Vibration reduction assembly with special section form and vibration isolation support

Abstract

The invention relates to a vibration reduction assembly with a special section form and a vibration isolation support, and belongs to the technical field of vibration isolation of precision equipment. The composite material comprises a plurality of elastic layers and rigid interlayer ring plates which are alternately overlapped, wherein the single elastic layer adopts a C-shaped, reverse C-shaped, S-shaped, catenary line-shaped, upper and lower unequal-thickness and / or middle-thinned section form. According to the vibration reduction assembly and the vibration isolation support, stress distribution of the rubber layer can be balanced, the broadband vibration suppression efficiency is improved, the structure is compact, by adopting the C-shaped, reverse-C-shaped, S-shaped and catenary line type section form with the upper end thickness and the lower end thickness unequal and the middle thickness reduced, stress distribution in the elastic layer is effectively optimized, the maximum stress in the elastic layer is remarkably reduced, and the service life of the vibration isolation support is prolonged. Therefore, the fatigue life and the overall reliability of the vibration reduction assembly are improved.

Description

Technical Field

[0001] This invention relates to a vibration damping component and vibration isolation support with a special cross-sectional shape, belonging to the field of vibration isolation technology for precision equipment. Background Technology

[0002] With the rapid development of ultra-precision machining, aerospace, microelectronics, and other fields, the precision requirements for machining mechanical parts are constantly increasing, leading to the emergence of precision machining platforms with micron or even nanometer-level accuracy. Precision equipment such as optical instruments, semiconductor manufacturing equipment, and medical imaging equipment are extremely sensitive to vibration; even minute vibrations can cause performance degradation or damage. Environmental vibrations are mainly divided into seismic ground motion and rail transit vibration. The impact of vibration on precision equipment manifests in the following aspects:

[0003] (1) It causes a decrease in equipment accuracy. Vibration can cause small displacements of internal components, thus affecting the accuracy of the equipment output results. For example, the optical path in an optical instrument may be shifted due to vibration, resulting in blurred imaging or deviations in the generated data.

[0004] (2) Damage to equipment structure. Vibrations with large amplitude, such as earthquakes, may directly damage the structure of the equipment, such as sensor breakage, loosening of optical components, or detachment of electronic chips.

[0005] (3) It leads to a decrease in the service life of the equipment. Mechanical vibration can cause fatigue damage and breakage of equipment parts, thereby shortening the service life of the equipment. For example, vibration can cause premature wear of bearings, accelerate equipment damage, and make the equipment more prone to failure.

[0006] To address the aforementioned issues, dual-control technology for vibration and seismic vibration has been proposed as a comprehensive solution. This technology integrates vibration control and seismic control to reduce the impact of earthquakes and environmental vibrations on buildings and equipment. In recent years, with the acceleration of urbanization and the increase in buildings above subway depots, dual-control technology has gradually become a research hotspot. It is mainly applied in vibration-sensitive applications such as subway buildings, vibration isolation for precision instruments, and theaters. By combining passive isolation and active control, dual-control technology can simultaneously handle low-frequency, high-energy, large-amplitude seismic ground motions and high-frequency, relatively small-amplitude rail transit vibrations, achieving broadband vibration suppression. This technology effectively reduces the impact of vibration on equipment accuracy and lifespan, meeting the normal operation requirements of precision equipment in complex environments.

[0007] However, the core vibration isolation component of the pre-vibration dual control system, namely the traditional laminated rubber bearing, has inherent defects. For example, the horizontally laminated rubber sheet generates edge stress concentration under vertical load, leading to premature local aging and reduced service life; the homogeneous rubber layer is difficult to optimize the low-frequency and high-frequency vibration attenuation performance at the same time, and the broadband vibration suppression effect is limited; the horizontal stability deteriorates sharply when relying on the thick rubber layer to achieve large deformation, and the bearing size needs to be increased in order to maintain lateral stiffness.

[0008] Therefore, there is an urgent need to propose a vibration reduction component and vibration isolation support with a special cross-sectional shape to solve the above-mentioned technical problems. Summary of the Invention

[0009] The purpose of this invention is to solve the problem of achieving balanced stress distribution in the rubber layer, improving broadband vibration suppression efficiency, and maintaining structural compactness in vibration isolation bearings. A brief overview of the invention is provided below to offer a basic understanding of certain aspects of it. It should be understood that this overview is not an exhaustive summary of the invention. It is not intended to identify key or essential parts of the invention, nor is it intended to limit the scope of the invention.

[0010] The technical solution of the present invention:

[0011] Option 1: A vibration damping component with a special cross-sectional shape, comprising multiple layers of alternating elastic layers and rigid interlayers, wherein the single elastic layer adopts a C-shaped, inverse C-shaped, S-shaped, catenary-shaped, unequal thickness at the top and bottom or thinned in the middle cross-section shape.

[0012] Preferably, the C-shaped cross-section protrudes towards the support platform in the middle, the inverted C-shaped cross-section protrudes towards the base in the middle, the S-shaped cross-section has a bidirectional wavy protrusion, and the catenary-shaped cross-section conforms to the catenary function profile.

[0013] Preferably, the upper end of the single-layer elastic layer with unequal thickness is thicker than the lower end, or the lower end is thicker than the upper end.

[0014] Preferably, the thinning in the middle is a single-layer elastic layer with a radially concave thinning zone in the middle.

[0015] Preferably, the material of the elastic layer is one or a combination of rubber, polyurethane, thermoplastic, silicone, and fiber-reinforced composite materials.

[0016] Option 2: A vibration isolation support with a special cross-sectional shape, comprising a support platform, a base, and a vibration damping component. The vibration damping component is the same as the vibration damping component with a special cross-sectional shape described in Option 1. The vibration damping component is disposed between the support platform and the base. The bottom side of the support platform is a first side that gradually converges from top to bottom. The base has a second side on the side facing the support platform. The vibration damping component is disposed between the first side and the second side.

[0017] Preferably, the vibration damping component and the base constitute a vibration damping unit, and the vibration damping unit is provided in N groups, where N≥2, and the N groups of vibration damping units form a nested structure.

[0018] Preferably, the number of elastic layers in the vibration damping components of each group of vibration damping units is the same or different.

[0019] The present invention has the following beneficial effects:

[0020] 1. By adopting C-shaped, inverted C-shaped, S-shaped, catenary-shaped, and uneven thickness at the top and bottom with reduced thickness in the middle cross-section, this invention effectively optimizes the stress distribution inside the rubber layer, significantly reduces the maximum stress inside the rubber layer, and thus improves the fatigue life and overall reliability of the vibration damping component.

[0021] 2. The vibration damping component of the present invention adopts an inclined annular arrangement and a rigid interlayer is set between the rubber layers, which enhances the constraint force of the structure on the rubber layers, significantly improves the support's ability to resist horizontal loads and lateral deformation, and ensures the lateral stability of the support while providing effective vertical vibration isolation.

[0022] 3. This invention utilizes the synergistic effect of compression and shear deformation of the rubber layer to give the support a lower initial stiffness and frequency in the vertical direction, effectively isolating micro-vibrations; at the same time, its vertical stiffness has nonlinear characteristics, increasing with the increase of deformation, ensuring the self-stability of the support under large loads and avoiding instability.

[0023] 4. Compared with traditional thick rubber vertical vibration isolation devices, this invention requires a more compact structure while providing the same vertical deformation capacity. By flexibly adjusting the tilt angle of the annular plate, the number of rubber layers (single or multiple layers), and adopting a multi-ring nested structure, the vertical stiffness, deformation capacity, and bearing capacity of the support can be easily adjusted to meet diverse engineering load requirements.

[0024] 5. Compared with pure spring-type vibration isolation devices, this structure provides excellent vertical vibration isolation while having a significantly stronger ability to resist horizontal loads, thus better ensuring the safety of the isolated building or equipment. Attached Figure Description

[0025] Figure 1 This is a perspective view of a vibration damping component with a special cross-sectional shape as described in Embodiment 1;

[0026] Figure 2 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Embodiment 2;

[0027] Figure 3 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Embodiment 2;

[0028] Figure 4 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 3;

[0029] Figure 5 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 3;

[0030] Figure 6 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 4;

[0031] Figure 7 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 4;

[0032] Figure 8 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 5;

[0033] Figure 9 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 5;

[0034] Figure 10 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 6;

[0035] Figure 11 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 6;

[0036] Figure 12 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 7;

[0037] Figure 13 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 7;

[0038] Figure 14 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 8;

[0039] Figure 15 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 8;

[0040] Figure 16 This is a schematic diagram of the structure of a vibration isolation support with a special cross-sectional shape as described in Example 9;

[0041] Figure 17 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 9;

[0042] Figure 18 This is a schematic diagram of the structure of a vibration isolation support with a special cross-sectional shape as described in Embodiment 10;

[0043] Figure 19 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Embodiment 10;

[0044] Figure 20 This is a schematic diagram of the structure of a vibration isolation support with a special cross-sectional shape as described in Embodiment 11;

[0045] Figure 21 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 11;

[0046] Figure 22 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Example 12;

[0047] Figure 23 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 12;

[0048] Figure 24 This is a schematic diagram of a vibration isolation support with a special cross-sectional shape as described in Embodiment 13;

[0049] Figure 25 This is a perspective view of a vibration isolation support with a special cross-sectional shape as described in Example 13.

[0050] In the figure, 1-support platform, 2-base, 3-vibration damping component, 11-first side, 21-second side, 31-elastic layer, 32-rigid interlayer. Detailed Implementation

[0051] To make the objectives, technical solutions, and advantages of this invention clearer, the invention is described below with reference to specific embodiments shown in the accompanying drawings. However, it should be understood that these descriptions are merely exemplary and not intended to limit the scope of the invention. Furthermore, descriptions of well-known structures and technologies are omitted in the following description to avoid unnecessarily obscuring the concept of the invention.

[0052] The connections mentioned in this invention are divided into fixed connections and detachable connections. Fixed connections (i.e., non-detachable connections) include, but are not limited to, conventional fixed connection methods such as folded connections, riveted connections, adhesive connections, and welded connections. Detachable connections include, but are not limited to, conventional disassembly methods such as threaded connections, snap-fit ​​connections, pin connections, and hinged connections. When a specific connection method is not explicitly defined, it is assumed that at least one existing connection method can always be found to achieve the function, and those skilled in the art can choose according to their needs. For example, a welded connection can be chosen for fixed connections, and a hinged connection can be chosen for detachable connections.

[0053] Example 1: Combination Figures 1-25This embodiment describes a vibration damping component with a special cross-sectional shape, comprising multiple layers of alternating elastic layers 31 and rigid interlayers 32. The single-layer elastic layer 31 adopts a C-shaped, inverse C-shaped, S-shaped, catenary-shaped, unequal thickness at the top and bottom, or thinned in the middle cross-section shape.

[0054] More preferably, the material of the elastic layer 31 is one or a combination of rubber, polyurethane, thermoplastic, silicone, and fiber-reinforced composite materials. The combination can be an alternating combination of rubber and polyurethane, a layered combination of silicone and fiber-reinforced composite materials, etc., that is, any single layer or multiple layers of various combinations. The combination of different materials can make full use of the characteristics of each material and select the design according to different application scenarios. The diversity and flexible combination of the elastic layer 31 materials (single layer or multiple layers, the same type or different types) enable the component to be precisely optimized for different working conditions (such as load, frequency, temperature, environment) to achieve the best vibration reduction effect and application adaptability.

[0055] The elastic layer 31, which is a single layer with unequal thickness at the top and bottom, has a thickness at the top that is greater than the thickness at the bottom, or vice versa.

[0056] The thinned middle section is a single-layer elastic layer 31 with a radially concave thinning zone in the middle.

[0057] For cross-sectional shapes with unequal thickness at the top and bottom or thinning in the middle, the thickness of the elastic layer 31 along the vertical direction is adjusted by modifying the tilt angle of the inner and outer annular surfaces of the elastic layer 31, thereby optimizing and adjusting the uneven stress distribution within the cross-section of the single-layer elastic layer 31.

[0058] For C-shaped, inverse C-shaped, S-shaped, and catenary-shaped cross-sectional shapes, the uneven stress distribution within the cross-section of the single-layer elastic layer 31 is optimized and adjusted by increasing the inclination angle of the middle part of the elastic layer 31 and decreasing the inclination angle of the lower end or both ends of the elastic layer 31.

[0059] Example 2: Combination Figure 2-3This embodiment describes a vibration-damping support with a special cross-sectional shape, comprising a support platform 1, a base 2, and a vibration-damping component 3. The support platform 1 has a first side surface 11 that converges from top to bottom at its bottom, and the base 2 has a second side surface 21 at its top. The lower end of the support platform 1 is higher than the lower end of the base 2, forming a stepped support structure. The vibration-damping component 3 is filled between the two inclined surfaces and consists of alternating layers of a single elastic layer 31 and a rigid interlayer 32. The elastic layer 31 has a C-shaped curve cross-section: by adjusting the contours of the inner and outer annular surfaces, the middle of the cross-section bulges towards the support platform, forming a curved cross-section that continuously transitions from the outer ring to the inner ring. This design optimizes the stress distribution of the elastic layer and reduces the maximum internal stress; the rigid interlayer 32 constrains the lateral deformation of the rubber, enhancing horizontal stability. Under vertical loads, the elastic layer achieves low-frequency vibration isolation through compression-shear coordinated deformation.

[0060] The vibration damping component 3 and the base 2 constitute a vibration damping unit. N sets of vibration damping units are provided, where N≥2. These N sets of vibration damping units form a nested structure, enabling zoned dissipation of vibration energy and multiple blocking of transmission paths, significantly improving vibration isolation efficiency, especially for complex multi-directional vibrations and broadband interference. The number of elastic layers 31 in the vibration damping component 3 within each set of vibration damping units may be the same or different. The number of elastic layers 31 in each ring of the vibration damping component 3 can be designed independently (same or different), providing differentiated stiffness and damping characteristics for each ring, achieving a gradient distribution or precise matching of stiffness, and greatly enhancing the adaptability of the support to non-uniform loads and broadband vibration isolation requirements.

[0061] Example 3: Combination Figure 4-5 This embodiment describes a vibration-damping support with a special cross-sectional shape. Based on Embodiment 2, the vibration-damping component 3 is an extension of the original, with a double-ring nested structure. The vibration-damping unit consists of two sets: two concentric C-shaped elastic layers 31 separated by a rigid interlayer 32. The C-shaped cross-section continuously optimizes stress uniformity, and the double-ring design expands the load-bearing capacity. The stepped support structure suppresses horizontal displacement, and the rigid interlayer 32 strengthens interlayer constraint.

[0062] Example 4: Combination Figure 6-7 This embodiment describes a vibration-damping support with a special cross-sectional shape. Based on Embodiment 2, the elastic layer 31 in this embodiment has an inverted C-shaped cross-section: the middle of the cross-section bulges towards the base, forming a continuous transition profile. This shape transfers the high-stress area from the bearing platform side to the base side, optimizing the vibration energy dissipation path. The stepped structure combined with the inverted C-shaped cross-section reduces vibration transmission.

[0063] Example 5: Combination Figure 8-9This embodiment, based on Example 2, adopts a double-ring inverted C-shaped cross-section. The bidirectional protrusions of the inverted C-shaped cross-section, combined with the double-ring nesting, achieve frequency division control of low-frequency and high-frequency vibrations. The rigid interlayer 32 enhances interlayer constraint and significantly improves horizontal stability.

[0064] Example 6: Combination Figure 10-11 This embodiment, based on Example 2, uses an elastic layer 31 with an S-shaped bidirectional wavy convex cross-section and continuously varying thickness. The S-shaped curve forms a distributed stress zone in the middle of the rubber layer, eliminating the single-point stress concentration of traditional designs. The stepped structure of the support platform 1 effectively resists overturning moments.

[0065] Example 7: Combination Figure 12-13 This embodiment, based on Example 2, adopts a double-ring S-shaped cross-section with phase misalignment of the inner and outer ring wavy contours. The wavy protrusions of the S-shaped cross-section form multi-level energy dissipation units, expanding the vibration isolation frequency band. The stiffness of the multi-ring nested structure is adjusted by adjusting the tilt angle of the ring plates.

[0066] Example 8: Combination Figure 14-15 This embodiment, based on Example 2, uses a cross-sectional shape of the elastic layer 31 that conforms to a catenary function: the thickness gradually changes continuously along the height, achieving uniform stress distribution throughout the entire area. The catenary profile eliminates abrupt changes in edge stress, and the stepped structure forms a pull-out resistance node at the lower end of the support platform 1.

[0067] Example 9: Combination Figure 16-17 This embodiment, based on Example 2, adopts a double-ring catenary cross-section. The continuous gradient characteristics of the catenary cross-section adapt to large deformation conditions, and the double-ring design achieves load-level adaptation through function coefficient adjustment.

[0068] Example 10: Combination Figure 18-19 This embodiment, based on Example 2, uses an asymmetrical cross-sectional shape for the elastic layer 31: the upper end is thicker than the lower end, while the middle part has the same thickness. The thicker upper layer and thinner lower layer distribution is achieved by increasing the inclination angle on the inner ring surface, thus strengthening the high-stress area on the support platform side. The stepped structure restricts the displacement of the base.

[0069] Example 11: Combination Figure 20-21 This embodiment, based on Example 2, adopts a double-ring asymmetrical cross-sectional shape, with the outer and inner rings having opposite thickness distributions (the outer ring is thicker at the top and thinner at the bottom / the inner ring is thicker at the bottom and thinner at the top). The differentiated thickness matches the stress requirements of the double rings, and the adjustable tilt angle mechanism of the rigid interlayer 32 enhances design flexibility.

[0070] Example 12: Combination Figure 22-23This embodiment, based on Example 2, uses an elastic layer 31 with a symmetrical cross-sectional shape: the upper and lower ends have equal thickness, and the middle part is concave radially to form a thinning zone. The thinning zone releases bending stress and eliminates stress concentration at the center. The stepped structure provides torsional support.

[0071] Example 13: Combination Figure 24-25 This embodiment, based on Example 2, adopts a double-ring, centrally thinned cross-section. The centrally thinned cross-section creates a graded energy dissipation mechanism: energy is dissipated at the ends during small deformations, while the central section absorbs energy during large deformations. Multi-ring nesting and expansion achieve multi-level stiffness adjustment.

[0072] It should be noted that in the above embodiments, as long as the technical solutions are not contradictory, they can be permuted and combined. Those skilled in the art can exhaust all possibilities based on the mathematical knowledge of permutation and combination. Therefore, the present invention will not describe the technical solutions after permutation and combination one by one, but it should be understood that the technical solutions after permutation and combination have been disclosed by the present invention.

[0073] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. 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 component with a special cross-sectional shape, characterized in that: It includes multiple layers of alternating elastic layers (31) and rigid interlayers (32), wherein the elastic layers (31) adopt a cross-sectional form of C-shaped, inverse C-shaped, S-shaped or catenary.

2. The vibration damping component with a special cross-sectional shape according to claim 1, characterized in that: The single-layer elastic layer (31) adopts a cross-sectional form with unequal thickness at the top and bottom or thinning in the middle.

3. A vibration damping component with a special cross-sectional shape according to claim 1, characterized in that: The C-shaped cross-section bulges towards the support platform in the middle, the inverted C-shaped cross-section bulges towards the base in the middle, the S-shaped cross-section has a bidirectional wavy bulge, and the catenary-shaped cross-section conforms to the catenary function profile.

4. A vibration damping component with a special cross-sectional shape according to claim 2, characterized in that: The elastic layer (31) with unequal thickness at the top and bottom is a single layer, with the upper end thickness greater than the lower end thickness, or the lower end thickness greater than the upper end thickness.

5. A vibration damping component with a special cross-sectional shape according to claim 2, characterized in that: The thinned middle section is a single-layer elastic layer (31) with a radially concave thinning zone in the middle.

6. A vibration damping component with a special cross-sectional shape according to claim 1, characterized in that: The material of the elastic layer (31) is one or a combination of rubber, polyurethane, thermoplastic, silicone, and fiber-reinforced composite materials.

7. A vibration isolation bearing with a special cross-sectional shape, characterized in that: The device includes a support platform (1), a base (2), and a vibration damping component with a special cross-sectional shape according to any one of claims 1-6. The vibration damping component (3) is disposed between the support platform (1) and the base (2). The bottom side of the support platform (1) is a first side (11) that gradually converges from top to bottom. The base (2) has a second side (21) on the side facing the support platform. The vibration damping component (3) is disposed between the first side (11) and the second side (21).

8. A vibration isolation bearing with a special cross-sectional shape according to claim 7, characterized in that: The vibration damping component (3) and the base (2) constitute a vibration damping unit. There are N sets of vibration damping units, where N≥2, and the N sets of vibration damping units constitute a nested structure.

9. A vibration isolation bearing with a special cross-sectional shape according to claim 8, characterized in that: The number of elastic layers (31) in the vibration damping components (3) of each group of vibration damping units may be the same or different.

Images