A dual-redundancy helical screen damper suitable for high-frequency pressure pulse impact

Abstract

This invention discloses a dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact, relating to the technical field of mechanical structures and hydraulic systems. It includes an inlet section, a damping section, and an outlet section sequentially arranged on the filter damper body. The inlet section has a boss and a groove at the end furthest from the damping section, arranged in a stepped manner. A guide channel is provided at the end of the inlet section facing the damping section, communicating with both the first and second mesh openings. The spiral flow channel of the damping section is connected to the guide channel and the outlet section. The stepped inlet structure enables graded interception and sedimentation of impurities. The spiral flow channel extends the damping path, weakens fluid coupling interference, efficiently attenuates kilohertz-level high-frequency pulsations, suppresses hydraulic resonance, improves sensor signal distortion, and protects the sensor for stable operation. Simultaneously, the dual spiral flow channels constitute a physical redundancy architecture; if one flow channel fails due to blockage, the remaining channels can continue to operate normally, completely eliminating the risk of single-point failure.

Description

Technical Field

[0001] This invention relates to the field of mechanical structure and hydraulic system technology, and in particular to a dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact. Background Technology

[0002] In hydraulic systems operating under high-frequency pressure pulse conditions, hydraulic dampers are core components that protect precision pressure sensors, attenuate pressure pulsations, and stabilize pipeline pressure. Currently, most mainstream dampers in the industry adopt a single throttling orifice, capillary tube, or variable throttling valve structure, which can meet the needs of conventional operating conditions. However, in demanding scenarios such as aerospace, heavy equipment, and high-frequency servo control, these traditional dampers have several key technical defects and are difficult to adapt to high-end operating conditions.

[0003] Traditional dampers are designed based on steady-state throttling theory, with fixed throttling structure dimensions and extremely poor dynamic response performance. When faced with high-frequency pressure pulses at the 100Hz or even 1000Hz levels, the coupling of fluid inertia and cavity effects significantly alters the dynamic impedance of the throttling orifice, leading to a sharp drop in high-frequency pressure pulsation attenuation efficiency and even causing hydraulic resonance amplification. This not only causes phase lag and amplitude distortion in sensor measurement signals, reducing system control accuracy, but also fails to effectively dissipate instantaneous overpressure energy, subjecting the sensor diaphragm to prolonged excessive alternating stress, making it highly susceptible to fatigue fracture, zero-point drift, and other faults, endangering the safe operation of the control system. Furthermore, existing dampers have poor media adaptability; the narrow throttling gap is easily blocked by metal shavings, rust particles, and colloidal deposits in the hydraulic medium. The accumulation and wedging of solid particles can cause orifice narrowing and blockage, altering damping attenuation performance, and can also erode the throttling orifice, causing permanent wear, leading to equipment performance degradation, forcing frequent system shutdowns for maintenance, and significantly increasing maintenance costs and production losses.

[0004] Therefore, there is an urgent need for a filter damper suitable for high-frequency pressure pulse impact. Summary of the Invention

[0005] To solve the above technical problems, the present invention provides a dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact.

[0006] To achieve the above objectives, the present invention provides the following solution: This invention provides a dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact, comprising a filter damper body, wherein along a first direction, the filter damper body comprises an inlet section, a damping section and an outlet section arranged sequentially; The inlet section is provided with a boss and a groove at the end away from the damping section, and the boss and the groove are arranged in a stepped manner along the first direction; the boss is provided with a first mesh, and the groove is provided with a second mesh; A flow guide groove is provided at one end of the inlet section facing the damping section, and the flow guide groove is connected to both the first mesh and the second mesh. The damping section includes at least two helical channels, one end of which is connected to the guide groove, and the other end of which is connected to the outlet section.

[0007] Optionally, a first guide hole is provided at one end of the damping section facing the inlet section, and the first guide hole is connected to both the guide groove and the spiral flow channel.

[0008] Optionally, along the second direction, the projection of the first guide hole coincides with the projections of the guide groove and the spiral flow channel, and the second direction is perpendicular to the first direction.

[0009] Optionally, the outlet section is provided with a pressure chamber, and the spiral flow channel is connected to the pressure chamber.

[0010] Optionally, the effective volume of the pressure chamber is greater than the volume of a single spiral flow channel.

[0011] Optionally, a second guide hole is provided at one end of the spiral flow channel facing the outlet section, and the axis of the second guide hole is perpendicular to the first direction; the second guide hole is connected to the pressure chamber.

[0012] Optionally, the second guide hole is connected to the pressure chamber through a third guide hole.

[0013] Optionally, a fourth guide hole is provided at the end of the pressure chamber away from the damping section.

[0014] Optionally, the bottom surface of the groove is a flow guide surface, and the second mesh is disposed on the flow guide surface near the boss.

[0015] Optionally, the guide surface is an inclined surface, a curved surface, or a stepped surface.

[0016] The present invention achieves the following technical effects compared to the prior art: When using the dual-redundant spiral filter damper for high-frequency pressure pulse impact provided by this invention, the hydraulic medium first undergoes staged filtration through the bosses and grooves in the inlet section. This intercepts impurities such as metal shavings and rust particles in the medium, trapping them in the grooves. This prevents solid particles from directly impacting the damping channel, reducing channel blockage, particle wedging, and channel erosion and wear. This achieves a self-cleaning filtration effect, significantly improving the damper's adaptability to hydraulic media with complex cleanliness levels. It effectively solves the technical problems of traditional dampers, such as easy clogging, permanent performance degradation, and high maintenance costs. After filtration, the medium is evenly distributed through the guide channel and smoothly introduced into the spiral channel of the damping section. Compared to the steady-state throttling mode of traditional fixed orifices, the spiral channel can extend the fluid damping path, change the flow state of the high-frequency fluid, weaken the coupling interference of fluid inertia and cavity effect, and adapt to kilohertz-level high-frequency pressure pulse conditions. Through the multi-stage buffering and energy dissipation effect of the helical flow channel, high-frequency pressure pulsation can be efficiently attenuated and hydraulic resonance can be suppressed. This effectively eliminates the problems of sensor signal phase lag and amplitude distortion, improving the control accuracy of the servo control system. At the same time, it fully dissipates instantaneous overpressure energy, preventing the sensor diaphragm from being subjected to alternating over-limit stress, eliminating fatigue fracture and zero-point drift failures, and ensuring the long-term stable operation of the hydraulic system. Furthermore, this invention adopts a dual-redundant architecture with multiple helical flow channels, forming multiple independent flow damping channels, completely eliminating the defects of traditional single-channel single-point failure. Even if a single spiral flow channel experiences flow obstruction due to extreme impurity accumulation or low-temperature ice blockage, the remaining flow channels can still perform damping and pressure stabilization normally. This prevents situations such as pipeline breakage or high-pressure medium directly impacting the sensor, avoiding a chain of safety problems caused by single-point failures, such as sensor damage, equipment shutdown, and power unit malfunction. It greatly improves the operational reliability and fault tolerance of the damper, and can be widely adapted to harsh operating conditions with high reliability and high safety levels, such as aerospace, heavy equipment, and nuclear power. It effectively fills the technical gaps in existing damping devices in terms of high-frequency attenuation, anti-clogging self-cleaning, and fault-tolerant protection. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the structure of the dual-redundant spiral filter damper applicable to high-frequency pressure pulse impact according to the present invention; Figure 2 for Figure 1 AA section view diagram; Figure 3This is a top-view three-dimensional structural diagram of the dual-redundant spiral filter damper applicable to high-frequency pressure pulse impact according to the present invention. Figure 4 This is a bottom-view three-dimensional structural diagram of the dual-redundant spiral filter damper applicable to high-frequency pressure pulse impact of the present invention. Figure 5 This is a schematic diagram of a second embodiment of the dual-redundant spiral filter damper applicable to high-frequency pressure pulse impact of the present invention. Figure 6 This is a schematic diagram of the third embodiment of the dual-redundant spiral filter damper applicable to high-frequency pressure pulse impact of the present invention. Figure 7 This is a schematic diagram of the fourth embodiment of the dual-redundant spiral filter damper applicable to high-frequency pressure pulse impact of the present invention.

[0019] Explanation of reference numerals in the attached drawings: 1. Filter damper body; 2. First mesh; 3. Boss; 4. Groove; 5. Guide groove; 6. First guide hole; 7. Spiral flow channel; 8. Second guide hole; 9. Third guide hole; 10. Pressure chamber; 11. Fourth guide hole; 12. Bearing; 13. Fixing sleeve; 14. Receiving groove; 15. Filter damping mesh. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0021] Example 1: like Figures 1 to 4 As shown, this embodiment provides a dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact, including a filter damper body 1. Along the first direction, the filter damper body 1 includes an inlet section, a damping section and an outlet section arranged sequentially. The end of the inlet section away from the damping section is provided with a boss 3 and a groove 4. Along the first direction, the boss 3 and the groove 4 are arranged in a stepped manner. The boss 3 is provided with a first mesh 2, and the groove 4 is provided with a second mesh. A guide channel 5 is provided at the end of the inlet section facing the damping section, and the guide channel 5 is connected to both the first mesh 2 and the second mesh. The damping section includes at least two helical channels 7, one end of which is connected to the guide channel 5, and the other end of which is connected to the outlet section.

[0022] When using the dual-redundant spiral filter damper for high-frequency pressure pulse impact provided by this invention, the hydraulic medium first undergoes staged filtration through the boss 3 and groove 4 in the inlet section. This intercepts impurities such as metal shavings and rust particles in the medium, trapping them in the groove 4. This prevents solid particles from directly impacting the damping channel, reducing channel blockage, particle wedging, and channel erosion and wear. This achieves a self-cleaning filtration effect, significantly improving the damper's adaptability to hydraulic media with complex cleanliness levels. It effectively solves the technical problems of traditional dampers, such as easy clogging, permanent performance degradation, and high maintenance costs. After filtration, the medium is evenly distributed through the guide groove 5 and smoothly introduced into the spiral channel 7 of the damping section. Compared to the steady-state throttling mode of the traditional fixed throttling orifice, the spiral channel 7 can extend the fluid damping path, change the flow state of the high-frequency fluid, weaken the coupling interference of fluid inertia and cavity effect, and adapt to kilohertz-level high-frequency pressure pulse conditions. Through the multi-stage buffering and energy dissipation effect of the spiral flow channel 7, high-frequency pressure pulsation can be efficiently attenuated and hydraulic resonance can be suppressed. This effectively eliminates the problems of sensor signal phase lag and amplitude distortion, improving the control accuracy of the servo control system. At the same time, it fully dissipates instantaneous overpressure energy, preventing the sensor diaphragm from being subjected to alternating over-limit stress, eliminating fatigue fracture and zero-point drift failures, and ensuring the long-term stable operation of the hydraulic system. Furthermore, this invention adopts a dual-redundancy architecture with multiple spiral flow channels 7, forming multiple independent flow damping channels, completely eliminating the defects of traditional single-channel single-point failure. Even if the flow of a single spiral channel 7 is obstructed due to extreme impurity accumulation or low-temperature ice blockage, the remaining channels can still perform damping and pressure stabilization normally. There will be no pipe breakage or high-pressure medium directly impacting the sensor. This avoids the chain of safety problems caused by single-point failure, such as sensor damage, equipment shutdown, and power unit malfunction. It greatly improves the operational reliability and fault tolerance of the damper and can be widely adapted to the harsh conditions of high reliability and high safety in aerospace, heavy equipment, nuclear power, etc. It effectively fills the technical gap of existing damping devices in high-frequency attenuation, anti-clogging self-cleaning, fault tolerance and multi-dimensional performance.

[0023] A first guide hole 6 is provided at the end of the damping section facing the inlet section. The first guide hole 6 is connected to both the guide groove 5 and the spiral flow channel 7. The parallel layout of the double spiral flow channels 7 forms a physical redundant path, which can realize multi-stage spiral damping with fluid splitting. When any one spiral flow channel 7 is blocked by extreme pollutants or ice crystals, the other independent flow channel can still continue to work, ensuring that the pressure sensor will not be directly exposed to high pressure impact due to damper failure. This completely eliminates the risk of single-point failure in the existing technology, and is especially suitable for fields with high reliability requirements such as aerospace and deep-sea equipment. It utilizes the centrifugal dissipation effect generated by spiral swirling flow to efficiently break up and attenuate high-frequency pressure pulsations, solving the problems of high-frequency resonance and insufficient attenuation capability of traditional straight-hole throttling structures.

[0024] Along the second direction, the projection of the first guide hole 6 coincides with the projections of the guide groove 5 and the spiral flow channel 7, and the second direction is perpendicular to the first direction. This coaxial projection matching structure enables fluid to be introduced into the spiral flow channel 7, improving the synchronization and stability of the damping response under high-frequency pressure pulses.

[0025] The outlet section is equipped with a pressure chamber 10, and the spiral flow channel 7 is connected to the pressure chamber 10. The fluids in the two spiral flow channels 7, after being damped and attenuated, flow out of the spiral flow channels 7 through the second guide hole 8 and the third guide hole 9 respectively, and then re-merge in the pressure chamber 10.

[0026] The effective volume of pressure chamber 10 is greater than the volume of a single spiral channel 7. Since the volume of pressure chamber 10 is significantly larger than the single-turn volume of the guide hole and spiral channel 7, the liquid or gas flowing into it forms an elastic buffer "air cushion". When the upstream pressure pulse peak arrives, the medium in the chamber is compressed and absorbs excess energy; when the trough arrives, the medium expands and releases energy to replenish the pressure, thereby performing a second integral smoothing of the residual pressure gradient and further reducing the pulsation amplitude.

[0027] A second guide hole 8 is provided at one end of the spiral flow channel 7 facing the outlet section. The axis of the second guide hole 8 is perpendicular to the first direction. The second guide hole 8 is connected to the pressure chamber 10. The second guide hole 8 and the pressure chamber 10 are connected through a third guide hole 9. The multi-stage vertical reversing flow guide structure can perform secondary rectification and throttling buffering on the pulsating fluid output from the spiral flow channel 7, dissipate residual pressure peaks step by step, break the continuous impact of fluid inertia, further weaken the high-frequency pulsation amplitude, and avoid the problem of pressure signal phase lag.

[0028] A fourth guide hole 11 is provided at the end of the pressure chamber 10 away from the damping section. After the fluid is stabilized and smoothed by the pressure chamber 10, it is uniformly output to the downstream sensor pipeline through the fourth guide hole 11, ensuring stable outlet pressure and uniform flow field, effectively isolating instantaneous overpressure impact, and protecting the precision pressure sensor from high-frequency alternating stress damage in all aspects.

[0029] The bottom surface of the groove 4 is a guide surface, and the second mesh is located on the guide surface near the boss 3. This allows impurities falling into the groove 4 to automatically slide towards the storage dead corner at the bottom of the groove 4 under the combined action of gravity and pulse vibration, preventing intercepted particles from being swept up by the high-speed fluid and clogging the mesh again. The guide surface can be a sloped surface, a curved surface, or a stepped surface.

[0030] After undergoing the three-stage treatment of filtration, damping, and buffering, the stable pressure medium finally flows smoothly through the fourth guide hole 11 to the sensitive element of the downstream pressure sensor, ensuring that the pressure signal obtained by the sensor is real, stable, and free of spikes.

[0031] In a more specific embodiment, the guide channels 5 are arranged in a ring or radial pattern to collect the filtered cleaning medium.

[0032] The cross-sectional shapes of the two helical grooves are preferably semi-circular, rectangular, or trapezoidal, with consistent effective cross-sectional areas. Furthermore, the number of helical turns, pitch, and helix angle are identical for both grooves to ensure perfectly symmetrical flow resistance characteristics in normal operation. The two helical grooves are completely separated by a solid partition wall, preventing fluid interference. They share a common guide hole at the starting end and exit through independently opened guide holes at the ends. To ensure structural strength under high pressure, the thickness of the solid partition wall is sufficient to withstand the ultimate pressure difference that may occur on both sides without fracturing.

[0033] Furthermore, such as Figure 5 As shown, a fixed sleeve 13 is also provided on the outside of the filter damper body 1, and a bearing 12 is provided between the fixed sleeve 13 and the filter damper body 1, so that the filter damper body 1 can rotate relative to the fixed sleeve 13. In use, since the fixed sleeve 13 is a fixed installation structure, when the fluid flows through the filter damper body 1, it flows along the spiral flow channel 7, forming a spiral reaction force on the filter damper body 1, driving the filter damper body 1 to rotate relative to the fixed sleeve 13, converting the kinetic energy of the fluid into the mechanical energy of the rotation of the filter damper body 1, further consuming the kinetic energy of the fluid. At the same time, it can centrifugally filter the fluid and impurities in the groove 4, so that the impurities are concentrated at the edge of the groove 4. At this time, it is only necessary to set the second mesh near the center of the groove 4 to reduce the possibility of impurities clogging or entering the second mesh, and further improve the filtration effect.

[0034] More specifically, such as Figure 6 As shown, a receiving cavity is provided between the fixed sleeve 13 and the filter damper body 1. The receiving cavity is located at one end of the spiral flow channel 7 near the guide groove 5. After the fluid is introduced into the receiving cavity through the guide groove 5, it smoothly enters the spiral flow channel 7. The receiving cavity can temporarily retain some solid impurities in the fluid, reducing the direct impact of impurities into the spiral flow channel 7, which would cause flow channel wear and blockage, and extend the service life of the device. After the fluid completes pre-pressure stabilization in the receiving cavity, it spirals along the spiral flow channel 7. Relying on the friction resistance and swirling dissipation of the spiral flow channel, it continuously consumes the fluid's kinetic energy, working together with the downstream filter damper to achieve a multi-stage damping and pressure stabilization effect.

[0035] To further enhance the impurity interception effect, the inner wall of the receiving cavity is provided with several interception teeth, each with a rotation direction opposite to that of the spiral flow channel 7. Adjacent interception teeth enclose and form a receiving groove 14. After entering the receiving cavity from the guide channel 5, the fluid enters the spiral flow channel 7. Under the interaction between the spiral flow channel 7 and the fluid, the filter damper body 1 rotates, causing the fluid within the receiving cavity to rotate. Solid impurities carried by the fluid adhere to the inner wall of the receiving cavity under centrifugal force. When impurities collide with the counter-rotating interception teeth, the flow direction is disturbed, and the kinetic energy is significantly reduced. Heavier impurities settle due to their own weight and are collected in the receiving groove, achieving pre-interception of impurities. The counter-rotating interception teeth can disrupt the original swirling state of the fluid, inhibiting impurities from directly entering the spiral flow channel 7 with the fluid, reducing the risk of particle erosion and abrasion of the inner wall of the spiral flow channel and channel blockage. The intercepted fluid continues to be conveyed backward around the intercepting teeth and smoothly enters the spiral flow channel for damping and energy dissipation. Together with the downstream filter damping mesh, it forms a graded impurity interception structure, which significantly improves the overall filtration reliability.

[0036] In another specific embodiment, such as Figure 7 As shown, a filter damping mesh 15 is also provided at the outlet end of the filter damper body 1. The filter damping mesh 15 can not only further filter impurities in the fluid, but also further damp the fluid, optimizing the flow velocity and pressure distribution when the fluid flows out. The filter damping mesh 15 and the filter damper body 1 are assembled by a detachable snap-fit ​​method, which facilitates the later disassembly and cleaning of the trapped solid impurities and avoids long-term accumulation of impurities causing channel blockage. At the same time, the filter damping mesh 15 is arranged perpendicular to the fluid outflow direction. When the fluid passes through the mesh, local eddies are generated, which consume the fluid kinetic energy. Combined with the internal damping structure of the body, a multi-stage damping effect is formed, which improves the overall vibration reduction and pressure stabilization effect. In addition, the filter damping mesh 15 is made of erosion-resistant and corrosion-resistant metal woven mesh. The mesh size is smaller than that of the upstream filter structure, realizing gradient filtration, preventing small particles from being output with the fluid, and ensuring that downstream pipeline components are not worn by impurities.

[0037] It should be noted that, for those skilled in the art, it is obvious that the present invention is not limited to the details of the above exemplary embodiments, and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention, and no reference numerals in the claims should be construed as limiting the scope of the claims.

[0038] This specification uses specific examples to illustrate the principles and implementation methods of the present invention. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of the present invention. Furthermore, those skilled in the art will recognize that, based on the ideas of the present invention, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact, characterized in that, The filter damper body includes an inlet section, a damping section, and an outlet section arranged sequentially along a first direction. The inlet section is provided with a boss and a groove at the end away from the damping section, and the boss and the groove are arranged in a stepped manner along the first direction; the boss is provided with a first mesh, and the groove is provided with a second mesh; A flow guide groove is provided at one end of the inlet section facing the damping section, and the flow guide groove is connected to both the first mesh and the second mesh. The damping section includes at least two helical channels, one end of which is connected to the guide groove, and the other end of which is connected to the outlet section.

2. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 1, characterized in that, The damping section is provided with a first guide hole at one end facing the inlet section, and the first guide hole is connected to both the guide groove and the spiral flow channel.

3. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 2, characterized in that, Along the second direction, the projection of the first guide hole coincides with the projections of the guide groove and the spiral flow channel, and the second direction is perpendicular to the first direction.

4. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 1, characterized in that, The outlet section is provided with a pressure chamber, and the spiral flow channel is connected to the pressure chamber.

5. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 4, characterized in that, The effective volume of the pressure chamber is greater than the volume of a single spiral flow channel.

6. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 4, characterized in that, The spiral flow channel is provided with a second guide hole at one end facing the outlet section, and the axis of the second guide hole is perpendicular to the first direction; the second guide hole is connected to the pressure chamber.

7. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 6, characterized in that, The second guide hole is connected to the pressure chamber through a third guide hole.

8. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 4, characterized in that, A fourth guide hole is provided at the end of the pressure chamber away from the damping section.

9. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 1, characterized in that, The bottom surface of the groove is a flow guide surface, and the second mesh is located on the flow guide surface near the boss.

10. The dual-redundant spiral filter damper suitable for high-frequency pressure pulse impact according to claim 9, characterized in that, The guiding surface is an inclined surface, a curved surface, or a stepped surface.

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