Vibration reduction base based on rigid support and multi-frequency-band collaborative energy consumption and application of vibration reduction base

Abstract

The invention discloses a vibration reduction base based on rigid supporting and frequency-division-band cooperative energy consumption and application thereof, and belongs to the technical field of vibration reduction and isolation of ship equipment. The vibration reduction base comprises a main body supporting structure, an energy consumption unit and a local resonance unit; the main body supporting structure is composed of an upper panel, a lower panel and an orthogonal rib plate support, the upper panel and the lower panel are parallel to each other, the orthogonal rib plate support is arranged between the upper panel and the lower panel, a cylindrical container is arranged in the center of the orthogonal rib plate, the orthogonal rib plate and the cylindrical container are integrally formed, and the central axis of the cylindrical container coincides with the crossed axis of the orthogonal rib plate; the energy consumption unit is positioned in the upper panel and the cylindrical container; the local resonance units are located in four independent spaces formed by the orthogonal rib plates; and the upper panel is connected with the lower panel. Low-frequency vibration energy is focused and blocked through the local resonance unit, meanwhile, the low-frequency focusing energy and medium-high frequency vibration energy are subjected to broadband energy efficient dissipation through the multi-stage particle damping system, and broadband cooperative efficient vibration reduction is achieved.

Description

Technical Field

[0001] This invention belongs to the field of vibration reduction and isolation technology for marine equipment, specifically relating to a vibration reduction base based on rigid support and frequency band coordinated energy dissipation and its application. Background Technology

[0002] During navigation, a ship's main structure experiences continuous broadband vibrations due to factors such as the main engine, propeller, and wave impact. Various detection instruments and equipment installed on the hull (such as navigation, communication, and detection equipment) are sensitive to the vibration environment. Vibrations transmitted to these instruments and equipment can lead to increased measurement errors, decreased performance, or even damage. Furthermore, the vibrating mechanical equipment inside the ship's cabins is a major excitation source for the hull structure, capable of inducing structural vibrations and radiating noise outwards, thus affecting the ship's acoustic stealth performance.

[0003] The connection base between instruments / equipment and the ship's hull structure is the primary path for vibration transmission and a key structure for vibration reduction and isolation. However, traditional instrument / equipment bases, due to the requirement for reliable and stable support, are typically rigid bases welded from metal. Vibration reduction and isolation are achieved by placing rubber vibration isolators between the rigid base and the equipment. Rigid bases lack vibration reduction and isolation capabilities, and the low-to-medium frequency vibration energy that rubber isolators cannot dissipate is directly transmitted to the testing equipment, or from the vibrating equipment to the hull. To effectively solve these problems, the rigid support performance of the base needs to be integrated with its broadband and efficient vibration reduction performance in a unified design, achieving a unified base load-bearing and vibration reduction function. Summary of the Invention

[0004] This invention provides a vibration damping base based on rigid support and frequency band synergistic energy dissipation and its application. High rigidity support is achieved through an integrated structure of orthogonal ribs and a cylindrical container. Low-frequency vibration energy is focused and blocked through local resonance units. At the same time, a multi-level particle damping system efficiently dissipates low-frequency focused energy and mid-to-high-frequency vibration energy over a wide frequency band, achieving synergistic effect of "low-frequency blocking" and "wide frequency dissipation".

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] The vibration damping base based on rigid support and frequency band coordinated energy dissipation includes: main support structure, energy dissipation unit, and local resonance unit;

[0007] The main support structure consists of a parallel upper panel, a lower panel, and orthogonal ribs between them. A cylindrical container is set in the upper center of the orthogonal ribs. The orthogonal ribs and the cylindrical container are integrally formed. The central axis of the cylindrical container coincides with the cross axis of the orthogonal ribs. The energy dissipation unit is located inside the upper panel and the cylindrical container. The local resonance unit is located in the four independent spaces formed by the orthogonal ribs and is connected to the upper panel and the lower panel.

[0008] The upper panel is used to install instruments and equipment requiring vibration reduction; the lower panel is fixedly connected to the ship's deck or main structure.

[0009] The upper panel has a cylindrical hole at its center that connects to the cylindrical container, and the cylindrical container is filled with damping energy-dissipating particles.

[0010] The upper panel has four energy-consuming unit chambers that are centrally symmetrical about its center line. The energy-consuming unit chambers are covered by the same cover plate, which is connected to the upper panel by fasteners to seal the chambers. Each energy-consuming unit chamber is filled with damping energy-consuming particles.

[0011] The orthogonal ribs are cross-shaped, dividing the space between the upper and lower panels into four independent spatial regions. Each of the four independent spatial regions is provided with a set of local resonance units. The local resonance unit includes a hollow mass block, an upper tension spring, and a lower tension spring. The hollow mass block is filled with damping energy-dissipating particles. The hollow mass block is suspended between the upper and lower panels by the upper and lower tension springs.

[0012] The damping energy-dissipating particles have a filling rate of 50% to 95% in the cylindrical container, energy-dissipating unit chamber, and hollow mass block.

[0013] The local resonant units are centrally symmetrically distributed around the cylindrical container. When performing vibration absorption, they avoid introducing additional tilting or torsional moments to the base, thereby balancing the inertial forces of the base under vibration and enhancing the dynamic stability of the base.

[0014] The damping energy dissipation particles can be one or more combinations of various materials such as metal particles, ceramic particles, other non-metallic particles, and composite particles with high damping material on the surface, and the particle size of any of the damping energy dissipation particles is 1mm to 5mm.

[0015] The hollow mass block is generally cubic in shape, but cylindrical or other shapes can also be selected.

[0016] The aforementioned vibration-damping base, based on rigid support and frequency-band coordinated energy dissipation, can be used to install various detection instruments and equipment on the ship's hull, achieving broadband and efficient vibration reduction.

[0017] Beneficial effects: This invention provides a vibration damping base based on rigid support and frequency band coordinated energy dissipation and its application, which has the following advantages compared with the prior art:

[0018] 1. Enhanced dynamic stability: The local resonant units of this invention are centrally symmetrically distributed around the cylindrical container. When performing vibration absorption, they avoid introducing additional tilting or torsional moments to the base, thereby balancing the inertial force of the base when subjected to vibration and enhancing the dynamic stability of the base.

[0019] 2. Provides high rigidity support: The axis of the cylindrical container coincides with the intersection axis of the orthogonal ribs, and the outer wall of the cylindrical container is integrally formed with the orthogonal ribs, which enhances the overall structural rigidity and stability of the base.

[0020] 3. Multi-dimensional vibration reduction effect: The design of the central cylindrical container and the distributed particle damping chamber on the upper panel enables the base to have a good suppression effect on vibrations in multiple directions.

[0021] 4. Low-frequency bandgap blocking: Utilizing the dynamic vibration absorption principle of the local resonance unit, anti-resonance is generated in the designed low-frequency resonance section, effectively blocking the transmission of low-frequency vibration between the equipment and the hull, thus solving the problem of poor low-frequency effect of traditional passive vibration isolation.

[0022] 5. Flexible design: By changing parameters such as the stiffness of the first and second tension springs and the mass of the mass block, the equivalent stiffness and equivalent mass of the local resonance unit can be adjusted, thereby making the natural frequency of the local resonance unit match the main low-frequency vibration of the hull.

[0023] 6. Multi-stage particle damping frequency band coordinated energy dissipation: During local resonance, the particle damping within the mass block efficiently dissipates low-frequency energy, while the central cylindrical container and the top particle damping chamber absorb multi-directional mid-to-high frequency vibration energy, forming a multi-stage particle damping frequency band coordinated energy dissipation mechanism. This achieves high-efficiency vibration reduction over a wide frequency band, effectively solving the problem of the incompatibility between the rigid support requirements of ship equipment foundations and high-efficiency vibration reduction over a wide frequency band. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the vibration damping base structure in an embodiment of the present invention;

[0025] Figure 2 This is a front partial cross-sectional view of the vibration damping base in an embodiment of the present invention;

[0026] Figure 3 This is a schematic diagram of the orthogonal ribs and cylindrical container structure in the vibration damping base of this invention embodiment;

[0027] In the diagram, 101-upper panel, 102-lower panel, 103-cylindrical container, 104-orthogonal rib, 105-hook structure, 106-cylindrical hole, 107-particle damping chamber, 2-hollow mass block, 3-damping energy-dissipating particle, 4-upper tension spring, 5-lower tension spring, 6-fastener, 7-rubber piston a, 8-cover plate, 9-rubber piston b. Detailed Implementation

[0028] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments:

[0029] like Figures 1-2 As shown, the vibration damping base based on rigid support and frequency band coordinated energy dissipation includes: main frame structure, top energy dissipation unit, central energy dissipation unit, and local resonance unit;

[0030] Main frame structure: It consists of a parallel upper panel 101, a lower panel 102 and an orthogonal rib plate 104 supporting the structure between them. The upper surface of the upper panel 101 is used to install the instruments and equipment that need to be vibration damped. The lower surface of the lower panel 102 is fixedly connected to the ship deck or main structure. The orthogonal rib plate 104 is cross-shaped, dividing the space between the upper panel 101 and the lower panel 102 into four independent spatial regions.

[0031] Top energy dissipation unit: The upper panel 101 has four particle damping chambers 107 that are centrally symmetrical about its center line. The particle damping chambers 107 are covered by the same cover plate 8. The cover plate 8 is connected to the upper panel 101 by fasteners 6 to seal the particle damping chambers 107. The fasteners 6 are slotted cylindrical head screws. Each particle damping chamber 107 contains damping energy dissipation particles 3 with a filling rate of 90%.

[0032] Central energy dissipation unit: A cylindrical container 103 is set at the center of the orthogonal rib plate 104. The central axis of the cylindrical container 103 coincides with the cross axis of the orthogonal rib plate 104. At the same time, the outer wall of the cylindrical container 103 is integrally formed with the orthogonal rib plate 104 to enhance the overall structural rigidity of the base. The cylindrical container 103 contains damping energy dissipation particles 3 with a filling rate of 90%. The upper surface and the bottom of the side of the cylindrical container 103 are provided with openings to facilitate the filling and replacement of damping energy dissipation particles 3. The bottom opening of the side is sealed by a rubber piston a7. A cylindrical hole 106 connected to the upper surface of the cylindrical container 103 is provided at the center of the upper panel 101.

[0033] Local resonance unit: Each of the four independent spatial regions between the upper panel 101 and the lower panel 102 is provided with a set of local resonance units. The local resonance unit includes a hollow mass block 2, an upper tension spring 4, and a lower tension spring 5. The hollow mass block 4 contains damping energy dissipation particles 3 with a filling rate of 90%. The hollow mass block 2 is suspended between the upper panel 101 and the lower panel 102 by the upper tension spring 4 and the lower tension spring 5. The connection between the hollow mass block 2 and the tension spring, and the connection between the tension spring and the upper and lower panels, are all achieved through a hook structure 105. The hollow mass block 2 is cubic in shape, or it can be cylindrical. It has openings on its upper and lower surfaces to facilitate the filling and replacement of the damping energy dissipation particles 3. The opening on the lower surface is sealed by a rubber piston b9.

[0034] The damping energy dissipation particle 3 is an iron ball with a diameter of 2mm, and its surface is wrapped with a damping rubber layer.

[0035] Design and calculation of the parameters of the local resonance element:

[0036] The core design of the local resonance unit lies in: designing the natural frequency of the local resonance unit by adjusting the parameters of the tension spring and mass block 2, and then designing the low-frequency resonance range. The design formulas for the equivalent stiffness and resonance frequency of the local resonance unit are given below:

[0037] (1) Calculation of equivalent stiffness

[0038] Since the forces exerted by the first tension spring 4 and the second tension spring 5 on the mass block 2 during its movement are the same (i.e., the directions of the forces are the same), the effects of the first tension spring 4 and the second tension spring 5 on the mass block 2 are parallel. Therefore, the equivalent stiffness K of the system is... eq for:

[0039] (2) Resonance frequency design

[0040] Assuming the main low-frequency vibration frequency of the ship's hull is (e.g., 20Hz), while the natural angular frequency of the local resonant unit for: ;

[0041] The natural frequency of a local resonant unit (Hz) is: ; Wherein, k1 is the stiffness of the first tension spring 4; k2 is the stiffness of the second tension spring 5; and m is the total mass of the hollow mass block 2 and the damping energy dissipation particles 3 filled inside.

[0042] The aforementioned vibration-damping base, based on rigid support and frequency-band coordinated energy dissipation, can be used to install various detection instruments and equipment on the ship's hull. The integrated support structure design of the orthogonal ribs 104 and the central cylindrical container 103, along with the centrally symmetrical distribution of each structural component, enhances the overall dynamic stability of the base, providing high-rigidity support for the instruments and equipment installed on the upper panel 101. By changing parameters such as the stiffness of the first tension spring 4 and the second tension spring 5, and the mass of the hollow mass block 2 and the internally filled damping energy-dissipating particles 3, the equivalent stiffness of the local resonance unit can be adjusted. The equivalent mass allows the natural frequency of the local resonant unit to match the main low-frequency vibration of the hull. When the local resonant unit resonates at low frequencies, it causes violent movement of the damping energy-dissipating particles 3 in the hollow mass block 2, which efficiently dissipates the low-frequency vibration energy. At the same time, the damping energy-dissipating particles in the cylindrical container 103 and the particle damping chamber 107 of the upper panel 101 efficiently dissipate the mid-to-high frequency vibration energy, forming a multi-level particle damping frequency-segmented coordinated energy dissipation mechanism. The device of this invention can provide high-strength rigid support and achieve broadband efficient vibration reduction from low frequency to mid-to-high frequency.

[0043] The above description is merely a preferred embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A vibration-damping base based on rigid support and frequency band coordinated energy dissipation, characterized in that, include: The system comprises a main support structure, energy-dissipating units, and local resonance units. The main support structure consists of a parallel upper panel, a lower panel, and orthogonal ribs between them. A cylindrical container is centrally located on each orthogonal rib, and the orthogonal ribs and cylindrical container are integrally formed. The central axis of the cylindrical container coincides with the intersecting axis of the orthogonal ribs. The energy-dissipating units are located within the upper panel and the cylindrical container. The local resonance units are located within four independent spaces formed by the orthogonal ribs and are connected to the upper and lower panels.

2. The vibration damping base based on rigid support and frequency band coordinated energy dissipation as described in claim 1, characterized in that, The upper panel has four sealed energy-dissipating unit chambers that are centrally symmetrical about its center line, and each energy-dissipating unit chamber is filled with damping energy-dissipating particles.

3. The vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 2, characterized in that, The energy-consuming unit chamber is provided with a cover plate above it, and the cover plate is connected to the upper panel by fasteners to seal the energy-consuming unit chamber.

4. The vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 1, characterized in that, The local resonance unit includes a hollow mass block, an upper tension spring, and a lower tension spring; the hollow mass block is filled with damping energy-dissipating particles; the hollow mass block is suspended between the upper panel and the lower panel by the upper tension spring and the lower tension spring.

5. The vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 1, characterized in that, The cylindrical container is filled with damping energy-dissipating particles.

6. The vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 2, 4 or 5, characterized in that, The damping energy-dissipating particles have a filling rate of 50% to 95% in the cylindrical container, energy-dissipating unit chamber, and hollow mass block.

7. The vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 6, characterized in that, The particle size of the damping energy-dissipating particles is 1mm to 5mm.

8. The vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 4, characterized in that, By adjusting the parameters of the tension spring and the mass block, the natural frequency of the local resonance element is designed to match the main low-frequency vibration frequency of the hull. The natural frequency of the local resonant unit for: ， Where k1 is the stiffness of the first tension spring; k2 is the stiffness of the second tension spring; and m is the total mass of the hollow mass block and the damping energy-dissipating particles filling it.

9. The application of the vibration damping base based on rigid support and frequency band coordinated energy dissipation as described in any one of claims 1-8, characterized in that, The vibration damping base is used to install various detection instruments and equipment on the hull that require vibration damping.

10. The application of the vibration damping base based on rigid support and frequency band coordinated energy dissipation according to claim 9, characterized in that, The application process of the vibration damping base is as follows: the support structure formed by the orthogonal ribs and the cylindrical container provides high-rigidity support for the instruments and equipment installed on the upper plate; when the local resonance unit resonates at low frequency, it causes violent movement of the damping energy dissipation particles in the hollow mass block, which efficiently dissipates the low-frequency vibration energy. At the same time, the damping energy dissipation particles in the cylindrical container and the upper plate efficiently dissipate the mid-to-high frequency vibration energy, forming a multi-level particle damping frequency band coordinated energy dissipation mechanism to achieve broadband high-efficiency vibration reduction.

Images