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

Abstract

The invention discloses an anti-vibration stabilizing device for an air outlet pipeline of an electrolytic cell, 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] The present invention relates to the technical field of electrolytic cells, and in particular to a device and method for stabilizing an electrolytic cell gas outlet pipeline from vibration. Background Art

[0002] During hydrogen production in electrolyzers, the outlet pipes are responsible for discharging hydrogen and oxygen, but face complex vibration issues during actual operation. Existing rigid mounting brackets can only limit pipe displacement but are unable to absorb high-frequency vibration energy. When the pipes are affected by fluctuations in the flow of electrolytic gas, such as airflow shock caused by unstable green electricity supply, resonance occurs when the operating frequency of the equipment approaches the natural frequency of the pipes, or when mechanical vibrations from pumps, compressors, or other devices are transmitted to the pipes, the rigid connection can directly affect the vibration energy in the pipe welds, causing them to be subjected to long-term alternating stress and fatigue cracking.

[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 to one hardness. When green electricity fluctuations cause changes in airflow frequency or the external environment (such as wind or earthquakes) produces excitations of different frequencies, the damper is difficult to match the real-time vibration characteristics, and the shock absorption effect is greatly reduced.

[0004] At the monitoring level, the existing system relies on manual inspections to identify potential pipeline vibration hazards. This method is not only time-consuming and labor-intensive, but also fails to capture real-time vibration data. When pipeline vibration amplitude gradually increases and welds begin to crack, manual inspections often fail to detect them in time. These hazards can escalate during continued operation, ultimately leading to pipeline leaks or even downtime, seriously impacting equipment safety and production efficiency.

[0005] The core drawbacks of existing technologies are: the rigid fixed structure lacks vibration buffering capacity, the single damper cannot dynamically respond to complex vibration sources, and the manual monitoring mode has lags and the risk of missed detection. These three factors together lead to a high risk of fatigue damage to the electrolyzer outlet pipe. There is an urgent need for a new shockproof system that can take into account broadband vibration suppression, dynamic adaptive adjustment and intelligent monitoring.

[0006] In view of the above reasons, it is necessary to propose an anti-vibration stabilization device and method for an electrolytic cell gas outlet pipe to solve the above problems. Summary of the Invention

[0007] The purpose of the present invention is to overcome the defects in the prior art and provide an anti-vibration stabilization device and method for an electrolytic cell gas outlet pipe.

[0008] To achieve the above object, the technical solution of the present invention is as follows: An anti-vibration stabilization device for an electrolytic cell gas outlet pipe comprises a ring-shaped pipe rack arranged around the periphery of a material pipe in a form of full or partial surrounding, and a multi-layer composite vibration isolation portion is filled between the inner side of the ring-shaped pipe rack and the contact side of the material pipe; It also includes a fixed frame, an adaptive damping adjustment member is provided between the ring-shaped pipe frame and the fixed frame; and a vibration data collection mechanism arranged on the material pipeline.

[0009] Furthermore, the multi-layer composite vibration isolation part includes a shock-absorbing layer and a wear-resistant layer, and the wear-resistant layer and the shock-absorbing layer are sequentially arranged from the inside to the outside between the material pipeline and the ring-shaped pipe rack.

[0010] Furthermore, a plurality of air cavities are preset in the shock-absorbing layer, and the air cavities form the skeleton support of the shock-absorbing layer between the ring-shaped pipe rack and the material pipeline. The air cavities are closed chambers or open chambers with micropores. When the chamber is closed, the air cavity is filled with a medium or external pressure is applied to the air cavity to reach a preset pressure.

[0011] Furthermore, the air cavity is in the shape of a regular hexagonal column, and several air cavities are connected in a honeycomb shape. The setting direction of the air cavity is: 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 along the material pipeline; one or two stacked settings can be selected.

[0012] Furthermore, the shock-absorbing layer is made of any one or more materials selected from the group consisting of silicone rubber, nitrile rubber, polyurethane, asphalt-based damping rubber, and stainless steel wire braid. The shock-absorbing layer is a polytetrafluoroethylene coating.

[0013] Furthermore, the adaptive damping adjustment component includes a magnetorheological damper, and the damping force adjustment range is 0~500N·s / m; the response time is ≤20ms.

[0014] Furthermore, the ring-shaped pipe rack is installed in a suspended manner on the lower side of the fixed frame through an adaptive damping adjustment member; at least two groups of adaptive damping adjustment members are symmetrically arranged on both sides of the ring-shaped pipe rack; the two groups of adaptive damping adjustment members are erected in a diagonal form, and ball hinge structures are respectively provided at the ends of the adaptive damping adjustment members to connect the ring-shaped pipe rack and the fixed frame respectively.

[0015] Furthermore, the magnetorheological damper is arranged on the lower side of the ring-shaped pipe frame and is arranged between the ring-shaped pipe frame and the fixed frame in a supporting form.

[0016] Furthermore, it also includes an air pressure buffer chamber, which is a cylindrical cavity arranged at the elbow of the material pipeline, with a porous throttle plate inside, and a number of circular holes evenly distributed on the porous throttle plate. An elastic bellows is respectively provided at both ends of the inlet and outlet of the cylindrical cavity.

[0017] A control method for an anti-vibration stabilization device for an electrolytic cell gas outlet pipeline comprises the following steps: S1: The vibration data acquisition mechanism includes acceleration sensors, which 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; S2: The PLC control system performs fast Fourier transform on the received original vibration signal, decomposes the main frequency component of the vibration and the corresponding amplitude, and determines whether the vibration is low-frequency vibration or high-frequency vibration; S3: Based on the preset safety threshold and the vibration main frequency range, trigger the damping adjustment command and call the preset damping adjustment strategy; S4: The PLC system uses the proportional-integral-differential algorithm to calculate the required current value and adjusts the current required by the electromagnetic coil of the magnetorheological damper through the proportional, integral, and differential links; S5: By continuously adjusting the electromagnetic coil current, the damping force of the magnetorheological damper varies linearly within the range of 0-500N·s / m, covering a wide frequency vibration range of 0.1-50Hz, and the system delay from monitoring to adjustment is within 0.5 seconds.

[0018] The advantages and beneficial effects of the present invention are: 1. Multi-layer composite vibration isolation part: through the wear-resistant layer and shock-absorbing layer, with honeycomb air cavity design, it has both wear resistance and broadband shock-absorbing capabilities, and the high-frequency vibration attenuation rate is ≥90%.

[0019] 2. Honeycomb air cavity, 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.

[0020] 3. The regular hexagonal honeycomb structure has strong geometric stability and uniform stress dispersion, which reduces material consumption by 30-40%, is lightweight and has a longer fatigue life.

[0021] 4. Flexible axial arrangement of air cavities: they can be arranged along the axial or radial direction of the pipeline, or in a stacked combination to absorb vibrations in different directions in a targeted manner and enhance the multi-dimensional shock absorption effect.

[0022] 5. Structural integration optimization, the honeycomb cavity is embedded between the ring-shaped pipe rack and the pipeline, without the need for additional space, suitable for dense installation scenarios, and easy maintenance. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 This is a schematic longitudinal section diagram of a multi-layer composite vibration isolation portion of the anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to the present invention; Figure 2 This is a second schematic longitudinal cross-sectional view of the multi-layer composite vibration isolation portion of the anti-vibration stabilization device for the electrolytic cell outlet pipe of the present invention; Figure 3This is the third schematic longitudinal section diagram of the multi-layer composite vibration isolation portion of the anti-vibration stabilization device for the electrolytic cell outlet pipe of the present invention; Figure 4 This is a fourth schematic longitudinal cross-sectional view of the multi-layer composite vibration isolation portion of the anti-vibration stabilization device for the electrolytic cell outlet pipe of the present invention; Figure 5 This is one of the schematic diagrams of the installation method of the anti-vibration stabilization device for the electrolytic cell outlet pipe of the present invention; Figure 6 This is the second schematic diagram of the installation method of the anti-vibration stabilization device for the electrolytic cell outlet pipe of the present invention; Figure 7 Schematic diagram of the structure of the air pressure buffer chamber of the anti-vibration stabilization device for the gas outlet pipe of the electrolyzer of the present invention; In the figure: 1. Electrolytic cell body; 2. Material pipeline; 3. Ring-shaped pipe rack; 4. Multi-layer composite vibration isolation part; 5. C-shaped clamp; 6. Fixed frame; 7. Adaptive damping adjustment part; 8. Shock-absorbing layer; 9. Wear-resistant layer; 10. Air cavity; 11. Axially parallel arrangement; 12. Radially parallel arrangement; 13. Upper end plate; 14. Lower end plate; 15. Capsule cavity; 16. Magnetorheological fluid; 17. Electromagnetic coil; 18. Damping unit; 19. Elastic support assembly; 20. Guide rod; 21. Spring; 22. Limit nut; 23. Air pressure buffer cavity; 24. Cylindrical cavity; 25. Multi-porous throttling plate; 26. Elastic bellows; 27. Ball joint connection. DETAILED DESCRIPTION

[0024] The following embodiments are further described in conjunction with the accompanying drawings and examples. The following embodiments are only used to more clearly illustrate the technical solutions of the present invention and are not intended to limit the scope of protection of the present invention.

[0025] An anti-vibration stabilization device for an electrolytic cell gas outlet pipe comprises a ring-shaped pipe rack 3 arranged around the outer periphery of a material pipe 2 in a fully or partially enclosed form, and a multi-layer composite vibration isolation portion 4 is filled between the inner side of the ring-shaped pipe rack 3 and the contact side of the material pipe 2; Figure 1 shown.

[0026] In this embodiment, a multi-layer composite vibration isolation part 4 is formed by a multi-layer composite structure, specifically, it includes at least a three-layer structure of "rigid support + flexible shock absorption + wear-resistant coating", thereby solving the defect of excessive or low rigidity of traditional brackets. The rigid support is the ring-shaped pipe rack 3, and the ring-shaped pipe rack 3 is constructed as a C-shaped clamp 5 structure that matches the diameter of the material pipeline 2. It can be understood that a vibration isolation part needs to be set on the inner side of the ring-shaped pipe rack 3, so space for setting the vibration isolation part needs to be reserved between it and the material pipeline 2. In actual use, the ring-shaped pipe rack 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. The two clamp structures can form a circular pipe clamp shape relative to each other, such as Figure 2As shown, the material pipeline 2 is fixed in a fully enclosed manner; as another embodiment, 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.

[0027] The fully enclosed ring-shaped pipe rack 3 also includes a fixed frame 6, with an adaptive damping adjustment member 7 disposed between the ring-shaped pipe rack 3 and the fixed frame 6. A vibration data acquisition mechanism is also provided on the material pipeline 2. The vibration spectrum is collected in real time by an acceleration sensor array, combined with fluid pressure and temperature data, to achieve multi-dimensional hazard warning and adaptive adjustment of damping parameters through a PLC algorithm. The adaptive damping adjustment member 7 can be a magnetorheological damper, but other dampers with adjustable damping functions can also be used instead. This embodiment uses a magnetorheological damper as an example, and based on the intelligent damping adjustment of magnetorheological fluid 16, it achieves a wide-band vibration response of 0.1 to 50 Hz, addressing the poor frequency adaptability of a single damper.

[0028] Specifically, the multi-layer composite vibration isolation unit 4 includes a shock-absorbing layer 8 and a wear-resistant layer 9, which are positioned sequentially from the inside out between the material pipeline 2 and the ring-shaped pipe rack 3. In one embodiment, the shock-absorbing layer 8 is a polytetrafluoroethylene (PTFE) coating; the wear-resistant layer 9 utilizes an embedded silicone shock-absorbing layer 8 with a hardness of 30-50 Shore A. The contact surface with the pipeline is covered with a polytetrafluoroethylene (PTFE) wear-resistant coating, i.e., the wear-resistant layer 9, thereby reducing frictional vibration.

[0029] Furthermore, in addition to silicone, the shock-absorbing layer 8 can also be made of materials such as nitrile rubber, polyurethane, asphalt-based damping rubber, 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 rubber 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. Preferably, a silicone shock-absorbing layer 8 is used due to its low elastic modulus (0.1-10 MPa) and high loss factor (0.1-0.3), which is most effective in suppressing the resonance peak of high-frequency vibrations. For high-temperature environments (>100°C), a metallic rubber can be used; for oily environments, a nitrile rubber with a PTFE wear-resistant layer 9 can be used.

[0030] As an embodiment of the structure of the shock-absorbing layer 8, a plurality of air cavities 10 are preset in the shock-absorbing layer 8. The air cavities 10 form the skeleton support of the shock-absorbing layer 8 and are arranged between the ring-shaped pipe rack 3 and the material pipeline 2. Preferably, the air cavity 10 is in the shape of a regular hexagonal column, and a plurality of air cavities 10 are connected in a honeycomb shape.

[0031] Through the composite structure of "elastic material + air cavity 10", the following mechanisms are used to enhance high-frequency vibration absorption: 1. Elastic deformation of the silicone matrix: Vibration energy is consumed through the bending and stretching of the honeycomb wall; 2. Air cushion effect of the air cavity 10: Air compression / expansion generates damping force, suppressing vibration transmission; 3. Modal dispersion: The honeycomb array decomposes the overall vibration into multiple local vibrations to avoid a single resonant frequency.

[0032] The specific structural design is as follows: the honeycomb shape adopts the optimal geometric stability of a regular hexagon, with a side length of 3-5 mm and a cavity depth adapted to the thickness direction of the ring-shaped pipe frame 3; the wall thickness is 0.5-1 mm. The thinner the silicone wall, the better the elasticity, but the structural strength must be guaranteed; the distribution density is evenly distributed along the circumference of the pipe, containing 15-20 honeycomb units per 10 cm². In this embodiment, at least one of the two ends of the air cavity 10 is open, and the direction of the opening is: the honeycomb opening is perpendicular to the pipe axis to ensure that the vibration transmission direction (radial direction) is consistent with the air compression direction.

[0033] The honeycomb structure reduces material usage by 30-40%, lowering the overall weight of the bracket. It has a better attenuation effect on high-frequency vibrations, increasing the 30Hz vibration attenuation rate by 20%. However, since the air cavity 10 increases damping loss, solid silicone relies only on internal friction of the material, resulting in a lower attenuation efficiency.

[0034] As a second embodiment of the structure of the shock-absorbing layer 8, the air cavity 10 is a closed cavity. When set as a closed cavity, the air cavity 10 is filled with a medium or external pressure is applied to the air cavity 10 to achieve 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 of the air cavity 10 or changing the medium properties, thereby suppressing pipeline vibration. The method of applying external pressure is to squeeze and tighten the air cavity 10 by tightening the ring-shaped pipe frame 3 when providing a multi-layer composite vibration isolation part 4, thereby increasing the pressure of the internal closed cavity. This method is relatively simple and quick.

[0035] Filling medium: By filling the air chamber 10 with pure gas, such as nitrogen, increasing the internal pressure can increase the elastic modulus of the air chamber 10, thereby improving the ability to attenuate low-frequency vibrations (<20Hz). This method is low-cost and easy to implement, and is suitable for scenarios where low-frequency airflow pulsation is predominant, such as green power fluctuations <10Hz.

[0036] Alternatively, a gas-liquid mixture can be filled, specifically a gas-silicone oil mixture. This approach utilizes liquid to increase damping within the cavity. During high-frequency vibrations, the liquid inertia generates shear forces, while the gas provides elastic support, achieving broadband vibration reduction (5-50Hz). This implementation provides a more balanced vibration reduction effect.

[0037] Specific implementation plan: Gas filling solution: A filling hole is opened at the top of the honeycomb air cavity 10 in the silicone layer of the multi-layer composite stent, and a one-way valve (such as a duckbill valve) is installed. Nitrogen is initially filled to 0.05 MPa (gauge pressure). The pressure in the cavity is monitored by an air pressure sensor, and air is automatically replenished when it is lower than 0.03 MPa. A pressure relief hole can also be provided to automatically exhaust air when the pressure exceeds 0.1 MPa to prevent cavity explosion.

[0038] Gas-liquid mixing solution: A liquid injection hole is reserved at the bottom of the honeycomb cavity, and methyl silicone oil (viscosity 50cst, temperature resistance -30~200℃) accounting for 30% by volume 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.

[0039] As a third embodiment of the structure of the shock-absorbing layer 8, the air cavity 10 is an open chamber with micropores. Its principle is that air enters and exits through the micropores at both ends of the honeycomb cavity, creating a "piston-like" breathing effect. Vibration energy is dissipated through air viscous damping. The size of the micropores determines the resonant frequency, achieving resonant absorption of vibrations at specific frequencies. This viscous damping effect creates friction between the air passing through the micropores and the pore walls, creating a "damper"-like effect that suppresses non-resonant frequency vibrations. For specific frequency vibrations, such as the natural frequency of the pipeline, the attenuation rate can reach over 90%, without the need for active control, resulting in a purely passive structure.

[0040] Specific structural design: To simulate the short tube effect, a microhole is opened at each end of the honeycomb air cavity 10, with a pore diameter of φ0.5-1mm and a pore 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 and a cavity depth of 5mm, and a volume of about 2cm³.

[0041] Frequency matching calculation: Assuming the target attenuation frequency f0 = 25 Hz and the air sound speed c = 340 m / s, according to the Helmholtz formula: Take the micropore area A: Cavity volume V: Then the micropore length L is: 3D printing technology, such as silicone SLS printing, can be used to produce a honeycomb structure with micropores. The micropores must penetrate the silicone layer and have a smooth inner wall (roughness Ra ≤ 1.6 μm) to reduce air flow resistance loss.

[0042] This embodiment is more suitable for scenarios where the main frequency of the pipeline has been clearly identified through vibration testing, such as when the vibration amplitude of a certain frequency is prominent during long-term operation.

[0043] As a fourth embodiment of the structure of the shock-absorbing layer 8, based on the first embodiment of the structure of the shock-absorbing layer 8, 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 pipeline 2 11; or the axial direction of the air cavity 10 is parallel to the radial direction of the material pipeline 2 12; one or both of them can be stacked; when the two are stacked, the shock-absorbing layer 8 forms a multi-layer stacked structure design, such as Figure 4 shown.

[0044] Furthermore, the adaptive damping adjustment element 7 comprises a magnetorheological damper. The magnetorheological fluid 16 is composed of micron-sized magnetic particles (such as iron powder) dispersed in an insulating base fluid (such as silicone oil). In the absence of a magnetic field, the fluid is in a low-viscosity liquid state, allowing the piston in the damper to move freely and maintain a low-damping state. When a magnetic field is applied, the magnetic particles align in a chain-like structure along the magnetic field, hindering piston motion. This causes a sharp increase in viscosity and shear stress, shifting the damping force to a high-damping state. By varying the current in the electromagnetic coil 17, the magnetic field strength is adjusted in real time, creating a linear response relationship between "current-magnetic field-damping force," providing the physical conditions for damping adjustment. Leveraging the rheological properties of the magnetorheological fluid 16, under the influence of a magnetic field, the fluid can transition from a liquid state to a semi-solid state within milliseconds, significantly increasing the damping force. The damping force is then controlled by the intensity of the magnetic field generated by the electromagnetic coil 17. The damping force is continuously adjustable from 0 to 500 N·s / m. Dynamic control of the damping force is achieved by varying the input current or magnetic field strength, making it suitable for vibration suppression under different operating conditions. With a response time of ≤20ms, the system possesses rapid dynamic adjustment capabilities, enabling timely tracking of changes in external excitation and effectively improving the system's seismic resistance.

[0045] As an embodiment of the adaptive damping adjustment member 7, the ring-shaped pipe frame 3 is suspended and mounted on the lower side of the fixed frame body 6 through the adaptive damping adjustment member 7; Figure 5 As shown, at least two sets of adaptive damping adjustment members 7 are symmetrically arranged on both sides of the ring-shaped pipe frame 3; the two sets of adaptive damping adjustment members 7 are erected in a diagonal manner, and the ends of the adaptive damping adjustment members 7 are respectively provided with ball joint structures to connect the ring-shaped pipe frame 3 and the fixed frame body 6 respectively. Figure 5As shown, there is a fixed frame body 6 above the ring-shaped pipe rack 3, and a ball joint structure for suspension connection is provided on the upper outer wall of the ring-shaped pipe rack 3. Similarly, a corresponding ball joint structure is provided on the lower side of the fixed frame body 6. A rod-shaped magnetorheological damper is connected between the ball joint structures on both sides. In this way, under the dead weight of the material pipeline 2, it can be suspended in a balanced and stable position. When vibration occurs, not only the first-level vibration isolation is performed by the multi-layer composite vibration isolation part 4, but when the vibration is transmitted to the ring-shaped pipe rack 3, the second-level vibration isolation can be performed by the magnetorheological damper. The ball joint structure allows an angular deviation of ±5°. It can be understood that the ball joint deviation angle is not limited here and can be flexibly set according to actual needs to adapt to the axial or radial displacement with the pipeline.

[0046] As another embodiment of the adaptive damping adjustment member 7, the magnetorheological damper is arranged on the lower side of the ring-shaped pipe frame 3 and is arranged in a supporting form between the ring-shaped pipe frame 3 and the fixed frame body 6. Figure 6 As 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 capsule 15 with a certain deformation support capacity filled with magnetorheological fluid 16 is provided in the gap between the two, so that it can adapt to the slight change of the gap between the upper and lower end plates 14 when they vibrate; an electromagnetic coil 17 is provided on the periphery of the magnetorheological fluid 16, and the size of its magnetic field is changed by controlling the current of the coil, thereby changing the overall damping. It can be understood that the electromagnetic coil 17 and the magnetic The rheological fluid 16 forms a damping unit 18, and multiple such damping units 18 can be set between the upper and lower end plates 14. The figure only takes the setting of one unit as an example. Multiple damping units 18 are laid flat in the gap, and the number of units is selected according to the area of ​​the end plate; and an elastic support component 19 can be added around the outer periphery of the adaptive damping adjustment member 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 the upper end of the guide rod 20 passes through the upper end plate 13 to set a limit nut 22.

[0047] Furthermore, it also includes an air pressure buffer chamber 23, which is a cylindrical cavity 24 set at the elbow of the material pipeline 2. In actual use, the air pressure buffer chamber 23 can be set as an independent and detachable cylindrical cavity 24, and formed and installed at the 90° elbow of the electrolytic cell outlet pipe. The elbow is the place where the air flow turns most violently. It is rigidly connected to the pipe through a flange to form a "pipeline-buffer chamber-pipeline" series structure. Specifically, as Figure 7 As shown, its core components are as follows: The chamber body is made of corrosion-resistant 304 stainless steel, suitable for hydrogen environments. Its wall thickness is 5-8mm to ensure pressure resistance, with a design pressure of 1.0MPa and an operating pressure of 0.1-0.5MPa. Its cylindrical shape matches the pipe's inner diameter. 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.

[0048] The core internal components include a multi-hole throttle plate 25, located in the center of the cavity, perpendicular to the airflow direction. The plate features evenly distributed circular holes with a diameter of 2 to 5 mm, 10 to 30 holes, and a spacing of 10 to 15 mm. Also included is an elastic bellows 26, located at each cavity inlet and outlet. The length is approximately 50 to 80 mm and is made of corrugated stainless steel, allowing ±10 mm of axial and radial displacement. A pressure sensor interface is also provided at the top for real-time monitoring of the cavity pressure, and a drain outlet is located at the bottom to regularly remove condensate or impurities.

[0049] Its specific operating principle is to use a porous throttle plate 25 to "cut" the high-speed airflow, breaking down large-scale pulsations into small-scale vortices and reducing the amplitude of the airflow pressure fluctuations. An elastic bellows 26 isolates the vibration transmission between the cavity and the pipeline, preventing the buffer chamber itself from becoming a vibration source. When air flows through the throttle plate, friction between the high-speed airflow in the holes and the hole walls produces viscous damping. At the same time, the airflow between the holes collides with each other, forming vortices that consume the airflow kinetic energy. Tests have shown that this can reduce the amplitude of airflow pulsation by 30% to 50%, thereby reducing the impact force of the airflow on the pipeline. Regarding vibration isolation, the flexible connection of the elastic bellows 26 allows for small relative motion between the pipeline and the buffer chamber, acting like a "soft connection" that disconnects the vibration transmission path and prevents pressure fluctuations within the buffer chamber from being directly transmitted to the pipe elbow weld. The cavity volume acts as an "air spring 21." When the airflow suddenly changes, such as when the green power load jumps, the gas in the cavity compresses and expands to absorb energy, thus preventing transient high-pressure shocks in the pipeline.

[0050] The pneumatic buffer chamber 23 and the ring-shaped pipe frame 3 formed by the multi-layer composite vibration isolation portion 4 work synergistically: the frame's silicone damping layer 8 absorbs high-frequency structural vibrations (>20Hz), while the buffer chamber attenuates low-frequency airflow pulsations (5-20Hz), providing full coverage of both high and low-frequency vibrations. When the green power 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, while the frame absorbs the residual structural vibrations, ultimately achieving a total vibration attenuation rate of over 90%. The synergistic effect of the linkage between the air pressure buffer chamber 23 and the magnetorheological damper is as follows: the PLC system judges the air flow pulsation intensity based on the air pressure sensor data in the buffer chamber: if the air pressure fluctuation is greater than 0.1MPa (corresponding to high pulsation conditions), the magnetorheological damper current is synchronously increased to 1.2A to enhance the bracket's suppression of low-frequency vibration; if the air pressure is stable, the damper maintains a low current (0.3A) to save energy.

[0051] A control method for an anti-vibration stabilization device for an electrolytic cell gas outlet pipeline comprises the following steps: S1: The vibration data acquisition mechanism includes an acceleration sensor, which is arranged at the key points of the material pipeline 2 to collect vibration signals in real time and transmit the vibration acceleration time domain waveform to the PLC control system. Specifically, data acquisition relies on the acceleration sensors arranged at the key points of the pipeline (such as elbows and bracket connections) to monitor the vibration signal in real time (range ±50g, accuracy ±1%) and transmit the vibration acceleration time domain waveform (such as vibration amplitude and frequency component) to the PLC control system.

[0052] 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 the corresponding amplitude, and determines whether the vibration is low-frequency vibration or high-frequency vibration; 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 the corresponding amplitude, and determines whether the current vibration is low-frequency vibration (≤20Hz, such as caused by airflow pulsation) or high-frequency vibration (>20Hz, such as caused by mechanical resonance).

[0053] S3: Based on the preset safety threshold and the dominant vibration frequency range, the damping adjustment command is triggered and the preset damping adjustment strategy is invoked. Preset safety thresholds: If the pipe displacement exceeds 5mm or the amplitude of a certain frequency exceeds 80% of the natural frequency amplitude, the damping adjustment command is triggered. Vibration type matching: Based on the dominant frequency range, the preset damping adjustment strategy is invoked, such as increasing damping at low frequencies and prioritizing passive vibration reduction through the silicone layer at high frequencies.

[0054] S4: The PLC system calculates the required current value using a proportional-integral-differential algorithm, and adjusts the current required by the electromagnetic coil 17 of the magnetorheological damper through proportional, integral, and differential links; Specific implementation of regulation control: accurate mapping of current and damping force; Actuator: electromagnetic coil 17 and piston structure; The magnetorheological damper contains: Electromagnetic coil 17: Wound around the outside of the damper cylinder, power 50~100W, current adjustment range 0~2A.

[0055] Piston assembly: A flow channel is opened on the piston, and the resistance of the magnetorheological fluid 16 when passing through the flow channel is the source of the damping force.

[0056] Control Algorithm: PID closed-loop regulation. The PLC system calculates the required current value using the proportional-integral-derivative (PID) algorithm based on the vibration spectrum analysis results. The specific process is as follows: Proportional Phase: Rapidly adjusts the current based on the deviation between the current vibration amplitude and the target value. A larger deviation results in a higher current. Integral Phase: Eliminates long-term deviations to ensure that the damping force remains stable at the target value. For example, during continuous low-frequency vibration, a high current is maintained. Differential Phase: Predicts vibration trends and adjusts the current in advance to suppress vibration peaks. For example, if high-frequency vibration is anticipated, the current damping is increased preemptively.

[0057] S5: Continuous adjustment of the current of the electromagnetic coil 17 causes the damping force of the magnetorheological damper to vary linearly within the range of 0-500 N·s / m, covering a wide frequency vibration range of 0.1-50 Hz, and the delay from monitoring to adjustment of the system is within 0.5 seconds.

[0058] Dynamic response process: When low-frequency vibration is detected, such as green power fluctuations causing an airflow frequency of 5Hz, the PLC output current increases to 1.5A. The enhanced magnetic field increases the viscosity of the magnetorheological fluid 16, and the damping force increases from the initial 100N·s / m to 400N·s / m, suppressing low-frequency shaking of the pipeline.

[0059] When high-frequency vibrations, such as 30 Hz vibrations caused by a compressor, occur, the PLC determines that the energy is mainly absorbed by the silicone shock-absorbing layer 8, maintaining a current of only 0.5 A and a damping force of 150 N·s / m to prevent excessive damping from affecting pipeline flexibility.

[0060] The unity of broadband response and adaptive adjustment; 0.1~50Hz broadband coverage: Through continuous current adjustment (0~2A), the damping force can be linearly varied in the range of 0~500N・s / m, matching the full frequency band requirements from slow airflow pulsation 0.1Hz to high-speed mechanical vibration 50Hz.

[0061] Adjustment delay ≤ 0.5 seconds: The magnetic field response of the magnetorheological fluid 16 is in the millisecond range (≤ 20ms). Combined with the PLC's data processing and command transmission time, the overall system delay from monitoring to adjustment is controlled within 0.5 seconds, which can promptly suppress sudden vibrations such as load changes.

[0062] This closed-loop mechanism of "monitoring-analysis-control" enables the magnetorheological damper to dynamically adjust the damping parameters according to the real-time vibration characteristics, avoiding the "one-size-fits-all" limitations of traditional single dampers and achieving precise suppression of the vibration of the electrolytic cell outlet pipe.

[0063] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present invention. These improvements and modifications should also be regarded as within the scope of protection of the present invention.

Claims

1. An anti-vibration stabilization device for an electrolytic cell gas outlet pipe, characterized in that: A ring-shaped pipe rack is provided around the outer periphery of the material pipeline in a form of full or partial surrounding, and a multi-layer composite vibration isolation part is filled between the inner side of the ring-shaped pipe rack and the contact side of the material pipeline; It also includes a fixed frame, an adaptive damping adjustment member is provided between the ring-shaped pipe frame and the fixed frame; and a vibration data collection mechanism arranged on the material pipeline.

2. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 1, characterized in that: The multi-layer composite vibration isolation part includes a shock-absorbing 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 rack.

3. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 2, characterized in that: A plurality of air cavities are preset in the shock-absorbing layer, and the air cavities form the skeleton support of the shock-absorbing layer between the ring-shaped pipe rack and the material pipeline. The air cavities are closed chambers or open chambers with micropores; When the chamber is closed, the air cavity is filled with a medium or external pressure is applied to the air cavity to reach a preset pressure.

4. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 3, characterized in that: The air cavity is in the shape of a regular hexagonal column, and a plurality of air cavities are connected and arranged in a honeycomb shape.

5. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 3, characterized in that: The shock-absorbing layer is made of any one or more materials selected from the group consisting of silicone rubber, nitrile rubber, polyurethane, asphalt-based damping rubber, and stainless steel wire braid. The shock-absorbing layer is a polytetrafluoroethylene coating.

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

7. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 1, characterized in that: The ring-shaped pipe rack is suspended and installed on the lower side of the fixed frame through an adaptive damping adjustment member; at least two sets of adaptive damping adjustment members are symmetrically arranged on both sides of the ring-shaped pipe rack; the two sets of adaptive damping adjustment members are erected in an obliquely pulled form, and ball hinge structures are respectively provided at the ends of the adaptive damping adjustment members to connect the ring-shaped pipe rack and the fixed frame respectively.

8. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 6, characterized in that: The magnetorheological damper is arranged on the lower side of the ring-shaped pipe frame and is arranged between the ring-shaped pipe frame and the fixed frame in a supporting form.

9. The anti-vibration stabilization device for the gas outlet pipe of an electrolyzer according to claim 1, characterized in that: It also includes an air pressure buffer chamber, which is a cylindrical cavity arranged at the elbow of the material pipeline. A porous throttle plate is provided inside the cavity, and a number of circular holes are evenly distributed on the porous throttle plate. An elastic bellows is provided at both ends of the inlet and outlet of the cylindrical cavity.

10. A control method for an anti-vibration stabilization device for an electrolytic cell outlet pipe, characterized in that: The following steps are involved: S1: The vibration data acquisition mechanism includes acceleration sensors, which 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; S2: The PLC control system performs fast Fourier transform on the received original vibration signal, decomposes the main frequency component of the vibration and the corresponding amplitude, and determines whether the vibration is low-frequency vibration or high-frequency vibration; S3: Based on the preset safety threshold and the vibration main frequency range, trigger the damping adjustment command and call the preset damping adjustment strategy; S4: The PLC system uses the proportional-integral-differential algorithm to calculate the required current value and adjusts the current required by the electromagnetic coil of the magnetorheological damper through the proportional, integral, and differential links; S5: Through continuous adjustment of the electromagnetic coil current, the damping force of the magnetorheological damper changes linearly in the range of 0-500N·s / m, covering the wide frequency vibration range of 0.1-50Hz.

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