Anti-vibration stabilizing device for gas outlet pipeline of electrolytic cell

Abstract

The utility model discloses an anti-vibration stabilizing device for an air outlet pipeline of an electrolytic bath, which is characterized in that a ring-shaped pipe frame is arranged on the periphery of a material pipeline in a full-surrounding or partial-surrounding manner, and a multi-layer composite vibration isolation part is filled between the inner side of the ring-shaped pipe frame and the contact side of the material pipeline; a self-adaptive damping adjusting piece is arranged between the ring-shaped pipe frame and the fixed frame body; the device further comprises a vibration data acquisition mechanism arranged on the material pipeline. And the multi-layer composite vibration isolation part has the wear-resisting and broadband damping capabilities through the wear-resisting layer and the damping layer, and the high-frequency vibration attenuation rate is larger than or equal to 90%. A honeycomb air cavity and a closed cavity are filled with media or open cavity micropores are designed, the rigidity and damping can be adjusted in a self-adaptive mode, and low-frequency buffering or specific-frequency resonance suppression is achieved. The regular hexagonal honeycomb structure is high in geometric stability and uniform in stress dispersion, the material consumption is reduced by 30-40%, the weight is reduced, and the anti-fatigue life is prolonged. The air cavity is axially and flexibly arranged, vibration in different directions is absorbed in a targeted mode, and the multi-dimensional damping effect is improved.

Description

Technical Field

[0001] This utility model relates to the field of electrolytic cell technology, specifically to a vibration-damping and stabilizing device for the gas outlet pipe of an electrolytic cell. Background Technology

[0002] In the hydrogen production process of an electrolyzer, the outlet pipeline needs to handle the discharge of hydrogen and oxygen, but it faces complex vibration problems in actual operation. In existing technologies, traditional rigid fixed supports can only restrict pipeline displacement but cannot absorb high-frequency vibration energy. When the pipeline experiences fluctuations in the flow rate of the electrolysis reaction gas, such as airflow impact caused by unstable green electricity supply, resonance caused by the equipment operating frequency being close to the natural frequency of the pipeline, or mechanical vibrations from pumps, compressors, etc., transmitted to the pipeline, the rigid connection will cause the vibration energy to act directly on the pipeline weld, resulting in fatigue cracking of the weld due to long-term alternating stress.

[0003] The application of a single damper also has obvious limitations. Its damping parameters are fixed and cannot be dynamically adjusted according to changes in vibration frequency. It is like a spring that can only be set with one stiffness. When green electricity fluctuations cause changes in airflow frequency or external environment (such as wind or earthquake) generates different frequency excitations, the damper is difficult to match the real-time vibration characteristics, and the vibration reduction effect is greatly reduced.

[0004] At the monitoring level, existing systems rely on manual inspections to identify potential pipeline vibration hazards. This method is not only time-consuming and labor-intensive, but also cannot capture vibration data in real time. When the vibration amplitude of the pipeline gradually increases and the welds begin to crack, it is often difficult for humans to detect it in time. The hidden danger may gradually expand during continuous operation, eventually leading to pipeline leaks or even shutdown accidents, which seriously affect equipment safety and production efficiency.

[0005] The core drawbacks of existing technologies are: rigid fixed structures lack vibration buffering capabilities, single dampers cannot dynamically respond to complex vibration sources, and manual monitoring modes have lag and the risk of missed detection. All three factors together lead to a high risk of fatigue damage to the gas outlet pipe of the electrolytic cell. There is an urgent need for a new type of anti-vibration system that can take into account broadband vibration suppression, dynamic adaptive adjustment, and intelligent monitoring.

[0006] For the reasons mentioned above, it is necessary to propose a vibration-damping and stabilizing device for the gas outlet pipeline of an electrolytic cell to solve the above problems. Utility Model Content

[0007] The purpose of this invention is to overcome the defects in the existing technology and provide a vibration-proof and stabilizing device for the gas outlet pipe of an electrolytic cell.

[0008] To achieve the above objectives, the technical solution of this utility model is as follows:

[0009] An anti-vibration stabilization device for an electrolytic cell outlet pipeline includes a ring-shaped pipe frame that is fully or partially enclosed around the material pipeline, and a multi-layer composite vibration isolation part is filled between the inner side of the ring-shaped pipe frame and the side in contact with the material pipeline.

[0010] It also includes a fixed frame, with an adaptive damping adjustment component between the ring-shaped pipe frame and the fixed frame; and a vibration data acquisition mechanism arranged on the material pipeline.

[0011] Furthermore, the multi-layer composite vibration isolation section includes a damping layer and a wear-resistant layer, which are sequentially arranged from the inside to the outside between the material pipeline and the ring-shaped pipe frame.

[0012] Furthermore, several air cavities are pre-formed within the shock-absorbing layer. These air cavities form the framework of the shock-absorbing layer and are supported between the ring-shaped tube frame and the material pipeline. The air cavities are either closed chambers or open chambers with micropores.

[0013] When set as a closed chamber, the air chamber is filled with a medium or external pressure is applied to bring the air chamber to a preset pressure.

[0014] Furthermore, the air cavity is in the shape of a regular hexagonal column, and several air cavities are connected in a honeycomb pattern. The air cavities are arranged in the following directions: the axial direction of the air cavity is parallel to the axial direction of the material pipeline; or the axial direction of the air cavity is radially arranged along the material pipeline; one or both can be stacked.

[0015] Furthermore, the raw materials for manufacturing the damping layer include any one or more of silicone, nitrile rubber, polyurethane, asphalt-based damping adhesive, and stainless steel wire braid.

[0016] The damping layer is a polytetrafluoroethylene coating.

[0017] Furthermore, the adaptive damping adjustment component includes a magnetorheological damper with a damping force adjustment range of 0~500 N·s / m and a response time ≤20 ms.

[0018] Furthermore, the circular tube frame is suspended and installed under the fixed frame via adaptive damping adjustment components; at least two sets of adaptive damping adjustment components are symmetrically arranged on both sides of the circular tube frame; the two sets of adaptive damping adjustment components are erected in a diagonal bracing manner, and the ends of the adaptive damping adjustment components are respectively provided with ball joint structures to connect the circular tube frame and the fixed frame.

[0019] Furthermore, the magnetorheological damper is disposed on the lower side of the coiled tube frame and is supported between the coiled tube frame and the fixed frame.

[0020] Furthermore, it also includes a pressure buffer chamber, which is a cylindrical cavity located at the bend of the material pipeline. Inside the cavity is a perforated throttling plate with several circular holes evenly distributed on it. A section of elastic corrugated pipe is installed at both the inlet and outlet of the cylindrical cavity.

[0021] A control method for a vibration damping and stabilizing device for an electrolytic cell outlet pipe includes the following steps:

[0022] S1: The vibration data acquisition mechanism includes an accelerometer. Accelerometers are arranged at key points in the material pipeline to collect vibration signals in real time and transmit the vibration acceleration time-domain waveform to the PLC control system.

[0023] S2: The PLC control system performs a fast Fourier transform on the received raw vibration signal to decompose the main frequency component of the vibration and its corresponding amplitude, and determines whether the vibration is low-frequency or high-frequency.

[0024] S3: Based on the preset safety threshold and vibration frequency range, trigger the damping adjustment command and call the preset damping adjustment strategy;

[0025] S4: The PLC system uses a proportional-integral-derivative algorithm to calculate the required current value, and adjusts the current required by the electromagnetic coil of the magnetorheological damper through proportional, integral and derivative links.

[0026] S5: By continuously adjusting the current of the electromagnetic coil, the damping force of the magnetorheological damper can be linearly varied in the range of 0-500 N·s / m, covering a wide frequency range of 0.1-50 Hz, and the system delay from monitoring to adjustment is within 0.5 seconds.

[0027] The advantages and beneficial effects of this utility model are as follows:

[0028] 1. Multi-layer composite vibration isolation section: Through wear-resistant layer and damping layer, with honeycomb air cavity design, it has wear resistance and wide frequency damping capability, and high frequency vibration attenuation rate ≥90%.

[0029] 2. The honeycomb air cavity, with its closed cavity filled with medium or open cavity micropore design, can adaptively adjust stiffness and damping to achieve low-frequency buffering or specific frequency resonance suppression.

[0030] 3. The regular hexagonal honeycomb structure has strong geometric stability, uniform stress distribution, reduces material usage by 30-40%, is lightweight, and extends fatigue life.

[0031] 4. Flexible axial arrangement of air chambers: They can be set along the axial or radial direction of the pipeline, or stacked in combination, to absorb vibrations in different directions and improve the multi-dimensional vibration reduction effect.

[0032] 5. Optimized structural integration: The honeycomb cavity is embedded between the ring-shaped pipe rack and the pipe, requiring no additional space, making it suitable for dense installation scenarios and easy to maintain. Attached Figure Description

[0033] Figure 1 This is one of the longitudinal cross-sectional schematic diagrams of the multi-layer composite vibration isolation part of the anti-vibration and stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0034] Figure 2 This is the second longitudinal cross-sectional schematic diagram of the multi-layer composite vibration isolation part of the anti-vibration and stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0035] Figure 3 This is the third longitudinal cross-sectional schematic diagram of the multi-layer composite vibration isolation part of the anti-vibration and stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0036] Figure 4 This is the fourth longitudinal cross-sectional schematic diagram of the multi-layer composite vibration isolation part of the anti-vibration and stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0037] Figure 5 This is one of the schematic diagrams of the installation method of the anti-vibration stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0038] Figure 6 This is the second schematic diagram of the installation method of the anti-vibration stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0039] Figure 7 This is a schematic diagram of the air pressure buffer chamber of the anti-vibration stabilization device for the gas outlet pipe of the electrolytic cell of this utility model;

[0040] In the diagram: 1. Electrolytic cell body; 2. Material pipeline; 3. Circular pipe rack; 4. Multi-layer composite vibration isolation section; 5. C-type clamp; 6. Fixing frame; 7. Adaptive damping adjustment component; 8. Vibration damping layer; 9. Wear-resistant layer; 10. Air cavity; 11. Axially parallel arrangement; 12. Radial parallel arrangement; 13. Upper end plate; 14. Lower end plate; 15. Enclosure; 16. Magnetorheological fluid; 17. Electromagnetic coil; 18. Damping unit; 19. Elastic support assembly; 20. Guide rod; 21. Spring; 22. Limiting nut; 23. Air pressure buffer chamber; 24. Cylindrical cavity; 25. Porous throttling plate; 26. Elastic bellows; 27. Ball joint connection. Detailed Implementation

[0041] The specific embodiments of this utility model will be further described below with reference to the accompanying drawings and examples. The following examples are only used to more clearly illustrate the technical solution of this utility model and should not be construed as limiting the scope of protection of this utility model.

[0042] A vibration damping and stabilizing device for an electrolytic cell outlet pipeline includes a ring-shaped pipe frame 3 that is fully or partially enclosed around the material pipeline 2. The inner side of the ring-shaped pipe frame 3, in contact with the material pipeline 2, is filled with a multi-layered composite vibration damping section 4. Figure 1 As shown.

[0043] In this embodiment, a multi-layer composite vibration isolation section 4 is formed using a multi-layer composite structure. Specifically, it includes at least three layers: "rigid support + flexible damping + wear-resistant coating," thereby solving the defects of traditional supports having excessively high or low stiffness. The rigid support is a ring-shaped pipe support 3, which is constructed as a C-shaped clamp 5 structure that matches the diameter of the material pipe 2. It is understood that since a vibration isolation section needs to be installed on the inner side of the ring-shaped pipe support 3, space needs to be reserved between it and the material pipe 2 for the installation of the vibration isolation section. In actual use, the ring-shaped pipe support 3 can be made of high-strength stainless steel, such as 316L, with a thickness of 8-12mm, and designed as a C-shaped clamp 5 structure. Two clamp structures facing each other can form a circular pipe clamp shape, such as... Figure 2 As shown, this means that the material pipeline 2 is fixed in a fully enclosed manner; as another embodiment, this means a semi-enclosed or partially enclosed form, such as... Figure 3 As shown, a C-shaped clamp 5 structure can be used, with both ends connected to the fixed frame 6 by bolts.

[0044] The fully enclosed circular pipe rack 3 also includes a fixed frame 6, with an adaptive damping adjustment component 7 between the circular pipe rack 3 and the fixed frame 6; it also includes a vibration data acquisition mechanism arranged on the material pipeline 2. The vibration spectrum is collected in real time by an array of accelerometers, and combined with fluid pressure and temperature data, a PLC algorithm is used to achieve multi-dimensional hazard warning and adaptive adjustment of damping parameters; the adaptive damping adjustment component 7 can be a magnetorheological damper, or other dampers with adjustable damping functions can be used instead; this embodiment takes a magnetorheological damper as an example, based on the intelligent damping adjustment of the magnetorheological fluid 16, to achieve a wide frequency response of 0.1~50Hz, solving the problem of poor frequency adaptability of a single damper.

[0045] Specifically, the multi-layer composite vibration isolation section 4 includes a damping layer 8 and a wear-resistant layer 9, which are sequentially arranged from the inside to the outside between the material pipeline 2 and the ring-shaped pipe support 3. In one embodiment, the damping layer 8 is a polytetrafluoroethylene (PTFE) coating; the wear-resistant layer 9 uses an embedded silicone damping layer 8 with a hardness of 30-50 Shore A, and the surface in contact with the pipeline is covered with a PTFE wear-resistant coating, i.e., the wear-resistant layer 9, thereby reducing frictional vibration.

[0046] Furthermore, in addition to silicone, the damping layer 8 can also be made of materials such as nitrile rubber, polyurethane, asphalt-based damping adhesive, and stainless steel wire braid. Specifically, nitrile rubber (NBR) has a hardness range of 30-90 Shore A and an operating temperature of -40 to 120°C; polyurethane (TPU) has a hardness range of 60-95 Shore D and an operating temperature of -30 to 80°C; asphalt-based damping adhesive has a non-standard hardness (soft colloid) and an operating temperature of -20 to 60°C; and stainless steel wire braid has an equivalent hardness of 20-50 Shore A and an operating temperature of -200 to 600°C.

[0047] Preferably, the silicone damping layer 8 is used because it has a low elastic modulus (0.1-10MPa) and a high loss factor (0.1-0.3), which provides the best suppression effect on the resonance peak of high-frequency vibration. For high-temperature special environments (>100℃), metal rubber can be selected; for oily environments, nitrile rubber with a PTFE wear-resistant layer 9 coated on the surface can be selected.

[0048] As one embodiment of the structure of the damping layer 8, a plurality of air cavities 10 are pre-formed within the damping layer 8. The air cavities 10 form the skeleton support of the damping layer 8 and are arranged between the ring-shaped pipe frame 3 and the material pipe 2. Preferably, the air cavities 10 are in the shape of regular hexagonal columns, and the plurality of air cavities 10 are connected in a honeycomb pattern.

[0049] The high-frequency vibration absorption is enhanced by the following mechanisms through the composite structure of "elastic material + air cavity 10": 1. Elastic deformation of silicone matrix: vibration energy is consumed by bending and stretching of the honeycomb wall; 2. Air cushion effect of air cavity 10: air compression / expansion generates damping force to suppress vibration transmission; 3. Modal dispersion: the honeycomb array decomposes the overall vibration into multiple local vibrations to avoid a single resonant frequency.

[0050] The specific structural design is as follows: the honeycomb shape adopts the optimal geometrically stable shape of a regular hexagon with a side length of 3-5mm, and the cavity depth is adapted to the thickness direction of the ring-shaped tube frame 3; the wall thickness is 0.5-1mm, the thinner the silicone wall, the better the elasticity, but the structural strength must be guaranteed; the distribution density is uniformly distributed along the circumference of the pipe, containing 15-20 honeycomb units per 10cm²; in this embodiment, at least one end of the air cavity 10 is open, and the opening direction is: the honeycomb opening is perpendicular to the pipe axis to ensure that the vibration transmission direction (radial) is consistent with the air compression direction.

[0051] The honeycomb structure reduces material usage by 30-40%, lowers the overall weight of the support, and has a better effect on high-frequency vibration attenuation, improving the attenuation rate of 30Hz vibration by 20%. However, due to the increased damping loss caused by the air cavity 10, solid silicone relies solely on internal material friction, resulting in lower attenuation efficiency.

[0052] As a second embodiment of the vibration damping layer 8 structure, the air cavity 10 is a closed chamber. When it is a closed chamber, the air cavity 10 is filled with a medium or subjected to external pressure to reach a preset pressure. The principle of this embodiment is to enhance the "air cushion stiffness" of the air cavity 10 by increasing the internal pressure or changing the characteristics of the medium, thereby suppressing pipeline vibration. The method of applying external pressure is, when including the multi-layer composite vibration isolation section 4, to compress and tighten the air cavity 10 by tightening the ring-shaped pipe frame 3, thereby increasing the pressure in its internal closed chamber. This method is relatively simple and quick.

[0053] Filling medium:

[0054] If filled with pure gas, taking nitrogen as an example, increasing the internal pressure of air cavity 10 can increase the elastic modulus of air cavity 10, which can improve the attenuation capability of low-frequency vibration (<20Hz). This method is low-cost, easy to implement, and suitable for scenarios dominated by low-frequency airflow pulsation, such as green electricity fluctuation frequency <10Hz.

[0055] Alternatively, a gas-liquid mixture can be filled in; specifically, a gas-silicone oil mixture can be used as an example. This method utilizes the liquid to increase the damping within the cavity. During high-frequency vibration, the liquid will generate shear force due to inertia, while the gas provides elastic support, thus achieving wide-frequency vibration reduction (5-50Hz). This implementation method provides a more balanced vibration reduction effect.

[0056] Specific implementation plan:

[0057] Gas filling scheme: An inflation hole is opened at the top of the honeycomb air cavity 10 of the silicone layer of the multi-layer composite support, and a one-way valve (such as a duckbill valve) is installed; nitrogen is initially filled to 0.05MPa (gauge pressure), and the pressure inside the cavity is monitored by a pressure sensor. When the pressure is lower than 0.03MPa, gas is automatically replenished; a pressure relief hole can also be set, and the pressure is automatically vented when the pressure exceeds 0.1MPa to prevent the cavity from bursting.

[0058] Gas-liquid mixing scheme: A liquid injection hole is reserved at the bottom of the honeycomb cavity, and methyl silicone oil (viscosity 50cst, temperature resistance -30~200℃) with a volume ratio of 30% is injected; the top is inflated to 0.05MPa, and a gas-liquid two-phase buffer medium is formed in the air cavity 10; the outer surface of the silicone layer is coated with a fluororubber sealing ring to prevent liquid leakage.

[0059] As a third embodiment of the damping layer 8 structure, the air cavity 10 is an open-mouth chamber with micropores. Its principle is that air enters and exits through the micropores at both ends of the honeycomb cavity, forming a "piston-like" breathing effect. This utilizes air viscosity damping to dissipate vibrational energy. Simultaneously, the size of the micropores determines the resonant frequency, achieving resonant absorption of vibrations at specific frequencies. This creates a viscous damping effect; as air passes through the micropores, it rubs against the pore walls, producing a damper-like effect that suppresses vibrations at non-resonant frequencies. For vibrations at specific frequencies, such as the natural frequency of the pipe, the attenuation rate can reach over 90%, and no active control is required, making it a purely passive structure.

[0060] Specific structural design: Simulating the short tube effect, each end of the honeycomb air cavity 10 has a micropore with a diameter of φ0.5-1mm and a length of 2-3mm; the volume of a single honeycomb cavity is 1-3cm³, such as a regular hexagon with a side length of 3mm, a cavity depth of 5mm, and a volume of about 2cm³.

[0061] Frequency matching calculation: Assuming the target attenuation frequency f0 = 25Hz and the speed of sound in air c = 340m / s, then according to the Helmholtz formula:

[0062]

[0063] Take the micropore area A:

[0064]

[0065] Cavity volume V:

[0066]

[0067] Then the length of the micropore L:

[0068]

[0069] 3D printing technology, such as silicone SLS printing, can be used to create honeycomb structures with micropores; the micropores need to penetrate the silicone layer and have smooth inner walls (roughness Ra≤1.6μm) to reduce airflow resistance loss.

[0070] This embodiment is more suitable for scenarios where the main frequency of the pipeline has been determined through vibration testing, such as when the vibration amplitude of a certain frequency is prominent during long-term operation.

[0071] As a fourth embodiment of the damping layer 8 structure, based on the aforementioned first embodiment of the damping layer 8 structure, the direction of the air cavity 10 is further designed: the axial direction of the air cavity 10 is parallel to the axial direction of the material pipe 2 11; or the axial direction of the air cavity 10 is radially parallel to the material pipe 2 12; one or both can be stacked; when both are used in a stacked manner, the damping layer 8 forms a multi-layered stacked structure design, such as... Figure 4 As shown.

[0072] Furthermore, the adaptive damping adjustment component 7 includes a magnetorheological damper, and the magnetorheological fluid 16 is composed of micron-sized magnetic particles (such as iron powder) dispersed in an insulating base liquid (such as silicone oil). In the absence of a magnetic field, it is a low-viscosity liquid, and the piston within the damper moves freely, resulting in a low-damping state. After a magnetic field is applied, the magnetic particles align in a chain-like structure along the magnetic field direction, hindering piston movement, causing a sharp increase in viscosity and shear stress, switching to a high-damping state. By changing the current in the electromagnetic coil 17, the magnetic field strength is adjusted in real time, forming a linear response relationship of "current-magnetic field-damping force," providing the physical conditions for damping adjustment. Utilizing the rheological properties of the magnetorheological fluid 16, under the action of a magnetic field, the liquid can change from a liquid state to a semi-solid state within milliseconds, significantly increasing the damping force. The damping force is controlled by the magnetic field strength generated by the electromagnetic coil 17. The damping force is continuously adjustable within the range of 0~500 N·s / m. By changing the input current or magnetic field strength, the damping force can be dynamically controlled, making it suitable for vibration suppression under different working conditions. The response time is ≤20ms, which has the ability to quickly and dynamically adjust the system. It can track changes in external excitation in a timely manner and effectively improve the seismic resistance of the system.

[0073] As one embodiment of the adaptive damping adjustment element 7, the circular tube frame 3 is suspended and mounted on the underside of the fixed frame 6 via the adaptive damping adjustment element 7; for example... Figure 5 As shown, at least two sets of adaptive damping adjustment components 7 are symmetrically arranged on both sides of the circular tube frame 3; the two sets of adaptive damping adjustment components 7 are erected in a diagonal bracing manner, and the ends of the adaptive damping adjustment components 7 are respectively provided with ball joint structures to connect the circular tube frame 3 and the fixed frame 6. Figure 5 As shown, the ring-shaped pipe support 3 has a fixed frame 6 above it. The upper outer wall of the ring-shaped pipe support 3 is provided with a ball joint structure for suspension connection. Similarly, a corresponding ball joint structure is provided on the lower side of the fixed frame 6. A rod-shaped magnetorheological damper is connected between the two ball joint structures. In this way, under the self-weight of the material pipeline 2, it can be suspended in a balanced and stable position. When vibration occurs, not only is primary vibration isolation achieved through the multi-layer composite vibration isolation part 4, but secondary vibration isolation is also achieved through the magnetorheological damper when the vibration is transmitted to the ring-shaped pipe support 3. The ball joint structure allows for ±5° angular displacement. It can be understood that the ball joint displacement angle is not limited here and can be flexibly set according to actual needs to adapt to the axial or radial displacement of the pipeline.

[0074] In another embodiment of the adaptive damping adjustment element 7, the magnetorheological damper is disposed on the lower side of the coiled tube frame 3, and is supported between the coiled tube frame 3 and the fixed frame 6. Figure 6As shown, this embodiment is a lower support mode. In this embodiment, the magnetorheological damper is a flat plate structure, which includes an upper end plate 13 and a lower end plate 14. A cavity 15 filled with magnetorheological fluid 16 with a certain deformation support capacity is set in the gap between the two, so that it can adapt to the slight change in the gap between the upper and lower end plates 14 during vibration. An electromagnetic coil 17 is set on the outer periphery of the magnetorheological fluid 16. By controlling the current of the coil, the magnitude of its magnetic field is changed, thereby changing the overall damping. It can be understood that the electromagnetic coil 17 and the magnetic field are related. The rheological fluid 16 forms a damping unit 18. Multiple such damping units 18 can be set between the upper and lower end plates 14. The figure only shows one unit as an example. Multiple damping units 18 are laid flat between the gaps. The number of units is selected according to the area of ​​the end plate. Elastic support components 19 can be added around the adaptive damping adjustment component 7 of the upper and lower end plates 14. For example, a guide rod 20 is set on the lower end plate 14, a spring 21 is wound on the guide rod 20, and a limiting nut 22 is set on the upper end plate 13 through the upper end of the guide rod 20.

[0075] Furthermore, it also includes a pressure buffer chamber 23, which is a cylindrical cavity 24 located at the bend of the material pipeline 2. In actual use, the pressure buffer chamber 23 can be configured as an independent and detachable cylindrical cavity 24, and installed at the 90° bend of the electrolytic cell outlet pipeline. The bend is where the airflow changes most violently. It is rigidly connected to the pipeline through a flange, forming a series structure of "pipeline-buffer chamber-pipeline". Specifically, as shown... Figure 7 As shown, its core components are as follows:

[0076] The main body of the chamber is made of 304 stainless steel, which is corrosion-resistant and suitable for hydrogen environments. The wall thickness is 5-8mm to ensure pressure resistance, with a design pressure of 1.0MPa and a working pressure of 0.1-0.5MPa. It is cylindrical in shape, with a diameter matching the inner diameter of the pipe. For example, a DN100 pipe corresponds to a chamber diameter of 120mm, a length of 200-300mm, and a volume of 0.5-1.0L.

[0077] The internal core components include a perforated throttling plate 25, located in the center of the cavity, perpendicular to the airflow direction. The plate has evenly distributed circular holes with a diameter of φ2~5mm, numbering 10~30 holes with a spacing of 10~15mm. It also includes an elastic bellows 26, with a section approximately 50~80mm long installed at both the cavity inlet and outlet. This section is made of stainless steel corrugated flexible tubing and allows for ±10mm axial / radial displacement. A pressure sensor interface can also be installed at the top to monitor the cavity pressure in real time; a drain port is located at the bottom to periodically discharge condensate or impurities.

[0078] Its specific operating principle is as follows: A porous throttling plate 25 "cuts" the high-speed airflow, decomposing large-scale pulsations into small-scale eddies, thus reducing the amplitude of airflow pressure fluctuations. An elastic bellows 26 isolates the cavity from the pipe's vibration transmission, preventing the buffer cavity itself from becoming a vibration source. When airflow passes through the throttling plate, the high-speed airflow inside the holes rubs against the hole walls, generating viscous damping. Simultaneously, the airflow between the holes collides, forming eddies that consume kinetic energy. Actual measurements show that this can reduce the airflow pulsation amplitude by 30% to 50%, thereby reducing the impact force of the airflow on the pipe. Regarding vibration isolation, the flexible connection of the elastic bellows 26 allows for small relative movements between the pipe and the buffer cavity, acting like a "soft connection" to break the vibration transmission path and prevent pressure fluctuations within the buffer cavity from being directly transmitted to the pipe elbow weld. The cavity volume acts as an "air spring 21," absorbing energy through gas compression / expansion within the cavity during sudden changes in airflow, such as sudden changes in green electricity load, preventing instantaneous high-pressure impacts within the pipe.

[0079] The synergistic effect of the ring-shaped pipe frame 3 formed by the air pressure buffer chamber 23 and the multi-layer composite vibration isolation section 4 is as follows: the silicone damping layer 8 of the frame absorbs high-frequency structural vibrations (>20Hz), and the buffer chamber attenuates low-frequency airflow pulsations (5~20Hz), forming full-frequency coverage of high and low frequency vibrations. When the green electricity load jumps from 30% to 100%, the airflow frequency increases from 10Hz to 15Hz. The buffer chamber first reduces the amplitude of the airflow pulsations, and the frame then absorbs the residual structural vibrations, ultimately achieving a total vibration attenuation rate of over 90%.

[0080] The synergistic effect of the air pressure buffer chamber 23 and the magnetorheological damper is as follows: The PLC system judges the airflow pulsation intensity based on the air pressure sensor data in the buffer chamber: if the air pressure fluctuation is >0.1MPa (corresponding to high pulsation condition), the current of the magnetorheological damper is increased to 1.2A simultaneously to enhance the support's suppression of low-frequency vibration; if the air pressure is stable, the damper maintains a low current (0.3A) to save energy.

[0081] A control method for a vibration damping and stabilizing device for an electrolytic cell outlet pipe includes the following steps:

[0082] S1: The vibration data acquisition mechanism includes an accelerometer. Accelerometers are placed at key points of the material pipeline 2 to collect vibration signals in real time and transmit the time-domain waveform of vibration acceleration to the PLC control system. Specifically, data acquisition relies on accelerometers placed at key points of the pipeline (such as elbows and support connections) to monitor vibration signals in real time (range ±50g, accuracy ±1%) and transmit the time-domain waveform of vibration acceleration (such as vibration amplitude and frequency components) to the PLC control system.

[0083] S2: The PLC control system performs a fast Fourier transform on the received original vibration signal to decompose the main frequency component of the vibration and its corresponding amplitude, and determines whether the vibration is low-frequency or high-frequency. The PLC performs a fast Fourier transform (FFT) on the original vibration signal to decompose the main frequency component of the vibration (such as 5Hz, 20Hz, 50Hz, etc.) and its corresponding amplitude, and determines whether the current vibration is low-frequency (≤20Hz, such as airflow pulsation) or high-frequency (>20Hz, such as mechanical resonance).

[0084] S3: Based on the preset safety threshold and vibration frequency range, trigger the damping adjustment command and call the preset damping adjustment strategy; Preset safety threshold: If the pipe displacement exceeds 5mm or the amplitude of a certain frequency exceeds 80% of the natural frequency amplitude, trigger the damping adjustment command. Vibration type matching: According to the frequency range, call the preset damping adjustment strategy, such as increasing damping for low frequencies and relying on the silicone layer for passive vibration reduction for high frequencies.

[0085] S4: The PLC system uses a proportional-integral-derivative algorithm to calculate the required current value, and adjusts the current required by the electromagnetic coil 17 of the magnetorheological damper through proportional, integral and derivative links.

[0086] The specific implementation of regulation and control: precise mapping of current and damping force;

[0087] Actuator: Electromagnetic coil 17 and piston structure;

[0088] The magnetorheological damper contains:

[0089] Electromagnetic coil 17: wound around the outside of the damper cylinder, power 50~100W, current adjustment range 0~2A.

[0090] Piston assembly: The piston has flow channels, and the resistance of the magnetorheological fluid 16 when it passes through the flow channels is the source of the damping force.

[0091] Control Algorithm: PID closed-loop control. The PLC system calculates the required current value based on vibration spectrum analysis results using a proportional-integral-derivative (PID) algorithm. The specific process is as follows: Proportional Component: Quickly adjusts the current based on the deviation between the current vibration amplitude and the target value; the larger the deviation, the larger the current. Integral Component: Eliminates long-term deviations, ensuring the damping force remains stable at the target value; for example, maintaining a high current during continuous low-frequency vibration. Derivative Component: Predicts vibration trends and adjusts the current in advance to suppress vibration peaks; for example, increasing the current damping in advance when high-frequency vibration is anticipated.

[0092] S5: Continuous adjustment of the current of electromagnetic coil 17 enables the damping force of the magnetorheological damper to change linearly in the range of 0-500 N·s / m, covering a wide frequency range of 0.1-50 Hz, and the system delay from monitoring to adjustment is within 0.5 seconds.

[0093] Dynamic response process: When low-frequency vibration is detected, such as green electricity fluctuation causing airflow frequency of 5Hz, the PLC output current increases to 1.5A, the magnetic field is enhanced, the viscosity of magnetorheological fluid 16 increases, and the damping force increases from the initial 100N·s / m to 400N·s / m, suppressing low-frequency swaying of the pipeline.

[0094] When high-frequency vibrations occur, such as 30Hz vibrations caused by a compressor, the PLC determines that the energy is mainly absorbed through the silicone damping layer 8, maintaining a current of only 0.5A and a damping force of 150N・s / m to avoid excessive damping affecting the flexibility of the pipeline.

[0095] The unity of wideband response and adaptive adjustment; 0.1~50Hz wideband coverage: Through continuous current adjustment (0~2A), the damping force can be linearly varied in the range of 0~500N・s / m to match the full frequency band requirements from slow airflow pulsation of 0.1Hz to high-speed mechanical vibration of 50Hz.

[0096] Adjustment delay ≤ 0.5 seconds: The magnetic field response of the magnetorheological fluid 16 is in the millisecond range (≤ 20ms). Combined with the data processing and instruction transmission time of the PLC, the overall system delay from monitoring to adjustment is controlled within 0.5 seconds, which can promptly suppress sudden vibrations, such as load jumps.

[0097] This closed-loop "monitoring-analysis-control" mechanism enables the magnetorheological damper to dynamically adjust its damping parameters based on real-time vibration characteristics, avoiding the limitations of traditional single dampers that apply only one type of damper, and achieving precise suppression of vibration in the electrolytic cell's outlet pipe.

[0098] The above description is only a preferred embodiment of the present utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present utility model, and these improvements and modifications should also be considered within the protection scope of the present utility model.

Claims

1. A vibration-damping and stabilizing device for the gas outlet pipe of an electrolytic cell, characterized in that, A ring-shaped pipe frame is set around the material pipeline in a fully or partially enclosed manner, and a multi-layer composite vibration isolation part is filled between the inner side of the ring-shaped pipe frame and the side in contact with the material pipeline. It also includes a fixed frame, with an adaptive damping adjustment component between the ring-shaped pipe frame and the fixed frame; and a vibration data acquisition mechanism arranged on the material pipeline.

2. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 1, characterized in that, The multi-layer composite vibration isolation section includes a damping layer and a wear-resistant layer, which are arranged sequentially from the inside to the outside between the material pipeline and the ring-shaped pipe frame.

3. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 2, characterized in that, Several air cavities are pre-formed within the shock-absorbing layer. The air cavities form the skeleton of the shock-absorbing layer and are supported between the ring-shaped pipe frame and the material pipeline. The air cavities are either closed chambers or open chambers with micropores. When set as a closed chamber, the air chamber is filled with a medium or external pressure is applied to bring the air chamber to a preset pressure.

4. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 3, characterized in that, The air cavity is in the shape of a regular hexagonal column, and several air cavities are connected in a honeycomb pattern.

5. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 1, characterized in that, The adaptive damping adjustment component includes a magnetorheological damper with a damping force adjustment range of 0~500 N·s / m and a response time ≤20 ms.

6. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 1, characterized in that, The circular tube frame is suspended and installed under the fixed frame via adaptive damping adjustment components; at least two sets of adaptive damping adjustment components are symmetrically arranged on both sides of the circular tube frame; the two sets of adaptive damping adjustment components are erected in an oblique manner, and the ends of the adaptive damping adjustment components are respectively provided with ball joint structures to connect the circular tube frame and the fixed frame.

7. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 5, characterized in that, The magnetorheological damper is located on the lower side of the circular tube frame and is supported between the circular tube frame and the fixed frame.

8. The anti-vibration stabilization device for the gas outlet pipeline of an electrolytic cell according to claim 1, characterized in that, It also includes a pressure buffer chamber, which is a cylindrical cavity located at the bend of the material pipeline. Inside the cavity is a perforated throttling plate with several circular holes evenly distributed on it. A section of elastic corrugated pipe is installed at both the inlet and outlet of the cylindrical cavity.

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