A disc-shaped double spiral wave manipulation dynamic vibration absorber structure

Abstract

The application discloses a disc-shaped double helical wave manipulation dynamic vibration absorbing structure and belongs to the technical field of equipment vibration reduction. The disc-shaped double helical wave manipulation dynamic vibration absorbing structure is designed in a variable thickness mode. The propagation speed of elastic waves gradually decreases with the decrease of the thickness. The vibration amplitude is concentrated at the position where the thickness of the variable thickness region of the disc-shaped double helical wave manipulation dynamic vibration absorbing structure is the thinnest. A small amount of viscoelastic damping material is combined at the edge position, so that the vibration energy is dissipated as heat energy, thereby achieving the purpose of vibration reduction. In addition, due to the disc-shaped double helical wave manipulation dynamic vibration absorbing structure, the full-band resonance peak of the controlled structure is efficiently suppressed, and the weight of the vibration reduction structure is reduced, and the installation space of the structure is compressed. The dynamic vibration absorbing effect and the overall loss factor of the structure are increased by improving the modal density and the loss factor density, so as to provide a novel vibration reduction structure for efficiently reducing the vibration of the covering structure in the full-band high, medium and low frequency range.

Description

Technical Field

[0001] This invention belongs to the field of vibration reduction and noise reduction technology, and relates to a disk-shaped double-helix wave-controlled dynamic vibration absorption structure. Background Technology

[0002] The core of wave-manipulated vibration reduction technology lies in adjusting the structural impedance. By changing the cross-sectional thickness of a specific region of the structure, the structural impedance characteristics of that region are altered. This change significantly affects the dynamic parameters of the flexural waves propagating within it, altering the wave propagation characteristics in the structure—especially the phase velocity and group velocity. Theoretical analysis shows that in an ideal structure that gradually thins to zero thickness, flexural waves become completely non-reflective due to their velocity approaching zero, with all energy concentrated at the structural tip. In practical applications, due to limitations in manufacturing capabilities, the tail of the structure cannot truly achieve zero thickness, but energy can still be efficiently concentrated in the region with the minimum thickness. Therefore, by applying a small amount of viscoelastic damping layer within this energy concentration region, the equivalent loss factor of the structure can be significantly improved, efficiently capturing and dissipating vibration energy, thereby achieving a significant vibration suppression effect.

[0003] Traditional wave-manipulated vibration reduction structures have limited ability to control low-frequency vibrations and low loss factor density. They may not have any vibration reduction effect on some frequencies within a wide frequency range. This results in low vibration reduction efficiency and poor vibration reduction effect in the vibration control of some large flexible equipment, especially in aerospace and other fields. Therefore, there is an urgent need to improve the wideband vibration control capability of wave-manipulated vibration reduction structures through new structural designs.

[0004] In summary, there is an urgent need in this field for a novel vibration reduction structure that can improve the structural loss factor with high density and achieve efficient vibration reduction across the entire frequency band of the structure, including high, medium and low frequencies, while meeting the requirements for lightweight vibration reduction. Summary of the Invention

[0005] The purpose of this invention is to provide a novel disc-shaped double-helix wave-manipulated dynamic vibration absorption structure. This structure achieves lightweight, wide-bandwidth vibration reduction by employing a double-helix winding design. It features high density to improve the structural loss factor, and while meeting the requirements for lightweight vibration reduction, it achieves efficient vibration reduction across the entire high, mid, and low frequency range of the structure.

[0006] To achieve the above objectives, the present invention provides the following solution: This invention provides a disk-shaped double-helix wave-controlled dynamic vibration absorption structure, characterized in that it comprises: It includes a central cylinder and a disc-shaped double helix variable thickness structure. The disc-shaped double helix variable thickness structure is formed by the spiral curling of two parts of a beam-shaped wedge structure symmetrically connected on both sides of the central cylinder. The two parts of the beam-shaped wedge structure are arranged in layers inside and outside, with gaps between them. The lower surface of the central cylinder is attached to the surface of the structure to be damped, and is used to connect the disc-shaped double helical wave manipulated dynamic vibration absorption structure to the structure to be damped. When the disc-shaped double-helix variable thickness structure unfolds, it unfolds into two parts: a beam-shaped wedge structure. The beam-shaped wedge structure is beam-shaped, meaning that the upper surface is a plane and the lower surface is a curved surface whose thickness gradually decreases from near the central cylinder to the far end.

[0007] Preferably, the width of the main body of the beam-shaped wedge structure is consistent. The width of the starting end of the beam-shaped wedge structure connected to the central cylinder gradually increases until it is consistent with the width of the main body. The starting end wraps around the outside of the central cylinder and is integrally connected to the central cylinder. The connection point with the central cylinder is smoothly transitioned.

[0008] Preferably, the radius of the central cylinder is the same as the width of the main body of the beam-shaped wedge structure.

[0009] Preferably, it further includes a viscoelastic damping material disposed on the upper surface of the beam-shaped wedge structure.

[0010] Preferably, the thickness of the left and right parts of the beam-shaped wedge structure decreases exponentially from the center to the outer end; and the thickest end of the beam-shaped wedge structure is the connection point to the central cylinder, which has the same thickness as the central cylinder, while the thinnest end of the beam-shaped wedge structure is the edge end of the disc-shaped double-helix variable thickness structure.

[0011] Preferably, the expression for the thickness of the beam-shaped wedge structure after unfolding and combining with the central cylinder is as follows: ; in, Indicates coefficient; This indicates the change in length of the beam-shaped wedge structure; It is a constant, and ≥2; The radius of the central cylinder is y1 represents the length of the left or right portion of the beam-shaped wedge structure; y2 represents the thickness of the thinnest end of the beam-shaped wedge structure; when the beam-shaped wedge structure is fully unfolded, the upper surface is a plane and the lower surface is a curved surface, and the distance between the plane and the curved surface is the thickness of the beam-shaped wedge structure.

[0012] The present invention achieves the following technical effects compared to the prior art: The proposed disc-shaped double-helix wave-controlled dynamic vibration absorption structure is novel and rational. It transforms the traditional beam-type wave-controlled dynamic vibration absorption structure through a double-helix winding design, causing the wave velocity of the flexural waves generated by vibration to gradually decrease with decreasing thickness within the structure. Vibration energy is concentrated at the thinnest point of the disc-shaped double-helix wave-controlled dynamic vibration absorption structure. Vibration suppression is achieved by laying viscoelastic damping material at the thinnest point, thus achieving structural vibration reduction. Furthermore, the double-helix design increases the structure's loss factor density, solving the problem of traditional vibration reduction structures having no vibration reduction effect at certain frequencies across a wide frequency range. This achieves full-frequency vibration reduction capability while meeting the requirements for lightweight vibration reduction. Attached Figure Description

[0013] 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.

[0014] Figure 1 This is a schematic diagram of the overall structure of the disk-shaped double-helix wave-controlled dynamic vibration absorption structure disclosed in the embodiments of the present invention; Figure 2 This is a front view of the disk-shaped double-helix wave-controlled dynamic vibration absorption structure disclosed in the embodiments of the present invention; Figure 3 This is a top view of the disk-shaped double-helix wave-controlled dynamic vibration absorption structure disclosed in the embodiments of the present invention; Figure 4 This is a cross-sectional view of the disk-shaped double-helix wave-controlled dynamic vibration absorption structure disclosed in the embodiments of the present invention; Figure 5 This is a schematic diagram of the disk-shaped double-helix wave-manipulated dynamic vibration absorption structure disclosed in the embodiments of the present invention when it is in a fully deployed state; Figure 6 This is a schematic diagram of the disk-shaped double-helix wave-manipulated dynamic vibration absorption structure disclosed in the embodiments of the present invention in polar coordinates; Figure 7 This is a schematic diagram of the installation of the disc-shaped double-helix wave-controlled dynamic vibration absorption structure disclosed in the embodiments of the present invention on an aluminum plate; Figure 8 This is a perspective view of the disk-shaped double-helix wave-controlled dynamic vibration-absorbing structure disclosed in the embodiments of the present invention mounted on an aluminum plate. Figure 9 This is a comparison chart of the loss factor characteristics of three cases disclosed in the embodiments of the present invention: aluminum plate (without vibration damping structure), aluminum plate with disc-shaped double helix wave-controlled dynamic vibration absorption structure, and aluminum plate with additional control group structure. Figure 10 This is a comparison diagram of the vibration characteristics of an aluminum plate with a disc-shaped double-helix wave control dynamic vibration absorption structure and an aluminum plate with an additional control group structure, as disclosed in the embodiments of the present invention.

[0015] The attached figures are labeled as follows: 1. Disc-shaped double-helix wave-controlled dynamic vibration absorption structure; 11. Disc-shaped double-helix variable thickness structure; 111. Beam-type wedge structure; 1111. Variable thickness region right; 1112. Variable thickness region left; 1113. Lower layer right; 1114. Upper layer right; 1115. Lower layer left; 1116. Upper layer left; 12. Viscoelastic damping material; 13. Central cylinder; 131. Upper surface of central cylinder; 132. Lower surface of central cylinder.

[0016] 2. Aluminum plate. Detailed Implementation

[0017] 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.

[0018] One of the objectives of this invention is to provide a novel disc-shaped double-helix wave-manipulated dynamic vibration absorption structure, which can achieve a more efficient vibration reduction effect while reducing the weight of traditional wave-manipulated vibration reduction structures, and increase the density of the loss factor, thereby suppressing vibrations across the high, medium, and low frequency bands of the structure.

[0019] Example 1: A disk-shaped double-helix wave-controlled dynamic vibration absorption structure includes: The disc-shaped double-helix variable thickness structure includes a central cylinder and a beam-shaped wedge structure (two parts arranged on the left and right sides of the symmetrical central cylinder) spirally rolled around the outside of the cylinder, which has a one-dimensional wave-manipulated vibration reduction effect and is used to concentrate the vibration energy in the structure; the lower surface of the central cylinder is attached to the surface of the structure to be damped, and is used to connect the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure to the structure to be damped. When the left and right parts of the disc-shaped double helix variable thickness structure are unfolded, the structure is beam-shaped (after unfolding, it becomes a beam-shaped wedge structure). Its upper surface is a plane; the lower surface is a curved surface from the central cylinder to the far end, where the thickness of the beam-shaped wedge structure gradually decreases.

[0020] The structure of the left and right parts of the beam-shaped wedge structure when spiraled is as follows: the outer end of the beam-shaped wedge structure, i.e. the main body, has the same width, while the inner end (the starting end) is connected to the central cylinder. Its width gradually increases, i.e., the inner end wraps around the outside of the central cylinder and is integrated with the central cylinder, forming a smooth transition at the connection point with the central cylinder.

[0021] The radius of the central cylinder is the same as the width of the main body of the beam-shaped wedge structure.

[0022] A viscoelastic damping material is disposed on the surface of the disc-shaped double-helix variable thickness structure to dissipate vibration energy.

[0023] Optionally, when the disc-shaped double-helix variable thickness structure is fully unfolded, it becomes a beam-shaped wedge structure, with the thickness decreasing exponentially from the central region to both ends; the thickest end of the disc-shaped double-helix variable thickness structure is the center position of the disc-shaped double-helix variable thickness structure (with uniform thickness), and the thinnest end of the disc-shaped double-helix variable thickness structure is the end of the disc-shaped double-helix variable thickness structure; the central cylinder has the same thickness as the thickest end of the disc-shaped double-helix variable thickness structure.

[0024] Optionally, the expression for the thickness of the beam-shaped wedge structure is: ; in, This indicates the thickness variation of the beam-shaped wedge structure; Indicates coefficient; This indicates the change in length of the beam-shaped wedge structure; It is a constant, and ≥2; This represents the thickness value of the thinnest end of the beam-wedge structure. This represents the thickness value of the thickest end of the beam-shaped wedge structure.

[0025] The radius of the central cylinder is The length of a beam-shaped wedge structure.

[0026] Optionally, when the disc-shaped double-helix variable thickness structure is fully unfolded, it becomes the beam-shaped wedge structure, with the upper layer being a plane and the lower layer being a curved surface. The distance between the plane and the curved surface is the thickness of the beam-shaped wedge structure.

[0027] Optionally, the viscoelastic damping material is a strip-shaped viscoelastic damping structure with uniform thickness, which is disposed on the plane of the beam-shaped wedge structure and spirally rolled along with the beam-shaped wedge structure.

[0028] Optionally, the width of the strip-shaped viscoelastic damping structure is the same as the width of the beam-shaped wedge structure.

[0029] Optionally, the viscoelastic damping material is a butyl rubber damping sheet.

[0030] Optionally, the central cylinder is a cylinder of uniform thickness, located at the center of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure, and connected to the structure to be damped through its lower surface.

[0031] Optionally, the thickness of the uniformly thick cylinder is the thickness of the thickest end of the disc-shaped double-helix variable thickness structure.

[0032] Optionally, the lower surface of the uniformly thick cylinder is bonded or welded to the surface of the structure to be vibration-damped.

[0033] Optionally, the connector and the beam-shaped wedge structure are made of aluminum alloy.

[0034] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0035] Example 2 like Figure 1 As shown, this embodiment provides a disc-shaped double-helix wave-manipulated dynamic vibration-absorbing structure 1, which includes a disc-shaped double-helix variable thickness structure 11, a viscoelastic damping material 12, and a central cylinder 13. The disc-shaped double-helix variable thickness structure 11 is formed by spirally coiling a beam-wedge structure 111 with wave-manipulated vibration reduction effect, used to absorb and dissipate the vibration energy generated at any position on the structure to be damped. Generally, the variable thickness regions 1111 (right) and 1112 (left) of the beam-wedge structure 111 are coiled and spiraled in the form of an Archimedean spiral. The viscoelastic damping material 12 is disposed on the surface of the disc-shaped double-helix variable thickness structure 11, forming the uppermost surface of the disc-shaped double-helix wave-manipulated dynamic vibration-absorbing structure 1, used to further dissipate vibration energy. The central cylinder 13 is disposed at the center of the disc-shaped double-helix variable thickness structure 11, used to connect the disc-shaped double-helix variable thickness structure 11 to the structure to be damped, thereby establishing a connection between the disc-shaped double-helix wave-manipulated dynamic vibration-absorbing structure 1 and the aluminum plate 2 of the structure to be damped. The aforementioned disc-shaped double-helix wave-manipulated dynamic vibration absorption structure 1, combined with the design of a double-helix structure, improves the loss factor density of the structure and enhances the control efficiency of the wave-manipulated dynamic vibration absorption structure for full-frequency vibration.

[0036] In this embodiment, as Figure 2 , Figure 3 , Figure 4 and Figure 5As shown, when the disc-shaped double helix variable thickness structure 11 is fully unfolded, the thickness decreases exponentially from the center end to both edges; and the thickest end of the beam-wedge structure 111 is the center end of the disc-shaped double helix variable thickness structure 11, while the thinnest end of the beam-wedge structure 111 is the edge ends of the disc-shaped double helix variable thickness structure 11; the central cylinder 13 is located at the center end of the disc-shaped double helix variable thickness structure 11.

[0037] In this embodiment, when the beam-wedge structure 111 is fully unfolded, its upper right surface 1114 and upper surface 1116 (the upper contour surface of the beam-wedge structure 111) are planes, and the upper right surface 1114 and upper surface 1116 are on the same plane; the lower right surface 1113 and lower left surface 1115 (the lower contour surface of the beam-wedge structure 111) are curved surfaces, and the distance between the plane and the curved surface is the thickness of the beam-wedge structure 111, which is expressed as: ;in, This indicates the thickness variation of the beam-type wedge structure 111; Indicates coefficient; This indicates the length variation of the beam-type wedge structure 111; It is a constant, and ≥2; This represents the thickness value at the thickest end of the beam-wedge structure 111; This represents the thickness value at the thinnest end of the beam-wedge structure 111. The beam-wedge structure 111 itself is a structure with wave-manipulation vibration reduction effect. When the variable thickness regions right 1111 and left 1112 at both ends are spiraled clockwise around the y-axis in the form of a standard Archimedean spiral, the lower right 1113 and lower left 1115 rotate with the upper right 1114 and upper left 1116 while maintaining the relative distance to the outline of the beam-wedge structure 111.

[0038] In this embodiment, the viscoelastic damping material 12 is preferably a uniformly thick strip-shaped viscoelastic damping structure, which is disposed on the plane of the beam-wedge structure 111, namely the upper right surface 1114 and the upper left surface 1116, and spirally curls along the variable thickness regions right 1111 and left 1112. In the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure 1, the viscoelastic damping material 12 has a spiral strip shape with the same trend as the disc-shaped double-helix variable thickness structure 11. As a further preferred embodiment, the width of the strip-shaped viscoelastic damping structure is the same as the width of the disc-shaped double-helix variable thickness structure 11.

[0039] In this embodiment, the viscoelastic damping material 12 is preferably a butyl rubber damping sheet.

[0040] In this embodiment, the upper surface 131 of the central cylinder 13 and the upper surface of the disc-shaped double-helix variable thickness structure 11 are on the same plane. The lower surface 132 of the central cylinder 13 is fixed to the surface of the structure to be damped by adhesive bonding or welding.

[0041] In this embodiment, the disc-shaped double-helix variable thickness structure 11 is made of aluminum alloy.

[0042] The aforementioned disc-shaped double-helix wave-manipulated dynamic vibration absorption structure 1 proposed in this technical solution is specifically a disc-shaped double-helix wave-manipulated dynamic vibration absorption structure. Its central cylinder 13 is fixed to the surface of the structure to be damped through the lower surface 132. The vibration energy on the structure to be damped is transferred to the variable thickness region of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure 11. Combining the characteristics of wave-manipulated vibration reduction, and at the same time, combining the uniform thickness of the spiral band viscoelastic damping material set on the upper surface of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure 11 to dissipate vibration energy, a low-frequency vibration reduction effect is achieved. At the same time, the spiral structure design of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure 1 increases the loss factor density of the structure, achieving a highly efficient broadband vibration reduction effect.

[0043] The working principle of the disk-shaped double-helix wave-controlled dynamic vibration absorption structure 1 in this scheme will be explained in detail below with specific examples: In the aforementioned Disc-shped Double-helical WaveManipulates Dynamic Vibration Absorber 1, based on the high-density loss factor and wave-manipulated vibration control characteristics of the Disc-shped Double-helical variable-thickness structure 11, and combined with the dynamic vibration absorption effect, high-efficiency vibration control of the main structure across the entire frequency band is achieved. Simultaneously, this vibration reduction structure possesses lightweight structural characteristics. The Disc-shped Double-helical WaveManipulates Dynamic Vibration Absorber 1 will be uniformly referred to as "DDWM-DVA" below.

[0044] 1. Formation formula of disk-shaped double-helix wave-controlled dynamic vibration-absorbing structure The disc-shaped double-helix wave-controlled dynamic vibration absorption structure consists of two variable-thickness regions, right 1111 and left 1112, on either side of the beam-shaped wedge structure 111, respectively, surrounding... y The shaft is obtained by rotating it clockwise according to the helical equation. O Establish a polar coordinate system with the origin as the origin. r r , )and( r l , l ),like Figure 6 As shown. Among them. R r It is the radius of the outer circle of the right-hand spiral;r r It is the radius of the inner circle of the right-hand spiral; n r It is the number of revolutions of the right-hand spiral; r It is the rotation angle to the right. q r This indicates how many degrees the right-hand spiral rotated from the starting point to the ending point. s r This represents a variable used to define the radius at each point on the right-hand spiral. R l It is the radius of the outer circle of the left spiral; r l It is the radius of the inner circle of the left spiral; n l It is the number of revolutions of the left spiral; l It's the rotation angle to the left. q l This indicates how many degrees the left-hand spiral rotated from its starting point to its ending point. s l Let represent a variable used to define the radius at each point on the left-hand spiral. The equations of the curves on both sides are as follows: ;

[0045] In the variable thickness region of the beam-wedge structure, the thickness variation law of DDWM-DVA is the same as that of the beam-wedge structure itself. To better express the positional relationship between the lower right 1113 and the upper right 1114 in the beam-wedge structure, the upper right 1114 is used as... Using the axis as an example, keeping the distance between the upper right (1114) and lower left (1113) layers constant, transforming them to a Cartesian coordinate system yields the equation for the lower right (1113) layer:

[0046]

[0047] Similarly, to better express the positional relationship between the lower left level 1115 and the upper left level 1116 in the beam-wedge structure, the upper left level 1116 is used as... Using the axis as an example, keeping the distance between the upper left (1116) and lower left (1115) layers constant, transforming it to a Cartesian coordinate system yields the equation for the lower left (1115) layer:

[0048]

[0049] in, This indicates the thickness variation of the beam-shaped wedge structure; Indicates coefficient; This indicates the length variation of the beam-like wedge structure; It is a constant, and ≥2; This indicates the thickness at the thinnest point of the beam-like wedge structure. This indicates the thickness of the thickest end of the beam-wedge structure.

[0050] The parameters of the variable thickness region in DDWM-DVA are the same as those of the variable thickness region in the beam-wedge structure, i.e., the parameters of the lower right 1113 and upper right 1114, and the lower left 1115 and upper left 1116 before and after the spiral transformation. The thickness remains unchanged in the direction.

[0051] 2. Vibration reduction of DDWM-DVA like Figure 7 and Figure 8 As shown, DDWM-DVA 1 is fixed to the structure to be vibration damped via the lower surface 132 of the central cylinder 13. The structure to be vibration damped can be a common uniform aluminum plate structure 2 in engineering.

[0052] The thickness of DDWM-DVA 1 decreases exponentially from the thickness of the beam-wedge structure 111, and the varying thickness regions on both sides of the beam-wedge structure 111 spiral into a disc-shaped double helix. The thickness of DDWM-DVA 1 is the same as the thickness of the beam-wedge structure 111. The exponential expression is as follows: In the formula, This indicates the thickness variation of the beam-type wedge structure 111; Indicates coefficient; This indicates the length variation of the beam-type wedge structure 111; It is a constant, and ≥2; This represents the thickness value at the thickest end of the beam-wedge structure 111; This represents the thickness value of the thinnest end of the beam-wedge structure 111. The method for determining is as follows: first determine the required amount. Figure 5 The minimum thickness of the beam-wedge structure 11 in the middle The maximum thickness of the beam-type wedge structure 111 The value; and the radius dimension of the central cylinder 13. x 1 and the length value of the beam-type wedge structure 111 x 2, then follow Figure 5 In xoy The coordinate system substitutes points into the expression The coefficients are obtained by solving the system of equations. .

[0053] A viscoelastic damping material 13 is adhered to the upper surface of the disc-shaped double-helix variable thickness structure 11. Its main function is to convert the energy generated by vibration into heat dissipation, thereby achieving vibration reduction. The viscoelastic damping material 13 is a helical strip structure, and an appropriate length is adhered to the upper surface of the disc-shaped double-helix variable thickness structure 11 from the minimum thickness point to the maximum thickness point. The length of the viscoelastic damping material 13 can be selected as needed.

[0054] The aforementioned DDWM-DVA 1 is based on the fact that vibration is essentially the transmission of elastic waves. The wave velocity of elastic waves in a solid medium is related to the structural thickness. As the structural thickness decreases according to a certain power law, the phase velocity and group velocity of the elastic wave also decrease. Due to energy conservation, while the wave velocity decreases, the vibration amplitude will increase, causing the elastic wave to concentrate in the region where the solid medium thickness decreases, such as... Figure 8 As shown, the vibration energy on aluminum plate 2 can be transferred to DDWM-DVA 1. In the disc-shaped double helix variable thickness structure 11 of DDWM-DVA 1, the propagation speed of the elastic wave decreases as the thickness of the disc-shaped double helix variable thickness structure 11 decreases, the wavelength of the elastic wave decreases, the vibration amplitude increases, and it concentrates in the region where the thickness of the disc-shaped double helix variable thickness structure 11 decreases. By combining the viscoelastic damping material 13, most of the elastic wave energy is consumed, thereby achieving high-efficiency broadband vibration reduction.

[0055] A uniform aluminum plate 2 with a total length of 600mm, width of 500mm, and height of 10mm is selected as the object to be damped. For example... Figure 7 The DDWM-DVA 1 shown is connected to the uniform aluminum plate 2 via the lower surface 132 of the central cylinder 13. In the disc-shaped double-helix variable thickness structure 11 of the DDWM-DVA 1, the outer radius of the right spiral... R r 100mm; inner radius of the right spiral r r 20mm; the number of revolutions of the right-side spiral n r The value is 3; the rotation angle on the right side is 3. r 150°; Radius of the outer circle of the left spiral R l 100mm; inner radius of the left spiral r l 20mm; number of revolutions of the left spiral n l The value is 3; the rotation angle on the left is 3. l The angle is 150°. In beam-type wedge structure 111, the constant is... The thickness is 3; the thickness value at the thickest end. It is 7mm; the thickness value of the thinnest end. It is 0.5mm; It is 9.06 10 -9 The radius of the central cylinder 13 x 1 is 20mm; the length value of beam-type wedge structure 111 x 2 is 915.28mm. The aluminum plate 2 is made of 7075 aluminum alloy, commonly used in engineering. The disc-shaped double-helix variable thickness structure 11 in DDWM-DVA 1 is also made of 7075 aluminum alloy. The viscoelastic damping material 12 in DDWM-DVA 1 is 197mm long, 13mm wide, and 2mm thick, using butyl rubber damping sheets, with a material loss factor (loss factor) set to 0.1. To compare and highlight the vibration reduction advantages of DDWM-DVA 1 compared to traditional wave-manipulated vibration reduction structures, a wave-manipulated vibration reduction disk with similar mass and dimensions was designed as a control group. The viscoelastic damping material 13 has the same width, width, and thickness as DDWM-DVA 1.

[0056] A model of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure was established in ABAQUS (a finite element software for existing engineering simulation) using the finite element method. The loss factor level and vibration velocity response of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure were calculated through steady-state dynamic analysis and modal superposition method.

[0057] Analysis of calculation results: (1) DDWM-DVA loss factor analysis DDWM-DVA 1 can significantly improve the loss factor of a structure, increasing it by 2-46 times across the entire frequency band. Furthermore, the loss factor density increases from the 32nd order to the 132nd order. This substantial increase in density means that the loss factor level of the structure is improved across the entire frequency band after installing DDWM-DVA 1, thus effectively attenuating the vibration amplitude across the entire frequency band. In contrast, while the system loss factor level also improves by 2-40 times after installing the control group wave-manipulated damping disk, its loss factor density is only 72nd order, far lower than that after installing DDWM-DVA 1. This results in the improvement in loss factor not being fully covered at certain frequencies, leading to insignificant or no vibration reduction effect at some frequencies. Therefore, DDWM-DVA 1 can significantly improve the loss factor of the structure and increase the density of the loss factor, resulting in a wider frequency coverage of high loss factor. It is superior to the control group wave-manipulated damping disk in terms of improving the level and density of loss factor. This has potential benefits for the full-frequency vibration suppression of aluminum plate structures. At the same time, under the same size, DDWM-DVA 1 makes the structure lighter and more practical through the disc-shaped double helix design.

[0058] (2) DDWM-DVA broadband vibration reduction analysis To evaluate the vibration reduction effect of DDWM-DVA1 on aluminum plate structures across the entire frequency range, the velocity response within the 0-2500Hz range at the excitation point on the aluminum plate was compared. Figure 10 It can be observed that after installing DDWM-DVA1 on the aluminum plate, compared with the aluminum plate without vibration damping structure, all resonance peaks in the entire frequency band are effectively reduced, with a reduction of 6-16dB in resonance peaks across the entire frequency band. The resonance peaks at multiple frequencies, such as 84Hz, 235Hz, and 650Hz, exhibit dynamic vibration absorption effect separation and attenuation. This is because DDWM-DVA has higher modal density and wave manipulation characteristics, making it easier for it to couple with the aluminum plate to generate a dynamic vibration absorption effect. At the same time, combined with a higher density and level of loss factor, the resonance peaks across the entire frequency band are attenuated. Furthermore, compared to the control group wave-controlled vibration damping disc, the DDWM-DVA1 exhibits superior full-band vibration damping performance. While the resonance peaks of the aluminum plate's vibration amplitude were attenuated at some frequencies after installing the control group wave-controlled vibration damping disc, no attenuation was observed at resonance peaks near frequencies such as 124Hz, 235Hz, 301Hz, 386Hz, 477Hz, and 840Hz. However, after installing the DDWM-DVA1, the resonance peaks at these frequencies were effectively suppressed. Moreover, the reduced resonance peaks after installing the control group wave-controlled vibration damping disc were further reduced after installing the DDWM-DVA1; for example, the resonance peak values ​​near 86Hz and 561Hz were reduced by approximately 4dB. Furthermore, the control group wave-controlled damping disc produced fewer resonance peaks for dynamic vibration absorption, with only a noticeable resonance peak splitting phenomenon at 84Hz. This resulted in poor dynamic vibration absorption. Additionally, the loss factor density after installing the control group wave-controlled damping disc was lower than that after installing the DDWM-DVA1, limiting the improvement in damping level across the entire frequency range and leading to poor overall vibration reduction. The DDWM-DVA1 design precisely addresses this shortcoming. The reason lies in the fact that the variable thickness structural design in DDWM-DVA1 alters the structural impedance, thus changing the propagation speed of elastic waves within the structure. As the wave speed gradually decreases with decreasing thickness, the energy generated by vibration is concentrated in the minimum thickness region of DDWM-DVA1, enabling it to possess wave-manipulated vibration reduction capabilities. Furthermore, the double-helix structural design in the variable thickness region allows DDWM-DVA1 to achieve a higher modal density, generating richer dynamic vibration absorption effects, while simultaneously lowering the minimum frequency for vibration control. Finally, by attaching viscoelastic damping material to the minimum thickness region, the density of the loss factor is further increased, effectively enhancing the structure's loss factor and achieving efficient vibration suppression across the entire frequency band.

[0059] The DDWM-DVA 1 technical solution combines the characteristics of wave-manipulated vibration damping structures, dynamic vibration absorber structures, and double Archimedean spiral structures. This addresses the limitations of traditional disk-shaped wave-manipulated vibration damping structures in controlling low-frequency vibrations, their low loss factor density, and the lack of vibration damping effect at certain frequencies within a wide frequency range. Furthermore, the double Archimedean spiral structure design increases the loss factor density, compresses the space in the variable thickness region, and increases the probability of DDWM-DVA coupling with the structure being damped across a wide frequency range, exhibiting excellent wideband vibration damping performance, improving the structure's damping efficiency, and achieving vibration suppression at almost all frequencies. During structural design, rational parameters can be designed based on the frequency characteristics of the structure to be damped, further optimizing the amplitude at the key damping frequencies.

[0060] The DDWM-DVA 1 in this technical solution has a small added mass, good vibration reduction effect across the entire frequency band, and high dynamic vibration absorption coupling rate, which meets the needs of engineering applications.

[0061] The DDWM-DVA 1 technical solution can increase the structural modal density and loss factor density by designing the variable thickness region as a disc-shaped double helix, thus widening the vibration reduction frequency range and reducing the minimum vibration reduction frequency of other vibration reduction structures of the same size.

[0062] The DDWM-DVA 1 in this technical solution combines a disc-shaped double-helix design with wave manipulation principles and dynamic vibration absorber principles, resulting in a vibration reduction structure that is lightweight, effectively reduces vibration across the entire frequency range, and has a compact structure with minimal space requirements. For example, in this embodiment, installing one DDWM-DVA 1 only adds 3% to the mass of the aluminum plate to achieve good vibration reduction, while vibration reduction solutions using viscoelastic damping materials often require an increase of over 20%. Therefore, with the same added mass, the DDWM-DVA 1 offers superior broadband vibration reduction. Thus, the DDWM-DVA 1 in this technical solution is characterized by its lightweight added mass and high vibration control efficiency across the entire frequency range.

[0063] Therefore, compared with the prior art, the advantages of the present invention are as follows: 1. The variable thickness region of the traditional wave manipulation structure is designed as a disk-shaped double helix, which enables it to have higher modal density and loss factor density.

[0064] 2. Designing the variable thickness region of the traditional wave manipulation structure into a disk-shaped double helix can effectively suppress resonance peaks across the entire frequency band of the structure, thus broadening the vibration reduction range.

[0065] 3. Designing the variable thickness region of the traditional wave manipulation structure as a disk-shaped double helix can enhance the coupling efficiency between DDWM-DVA and the controlled structure, improve the dynamic vibration absorption effect, and enhance the loss factor.

[0066] 4. DDWM-DVA combines the advantages of wide-frequency vibration reduction capability of wave-manipulated vibration reduction structure, single-frequency control capability of dynamic vibration absorber structure, and rich dynamic characteristics of double-helix structure.

[0067] 5. SABH structural materials can be manufactured using the same materials as the controlled structure, increasing the service life and reliability of the vibration reduction structure in the project.

[0068] 6. DDWM-DVA can achieve the goals of lightweight added mass, high vibration control efficiency across the entire frequency range, compact space, and wideband vibration reduction.

[0069] 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.

[0070] Specific examples have been used to illustrate the principles and implementation methods of this invention. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of this invention. Furthermore, those skilled in the art will recognize that, based on the ideas of this 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 this invention.

Claims

1. A disk-shaped double-helix wave-controlled dynamic vibration absorption structure, characterized in that, include: It includes a central cylinder and a disc-shaped double helix variable thickness structure. The disc-shaped double helix variable thickness structure is formed by the spiral curling of two parts of a beam-shaped wedge structure symmetrically connected on both sides of the central cylinder. The two parts of the beam-shaped wedge structure are arranged alternately in the inner and outer layers, with gaps between them. The lower surface of the central cylinder is attached to the surface of the structure to be damped, and is used to connect the disc-shaped double helical wave manipulated dynamic vibration absorption structure to the structure to be damped. When the disc-shaped double-helix variable thickness structure unfolds, it unfolds into two parts: a beam-shaped wedge structure. The beam-shaped wedge structure is beam-shaped, meaning that the upper surface is a plane and the lower surface is a curved surface whose thickness gradually decreases from near the central cylinder to the far end.

2. The disk-shaped double-helix wave-controlled dynamic vibration absorption structure according to claim 1, characterized in that, The main body of the beam-shaped wedge structure has a consistent width. The starting part of the beam-shaped wedge structure at the connection with the central cylinder gradually increases in width until it matches the width of the main body. The starting part wraps around the outside of the central cylinder and is integrated with the central cylinder. The connection between the starting part and the central cylinder is smoothly transitioned.

3. The disk-shaped double-helix wave-controlled dynamic vibration absorption structure according to claim 1, characterized in that, The radius of the central cylinder is the same as the width of the main body of the beam-shaped wedge structure.

4. The disk-shaped double-helix wave-controlled dynamic vibration absorption structure according to claim 1, characterized in that, It also includes a viscoelastic damping material disposed on the upper surface of the beam-shaped wedge structure.

5. The disk-shaped double-helix wave-controlled dynamic vibration absorption structure according to claim 1, characterized in that, The thickness of the left and right parts of the beam-shaped wedge structure decreases exponentially from the center to the outer end; the thickest end of the beam-shaped wedge structure is where it connects to the central cylinder, and its thickness is the same as that of the central cylinder; the thinnest end of the beam-shaped wedge structure is the edge end of the disc-shaped double-helix variable thickness structure; when the beam-shaped wedge structure is fully unfolded, the upper surface is a plane and the lower surface is a curved surface, and the distance between the plane and the curved surface is the thickness of the beam-shaped wedge structure.

6. A disk-shaped double-helix wave-controlled dynamic vibration-absorbing structure according to claim 1 or 5, characterized in that, The expression for the thickness of the beam-wedge structure after it is unfolded and combined with the central cylinder is: ; in, Indicates coefficient; This indicates the change in length of the beam-shaped wedge structure; It is a constant, and ≥2; The radius of the central cylinder is y1 represents the length of the left or right portion of the beam-shaped wedge structure; y2 represents the thickness of the thinnest end of the beam-shaped wedge structure; y1 represents the thickness of the thickest end of the beam-shaped wedge structure.

7. The disk-shaped double-helix wave-controlled dynamic vibration absorption structure according to claim 4, characterized in that, The viscoelastic damping material is a uniformly thick strip-shaped viscoelastic damping structure, which is disposed on the plane of the upper layer of the beam-shaped wedge structure and is rolled into a spiral structure along with the beam-shaped wedge structure.

8. The viscoelastic damping material according to claim 4, characterized in that, The width of the strip-shaped viscoelastic damping structure is the same as the width of the beam-shaped wedge structure.

9. The disk-shaped double-helix wave-controlled dynamic vibration-absorbing structure according to any one of claims 4, 7, or 8, characterized in that, The viscoelastic damping material is a butyl rubber damping sheet.

10. The disk-shaped double-helix wave-controlled dynamic vibration absorption structure according to claim 1, characterized in that, The central cylinder is a cylinder of uniform thickness, located at the center of the disc-shaped double-helix wave-manipulated dynamic vibration absorption structure, and connected to the structure to be damped through its lower surface.

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