial kinetic energy of the fluid, thereby achieving in-situ aerodynamic head compensation within the critical acoustic purification zone.

[0077] The spiral direction of the multi-head spiral groove 701 matches the rotation direction of the drive motor 4, ensuring that the physical boundary of the groove can generate an upward exhaust pressure head during rotation. This secondary axial flow boosting mechanism effectively offsets the additional aerodynamic pressure drop caused by the setting of the sharp-angle shear teeth 10, the resonant microcavity 9, and the ultra-narrow gap, ensuring that the overall exhaust flow does not decrease while maintaining high-intensity acoustic purification output, thus maintaining the effective suction of the system under actual cooking conditions.

[0078] The multi-headed spiral groove 701 also enhances turbulent mixing during rotation. By introducing controlled spiral disturbances into the boundary layer, the multi-headed spiral groove 701 disrupts the laminar flow tendency of the fluid on the surface of the acoustic stator ring 8, allowing odor molecules in the oil fume airflow to more fully enter the core acoustic field region of the resonant microcavity 9. This synergistic effect of aerodynamic compensation and enhanced mixing further increases the probability of acoustic agglomeration of gaseous pollutants per unit time, improving the system's purification efficiency when handling large volumes of oil fumes.

[0079] The multi-head spiral structure of the helical corrugated rotor 7 also possesses a significant self-cleaning auxiliary function. Under the powerful axial shear force generated by high-speed rotation, the multi-head spiral grooves 701 can utilize the high-speed scouring effect of airflow to prevent some of the tiny droplets generated by phase change from statically depositing on the rotor surface. This pneumatically self-driven surface cleaning logic, combined with the aforementioned centrifugal sewage discharge design, ensures that the core purification components maintain precise geometric surfaces even after long-term operation, guaranteeing the long-term stability of the aeroacoustic coupling frequency.

[0080] The outlet end of the multi-head spiral groove 701 smoothly connects to the upper area of ​​the exhaust channel. Through the non-linear design of the spiral rise angle, the rotational kinetic energy of the fluid can be partially recovered and converted into stable axial climbing pressure when leaving the alternating gap. This precise flow field control method ensures that the purified air can be discharged from the machine at a constant rate, fundamentally solving the problem of exhaust obstruction caused by the complex internal structure of traditional oil fume purification equipment, and demonstrating the technical balance achieved by this solution between aerodynamic efficiency and purification intensity.

[0081] In this embodiment, the dynamic working logic of the integrated high-efficiency deodorizing fume purification machine begins with the drive motor 4 driving the central main shaft 5 and its rotating components into a preset high-speed working state. When the multiphase mixed fume airflow is forcibly drawn in through the intake port at the bottom of the main air duct shell 2, the fluid first establishes a high-energy swirling field through the centrifugal turbine impeller 6. During this process, large oil droplets with high mass inertia are thrown towards the wall under the action of strong radial centrifugal force and converge into the liquid collection guide trough 201, completing the first-stage physical interception of liquid-phase pollutants.

[0082] The airflow, after primary purification, is continuously propelled by the centrifugal turbine impeller 6 into the upper acoustic purification core area. As the airflow passes through the narrow boundary formed by the acute-angle shear teeth 10, the oil fume clusters within are mechanically fragmented, transforming from a macroscopic scale into a finer aerosol state. Subsequently, the high-speed rotating helical corrugated rotor 7 physically chops the airflow within the alternating gap, generating controlled high-frequency aerodynamic pulses. These pulses generate aeroacoustic coupling with the resonant microcavities 9 within the acoustic stator ring 8, inducing high-intensity ultrasonic standing wave fields within the cavity and at the gap edges.

[0083] When gaseous odor molecules pass through the aforementioned ultrasonic standing wave field, they undergo a violent acoustic aggregation effect due to the combined effects of the sound pressure gradient and the reciprocating displacement of particles. Molecular-level pollutants collide and aggregate with micro aerosols, rapidly undergoing a physical phase transition from the gas phase to the liquid phase. Driven by the centrifugal dynamic pressure generated by the helical corrugated rotor 7, these newly generated liquid contaminants slide outward along the smooth transition arc surface inside the resonant microcavity 9, and precisely penetrate the wall through the capillary drainage slits 11 opened at the acoustic displacement nodes, ultimately flowing into the annular liquid collection manifold 12.

[0084] While performing deep purification, the system utilizes the multi-head spiral grooves 701 on the outer periphery of the spiral corrugated rotor 7 to perform secondary axial flow pressurization on the airflow. This action offsets the aerodynamic losses caused by the fluid passing through the sub-millimeter narrow gap, ensuring that the purified air can be discharged from the exhaust port at the top of the main air duct shell 2 at a stable flow rate. This in-situ pressure head compensation mechanism ensures that the entire unit maintains excellent smoke and air exhaust capabilities while maintaining extremely high deodorization efficiency, achieving energy decoupling and efficient synergy between acoustic purification and aerodynamic transport.

[0085] The entire system's sewage system operates in a fully static, passive overflow state. Microscopic phase-change sludge flowing from the annular manifold 12 merges with macroscopic large-particle oil sludge flowing from the main oil outlet within the gravity liquid-sealed conduit 13. Due to the presence of the liquid column within the U-shaped liquid-sealed section 1301, the negative pressure environment inside the system is tightly locked, preventing external air backflow from interfering with the acoustic resonance frequency. When newly entering sludge accumulates to a certain height, its superimposed gravitational potential energy breaks the balance and drives the fluid to overflow unidirectionally to the external oil storage device, completing a fully closed-loop automatic waste recovery.

[0086] The aforementioned dynamic operating logic embodies a step-by-step processing approach, from macroscopic physical interception to microscopic acoustic phase transition. Since the purification process relies entirely on the physical action of aeroacoustic coupling, there are no filter media or easily worn chemical coatings obstructing flow within the entire unit. The mechanical oscillation characteristics of the high-frequency acoustic energy field endow the system with extremely strong self-cleaning capabilities, effectively inhibiting the adhesion and scaling of contaminants within the core acoustic unit. This ensures that the deodorization efficiency and aerodynamic performance do not degrade over time under long-term high-load operation.

[0087] By organically combining mechanical shearing, standing wave aggregation, centrifugal discharge, and gravity overflow within a unified coaxial dynamic framework, this invention resolves the contradictions between odor degradation thoroughness, operating energy consumption, and maintenance costs in traditional fume purification equipment. This highly efficient purification path based on physical energy field conversion provides a consumable-free, long-life, and stable technical solution for modern kitchen environments, significantly improving the technological integration and operational reliability in the field of fume purification.

[0088] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A high-efficiency deodorizing and fume purification integrated machine, comprising a casing (1), characterized in that, The top of the housing (1) is provided with a main air duct housing (2). The main air duct housing (2) is rotatably connected to the central main shaft (5) through two upper and lower brackets (3). The central main shaft (5) is driven to rotate by a drive motor (4). The outer wall of the central main shaft (5) is sequentially fitted with and fixedly connected to a centrifugal turbine impeller (6) and a spiral corrugated rotor (7). The spiral corrugated rotor (7) is located above the centrifugal turbine impeller (6). An acoustic stator ring (8) is arranged around the spiral corrugated rotor (7). The acoustic stator ring (8) is fixedly connected to the inner wall of the main air duct housing (2). An alternating gap is left between the outer peripheral surface of the spiral corrugated rotor (7) and the inner surface of the acoustic stator ring (8). The centrifugal turbine impeller (6) is used to push the multiphase mixed oil fume airflow upward into the alternating gap. Multiple resonant microcavities (9) are opened on the inner surface of the acoustic stator ring (8). When the spiral corrugated rotor (7) rotates at high speed, it periodically cuts off the airflow in the alternating gap to generate alternating aerodynamic pulses. The alternating aerodynamic pulses sweep the resonant microcavities (9) and generate an acoustic standing wave field, forcing the gaseous odor molecules in the airflow to undergo acoustic wave aggregation in the acoustic standing wave field and physically transform into liquid dirt.

2. The integrated oil fume purification machine with high efficiency deodorization according to claim 1, characterized in that, The main air duct housing (2) has a through exhaust channel inside. The bottom of the housing (1) has an air intake channel (101) connected to the exhaust channel. The lower part of the inner wall of the main air duct housing (2) and the radial outer side of the centrifugal turbine impeller (6) are provided with a liquid collection guide groove (201) for collecting large oil particles thrown to the inner wall by the centrifugal turbine impeller (6). The bottom of the liquid collection guide groove (201) is inclined and the lowest point is provided with a main oil outlet. A circular array of guide baffles (202) is provided above the opening of the liquid collection guide groove (201). The guide baffles (202) are inclined at an acute angle to the horizontal plane for physically shielding the oil accumulated in the liquid collection guide groove (201) and guiding the airflow upward.

3. The integrated oil fume purification machine with high efficiency deodorization according to claim 2, characterized in that, The inner surface of the acoustic stator ring (8) is also provided with acute-angle shear teeth (10). Multiple acute-angle shear teeth (10) and multiple resonant microcavities (9) are arranged alternately in an array along the circumferential direction of the acoustic stator ring (8). The multiphase mixed oil fume gas entering the alternating gap is mechanically sheared under the high-frequency geometric interference of the spiral corrugated rotor (7) and the acute-angle shear teeth (10), and then transformed into submicron-level aerosols that enter the acoustic standing wave field.

4. The integrated high-efficiency deodorizing and fume purification machine according to claim 3, characterized in that, The integrated fume purification unit also includes a sewage discharge module, which includes a capillary drainage slit (11) and an annular liquid collection manifold (12). The resonant microcavity (9) is a blind-end cavity recessed towards the back of the acoustic stator ring (8). The capillary drainage slit (11) radially penetrates the solid wall of the acoustic stator ring (8). The inlet of the capillary drainage slit (11) is opened at the lowermost edge of the bottom wall of the resonant microcavity (9), and the outlet is connected to the annular liquid collection manifold (12) fixedly covered on the back of the acoustic stator ring (8).

5. The integrated high-efficiency deodorizing and fume purification machine according to claim 4, characterized in that, The bottom wall of the resonant microcavity (9) is a solid structure with continuous main body, which is used to form an acoustic total reflection boundary. The entrance position of the capillary drainage slit (11) is anchored at the acoustic displacement node of the acoustic standing wave field, so that the liquid dirt generated by phase change in the resonant microcavity (9) is driven by the centrifugal dynamic pressure generated by the high-speed swirling flow, and is forced into and flows through the capillary drainage slit (11) in one direction, thereby achieving the separation and discharge of liquid dirt without destroying the macroscopic acoustic rigidity of the microcavity.

6. The integrated high-efficiency deodorizing and fume purification machine according to claim 5, characterized in that, The bottom wall of the resonant microcavity (9) is a smooth transition arc surface that is recessed towards the back of the acoustic stator ring (8). In the acoustic field, the smooth transition arc surface is used to geometrically focus the ultrasonic frequency band sound energy of total reflection towards the interior space of the resonant microcavity (9) to enhance the aggregation of sound waves. At the same time, it eliminates the right-angle vortex dead zone inside the resonant microcavity (9) at the fluid dynamic level, and guides the liquid dirt pushed by centrifugal dynamic pressure to slide and converge to the entrance of the capillary drainage slit (11) without hindrance in accordance with the curvature of the arc surface.

7. The integrated high-efficiency deodorizing and fume purification machine according to claim 4, characterized in that, The sewage discharge module also includes a gravity liquid seal conduit (13), the upper end of which is connected to the annular liquid collection manifold (12) and the main oil drain port respectively. Its pipe body extends downward and passes through the main air duct shell (2), and a U-shaped liquid seal section (1301) is provided on the pipe body path.

8. The integrated oil fume purification machine with high efficiency deodorization according to claim 7, characterized in that, The U-shaped liquid seal section (1301) contains a stationary liquid column. The gravity hydrostatic pressure generated by the stationary liquid column is used to block the external atmospheric pressure, so that it forms a hydrostatic balance with the Bernoulli local low pressure generated when the fluid flows through the alternating gap, thereby forming a unidirectional fluid barrier to prevent external air from flowing back along the capillary drainage slit (11).

9. The integrated oil fume purification machine with high efficiency deodorization according to claim 8, characterized in that, When the liquid waste continuously collected in the annular collection manifold (12) flows into the gravity liquid seal conduit (13), the gravitational potential energy of the newly added waste liquid breaks the original hydrostatic pressure balance and naturally pushes open the stationary liquid column, so that the overflowing liquid waste is discharged unidirectionally into the waste oil collection device connected to the end of the gravity liquid seal conduit (13).

10. The integrated oil fume purification machine with high efficiency deodorization according to claim 1, characterized in that, The outer circumferential surface of the spiral corrugated rotor (7) is provided with a macroscopic axisymmetric multi-head spiral groove (701). When the multi-head spiral groove (701) rotates with the central main shaft (5), it cooperates with the acoustic stator ring (8) to form a high-frequency chopping interface. At the same time, it provides secondary axial flow boosting thrust for the pure airflow after phase change deodorization to overcome the system fluid pressure drop and discharge along the top of the main air duct shell (2).

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