Load-adjustable magnetic ring type quasi-zero stiffness pipeline support hanger

Abstract

The invention provides a load-adjustable magnetic ring type quasi-zero stiffness pipeline support hanger, which relates to the technical field of support structures, and comprises an inner magnetic ring, an outer magnetic ring, a vertical spring, an upper shell, an upper cover, a screw rod, an inner cover, an outer magnetic ring gasket, an inner magnetic ring shaft, a base, a sleeve and a fastening screw. According to the pipeline vibration reduction system based on the quasi-zero stiffness, through coupling of linear vertical spring force and nonlinear magnetic force, efficient and passive control over broadband vibration (especially low-frequency vibration) and transient impact is achieved, and the defect that a traditional vibration isolator is poor in low-frequency vibration isolation effect is overcome.

Description

Technical Field

[0001] This invention relates to the technical field of support structures, and more particularly to a load-adjustable magnetic ring type quasi-zero stiffness pipe support. Background Technology

[0002] In the field of vibration control for vehicles such as automobiles and ships, vibration isolation technology in the low-frequency range (0.1-20Hz) has always been a core challenge in engineering design. Traditional linear vibration isolators, because their natural frequency is directly related to the system stiffness, struggle to simultaneously meet the contradictory requirements of high load-bearing capacity and low dynamic stiffness in the low-frequency range. Although quasi-zero stiffness (QZS) vibration isolators, by introducing a nonlinear negative stiffness mechanism, can achieve extremely low equivalent stiffness near the static equilibrium position, significantly reducing the system's natural frequency and widening the isolation frequency band, their structural design still faces two major bottlenecks: insufficient load adaptability and the risk of low-frequency resonance.

[0003] The survey revealed several problems with existing quasi-zero stiffness vibration isolators: First, existing quasi-zero stiffness vibration isolators mostly rely on mechanical negative stiffness elements (such as preloaded springs and buckling beams), whose stiffness characteristics are limited by fixed geometric parameters and material properties, making them difficult to adapt to load fluctuations under complex working conditions. Second, while quasi-zero stiffness vibration isolation technology can transmit high-frequency vibrations, its ability to dissipate low-frequency energy is limited. Third, existing quasi-zero stiffness vibration isolation systems are mostly designed and manufactured with automotive seats as a reference, resulting in large mass and volume. Furthermore, while the mass of quasi-zero stiffness structures in metamaterial structures is small, their load-bearing capacity is far less than that required by pipelines. In other words, general mechanical quasi-zero stiffness structures (QZS) are difficult to install under pipeline conditions with changing pressure and flow rates, and their mass is too large. Summary of the Invention

[0004] To address the technical problems mentioned in the background section, this invention provides a load-adjustable magnetic ring-type quasi-zero stiffness pipe support. This invention combines a positive stiffness linear helical spring with nonlinear magnetic force, achieving a cubic nonlinear change in the stiffness curve through magneto-mechanical coupling. Furthermore, the invention comprises nested permanent magnet rings, with the inner and outer magnetic rings arranged with opposite poles to form a gradient magnetic field space. Nonlinear stiffness changes are achieved through dynamic adjustment of the magnetic ring spacing. The invention includes a precision guide shaft and an adjusting sleeve, as well as a screw and an outer magnetic ring washer. Employing two sets of adjustment structures, both the inner and outer magnetic ring positions can be adjusted to ensure the entire system remains in static equilibrium under load.

[0005] The technical means employed in this invention are as follows: A load-adjustable magnetic ring type quasi-zero stiffness pipe support includes: Inner magnetic ring, outer magnetic ring, vertical spring, upper shell, upper cover, screw, inner cover, outer magnetic ring washer, inner magnetic ring on shaft, base, sleeve and fastening screw; The inner magnetic ring is disposed on the shaft where the inner magnetic ring is located and is fixed by the sleeve; when the external applied load is changed, the position of the inner magnetic ring on the shaft where the inner magnetic ring is located is changed by adjusting the fastening screw, so that when the balance position is reached, the vertical height of the inner magnetic ring and the outer magnetic ring is the same. The upper shell and the upper cover are connected by a thread to adjust the installation height; the upper cover and the shaft where the inner magnetic ring is located are also connected by a thread; an outwardly expanding cylindrical surface is provided between the upper cover and the base, and the vertical spring is fixed by the outwardly expanding cylindrical surface; the inner cover is fixed to one end of the screw. The outer magnetic ring is fixed to the outer magnetic ring washer by the outwardly expanding cylindrical surface on the outer magnetic ring washer; the outer magnetic ring washer is mounted on the screw.

[0006] Furthermore, the outer edge of the upper shell contains a thread.

[0007] Furthermore, the axis of the inner magnetic ring is coaxial with the vertical spring.

[0008] Furthermore, the coaxiality error between the inner and outer magnetic rings is ≤0.05mm.

[0009] Furthermore, under static equilibrium conditions, the inner magnetic ring deviates from its static equilibrium position by displacement. x, The axial repulsive force between the inner and outer magnetic rings is: ; in, Br 1. Br 3 represents the residual magnetic induction intensity of the inner and outer magnetic rings, respectively; R 1. R R1 and R2 are the inner and outer diameters of the inner magnetic ring, respectively; R3 and R4 are the inner and outer diameters of the outer magnetic ring, respectively; H1 and H2 are the axial thicknesses of the inner and outer magnetic rings, respectively; |、| |、| | represents the distance between two points on the mid-end surface.

[0010] ; Furthermore, the system's restoring resultant force and total stiffness are: ; ; in, and The restoring force and stiffness of the vertical spring; and The nonlinear restoring force and stiffness of the inner and outer magnetic rings; When the system stiffness satisfies At that time, the total magnetic-elastic force F To achieve the critical state of zero stiffness.

[0011] Furthermore, for every 30° rotation of the screw, its outer magnetic ring is displaced 0.0833 mm relative to its original position along the vertical axis.

[0012] Compared with the prior art, the present invention has the following advantages: The pipeline vibration reduction system based on quasi-zero stiffness provided by this invention achieves efficient and passive control of broadband vibration (especially low-frequency vibration) and transient impact through the coupling of linear vertical spring force and nonlinear magnetic force, overcoming the shortcomings of traditional vibration isolators with poor low-frequency vibration isolation effect.

[0013] The pipeline vibration reduction system based on quasi-zero stiffness provided by this invention achieves lightweighting by integrating it with the pipeline support structure, reducing the weight of the structure by 60% compared to traditional steel frames.

[0014] The pipeline vibration reduction system based on quasi-zero stiffness provided by this invention achieves active control of the overall stiffness curve shape of the system by adjusting the vertical position of the outer magnetic ring through a screw-shim composite adjustment system, that is, the load is adjustable, with a resolution of approximately 2.075N. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 This is a three-dimensional schematic diagram of the device of the present invention; Figure 2 This is a schematic diagram of the negative stiffness mechanism of the present invention; Figure 3 This is a schematic diagram of the inner magnetic ring position adjustment in this invention; Figure 4 This is a schematic diagram illustrating the adjustment and fixing of the outer magnetic ring position according to the present invention; Figure 5 This is a schematic diagram of the height adjustment mechanism of the present invention; Figure 6 This is a schematic cross-sectional view of the device of the present invention achieving near-zero stiffness; Figure 7 This is a schematic diagram of the aluminum alloy gasket of the present invention.

[0017] Wherein, 1 is the inner magnetic ring; 2 is the outer magnetic ring; 3 is the vertical spring; 4 is the upper shell; 5 is the upper cover; 6 is the screw; 7 is the inner cover; 8 is the outer magnetic ring washer; 9 is the inner magnetic ring on the shaft; 10 is the base; 11 is the sleeve; 11a is the fastening screw. Detailed Implementation

[0018] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0019] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, 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. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. 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.

[0020] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0021] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0022] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention. The directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0023] For ease of description, spatial relative terms such as "above," "over," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation besides the orientation of the device as described in the figures. For example, if the device in the figures is inverted, a device described as "above" or "above" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0024] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0025] like Figure 1-7 As shown, a load-adjustable magnetic ring type quasi-zero stiffness pipeline support includes: an inner magnetic ring 1, an outer magnetic ring 2, a vertical spring 3, an upper shell 4, an upper cover 5, a screw 6, an inner cover 7, an outer magnetic ring gasket 8, an inner magnetic ring on a shaft 9, a base 10, a sleeve 11, and a fastening screw 11a.

[0026] In a preferred embodiment, in this application, the inner magnetic ring 1 is disposed on the shaft 9 where the inner magnetic ring is located and is fixed by the sleeve 11; when the external applied load is changed, the position of the inner magnetic ring 1 on the shaft 9 is changed by adjusting the fastening screw 11a, so that the inner magnetic ring 1 and the outer magnetic ring 2 are at the same vertical height at the equilibrium position; the upper shell 4 and the upper cover 5 are connected by threads to adjust the installation height; the upper cover 5 and the shaft 9 where the inner magnetic ring is located are also connected by threads; an outwardly expanding cylindrical surface is also provided between the upper cover 5 and the base 10, and the vertical spring 3 is fixed by the outwardly expanding cylindrical surface; the inner cover 7 is fixed to one end of the screw 6; the outer magnetic ring 2 is fixed to the outer magnetic ring washer 8 by the outwardly expanding cylindrical surface; the outer magnetic ring washer 8 is installed on the screw 6.

[0027] The frame in this application comprises an upper shell 4, an upper cover 5, an inner cover 7, and a base 10; its material is 6061-T6 aluminum alloy with a wall thickness of 4mm. The inner magnetic ring is mounted on the shaft containing the inner magnetic ring 9 and fixed by a sleeve 11. To achieve adjustable load characteristics when the applied external load changes, the position of the inner magnetic ring 1 on the shaft containing the inner magnetic ring 9 can be changed by adjusting the fastening screw 11a, so that at the equilibrium position, the vertical height of the inner magnetic ring 1 and the outer magnetic ring 2 are the same. The upper shell 4 and the upper cover 5 are threaded together, allowing for adjustable installation height within a range of ±15mm. Simultaneously, the upper cover 5 and the shaft containing the inner magnetic ring 9 are threaded together, mounting the inner magnetic ring 1 onto the structure. The upper cover 5 and the base 10 contain outwardly expanding cylindrical surfaces for fixing the vertical spring 3.

[0028] During the installation of the outer magnetic ring, three screws 6, an inner cover 7, and a base 10 are threaded together to ensure structural stability without requiring load-bearing. The main load-bearing component is a vertical spring, which serves to fix the outer magnetic ring. Then, the two outer magnetic rings are fixed to the outer magnetic ring washers 8 by their outwardly expanding cylindrical surfaces. Finally, a nut is used to install the outer magnetic ring washer 8, combined with the outer magnetic ring 2, onto the screws 6. To achieve adjustable load characteristics when the applied external load changes, another method can be used: adjusting the nut changes the position of the outer magnetic ring washer 8 on the screws 6, ensuring that the inner magnetic ring 1 and the outer magnetic ring 2 are at the same vertical height at the equilibrium position.

[0029] Preferably, the outer edge of the upper shell 4 has a threaded line. The axis of the inner magnetic ring 1 is coaxial with the vertical spring 3. The coaxiality error between the inner magnetic ring 1 and the outer magnetic ring 2 is ≤0.05mm.

[0030] Under static equilibrium conditions, the inner magnetic ring deviates from its static equilibrium position by displacement. x, The axial repulsive force between the inner and outer magnetic rings is: ; in,Br 1. Br 3 represents the residual magnetic induction intensity of the inner and outer magnetic rings, respectively; R 1. R R1 and R2 are the inner and outer diameters of the inner magnetic ring, respectively; R3 and R4 are the inner and outer diameters of the outer magnetic ring, respectively; H1 and H2 are the axial thicknesses of the inner and outer magnetic rings, respectively; |、| |、| | represents the distance between two points on the mid-end surface.

[0031] ; The system's restoring resultant force and total stiffness are: ; ; in, and The restoring force and stiffness of the vertical spring; and The nonlinear restoring force and stiffness of the inner and outer magnetic rings; When the system stiffness satisfies At that time, the total magnetic-elastic force F To achieve the critical state of zero stiffness.

[0032] For every 30° rotation of the screw 6, the outer magnetic ring is displaced 0.0833 mm relative to its original position along the vertical axis.

[0033] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A load-adjustable magnetic ring type quasi-zero stiffness pipe support, characterized in that, include: Inner magnetic ring (1), outer magnetic ring (2), vertical spring (3), upper shell (4), upper cover (5), screw (6), inner cover (7), outer magnetic ring washer (8), inner magnetic ring on shaft (9), base (10), sleeve (11) and fastening screw (11a); The inner magnetic ring (1) is set on the shaft (9) where the inner magnetic ring is located and is fixed by the sleeve (11); when the external applied load is changed, the position of the inner magnetic ring (1) on the shaft (9) where the inner magnetic ring is located is changed by adjusting the fastening screw (11a) so that the vertical height of the inner magnetic ring (1) and the outer magnetic ring (2) is the same when at the equilibrium position; The upper shell (4) and the upper cover (5) are connected by a thread to adjust the installation height; the upper cover (5) and the shaft (9) where the inner magnetic ring is located are also connected by a thread; an outwardly expanding cylindrical surface is also provided between the upper cover (5) and the base (10), and the vertical spring (3) is fixed by the outwardly expanding cylindrical surface; the inner cover (7) is fixed to one end of the screw (6); The outer magnetic ring (2) is fixed to the outer magnetic ring washer by the outwardly expanding cylindrical surface on the outer magnetic ring washer (8); the outer magnetic ring washer (8) is mounted on the screw (6).

2. The load-adjustable magnetic ring type quasi-zero stiffness pipeline support according to claim 1, characterized in that, The outer edge of the upper shell (4) contains a thread.

3. The load-adjustable magnetic ring type quasi-zero stiffness pipeline support according to claim 1, characterized in that, The axis of the inner magnetic ring (1) is coaxial with the vertical spring (3).

4. The load-adjustable magnetic ring type quasi-zero stiffness pipeline support according to claim 1, characterized in that, The coaxiality error between the inner magnetic ring (1) and the outer magnetic ring (2) is ≤0.05mm.

5. A load-adjustable magnetic ring type quasi-zero stiffness pipe support according to claim 1, characterized in that, Under static equilibrium conditions, the inner magnetic ring deviates from its static equilibrium position by displacement. x, The axial repulsive force between the inner and outer magnetic rings is: ； in, Br 1. Br 3 represents the residual magnetic induction intensity of the inner and outer magnetic rings, respectively; R 1. R R1 and R2 are the inner and outer diameters of the inner magnetic ring, respectively; R3 and R4 are the inner and outer diameters of the outer magnetic ring, respectively; H1 and H2 are the axial thicknesses of the inner and outer magnetic rings, respectively; |、| |、| | represents the distance between two points on the mid-end surface. 。 6. The load-adjustable magnetic ring type quasi-zero stiffness pipeline support according to claim 1, characterized in that, The system's restoring resultant force and total stiffness are: ； ； in, and The restoring force and stiffness of the vertical spring; and The nonlinear restoring force and stiffness of the inner and outer magnetic rings; When the system stiffness satisfies At that time, the total magnetic-elastic force F To achieve the critical state of zero stiffness.

7. A load-adjustable magnetic ring type quasi-zero stiffness pipe support according to claim 1, characterized in that, The screw (6) rotates 30° and its outer magnetic ring is displaced 0.0833 mm relative to its original position along the vertical axis.

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