Vibration wave generating device capable of compressing fluid and reaction kettle

Abstract

The invention discloses a vibration wave generating device capable of compressing fluid and a reaction kettle, and relates to the technical field of chemical equipment, the vibration wave generating device comprises a vibration wave generating bin communicated with a feeding channel and a discharging channel, and the vibration wave generating bin is provided with two end plates which are oppositely arranged and parallel to each other; a rotating shaft parallel to the end plate is arranged in the bin, an oval disc is fixedly installed on the rotating shaft, a gap is reserved between the far end of the outer periphery of the oval disc and the inner wall of the vibration wave generating bin, and the gap size when the long shaft of the oval disc is parallel to the end plate is smaller than the gap size when the long shaft is perpendicular to the end plate. The effective sectional area of the vibration wave generating bin can be periodically changed along with rotation of the oval disc, and then compressible fluid entering the vibration wave generating bin is driven to generate pressure fluctuation. Precise generation of compressible fluid pressure waveforms is achieved through mechanical rotation movement, and the problems of uneven heat transfer, local channelization, poor fluidization stability and the like caused by constant-pressure fluid in a particle bed layer are solved.

Description

Technical Field

[0001] This invention relates to the field of chemical equipment technology, specifically to a vibration wave generator for compressible fluids and a reaction vessel. Background Technology

[0002] In industrial production processes, when using constant-pressure steam or compressed air to treat granular beds such as quartz sand in reactors, a series of challenges are often encountered. Among these, localized channeling is a particularly prominent problem. Localized channeling refers to the phenomenon where, as fluid flows through a granular bed, it does not fully contact the particles within the bed, but instead preferentially follows paths with less resistance, rapidly passing through the bed and forming flow paths resembling "channels." This phenomenon directly leads to airflow short-circuiting, causing a large amount of fluid to flow out of the bed without participating in effective heat and mass transfer processes. Consequently, this results in significant temperature differences between different regions within the granular bed, extremely uneven heat transfer, and severely impacts treatment efficiency and product quality stability.

[0003] When the flow rate of the constant pressure fluid exceeds the minimum fluidization velocity of the particles, it may also cause particle segregation, that is, finer particles in the bed are carried out of the bed by the fluid. It may also cause fluidization runaway, resulting in unstable states such as violent fluctuations and collapse of the bed, which greatly undermines the stability of the process and causes great trouble to the continuous production.

[0004] In existing technologies, mechanical stirring or constant-pressure pulsed fluidization is commonly used to apply external force to the materials in the reactor to achieve mixing and agitation of the particle bed. Mechanical stirring requires complex sealing structures, which not only increases manufacturing costs and maintenance difficulty but also makes the stirring components prone to wear during long-term operation, shortening the equipment's lifespan and increasing the frequency of downtime for maintenance. Constant-pressure pulsed fluidization makes it difficult to dynamically adjust the waveform and frequency according to the real-time state of the particle bed, thus failing to flexibly adapt to different operating conditions.

[0005] Existing technologies also disclose some traditional fluid ripple devices, but these devices rely on solenoid valve switching or pneumatic component driving, resulting in complex structures and slow response. For example, Chinese utility model patent application number CN213792248U discloses a fluid ripple device with a check valve. This device includes a back cover, an oscillator, a cavity, a sealing ring, and a check valve. The cavity contains a disc-shaped or flat cylindrical chamber. The oscillator and the cavity form a sealed chamber. The reciprocating motion of the oscillator causes the volume of the sealed chamber to periodically increase and decrease. Stable fluid with a certain flow rate enters the sealed chamber through the inlet. Driven by the reciprocating motion of the oscillator, the volume of the sealed chamber periodically increases and decreases, continuously discharging fluid pulses, thereby converting stable fluid into continuous fluid pulses.

[0006] In summary, existing solutions either suffer from high equipment wear and energy consumption or are overly sensitive to particle size, resulting in a narrow range of applications. Currently, there is a lack of efficient solutions that can achieve fluid dynamic disturbance through geometric structural innovation. Summary of the Invention

[0007] The present invention aims to provide a vibration wave generator and reaction vessel for compressible fluids, so as to achieve accurate generation of pressure waveforms of compressible fluids through mechanical rotational motion, and solve problems such as uneven heat transfer, local channelization and poor fluidization stability caused by constant pressure fluids in particle beds.

[0008] To solve the above technical problems, the specific solution adopted by the present invention is as follows: a vibration wave generating device for compressible fluid, comprising a vibration wave generating chamber, an inlet channel and an outlet channel for fluid to enter and exit the vibration wave generating chamber, the vibration wave generating chamber having two end plates arranged opposite to each other and parallel to each other, the inlet channel and the outlet channel being respectively connected to the two end plates of the vibration wave generating chamber, a rotating shaft parallel to the end plates being provided inside the vibration wave generating chamber, an elliptical disk being fixedly installed on the rotating shaft, a gap being left between the far end of the outer periphery of the elliptical disk and the inner wall of the vibration wave generating chamber, and the gap size when the major axis of the elliptical disk is parallel to the end plate is smaller than the gap size when the major axis is perpendicular to the end plate, the effective cross-sectional area of ​​the vibration wave generating chamber can exhibit periodic changes as the elliptical disk rotates, thereby driving the compressible fluid entering the vibration wave generating chamber to generate pressure fluctuations.

[0009] As a further optimization of the above technical solution: the end of the feeding channel is provided with an inclined section, the end of which is connected to the feed inlet of the vibration wave generating chamber, and the inclined section forms an angle of 20 to 30° with the end plate of the connected vibration wave generating chamber.

[0010] As a further optimization of the above technical solution: the discharge channel is a 90° bend.

[0011] As a further optimization of the above technical solution: the vibration wave generating chamber is rectangular, and the rotating shaft is installed on two opposite side walls of the vibration wave generating chamber. The other two opposite side walls inside the vibration wave generating chamber are respectively provided with strip grooves, and the height of the strip grooves is the same as the installation height of the rotating shaft.

[0012] As a further optimization of the above technical solution: the rotating shaft is fixedly inserted through the center of the elliptical disk.

[0013] As a further optimization of the above technical solution: the natural frequency of the shaft system composed of the rotating shaft and the elliptical disk is higher than the operating frequency of the vibration wave generator.

[0014] As a further optimization of the above technical solution: the ratio of the major axis to the minor axis of the elliptical disk is 4:2.5-3.5.

[0015] As a further optimization of the above technical solution: the elliptical disk is made of 17-4PH stainless steel with surface nitriding treatment, the vibration wave generating chamber is made of 316L stainless steel with nickel plating on the inner wall, the inner wall roughness Ra≤0.8μm, and the outer shell of the vibration wave generating chamber is made of 304 stainless steel with electrostatic spraying Teflon coating.

[0016] As a further optimization of the above technical solution: a variable frequency motor for driving its rotation is connected to the rotating shaft.

[0017] A reactor for purifying quartz sand includes a reactor body and a quartz sand bed disposed within the reactor body. The reactor has a fluid inlet for introducing a disturbed gas flow into the quartz sand bed. The fluid inlet is connected to the aforementioned vibration wave generator. The disturbed gas flow enters the reactor through the vibration wave generator. The motor used to drive the rotating shaft has a speed range of 0 to 3000 rpm, and the speed ratio of the reducer is 10:1.

[0018] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0019] This invention dynamically adjusts the effective cross-sectional area of ​​the pipe using an elliptical disk, causing the effective cross-sectional area to change sinusoidally. This allows for the precise generation of fluid pressure waves through purely mechanical rotation. Each rotation of the elliptical disk completes a sinusoidal cycle in the flow channel cross-sectional area, driving the compressible fluid to generate pressure fluctuations at the same frequency. These vibration waves create uniform disturbances in particle beds such as quartz sand, breaking up localized channels that easily form in constant-pressure fluids, preventing airflow short-circuiting, achieving uniform heating of the particle bed, and improving heat transfer efficiency. This addresses the core shortcomings of traditional constant-pressure fluid treatment methods.

[0020] This invention improves the equipment's resistance to damp heat, high temperature, and weak corrosion by using a material system consisting of a 17-4PH stainless steel elliptical disc, a 316L stainless steel cavity, and a 304 stainless steel outer shell, thereby extending its service life and adapting it to complex working conditions in the chemical industry.

[0021] The reactor for quartz sand pickling provided by this invention uses a variable frequency motor (0-3000 rpm) and a reducer (speed ratio 10:1) to control the elliptical disk rotation speed from 0 to 300 rpm, corresponding to a pressure wave frequency of 0-50 Hz, covering the resonant frequency range of the chemical particle bed (10-30 Hz). This avoids the channeling defects of traditional constant pressure fluids, allows for precise control of bed porosity, effectively suppresses particle segregation and fluidization runaway, and improves process stability. Attached Figure Description

[0022] Figure 1 This is a side cross-sectional view of the vibration wave generating device of the present invention;

[0023] Figure 2This is a three-dimensional side cross-sectional view of the vibration wave generating device of the present invention;

[0024] Figure 3 This is a three-dimensional cross-sectional view of the vibration wave generator of the present invention along the rotation axis.

[0025] Figure 4 This is a three-dimensional structural schematic diagram of the vibration wave generating device of the present invention;

[0026] Figure 5 This is a side view of the vibration wave generating device of the present invention;

[0027] Figure 6 A side cross-sectional view of the elliptical disk in the vibration wave generating chamber in a vertical position;

[0028] Figure 7 A side cross-sectional view of a vibration wave generating chamber with grooves, showing the minimum effective cross-sectional area.

[0029] Figure 8 This is a side cross-sectional view of the elliptical disk in the vibration wave generating chamber in a horizontal state.

[0030] Reference numerals: 1. Mounting plate, 2. Sealing flange, 3. Feed channel, 301. Vertical section, 302. Inclined section, 4. Vibration wave generating chamber, 401. End plate, 402. Side wall, 5. Groove, 6. Discharge port, 7. Discharge channel, 8. Rotating shaft, 9. Elliptical disk, 10. Feed port. Detailed Implementation

[0031] The technical solution of the present invention will be further described in detail below with reference to specific embodiments. Parts not described or disclosed in detail in the following embodiments of the present invention should be understood as prior art known or should be known by those skilled in the art.

[0032] like Figure 1 , 2 As shown, this invention discloses a vibration wave generating device for compressible fluids, including a vibration wave generating chamber 4. The vibration wave generating chamber 4 has an elongated inner cavity, and a feed channel 3 and a discharge channel 7 for fluid entry and exit are connected to the vibration wave generating chamber 4. In this embodiment, the elongated inner cavity is specifically a rectangular sealed cavity, including two end plates 401 arranged opposite to each other and four side walls 402 connected between the two end plates 401. The feed channel 3 is connected to the upper end plate 401, and the upper end plate 401 has a feed port 10 communicating with the feed channel 3. The discharge channel 7 is connected to the lower end plate 401, and the lower end plate 401 has a discharge port 6 communicating with the discharge channel 7. The feed port 10 and the discharge port 6 are respectively located in the middle of the corresponding end plates 401, and the diameter of the discharge channel 7 is larger than the diameter of the feed channel 3.

[0033] Combination Figure 5As shown, the feed channel 3 includes a vertical section 301 and an inclined section 302, wherein the inclined section 302 forms an angle of 20-30° with the feed end plate 401 of the vibration wave generating chamber 4. In this embodiment, the angle is 22°. This structural design is based on the principle of fluid dynamics and can guide the compressible fluid into the vibration wave generating chamber 4 with a stable flow rate and direction, thereby reducing turbulence disturbance at the fluid inlet.

[0034] Combination Figure 3 , 4 As shown, a sealing flange 2 is vertically installed at the upper end of the vertical section 301. The sealing flange 2 is fixedly connected to the vertical section 301, either by welding or threaded connection. A through hole with the same inner diameter as the vertical section 301 is provided on the sealing flange 2. A mounting plate 1 is connected to the side of the sealing flange 2 opposite to the vertical section 301. The mounting plate 1 has a through hole, facilitating the connection of the wave generator to an external fluid transport channel via the mounting plate 1 and the sealing flange 2. External fluid flows sequentially through the through holes in the mounting plate 1 and the sealing flange 2 into the vibration wave generating chamber 4, generating pressure fluctuations and being discharged through the discharge channel 7.

[0035] The discharge channel 7 is a 90° bend, which guides the compressible fluid treated by the vibration wave generating chamber 4 to smoothly change its flow direction, changing the fluid's flow from along the axial direction of the vibration wave generating chamber 4 to being output in a direction perpendicular to the axial direction, so as to adapt to the fluid inlet direction requirements of downstream equipment (such as a reactor). At the same time, this 90° bend structure can minimize pressure loss during the change of fluid flow direction, avoid vibration wave energy attenuation or waveform distortion caused by abrupt changes in the flow channel, ensure that pressure fluctuations are delivered to the downstream particle bed in a stable state, and ensure the consistency and effectiveness of the disturbance effect on the particle bed.

[0036] The vibration wave generating chamber 4 is equipped with a rotating shaft 8 and an elliptical disk 9 fixed on the rotating shaft 8. The rotating shaft 8 is parallel to the end plate 401 of the vibration wave generating chamber 4. The four side walls 402 of the vibration wave generating chamber 4 are arranged opposite each other in pairs. The rotating shaft 8 is installed on two of the opposite side walls 402. A gap is left between the far edge of the outer periphery of the elliptical disk 9 and the inner wall of the vibration wave generating chamber 4. The gap size when the major axis of the elliptical disk 9 is parallel to the end plate 401 is smaller than the gap size when the major axis is perpendicular to the end plate 401. The rotation of the elliptical disk 9 in the vibration wave generating chamber 4 can make the effective cross-sectional area of ​​the vibration wave generating chamber 4 change periodically, thereby driving the compressible fluid entering the vibration wave generating chamber 4 to generate pressure fluctuations.

[0037] It should be noted that the effective cross-sectional area of ​​the vibration wave generating chamber 4 refers to the cross-sectional area through which the fluid can actually pass during the rotation of the elliptical disk 9. Due to the unique elliptical structure of the elliptical disk 9 and its specific relative positional relationship with the inner wall of the vibration wave generating chamber 4, the flow channel space formed between the elliptical disk 9 and the inner wall of the vibration wave generating chamber 4 changes periodically with the rotation angle as the elliptical disk 9 rotates. This causes the cross-sectional area through which the fluid can pass to also change periodically, thereby driving the compressible fluid to generate pressure fluctuations.

[0038] The rotating shaft 8 is fixedly installed at the center of the elliptical disk 9, and the disk surface of the elliptical disk 9 is perpendicular to the axis of the rotating shaft 8. This ensures that the elliptical disk 9 is subjected to uniform force and rotates stably during rotation, and keeps the relative positional relationship between the elliptical disk 9 and the inner wall of the vibration wave generating chamber 4 consistent. This makes the periodic change law of the effective cross-sectional area of ​​the vibration wave generating chamber 4 stable and predictable, ensuring that the frequency and waveform of the generated pressure wave are precisely controllable, thereby achieving stable regulation of the vibration wave of compressible fluid to meet the needs of particle bed treatment.

[0039] The ratio of the major axis to the minor axis of the elliptical disk 9 is 4:2.5-3.5. In this embodiment, the major axis of the elliptical disk 9 is 80mm and the minor axis is 60mm. By driving the elliptical disk 9 to rotate, the gap between the elliptical disk 9 and the inner wall of the vibration wave generating chamber 4 is changed (0.5-5mm), thereby controlling the effective cross-sectional area change of the vibration wave generating chamber 4. The rotating shaft 8 is equipped with a bearing (not shown in the figure) at the mounting point on the inner wall of the vibration wave generating chamber 4 to allow the rotating shaft 8 to rotate freely. Through precision machining and assembly, the perpendicularity error between the axis of the rotating shaft 8 and the inner wall of the vibration wave generating chamber 4 is ≤0.02mm / m. This allows it to withstand the radial centrifugal force and axial thrust generated when the elliptical disk 9 rotates, and also ensures that the elliptical disk 9 rotates stably within the speed range of 0-300rpm, avoiding abnormal changes in the cross-sectional area of ​​the flow channel due to shaking or offset. A variable frequency motor (not shown in the figure) is connected to the rotating shaft 8 to drive its rotation, which in turn drives the elliptical disk 9 to rotate.

[0040] During the rotation of the elliptical disk 9, its elliptical profile dynamically interacts with the inner wall of the vibration wave generating chamber 4: when the major axis of the elliptical disk 9 is parallel to the end plate 401 of the vibration wave generating chamber 4, the effective cross-sectional area of ​​the flow channel is minimized; when the major axis of the elliptical disk 9 is perpendicular to the end plate 401 of the vibration wave generating chamber 4, the effective cross-sectional area of ​​the flow channel is maximized. This causes the effective cross-sectional area of ​​the flow channel within the vibration wave generating chamber 4 to change periodically with the rotation angle in a sinusoidal manner. According to the continuity equation of fluid mechanics and Bernoulli's principle, this change in cross-sectional area will induce synchronous periodic fluctuations in the pressure and velocity of the compressible fluid, thereby forming a sinusoidal vibration wave.

[0041] When the major axis of the elliptical disk 9 is parallel to the end plate 401 and the effective cross-sectional area of ​​the flow channel is at its minimum, a gap still exists between the elliptical disk 9 and the side wall 402. This not only ensures fluid continuity—the gap keeps the fluid flowing—but also generates sinusoidal pressure waves through continuous changes in cross-sectional area (rather than complete blockage). If there were contact, it would create pulsed, intermittent flow, making continuous frequency regulation from 0 to 50 Hz impossible. Furthermore, the gap can suppress sudden pressure changes: it buffers the rate of cross-sectional area change, preventing localized high-pressure impacts caused by complete closure and protecting the downstream reactor system. In addition, the gap prevents mechanical wear between the elliptical disk 9 and the side wall 402. If it were in contact with the inner wall of the pipe, high-speed rotation (0–300 rpm) would cause severe friction, shortening the equipment's lifespan. A gap of 0.5–5 mm reduces mechanical wear.

[0042] Inside the vibration wave generating chamber 4, two opposite inner sidewalls 402 are respectively provided with strip-shaped grooves 5, and the height of the strip-shaped grooves 5 is the same as the installation height of the rotating shaft 8. Figure 6 As shown, the effective cross-sectional area of ​​the flow channel is maximized when the major axis of the elliptical disk 9 is perpendicular to the end plate 401; Figure 7 As shown, the effective flow channel area is minimized when the major axis of the elliptical disk 9 is close to the edge of the strip groove 5; as Figure 8 As shown, when the major axis of the elliptical disk 9 is parallel to the end plate 401, the major axis of the elliptical disk 9 is at the same height as the strip groove 5, and the effective flow area increases briefly. Then, as the elliptical disk 9 continues to rotate, it reaches the minimum effective flow area again. This invention, by setting the strip groove 5, can refine the cross-sectional area adjustment accuracy. The groove 5 can provide a supplementary flow channel when the major axis of the elliptical disk 9 is parallel to the end plate 401, avoiding turbulence caused by a sudden decrease in cross-sectional area, making the pressure fluctuation closer to the ideal sine wave. On the other hand, it can reduce fluid retention: the groove 5 matches the rotation trajectory of the elliptical disk 9, guiding the fluid to flow along a specific path, reducing fluid retention in dead corners within the vibration wave generation chamber 4 (especially for condensate in high-pressure steam), and reducing the risk of corrosion. It can also assist in frequency adaptation: combined with the attenuation model (p(L)=p... ac ·e -αL sin(2πft)+p dc The groove allows for fine-tuning of the pressure wave amplitude, compensating for energy loss during pipeline transmission, and ensuring effective fluctuations within the reactor.

[0043] The natural frequency of the shaft system composed of the rotating shaft 8 and the elliptical disk 9 is higher than the operating frequency of the vibration wave generator. The natural frequency of the elliptical disk-shaft system has been optimized to 80Hz through finite element analysis, which is 50Hz higher than the upper limit of the operating frequency. The safety factor is 1.6, which avoids structural fatigue caused by resonance, ensures long-term stable operation of the equipment, and reduces the risk of failure caused by vibration.

[0044] This invention also discloses a reactor for purifying quartz sand, comprising a reactor body (not shown in the figure) and a quartz sand bed disposed within the reactor body. The reactor body has a fluid inlet for introducing a disturbed gas flow into the quartz sand bed. The internal structure of the reactor body is the same as that in the prior art and will not be described again here. It should be noted that, during use, the reactor processes "medium to coarse particles such as quartz sand with a particle size of 0.1–1 mm," and operates at a pressure of 0–6 bar and a temperature ≤150℃. Experimental verification shows that a pressure wave of 10–30 Hz can effectively loosen the quartz sand bed and suppress localized channeling. Under these conditions, the resonant frequency range of the particle bed within the reactor is 10–30 Hz.

[0045] The fluid inlet is connected to the aforementioned vibration wave generator. The disturbed airflow enters the reactor through the vibration wave generator. The variable frequency motor used to drive the rotating shaft 8 has a speed range of 0 to 3000 rpm, and the speed ratio of the reducer is 10:1.

[0046] The rotational power of the elliptical disk 9 is provided by a variable frequency motor. The motor's output speed is adjusted by a reducer with a speed ratio of 10:1 and then transmitted to the rotating shaft 8, allowing the rotational speed of the elliptical disk 9 to be continuously adjustable within the range of 0 to 300 rpm, corresponding to the generation of periodic pressure waves from 0 to 50 Hz. This covers the resonant frequency range of the chemical particle bed, avoiding the channeling defects of traditional constant pressure fluids.

[0047] The vibration wave is transported to the downstream reactor via discharge channel 7. Discharge channel 7 is a 90° bend with an inlet diameter of 120mm, an outlet diameter of 60mm, and a wall thickness of 2mm. Through the design of gradually changing pipe diameter and optimized curvature radius, the pressure loss is minimized while deflecting the fluid flow by 90°, ensuring that the vibration wave energy is transmitted to the downstream particle bed with high efficiency.

[0048] The device has end caps at both ends, which are connected to the sealing flange 2 by bolts. Combined with a high-temperature resistant sealing gasket, axial sealing is achieved, preventing external impurities from entering and enhancing the overall structural strength of the device, making it suitable for high-pressure (≤1.6MPa) and high-temperature (≤150℃) operating conditions. The inner wall of the vibration wave generating chamber 4 is manufactured using a one-piece molding process with 316L stainless steel and precision ground (roughness Ra≤0.8μm). This provides a stable rotation space for the elliptical disk 9, avoiding abnormal fluctuations in flow resistance due to cavity wall deformation or surface defects, and ensuring the consistency of parameters such as the frequency and amplitude of the vibration wave.

[0049] This invention utilizes a 1.5kW variable frequency motor (IP55 protection) paired with a double-end plate mechanical seal (temperature resistant to 150℃) to ensure shaft end sealing reliability at high-speed rotation (3000rpm), with a leakage rate ≤5mL / min. The motor power margin design (rated power 1.5kW, maximum torque 4.77N·m) can cover the fluid resistance torque (calculated value approximately 3.2N·m) under full-load conditions at 50Hz. The elliptical disk is made of 17-4PH precipitation-hardening stainless steel with nitriding surface to improve hardness and corrosion resistance; the cavity and pipes are made of 316L stainless steel with nickel plating on the inner wall to enhance resistance to weak acids / alkalis and surface smoothness to reduce fluid retention corrosion; the outer shell is made of 304 stainless steel with electrostatic spraying Teflon coating to improve resistance to humid heat corrosion. The overall material system enables the equipment to adapt to humid, high-temperature, and weakly corrosive media environments, extending service life and ensuring operational stability.

[0050] Traditional fluid wave devices rely on solenoid valve switching or pneumatic component actuation, resulting in complex structures and slow response times. Unlike traditional compressors that achieve gas compression through volume changes, this invention utilizes a concentric elliptical disk dynamic cross-sectional area modulation mechanism. Through purely mechanical rotation, it achieves precise generation and independent control of compressible fluid pressure waveforms. Each rotation of the elliptical disk completes a sinusoidal periodic change in the flow channel cross-sectional area, driving the compressible fluid (air / steam) to generate pressure waves at the same frequency. By leveraging the geometric eccentricity of the concentric elliptical disk, the kinetic energy of the motor rotation is converted into the potential energy of periodically changing fluid pressure waves.

[0051] The fluid dynamic principle by which the rotation of the elliptical disk in this invention generates vibration waves is as follows:

[0052] I. Structural Composition and Working Principle

[0053] 1) Drive Unit: A variable frequency motor (1.5kW, 0~3000rpm) drives the elliptical disc to rotate through a reducer (speed ratio 10:1), achieving frequency adjustment from 0 to 50Hz. The elliptical disc is made of 17-4PH stainless steel, with a nitrided surface treatment to enhance corrosion resistance.

[0054] (ii) Waveform Control Mechanism

[0055] (1) Geometric properties of elliptical disks

[0056] With a major axis of 80mm and a minor axis of 60mm, the elliptical disk is driven to rotate, thereby changing the gap (0.5-5mm) between the elliptical disk and the inner wall of the circular pipe, thus controlling the variation range of the effective cross-sectional area of ​​the pipe.

[0057] (iii) When the elliptical disk rotates, the effective cross-sectional area of ​​the vibration wave generation chamber changes in a sinusoidal pattern.

[0058] Vertical position (long axis direction): maximum cross-sectional area, pressure reaches peak value;

[0059] Horizontal position (short axis direction): minimum cross-sectional area (close to closed), pressure close to 0 bar.

[0060] This results in periodic pressure fluctuations, conforming to the sinusoidal function p(t) = p dc +p ac ·sin(2πft), where p dc As the reference pressure, p ac f is the fluctuation amplitude, and f is the frequency.

[0061] IV) Control Logic

[0062] The PLC receives set parameters (frequency, DC bias, duty cycle) through the RS485 communication interface, drives the frequency converter to adjust the motor speed, and monitors the chamber temperature (PT100 sensor) and pressure (safety valve opening pressure 8 bar) in real time.

[0063] II. Mathematical Model

[0064] 1) Fluid dynamics model: Mechanism of pressure wave generation

[0065] (1) Continuity equation for compressible fluids

[0066] Let the effective cross-sectional area of ​​the pipe when the elliptical disk rotates be A(t), the fluid mass flow rate be m, and the density be ρ(t) (compressible fluid), then:

[0067]

[0068] Where v(t) is the fluid velocity. For an ideal gas (compressed air / steam), the density satisfies the equation of state.

[0069]

[0070] (p(t) is pressure, M is molar mass, R is gas constant, and T is temperature. Assume constant temperature T = 120℃ = 393K).

[0071] (2) Bernoulli's equation (compressible fluid correction)

[0072] Ignoring the height difference, consider the conversion of kinetic energy into pressure energy:

[0073]

[0074] (p0, ρ0, v0 are initial state parameters)

[0075] Combining the continuity equation and eliminating v(t), we get:

[0076]

[0077] Key variable: A(t) is determined by the geometry of the elliptical disk and varies periodically with the rotation angle θ = 2πft.

[0078] (3) Elliptical disk cross-sectional area function

[0079] Let the major axis of the elliptical disk be 2a = 80 mm and the minor axis be 2b = 60 mm, then the equation of the ellipse is:

[0080]

[0081] The pipe is a circular pipe with an inner diameter D = 50 mm. The gap δ(t) between the elliptical disk and the pipe wall varies with the rotation angle. When the elliptical disk rotates to angle θ, the infinitesimal cross-sectional area element at the gap is...

[0082] dA=δ(t)·D·dθ

[0083] Simplifying assumptions: Ignore the thickness of the elliptical disk, approximate the problem as a two-dimensional plane problem, total effective cross-sectional area:

[0084]

[0085] in (Calculation of set gaps)

[0086] (ii) Mechanical transmission model: Relationship between frequency and rotational speed

[0087] (1) Rotation speed-frequency mapping relationship

[0088] The variable frequency motor speed n (r / min) and the elliptical disk rotation frequency f (Hz) satisfy the following:

[0089]

[0090] (2) Torque Calculation

[0091] When the elliptical disk rotates, it needs to overcome the fluid resistance torque Tf, which is determined by the pressure difference Δp = p. max -p min With the area of ​​action A avg Decide:

[0092] T f =Δp·A avg ·r

[0093] (r is the radius of rotation of the elliptical disk, taking half of the major axis r = a = 40mm, A) avg (This represents the average cross-sectional area.)

[0094] The motor output torque Tm must meet the following requirements:

[0095]

[0096] (P = 1.5kW is the motor power, ω = 2πf is the angular velocity)

[0097] III) Pressure Waveform and Attenuation Model

[0098] (1) Sine wave pressure function

[0099] Due to the uniform rotation of the elliptical disk, the pressure fluctuation approximates a sine curve:

[0100] p(t) = p dc +p ac sin(2πft+φ)

[0101] p dc DC bias pressure (reference pressure, 0-6 bar);

[0102] p ac AC amplitude (0-2 bar, controlled by gap δ);

[0103] φ: Phase angle; φ = 0 when the initial position is in the vertical direction.

[0104] (2) Attenuation Model: Influence of Pipe Distance

[0105] The attenuation of the pressure wave from the generator outlet to the reactor cavity conforms to the damping law of viscous fluids:

[0106] p(L)=p ac ·e -αL sin(2πft)+p dc

[0107] The attenuation coefficient α is related to the fluid viscosity coefficient μ and the pipe roughness μ.

[0108]

[0109] (v = μ / ρ is the kinematic viscosity, take the vapor viscosity μ≈2.1×10) -5 Pa·s, air μ≈1.9×10 -5 Pa·s)

[0110] Conclusion: Shorten the pipe length L or increase p ac It can compensate for attenuation and maintain effective pressure fluctuations within the reactor.

[0111] IV) Key Parameter Matching Verification

[0112] (1) Frequency range verification

[0113] When f = 50Hz, the rotational speed of the elliptical disk is n = 3000 r / min, corresponding to a period T = 0.02s.

[0114] If the fluid viscosity coefficient is too high (such as syrup), the pressure wave may be damped before it is fully formed. Therefore, this device is more suitable for gases (low viscosity coefficient), which is consistent with the application scenario of "high pressure gas" in this solution.

[0115] This invention achieves a deep coupling between fluid mechanics and mechanical engineering, and proposes a vibration attenuation compensation theory: when a periodically varying pressure wave propagates along a pipeline, it follows an exponential attenuation law p(L)=p0·e -αL The attenuation coefficient α is related to the fluid viscosity coefficient (μ≈1.9×10⁻⁶ for air). -5 Pa·s), pipe roughness (inner wall polishing Ra≤0.8μm, α≈0.05m) -1 Related to resonance avoidance technology, the natural frequency of the elliptical disk-axis system was optimized to 80Hz through finite element analysis (FEA), which is 50Hz higher than the upper limit of the operating frequency, thus avoiding structural fatigue caused by resonance (safety factor 1.6).

[0116] This invention does not require a complex external control system and can be directly integrated into existing reactor production lines, shortening the modification cycle and adapting to particle bed processing scenarios in multiple fields such as chemical engineering and building materials.

[0117] The above description of the disclosed embodiments enables those skilled in the art to make or use the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A vibration wave generating device for compressible fluid, comprising a vibration wave generating chamber (4), wherein the vibration wave generating chamber (4) is connected to an inlet channel (3) for fluid entry and exit and an outlet channel (7), characterized in that: The vibration wave generating chamber (4) has two end plates (401) that are arranged opposite to each other and parallel to each other. The feed channel (3) and the discharge channel (7) are respectively connected to the two end plates (401) of the vibration wave generating chamber (4). A rotating shaft (8) parallel to the end plate (401) is provided inside the vibration wave generating chamber (4). An elliptical disk (9) is fixedly installed on the rotating shaft (8). A gap is left between the far end of the outer periphery of the elliptical disk (9) and the inner wall of the vibration wave generating chamber (4). When the major axis of the elliptical disk (9) is parallel to the end plate (401), the gap size is smaller than the gap size when the major axis is perpendicular to the end plate (401). The effective cross-sectional area of ​​the vibration wave generating chamber (4) can change periodically as the elliptical disk (9) rotates, thereby driving the compressible fluid entering the vibration wave generating chamber (4) to generate pressure fluctuations.

2. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The end of the feeding channel (3) is provided with an inclined section (302), the end of which is connected to the feed inlet (10) of the vibration wave generating chamber (4), and the inclined section (302) forms an angle of 20 to 30° with the end plate (401) of the connected vibration wave generating chamber (4).

3. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The discharge channel (7) is a 90° bend.

4. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The vibration wave generating chamber (4) is rectangular. The rotating shaft (8) is installed on two opposite side walls (402) of the vibration wave generating chamber (4). The other two opposite side walls (402) inside the vibration wave generating chamber (4) are respectively provided with strip grooves (5), and the height of the strip grooves (5) is the same as the installation height of the rotating shaft (8).

5. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The rotating shaft (8) is fixedly inserted at the center of the elliptical disk (9).

6. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The natural frequency of the shaft system consisting of the rotating shaft (8) and the elliptical disk (9) is higher than the operating frequency of the vibration wave generator.

7. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The ratio of the major axis to the minor axis of the elliptical disk (9) is 4:2.5-3.

5.

8. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: The elliptical disk (9) is made of 17-4PH stainless steel with surface nitriding treatment. The vibration wave generating chamber (4) is made of 316L stainless steel with nickel plating on the inner wall. The inner wall roughness Ra≤0.8μm. The outer shell of the vibration wave generating chamber (4) is made of 304 stainless steel with electrostatic spraying Teflon coating.

9. The vibration wave generating device for compressible fluid according to claim 1, characterized in that: A variable frequency motor for driving its rotation is connected to the rotating shaft (8).

10. A reactor for purifying quartz sand, comprising a reactor body and a quartz sand bed disposed within the reactor body, wherein the reactor body has a fluid inlet for introducing a turbulent gas flow into the quartz sand bed, characterized in that, The fluid inlet is connected to the aforementioned vibration wave generator. The disturbed airflow enters the reactor through the vibration wave generator. The speed range of the motor used to drive the rotating shaft (8) is 0 to 3000 rpm, and the speed ratio of the reducer is 10:1.

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