Industrial pipeline resonance suppression damper

Abstract

The utility model discloses an industrial pipeline resonance suppression damper which comprises a plurality of upper frequency band vibration reduction pieces, a plurality of lower frequency band vibration reduction pieces and two damper installation bases. The upper frequency band vibration reduction parts and the lower frequency band vibration reduction parts are alternately arranged on the damper mounting seat at uniform intervals; the upper frequency band vibration reduction piece and the lower frequency band vibration reduction piece are each composed of a positioning guide rod and a plurality of mass block assemblies, and cylindrical spiral springs arranged on the positioning guide rods in a sleeving mode are arranged between every two adjacent mass block assemblies and the outer side of the mass block assembly located on the outermost side. According to the structural design, under the working condition of the same excitation, due to the resonance effect of the vibration reduction piece near the inherent frequency of the pipeline and meanwhile, due to the fact that part of energy is absorbed by the vibration reduction piece, the resonance phenomenon of the pipeline can be effectively restrained, the high-speed or high-amplitude resonance phenomenon can be coped with, and the safety of the pipeline is guaranteed.

Description

Technical Field

[0001] The utility model relates to the technical field of industrial pipeline protection devices, in particular to an industrial pipeline resonance suppression damper. Background Art

[0002] During the operation of industrial pipelines, internal excitations such as fluid movement, water hammer, air hammer, or external excitations such as compressors may cause the pipeline to resonate near the low-order natural frequency points, causing the pipeline vibration speed or amplitude to exceed the specification, seriously affecting the safety and life of the pipeline.

[0003] The main purpose of the resonance suppression damper is to simulate or eliminate pipeline resonance, so that when the pipeline works at the resonance point, the vibration speed and amplitude are controlled within the specification value, thereby achieving effective protection of pipeline safety and thus extending the life of the pipeline. However, the existing resonance suppression damper structure is too simple, the effect of simulating resonance is poor, and it cannot cope with high-speed or high-amplitude resonance phenomena. Summary of the invention

[0004] To solve the above technical problems, the utility model provides an industrial pipeline resonance suppression damper. In order to have a basic understanding of some aspects of the disclosed embodiments, a simple summary is given below. This summary is not a general review, nor is it intended to identify key / important components or describe the scope of protection of these embodiments. Its only purpose is to present some concepts in a simple form as a preface to the detailed description that follows.

[0005] The utility model adopts the following technical solutions:

[0006] Provided is an industrial pipeline resonance suppression damper, comprising: a plurality of upper frequency band vibration damping members, a plurality of lower frequency band vibration damping members and two damper mounting seats;

[0007] The two damper mounting seats are embracing the pipe and symmetrically arranged, and the upper frequency band vibration damping member and the lower frequency band vibration damping member are evenly spaced and alternately arranged on the damper mounting seats;

[0008] The upper frequency band vibration damper and the lower frequency band vibration damper are both composed of a positioning guide rod and a plurality of mass block assemblies arranged on the positioning guide rod, and a cylindrical coil spring sleeved on the positioning guide rod is arranged between two adjacent mass block assemblies and on the outside of the outermost mass block assembly.

[0009] Further, the number of the mass block components in the upper frequency band vibration damper is greater than the number of the mass block components in the lower frequency band vibration damper.

[0010] Furthermore, the upper frequency band vibration damper has four mass block assemblies, and the lower frequency band vibration damper has three mass block assemblies.

[0011] Furthermore, the mass block assembly includes: a mass block body and a sleeve; the mass block body gradually increases in width from the inner end to the outer end, the mass block body has a through hole on one side close to the inner end, and the sleeve is arranged in the through hole.

[0012] Furthermore, the inner end and the outer end of the mass block body are both arc-shaped end surfaces convex toward a side away from the mass block body.

[0013] Furthermore, four upper-band vibration-damping components and five lower-band vibration-damping components are arranged on each of the damper mounting seats.

[0014] Furthermore, the damper mounting seat includes: a pipe clamp and an arc plate arranged on both sides of the pipe clamp; a plurality of circular holes are opened on the arc plate, self-lubricating copper sleeves are arranged in the circular holes, and both ends of the positioning guide rod are embedded in the self-lubricating copper sleeves.

[0015] Furthermore, the pipe clamp includes: an arc-shaped plate and wing plates arranged at both ends of the arc-shaped plate, mounting plates are arranged at both ends of the wing plate, and bolt holes are provided on the arc plate, the wing plate and the mounting plate.

[0016] The beneficial effects brought about by the utility model are as follows: the upper frequency band vibration damping component and the lower frequency band vibration damping component are carried by the damper mounting seat, and the structural design of the present application enables the resonance of the pipeline to be effectively suppressed under the same excitation working conditions due to the resonance effect of the vibration damping component near the natural frequency of the pipeline and the absorption of part of the energy by the vibration damping component, and the high-speed or high-amplitude resonance phenomenon can be dealt with to ensure the safety of the pipeline. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0018] Figure 1 This is a structural schematic diagram of an industrial pipeline resonance suppression damper of the utility model;

[0019] Figure 2 It is a structural schematic diagram of two damper mounting seats of the utility model when they are butt-jointed;

[0020] Figure 3It is a schematic diagram of the distribution of the upper frequency band vibration damping parts and the lower frequency band vibration damping parts of the utility model;

[0021] Figure 4 It is a schematic diagram of the connection between the upper frequency band vibration damping member and the arc plate of the utility model;

[0022] Figure 5 It is a schematic diagram of the connection between the lower frequency band vibration damping member and the arc plate of the utility model;

[0023] Figure 6 It is a structural schematic diagram of the mass block assembly of the utility model;

[0024] Figure 7 It is a structural schematic diagram of the mass block main body of the utility model;

[0025] Figure 8 It is a structural schematic diagram of the arc plate of the utility model. DETAILED DESCRIPTION

[0026] The following is a detailed description of the embodiments of the utility model in conjunction with the accompanying drawings. It should be clear that the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0027] like Figure 1-8 As shown, in some illustrative embodiments, an industrial pipeline resonance suppression damper is provided, comprising: a plurality of upper frequency band vibration damping members 1 , a plurality of lower frequency band vibration damping members 2 , and two damper mounting seats 3 .

[0028] The two damper mounting seats 3 are symmetrically arranged around the pipe 4 and are fastened by bolts and nuts, so that the resonance suppression damper of this embodiment is mounted around the pipe 4 .

[0029] The upper-band vibration dampers 1 and the lower-band vibration dampers 2 are evenly spaced and alternately arranged on the damper mounting seat 1, that is, the spacing between the vibration dampers is the same, and the two vibration dampers are arranged alternately. Further, four upper-band vibration dampers 1 and five lower-band vibration dampers 2 are arranged on each damper mounting seat 1. Since the two vibration dampers need to be arranged alternately, the lower-band vibration dampers 2 are close to the two ends of the damper mounting seat 1, and an upper-band vibration damper 1 is arranged between every two adjacent lower-band vibration dampers 2.

[0030] The upper frequency band vibration damper 1 and the lower frequency band vibration damper 2 are both composed of a positioning guide rod 5 and a plurality of mass block assemblies 6, and the mass block assemblies 6 are sleeved on the positioning guide rod 5. At the same time, a cylindrical coil spring 7 sleeved on the positioning guide rod 5 is provided between two adjacent mass block assemblies 6 and on the outer side of the mass block assemblies 6 located on the outermost side, that is, a mass block assembly 6 is provided between every two cylindrical coil springs 7, and the cylindrical coil springs 7 are provided near the two ends of the positioning guide rod 5, so that the mass block assembly 6 has a certain moving space and is limited by the cylindrical coil springs 7.

[0031] The number of mass block assemblies 6 in the upper frequency band vibration damper 1 is greater than the number of mass block assemblies 6 in the lower frequency band vibration damper 2. Further, the upper frequency band vibration damper 1 has four mass block assemblies 6 and one positioning guide rod 5, and accordingly, the upper frequency band vibration damper 1 has five cylindrical helical springs 7; the lower frequency band vibration damper 2 has three mass block assemblies 6 and one positioning guide rod 5, and accordingly, the lower frequency band vibration damper 2 has four cylindrical helical springs 7.

[0032] The mass block assembly 6 includes: a mass block body 601 and a shaft sleeve 602 .

[0033] The width of the mass block body 601 gradually increases from the inner end to the outer end, so that the weight of the outer part of the mass block body 601 is greater, thereby ensuring the anti-resonance effect. The mass block body 601 is provided with a through hole 603 on one side close to the inner end, and the shaft sleeve 602 is arranged in the through hole 603. The positioning guide rod 5 passes through the shaft sleeve 602 to ensure the movement stability and strength of the mass block body 601.

[0034] The inner end and the outer end of the mass block body 601 are both arc-shaped end surfaces that bulge away from the mass block body 601 . The smooth arc-shaped end surfaces can avoid collision with other structural parts during installation.

[0035] The damper mounting seat 3 comprises: a pipe clamp and arc plates 301 arranged on both sides of the pipe clamp.

[0036] A plurality of circular holes 302 are provided on the arc plate 301, and the number of the circular holes 302 is nine, of which five are used to support the upper frequency band vibration damping member 1, and the remaining four are used to support the lower frequency band vibration damping member 2. Self-lubricating copper sleeves 303 are provided in the circular holes 302 to facilitate the free rotation of the positioning guide rod 5, and both ends of the positioning guide rod 5 are embedded in the self-lubricating copper sleeves 303.

[0037] The pipe clamp includes: an arc-shaped plate 304 and wing plates 305 arranged at both ends of the arc-shaped plate 304, and the arc-shaped plate 304 and the wing plates 305 are an integrally formed structure. Mounting plates 306 are arranged at both ends of the wing plates 305, and bolt holes are provided on the arc plate 301 and the mounting plate 306, so that the arc plate 301 can be fastened to the mounting plate 306 by bolts and nuts. Bolt holes are provided on the wing plates 305, so that the two damper mounting seats 3 can be fastened to the pipe 4 by bolts and nuts, and the structure is stable and easy to install.

[0038] Installation process:

[0039] First, fix the pipe clamp on the pipe 4; then install the two arc plates 301 on one of the pipe clamps and tighten the bolts. Do not tighten the bolts temporarily at this time; then install the four upper frequency band vibration dampers 1 and the five lower frequency band vibration dampers 2 on the two arc plates 301 in a spaced manner, adjust each upper frequency band vibration damper 1 and lower frequency band vibration damper 2 so that they can rotate freely, and finally tighten the 4 groups of bolts on the arc plate 301; install the parts on the pipe clamp on the other side in the same way.

[0040] Vibration reduction component parameters:

[0041] Assume that the radial first-order natural frequency of pipe 4 is f x Hertz, the first-order longitudinal natural frequency of the pipe is f z Hertz, the upper frequency band vibration damper 1, the mass block assembly 6 center of mass position and the stiffness of the cylindrical coil spring 7 should meet the following conditions:

[0042]

[0043]

[0044] The lower frequency band vibration damper 2, the mass block assembly 6 center of mass position and the stiffness of the cylindrical coil spring 7 should meet the following conditions:

[0045]

[0046]

[0047] Among them, g is the acceleration of gravity, l is the distance between the center of mass of the mass block assembly 6 and the center axis of the positioning guide rod 5, k is the stiffness of the cylindrical coil spring 7, and m is the mass of the mass block assembly 6.

[0048] From the above conditional relationship, it can be seen that the radial and longitudinal natural frequencies of the upper frequency band vibration damper 1 are 1.05 times the corresponding natural frequencies of the pipeline 4, and the radial and longitudinal natural frequencies of the lower frequency band vibration damper 2 are 0.95 times the corresponding natural frequencies of the pipeline 4.

[0049] Working principle:

[0050] Assume that before the resonance suppression damper of this embodiment is installed, the dynamic equilibrium equation of pipeline 4 is: [pipeline mass matrix]×[acceleration vector]+[pipeline damping matrix]×[pipeline velocity vector]+[pipeline stiffness matrix]×[pipeline displacement vector]=[excitation force vector].

[0051] When a resonance suppression damper of the present embodiment is installed on the pipeline 4, the dynamic equilibrium equation becomes: [pipeline mass matrix + damper consistent mass matrix]×[pipeline acceleration vector + mass block assembly acceleration vector]+[pipeline damping matrix]×[pipeline velocity vector]+[pipeline stiffness matrix + damper stiffness matrix]×[pipeline displacement vector + mass block assembly displacement vector]=[excitation force vector].

[0052] After installing the resonance suppression damper of this embodiment, the dynamic equilibrium equation of the system is changed, the number of axial degrees of freedom of the pipeline will increase by 63, and the number of longitudinal degrees of freedom of the pipeline will increase by 63. Under the same excitation working conditions, due to the resonance effect of the vibration damping component near the natural frequency of the pipeline, and at the same time, since part of the energy is absorbed by the vibration damping component, the pipeline system will not experience high-speed or high-amplitude resonance.

[0053] The above is only a specific implementation of the utility model, but the protection scope of the utility model is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed by the utility model should be included in the protection scope of the utility model. Therefore, the protection scope of the utility model should be based on the protection scope of the claims.

Claims

1. An industrial pipeline resonance suppression damper, characterized in that: include: a plurality of upper frequency band vibration dampers, a plurality of lower frequency band vibration dampers, and two damper mountings; The two damper mounting seats are embracing the pipe and symmetrically arranged, and the upper frequency band vibration damping member and the lower frequency band vibration damping member are evenly spaced and alternately arranged on the damper mounting seats; The upper frequency band vibration damper and the lower frequency band vibration damper are both composed of a positioning guide rod and a plurality of mass block assemblies arranged on the positioning guide rod, and a cylindrical coil spring sleeved on the positioning guide rod is arranged between two adjacent mass block assemblies and on the outside of the outermost mass block assembly.

2. The industrial pipeline resonance suppression damper according to claim 1 is characterized in that: The number of mass assemblies in the upper frequency-band vibration damper is greater than the number of mass assemblies in the lower frequency-band vibration damper.

3. The industrial pipeline resonance suppression damper according to claim 2 is characterized in that: The upper frequency band vibration damper has four of the mass assemblies, and the lower frequency band vibration damper has three of the mass assemblies.

4. The industrial pipeline resonance suppression damper according to claim 3 is characterized in that: The mass block assembly includes: a mass block body and a shaft sleeve; the width of the mass block body gradually increases from the inner end to the outer end, the mass block body is provided with a through hole on one side close to the inner end, and the shaft sleeve is arranged in the through hole.

5. The industrial pipeline resonance suppression damper according to claim 4 is characterized in that: The inner end and the outer end of the mass block body are both arc-shaped end surfaces convex toward a side away from the mass block body.

6. The industrial pipeline resonance suppression damper according to claim 5, characterized in that: Four upper frequency band vibration damping components and five lower frequency band vibration damping components are arranged on each damper mounting seat.

7. The industrial pipeline resonance suppression damper according to claim 6, characterized in that: The damper mounting seat includes: a pipe clamp and arc plates arranged on both sides of the pipe clamp; a plurality of circular holes are provided on the arc plates, self-lubricating copper sleeves are arranged in the circular holes, and both ends of the positioning guide rod are embedded in the self-lubricating copper sleeves.

8. The industrial pipeline resonance suppression damper according to claim 7, characterized in that: The pipe clamp comprises: an arc-shaped plate and wing plates arranged at both ends of the arc-shaped plate, mounting plates are arranged at both ends of the wing plate, and bolt holes are opened on the arc plate, the wing plate and the mounting plate.

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