Variable damping ball screw inerter shock absorber and method

Abstract

The invention provides a variable damping ball screw inerter shock absorber and method, the variable damping ball screw inerter shock absorber comprises an axial compression structure, a converter is arranged in the middle of the axial compression structure in a sliding and penetrating mode, and the converter reciprocates in the axial compression structure in the axial direction through a spring in the axial direction; the converter comprises a supporting cavity structure, an angular contact ball bearing is fixedly arranged in the middle of the supporting cavity structure, a ball screw is coaxially arranged on the angular contact ball bearing in a penetrating mode, the upper section of the ball screw and the angular contact ball bearing are sleeved in a sliding mode, and the lower section of the ball screw is meshed with the axial compression structure in a threaded mode. The bottom end of the ball screw is fixedly connected with an energy consumption flywheel; the technical problem that in the prior art, pipeline vibration cannot be effectively solved is solved.

Description

Technical Field

[0001] The invention belongs to the field of technology, and in particular to a variable damping ball screw inertia damper and a method. Background Art

[0002] In pipeline systems, changes in valve status and sudden changes in pipeline diameter usually cause pulsation shocks, leading to pipeline vibration problems; specifically, when a hydraulic valve is suddenly opened, the working medium near the valve, which was originally in a stationary state, will flow rapidly, and the pressure energy will be converted into kinetic energy, causing a sharp drop in pressure near the valve. However, due to inertia, the flow speed of the working medium far away from the valve has not yet caught up, so the pressure is relatively high. This pressure difference will form a pressure wave in the pipeline and propagate along the pipeline, thereby generating pulsation shocks; on the contrary, when the valve is suddenly closed, the speed of the working medium at the valve immediately becomes zero, while the working medium far away from the valve continues to move toward the valve due to inertia, squeezing the working medium near the valve and converting kinetic energy into pressure energy. After this pressure energy hits the closed valve, it will propagate in the opposite direction to form a pulsation shock. In pipeline systems, the diameter of the pipeline may change due to design or installation requirements. When the fluid flows through these parts with sudden changes in diameter, its flow velocity and pressure distribution will change significantly. In the parts where the diameter decreases, the fluid flow velocity increases and the pressure decreases; while in the parts where the diameter increases, the fluid flow velocity slows down and the pressure increases. This change in flow velocity and pressure will form pressure waves in the pipeline, thereby causing pulsation shocks.

[0003] At present, the main method of controlling pipeline vibration is to install tuned mass dampers or dampers externally. However, traditional dampers usually need to be grounded for use and have limited application range. For low-frequency vibration, it is necessary to design tuned mass dampers, which usually meet the tuning conditions and effectively control vibration by increasing the tuning mass or reducing the structural stiffness. Summary of the invention

[0004] In order to solve the problems existing in the prior art, the present invention provides a variable damping ball screw inertia damper and method to solve the technical problem that the existing related technology cannot effectively solve the pipeline vibration.

[0005] To achieve the above object, the present invention provides the following technical solutions:

[0006] A variable damping ball screw inertia damper comprises an axial compression structure, a converter is slidably arranged in the middle of the axial compression structure, and the converter reciprocates axially in the axial compression structure through a spring;

[0007] The converter includes a supporting cavity structure, an angular contact ball bearing is fixedly arranged in the middle of the supporting cavity structure, a ball screw is coaxially arranged through the angular contact ball bearing, the upper section of the ball screw is slidingly sleeved with the angular contact ball bearing, the lower section of the ball screw is threadedly engaged with the axial compression structure, and the bottom end of the ball screw is fixedly connected to an energy-consuming flywheel.

[0008] Furthermore, the axial compression structure comprises an upper top plate and a lower top plate, two parallel connecting rods are arranged between the upper top plate and the lower top plate, and fixing pieces are arranged at the ends of the connecting rods;

[0009] The connecting rods are each provided with two sections of springs, and a supporting cavity structure of the converter is provided between the two springs on the same connecting rod.

[0010] Furthermore, the axial compression structure also includes a lead screw nut fixedly disposed on the lower top plate near the converter, and the lead screw nut is threadedly engaged with the ball screw.

[0011] Furthermore, the total stiffness of the two springs on the same connecting rod is the same.

[0012] Furthermore, two linear bearings are fixedly arranged inside the support cavity structure. The linear bearings are arranged on both sides of the angular contact ball bearing and are respectively slidably sleeved in the middle of the axial compression structure.

[0013] Furthermore, a plurality of additional mass blocks are detachably arranged inside the support cavity structure, and the plurality of additional mass blocks are symmetrically arranged along the center of the support cavity structure.

[0014] Furthermore, a limit block is arranged on the top of the ball screw, and the bottom of the limit block abuts against the top of the supporting cavity structure.

[0015] Furthermore, the upper section of the ball screw is the optical axis, and the lower section is the threaded axis.

[0016] Furthermore, the energy-consuming flywheel is fixedly connected to the bottom end of the ball screw through a nut.

[0017] A method for a variable damping ball screw inertia damper comprises the following steps:

[0018] When the axial compression structure is impacted by pipeline pulsation, it transmits the pulsation impact downward to the converter. At the same time, the spring buffers and dissipates the axial force through deformation.

[0019] When the converter is subjected to the pulsating impact brought by the spring, the converter drives the ball screw to move up and down along the axial direction and rotate. During the rotation process, the ball screw rotates and consumes energy through the energy-consuming flywheel.

[0020] Compared with the prior art, the present invention has the following beneficial technical effects:

[0021] The present invention provides a variable damping ball screw inertia damper, comprising an axial compression structure, wherein a converter is slidably arranged in the middle of the axial compression structure, and the converter reciprocates axially in the axial compression structure through a spring; the converter comprises a supporting cavity structure, wherein an angular contact ball bearing is fixedly arranged in the middle of the supporting cavity structure, and a ball screw is coaxially arranged through the angular contact ball bearing, the upper section of the ball screw is slidably sleeved with the angular contact ball bearing, the lower section of the ball screw is threadedly engaged with the axial compression structure, and the bottom end of the ball screw is fixedly connected with an energy-consuming flywheel; the present application buffers and consumes energy for the axial force in the pulsating impact of the pipeline through the axial compression mechanism, and since the lower section of the ball screw is threadedly engaged with the axial compression structure, the converter drives the ball screw to rotate downward, and during the self-rotation process, the ball screw drives the energy-consuming flywheel to rotate and consume energy, and the present application converts the pulsating impact into axial force and radial force, and consumes energy in a targeted manner through the spring and the energy-consuming flywheel, thereby solving the technical problem that the existing related technologies cannot effectively solve the pipeline vibration.

[0022] Furthermore, the total stiffness of the two springs on the same connecting rod is the same, which can improve stability and evenly distribute the load.

[0023] The present invention provides a method for a variable damping ball screw inertia damper, comprising the following steps: when an axial compression structure is subjected to pipeline pulsation impact, the pulsation impact is transmitted downward to a converter, and at the same time, the axial force is buffered and energy is consumed by deformation of a spring; when the converter is subjected to pulsation impact brought by the spring, the converter drives the ball screw to rotate downward, and during the self-rotation of the ball screw, the ball screw rotates and consumes energy through an energy-consuming flywheel; the method can effectively convert the pulsation impact of the pipeline into axial force and radial force, and consume energy in a targeted manner through a spring and an energy-consuming flywheel, thereby solving the technical problem that the existing related technology cannot effectively solve the pipeline vibration. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 A schematic structural diagram of a variable damping ball screw inertia damper according to an embodiment of the present disclosure is shown;

[0025] Figure 2 A partial cross-sectional view of a variable damping ball screw inertia damper according to an embodiment of the present disclosure is shown;

[0026] Figure 3 A schematic structural diagram of a converter according to an embodiment of the present disclosure is shown.

[0027] Figure 4 A schematic diagram showing the force of the inertia capacity shock absorber of the embodiment of the present disclosure under the action of foundation excitation is shown;

[0028] In the attached figure:

[0029] 1. Connecting rod; 2. Lower top plate; 3. Bearing end cover; 4. Additional mass block; 5. Screw nut; 6. Upper top plate; 7. Ball screw; 8. Energy-absorbing flywheel; 9. Angular contact ball bearing; 10. Linear bearing; 11. Spring. DETAILED DESCRIPTION

[0030] In the following, only some exemplary embodiments are briefly described. As those skilled in the art will appreciate, the described embodiments may be modified in various ways without departing from the spirit or scope of the present invention. Therefore, the drawings and descriptions are considered to be exemplary and non-restrictive in nature.

[0031] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0032] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0033] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, an electrical connection, or a communication; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0034] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0035] It should be understood that when used in this specification and the appended claims, the terms "include" and "comprises" indicate the presence of described features, integers, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or combinations thereof.

[0036] It should also be understood that the terms used in the present specification are only for the purpose of describing specific embodiments and are not intended to limit the present invention. As used in the present specification and the appended claims, unless the context clearly indicates otherwise, the singular forms "a", "an" and "the" are intended to include plural forms.

[0037] It should be further understood that the term "and / or" used in the present description and the appended claims refers to any and all possible combinations of one or more of the associated listed items, and includes these combinations.

[0038] Various structural schematic diagrams of the embodiments disclosed in the present invention are shown in the accompanying drawings. These figures are not drawn to scale, and some details are magnified and some details may be omitted for the purpose of clear expression. The shapes of various regions and layers shown in the figures and the relative sizes and positional relationships therebetween are only exemplary, and may deviate in practice due to manufacturing tolerances or technical limitations, and those skilled in the art may additionally design regions / layers with different shapes, sizes, and relative positions according to actual needs.

[0039] The embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0040] Figure 1 A variable damping ball screw inertia damper according to an embodiment of the present disclosure is shown. Figure 1 As shown, it includes an axial compression structure, a converter is slidably arranged in the middle of the axial compression structure, and the converter reciprocates axially in the axial compression structure through a spring 11;

[0041] The converter includes a supporting cavity structure, an angular contact ball bearing 9 is fixedly arranged in the middle of the supporting cavity structure, a ball screw 7 is coaxially arranged through the angular contact ball bearing 9, the upper section of the ball screw 7 is slidably sleeved with the angular contact ball bearing 9, the lower section of the ball screw 7 is threadedly engaged with the axial compression structure, and the bottom end of the ball screw 7 is fixedly connected to an energy-consuming flywheel 8.

[0042] It should be noted that in the embodiments disclosed herein, the variable damping ball screw inertia shock absorber described in the present application is usually arranged at the pipe diameter mutation point of the pipeline system, near the valve, elbows, tees and other pipe fittings and / or the inlet and outlet of power equipment such as compressors and pumps; when connecting, welding or connecting parts can be used for connection, such as bolts and other structures for rigid connection, so as to improve the transmission of pulsation shock.

[0043] It should be further explained that the present embodiment adopts single-row or double-row angular contact ball bearings, which can withstand composite loads, and the double-row angular contact ball bearings can withstand radial and axial combined loads and moment loads dominated by larger radial loads, limiting the axial displacement of the shaft in both directions.

[0044] Preferably, in some embodiments, the axial compression structure comprises an upper top plate 6 and a lower top plate 2, two parallel connecting rods 1 are arranged between the upper top plate 6 and the lower top plate 2, and fixing pieces are arranged at the ends of the connecting rods 1;

[0045] Each of the connecting rods 1 is provided with two sections of springs 11, and a supporting cavity structure of the converter is provided between the two springs 11 on the same connecting rod 1;

[0046] Furthermore, the axial compression structure also includes a screw nut 5 fixedly disposed on the lower top plate 2 close to the converter, and the screw nut 5 is threadedly engaged with the ball screw 7.

[0047] It should be noted that in the embodiment of the present disclosure, the axial compression structure serves as an axial energy dissipation part and a support converter. Specifically, when subjected to a pulsating impact, the axial force generated is dissipated through the deformation of the spring 11 sleeved on the connecting rod 1. At the same time, the screw nut 5 fixedly arranged on the lower top plate 2 is coaxial with the ball screw 7 and threadedly engaged. When the converter receives a pulsating impact, it will drive the ball screw 7 to move downward or upward. At the same time, due to the threaded engagement, it will rotate, thereby converting the load into a radial force and eliminating the energy.

[0048] It should be further explained that, in some disclosed embodiments, the friction force between the screw nut 5 and the ball screw 7 is:

[0049] F f =μα ZQ (1)

[0050] Where Q is the contact load of the ball, μ α is the ball friction coefficient, and Z is the number of balls.

[0051] The contact load borne by the ball of the screw pair is:

[0052]

[0053] In the formula, F a is the working load and preload borne by the screw pair, β is the contact angle, and λ is the helix angle.

[0054] The ball friction coefficient is:

[0055]

[0056] Where E is the elastic modulus of the screw pair material, is the surface quality coefficient, τ M is the shear strength of the node, τ L Analyze the bond shear strength for the lubricating film, δ S is the yield limit of the softer material in the contact pair, and δ is the contact stress.

[0057] Specifically, the friction torque between the screw nut 5 and the ball screw 7 is directly related to the preload force borne by the screw pair and the working load borne by the screw pair. The friction force of the screw pair can dissipate vibration energy, which is equivalent to the damping effect. The greater the preload force and the working load borne by the screw pair, the greater the friction force borne by the screw pair, the better the energy dissipation effect, and the better the vibration reduction effect of the structure.

[0058] Furthermore, in the disclosed embodiment, the total stiffness of the two springs 11 on the same connecting rod 1 is the same; it should be noted that the same stiffness of the two springs 11 means that they will produce similar deformation when subjected to force, thereby maintaining the balance between the two ends of the connecting rod 1 and reducing the additional stress and vibration caused by the difference in stiffness. At the same time, in a dynamic environment, such as mechanical vibration or impact load, the combination of springs 11 with the same stiffness can better resist external interference and maintain the stable working state of the system. When the two springs 11 have the same stiffness, they can more evenly share the load acting on the connecting rod 1, avoid overloading of a single spring 11, and extend the service life of the spring 11. The evenly distributed load helps to reduce the stress concentration phenomenon at the connection between the connecting rod 1 and the spring 11, and reduce the risk of fatigue damage caused by stress concentration.

[0059] Preferably, Figure 2 and Figure 3As shown, two linear bearings 10 are fixedly arranged inside the support cavity structure. The linear bearings 10 are arranged on both sides of the angular contact ball bearing 9 and are respectively slidably sleeved in the middle of the axial compression structure.

[0060] It should be noted that the linear bearing 10 is used to guide the support cavity structure, reduce the friction of the support cavity structure when it makes axial movement on the connecting rod 1, and improve stability.

[0061] Preferably, in the embodiment of the present disclosure, a plurality of additional mass blocks 4 are detachably arranged inside the support cavity structure, and the plurality of additional mass blocks 4 are symmetrically arranged along the center of the support cavity structure; it should be noted that, in the embodiment of the present disclosure, the support cavity structure includes two groups of bearing end covers 3 arranged at the upper and lower ends, and a plurality of additional mass blocks 4 are arranged between the bearing end covers 3. The plurality of additional mass blocks 4 are arranged with gaps between the side walls of the ball screw 7 and with the linear bearing 10. The plurality of additional mass blocks 4 can fix the relative positions of the ball screw 7 and the linear bearing 10 on the one hand, and are used for counterweighting on the other hand to increase the working load.

[0062] Preferably, in the embodiment disclosed herein, a limit block is provided on the top of the ball screw 7, and the bottom of the limit block abuts against the top of the supporting cavity structure; it should be noted that, in the embodiment disclosed herein, the limit block is a nut adapted to the ball screw 7, and since the ball screw 7 is a variable diameter structure, the top of the supporting cavity structure is tightened and fixed by a corresponding nut, and the lower part of the supporting cavity structure abuts against the top of the variable diameter section of the ball screw 7.

[0063] Preferably, the upper section of the ball screw 7 is the optical axis, and the lower section is the threaded shaft; it should be noted that, in the embodiment disclosed herein, the top of the optical axis has a thread for threaded connection with a matching nut for limiting, and an annular support ring is arranged between the optical axis and the threaded shaft, and the annular support ring is used to abut against the upper support cavity structure.

[0064] Preferably, in the disclosed embodiment, the energy-consuming flywheel 8 is fixedly connected to the bottom end of the ball screw 7 by a nut; in some embodiments, the bottom of the energy-consuming flywheel 8 is fixed to the bottom end of the ball screw 7 by two nuts to improve the stability of the connection;

[0065] It should be noted that the present invention relies on the ball screw pair to amplify the axial speed of the two ends of the shock absorber into the linear speed of the energy-consuming flywheel 8, and uses the equivalent mass of the rotational inertia of the energy-consuming flywheel 8, and at the same time realizes the equivalent mass adjustment by increasing or decreasing the size and number of the energy-consuming flywheel 8. The adjustment is convenient, and the performance parameters of the damper can be quickly adjusted by adjusting the overall stiffness of the spring 11, the lead of the ball screw pair, and adjusting the diameter and mass of the flywheel.

[0066] This embodiment also discloses a method for a variable damping ball screw inertia damper, comprising the following steps:

[0067] When the axial compression structure is subjected to pipeline pulsation impact, the pulsation impact is transmitted downward to the converter, and at the same time, the axial force is buffered and energy is consumed by the spring 11 through deformation;

[0068] When the converter is subjected to the pulsating impact brought by the spring 11, the converter drives the ball screw 7 to move up and down along the axial direction and rotate. During the rotation process, the ball screw 7 rotates through the energy-consuming flywheel 8 and consumes energy.

[0069] Specifically, if Figure 4 As shown, Figure 4 The force diagram of the inertia capacity shock absorber described in this application under the action of foundation excitation is shown. Figure 4 The vibration control equation can be established as:

[0070]

[0071] in:

[0072] z=xy (5)

[0073]

[0074] In the formula, m is the main structure, is the second derivative of the main structure displacement, k is the spring stiffness, x is the main structure displacement, y is the basic excitation displacement, is the first derivative of the displacement of the basic excitation, F f is the friction between the ball screws;

[0075] When the vibration system of the inertia damper reaches a steady state, the mass m will generate a harmonic response with the same period as the exciting force but with a different phase. The period of the exciting force and the response is The maximum and minimum values ​​of the harmonic response are Within half a cycle, there is a phase difference between the harmonic response and the exciting force exist All within

[0076] Assume that the amplitude of the exciting force

[0077] Where Y is the basic excitation displacement amplitude;

[0078] Set the boundary conditions to:

[0079]

[0080] The displacement response of the boundary condition solution equation is:

[0081]

[0082] In the formula, is the frequency ratio, ω0 is the excitation force frequency, ω n Natural frequency of mass m, is the damping function, Friction function, z0 is the displacement response of the main structure;

[0083] Then in one vibration cycle, the work done by the equivalent viscous damping force is:

[0084]

[0085] Where A ep is the work done by the equivalent damping force, c ep is the equivalent damping coefficient;

[0086] The work done by the friction force in one cycle:

[0087]

[0088] In the formula The work done in one cycle;

[0089] The equivalent damping work is equal to the dry friction work, and the equivalent damping coefficient is:

[0090]

[0091] The above shows and describes the basic principles and main features of the present invention and the advantages of the present invention. It is obvious to those skilled in the art that the present invention is not limited to the details of the above exemplary embodiments, and the present invention can be implemented in other specific forms without departing from the spirit or basic features of the present invention. Therefore, no matter from which point of view, the embodiments should be regarded as exemplary and non-restrictive. The scope of the present invention is defined by the attached claims rather than the above description, and it is intended that all changes falling within the meaning and scope of the equivalent elements of the claims are included in the present invention. Any figure mark in the claims should not be regarded as limiting the claims involved.

[0092] In addition, it should be understood that although this specification is described in accordance with the implementation modes, not every implementation mode contains only one independent technical solution. This description of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other implementation modes that can be understood by those skilled in the art. The above content is only to illustrate the technical idea of ​​the present invention, and cannot be used to limit the protection scope of the present invention. Any changes made on the basis of the technical solution according to the technical idea proposed by the present invention shall fall within the protection scope of the claims of the present invention.

Claims

1. A variable damping ball screw inertia damper, characterized in that: It comprises an axial compression structure, a converter is slidably arranged in the middle of the axial compression structure, and the converter reciprocates axially in the axial compression structure through a spring (11); The converter comprises a supporting cavity structure, an angular contact ball bearing (9) is fixedly arranged in the middle of the supporting cavity structure, a ball screw (7) is coaxially arranged through the angular contact ball bearing (9), an upper section of the ball screw (7) is slidably sleeved with the angular contact ball bearing (9), a lower section of the ball screw (7) is threadedly engaged with the axial compression structure, and an energy-consuming flywheel (8) is fixedly connected to the bottom end of the ball screw (7).

2. The variable damping ball screw inertia damper according to claim 1, characterized in that: The axial compression structure comprises an upper top plate (6) and a lower top plate (2), two parallel connecting rods (1) are arranged between the upper top plate (6) and the lower top plate (2), and the ends of the connecting rods (1) are provided with fixing parts; The connecting rods (1) are each provided with two sections of springs (11), and a supporting cavity structure of the converter is provided between the two springs (11) located on the same connecting rod (1).

3. The variable damping ball screw inertia shock absorber according to claim 2, characterized in that: The axial compression structure also includes a lead screw nut (5) fixedly arranged on the lower top plate (2) close to the converter, and the lead screw nut (5) is threadedly engaged with the ball screw (7).

4. The variable damping ball screw inertia shock absorber according to claim 2, characterized in that: The total stiffness of the two springs (11) on the same connecting rod (1) is the same.

5. The variable damping ball screw inertia shock absorber according to claim 1, characterized in that: Two linear bearings (10) are fixedly arranged inside the support cavity structure. The linear bearings (10) are arranged on both sides of the angular contact ball bearing (9) and are respectively slidably sleeved in the middle of the axial compression structure.

6. The variable damping ball screw inertia shock absorber according to claim 1, characterized in that: A plurality of additional mass blocks (4) are detachably arranged inside the support cavity structure, and the plurality of additional mass blocks (4) are symmetrically arranged along the center of the support cavity structure.

7. The variable damping ball screw inertia shock absorber according to claim 1, characterized in that: A limit block is arranged on the top of the ball screw (7), and the bottom of the limit block abuts against the top of the supporting cavity structure.

8. The variable damping ball screw inertia shock absorber according to claim 1, characterized in that: The upper section of the ball screw (7) is an optical axis, and the lower section is a threaded axis.

9. The variable damping ball screw inertia shock absorber according to claim 1, characterized in that: The energy-consuming flywheel (8) is fixedly connected to the bottom end of the ball screw (7) via a nut.

10. A method for variable damping ball screw inertia damper, characterized in that: The variable damping ball screw inertia damper according to any one of claims 1 to 9 comprises the following steps: When the axial compression structure is subjected to pipeline pulsation impact, the pulsation impact is transmitted downward to the converter, and at the same time, the axial force is buffered and energy is consumed by deformation through the spring (11); When the converter is subjected to the pulsation impact brought by the spring (11), the converter drives the ball screw (7) to move up and down along the axial direction and to rotate. During the rotation process, the ball screw (7) rotates and consumes energy through the energy-consuming flywheel (8).

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