A sound-absorbing and vibration-isolating base and its design method

Abstract

The present invention provides a sound-absorbing and vibration-isolating base and a design method thereof. The design method includes dividing design parameters into multiple segments; combining the design parameters to determine the peak sound absorption coefficient of the sound-absorbing structure and the total acceleration level difference of the vibration-isolating structure under different combinations; normalizing the peak sound absorption coefficient of the sound-absorbing structure and the total acceleration level difference of the vibration-isolating structure under different combinations to determine a comprehensive performance evaluation value of the sound-absorbing and vibration-isolating base; and determining optimal design parameters based on the comprehensive performance evaluation value. The design method of the sound-absorbing and vibration-isolating base provided by the present invention automatically adjusts the design parameters of the sound-absorbing and vibration-isolating base based on multi-simulation software coupling, and collaboratively characterizes the comprehensive performance of the sound absorption level and vibration isolation capability of the sound-absorbing and vibration-isolating base by normalizing the peak sound absorption coefficient and the total acceleration level difference, and based on this, finds the optimal design parameters of the sound-absorbing and vibration-isolating base, thereby achieving an optimal design of the comprehensive sound absorption and vibration isolation performance of the sound-absorbing and vibration-isolating base.

Description

Technical Field

[0001] The present invention relates to the technical field of base design, and in particular to a sound-absorbing and vibration-isolating base and a design method thereof. Background Art

[0002] As ships become larger and faster, the vibration and noise levels of ship machinery and equipment have increased significantly. The current demand for ship vibration comfort is also becoming increasingly stringent, making vibration and noise important indicators that cannot be ignored in ship design and manufacturing. Ship cabin vibration and noise primarily originate from various rotating machinery and equipment.

[0003] Currently, ship vibration control measures primarily focus on isolating mechanical equipment vibration, for example, through the use of perforated sound-absorbing structures, to reduce further transmission of noise into the surrounding air. Currently, ship vibration control measures primarily focus on isolating mechanical equipment vibration, for example, through the deployment of vibration isolation bases such as honeycomb interlayers and airbags, to reduce or isolate further transmission of vibration to surrounding structures.

[0004] Due to the limited space in the ship's engine room, there is an urgent need to design a sound-absorbing and vibration-isolating base for ship machinery and equipment that can simultaneously achieve the dual functions of sound absorption and vibration isolation to solve the vibration noise problems of various rotating machinery and equipment. Summary of the Invention

[0005] The present invention provides a sound-absorbing and vibration-isolating base and a design method thereof, which are used to meet the technical requirements of achieving both sound absorption and vibration isolation, and solve the vibration noise problems of various rotating mechanical equipment in the prior art.

[0006] The present invention provides a design method for a sound-absorbing and vibration-isolating base, the sound-absorbing and vibration-isolating base comprising: a perforated plate, an intermediate base plate, a bottom rib plate, and an air bag arranged between the intermediate base plate and the bottom rib plate, the perforated plate and the intermediate base plate cooperating to form a sound-absorbing structure, and the intermediate base plate, the air bag, and the bottom rib plate cooperating to form a vibration-isolating structure;

[0007] The design method of the sound absorption and vibration isolation base includes:

[0008] dividing the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag into multiple segments within corresponding threshold ranges;

[0009] Combining the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag to determine the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations;

[0010] Normalizing the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations to determine the comprehensive performance evaluation value of the sound absorbing and vibration isolation base;

[0011] According to the comprehensive performance evaluation value, optimal design parameters are determined; the design parameters include the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag.

[0012] According to a design method for a sound-absorbing and vibration-isolating base provided by the present invention, the step of determining the peak sound absorption coefficient includes:

[0013] Obtaining the perforation diameter of the perforated plate and the thickness of the sound absorbing structure in the current combination;

[0014] Determine the sound absorption coefficient curve;

[0015] The peak sound absorption coefficient in the sound absorption coefficient curve is determined.

[0016] According to a design method for a sound-absorbing and vibration-isolating base provided by the present invention, the step of determining the total drop in acceleration level includes:

[0017] Obtaining vibration responses of the intermediate base plate and the bottom rib plate in the current combination;

[0018] The total drop in acceleration level of the vibration isolation structure is determined based on the minimum and maximum values ​​of the calculated frequency range.

[0019] According to a design method of a sound-absorbing and vibration-isolating base provided by the present invention, the total drop of the acceleration level is ;

[0020]

[0021] in, is the vibration response of the intermediate substrate, is the vibration response of the bottom rib, 、 It is the minimum and maximum value of the vibration frequency range of the mechanical equipment supported by the sound-absorbing and vibration-isolating base.

[0022] According to a design method for a sound-absorbing and vibration-isolating base provided by the present invention, the step of dividing the perforation diameter of the perforated plate, the thickness of the sound-absorbing structure, and the pressure of the airbag into multiple segments within corresponding threshold ranges includes:

[0023] The range of adjustment of the perforation diameter e of the perforated plate is [ , ], the perforation diameter e of the perforated plate is divided into n+1 segments, which are , , ,…, ;

[0024] The thickness of the sound absorbing structure The threshold range of adjustment is [ , ]; the thickness of the sound absorbing structure Divided into n+1 segments, respectively , , ,…, ;

[0025] The pressure of the airbag The threshold range of adjustment is [ , ], the pressure of the airbag Divided into n+1 segments, respectively , , ,…, .

[0026] According to a design method for a sound-absorbing and vibration-isolating base provided by the present invention, the step of determining the peak sound absorption coefficient of the sound-absorbing structure and the total drop in acceleration level of the vibration-isolating structure under different combinations includes:

[0027] For sound absorption and vibration isolation base Design parameter combinations to generate The peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure.

[0028] According to a design method for a sound-absorbing and vibration-isolating base provided by the present invention, the peak sound absorption coefficient of the sound-absorbing structure and the total drop of the acceleration level of the vibration-isolating structure under different combinations are normalized to determine the comprehensive performance evaluation value of the sound-absorbing and vibration-isolating base, including the following steps:

[0029] right The peak sound absorption coefficient of the sound absorption structure is normalized to obtain the evaluation value of the sound absorption level. ;

[0030] right The total difference in acceleration level of the vibration isolation structure is normalized to obtain the evaluation value of the vibration isolation capability. ;

[0031] Evaluation value based on sound absorption level and the estimated value of vibration isolation capability , determine the comprehensive performance evaluation value of the sound absorption and vibration isolation base .

[0032] According to a design method of a sound absorption and vibration isolation base provided by the present invention,

[0033] ;

[0034] ;

[0035] in, , and They are The minimum and maximum values ​​of the peak sound absorption coefficient G, and They are Total difference in acceleration level The minimum and maximum values ​​of .

[0036] According to a design method of a sound-absorbing and vibration-isolating base provided by the present invention,

[0037] ;

[0038] in, ; ,and .

[0039] The present invention also provides a sound-absorbing and vibration-isolating base, which is manufactured using the above-mentioned design method.

[0040] The design method of the sound-absorbing and vibration-isolating base provided by the present invention automatically adjusts the design parameters of the sound-absorbing and vibration-isolating base based on the coupling of multiple simulation software, and collaboratively characterizes the comprehensive performance of the sound absorption level and vibration isolation capability of the sound-absorbing and vibration-isolating base by normalizing the peak sound absorption coefficient and the total drop of the acceleration level. Based on this, the optimal design parameters of the sound-absorbing and vibration-isolating base are found, and the optimal design of the comprehensive performance of the sound absorption level and vibration isolation capability of the sound-absorbing and vibration-isolating base can be achieved. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] In order to more clearly illustrate the technical solutions in the present invention or the prior art, a brief introduction is given below to the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0042] Figure 1 It is a structural schematic diagram of the sound-absorbing and vibration-isolating base provided by the present invention.

[0043] Figure 2 This is one of the flow charts of the design method of the sound-absorbing and vibration-isolating base provided by the present invention.

[0044] Figure 3 This is the second flow chart of the design method of the sound-absorbing and vibration-isolating base provided by the present invention.

[0045] Figure 4 It is a schematic diagram of the sound absorption coefficient curve of the perforated plate sound absorption structure provided by the present invention.

[0046] Figure 5 This is the third flow chart of the design method of the sound-absorbing and vibration-isolating base provided by the present invention.

[0047] Figure 6 It is a schematic diagram of the center point of the vibration isolation structure in the sound absorption and vibration isolation base provided by the present invention.

[0048] Figure 7 A schematic diagram of the OPC UA-based software connection provided by the present invention.

[0049] Reference numerals:

[0050] 10. Perforated plate; 101. Perforation; 20. Intermediate base plate; 30. Bottom rib plate; 40. Sound-absorbing structure; 50. Vibration isolation structure; 60. Exhaust hole. DETAILED DESCRIPTION

[0051] To make the objectives, technical solutions, and advantages of the present invention more clear, the technical solutions of the present invention will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the embodiments described are only some of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts shall fall within the scope of protection of the present invention.

[0052] The following combination Figure 1-Figure 7 The present invention provides a sound-absorbing and vibration-isolating base and a design method thereof. Figure 1 As shown, the sound-absorbing and vibration-isolating base includes a perforated plate 101, an intermediate base plate 20, a bottom rib plate 30, and an airbag arranged between the intermediate base plate 20 and the bottom rib plate 30, which are arranged in sequence from top to bottom; the perforated plate 101 and the intermediate base plate 20 cooperate to form a sound-absorbing structure 40, and the intermediate base plate 20, the airbag and the bottom rib plate 30 cooperate to form a vibration-isolating structure 50.

[0053] In this embodiment, the perforated plate 101 is located at the top layer and is provided with a plurality of perforations 101. These perforations 101 allow air circulation and help absorb sound. The material of the perforated plate 101 can be metal, plastic, or other lightweight, high-strength materials to meet specific application scenarios and durability requirements. The intermediate substrate 20 is located below the perforated plate 101 and together with the perforated plate 101 constitutes the sound-absorbing structure 40. The material of the intermediate substrate 20 can be similar to that of the perforated plate 101, or customized as needed to ensure good fit with the perforated plate 101 and the stability of the overall structure. The airbag is arranged between the intermediate substrate 20 and the bottom rib 30 as an important component of the vibration isolation structure 50. The airbag can be made of a flexible material such as rubber, plastic, or other elastic material to provide an effective vibration isolation effect. The shape and size of the airbag can be adjusted as needed to meet specific vibration isolation requirements. The exhaust hole is connected to the airbag to facilitate pressure adjustment. The bottom rib 30 is located at the bottom layer and provides support and stability for the entire base. The structure of the bottom rib 30 can be designed in the form of a reinforcement rib to increase its load-bearing capacity and anti-deformation ability.

[0054] When using this sound-absorbing and vibration-isolating base for sound absorption and vibration isolation, when sound waves reach the perforated plate 101, some of them pass through the perforations 101 and enter the space between the intermediate substrate 20 and the perforated plate 101. In this space, the sound waves undergo multiple reflections and interference, converting them into heat or other forms of energy and dissipating them, achieving a sound-absorbing effect. When the sound-absorbing and vibration-isolating base is subjected to vibration, the airbag absorbs and disperses this vibration energy. The flexibility and elasticity of the airbag effectively reduce vibration transmission, thereby minimizing interference with the surrounding environment and equipment.

[0055] There are two aspects to consider in the design of the sound-absorbing and vibration-isolating base: on the one hand, based on the sound absorption requirement, the sound-absorbing and vibration-isolating base must be optimized as much as possible to improve the sound absorption level of the sound-absorbing structure 40 as much as possible; on the other hand, based on the vibration isolation requirement, the vibration isolation capability of the vibration isolation base must be improved.

[0056] Figure 2 This is one of the flow charts of the design method of the sound-absorbing and vibration-isolating base provided by the present invention, such as Figure 2 As shown, in order to improve the sound absorption level and vibration isolation capability, the design method includes the following steps:

[0057] Step 201: Segment the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag into multiple segments within corresponding threshold ranges.

[0058] Step 202: combining the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag to determine the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations.

[0059] Step 203: Normalize the peak sound absorption coefficients of the sound absorption structure and the total drop in acceleration levels of the vibration isolation structure under different combinations to determine a comprehensive performance evaluation value of the sound absorption and vibration isolation base.

[0060] Step 204: Determine optimal design parameters based on the comprehensive performance evaluation value; the design parameters include the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag.

[0061] After determining the perforated plate's hole diameter, the sound-absorbing structure's thickness, and the airbag's pressure threshold, the system was segmented into multiple sections within the corresponding thresholds. The perforated plate's hole diameter directly affects sound penetration and absorption efficiency. The thickness of the sound-absorbing material affects its absorption performance and structural strength. The airbag's pressure determines its vibration isolation effectiveness and stability.

[0062] In this embodiment, the design parameters are mainly concentrated on the perforation diameter , thickness of sound-absorbing structure , airbag structure thickness , airbag pressure In the specific design process, due to the characteristics of the mechanical equipment it supports and the limitations of the cabin space size, the thickness of the sound-absorbing structure and the thickness of the airbag structure The sum should be a fixed value ,The above design parameters are all set with an adjustable threshold range.

[0063] These parameters are divided into multiple segments within their respective threshold ranges so that they can be combined and tested. For example, the perforation diameter The threshold range of adjustment is [ , ]; Thickness of sound absorbing structure The threshold range of adjustment is [ , ]; Airbag structure thickness The threshold range of adjustment is [ , ]; airbag pressure The threshold range of adjustment is [ , ], each parameter can be evenly divided into multiple small segments within this range.

[0064] The perforation diameter, sound-absorbing structure thickness, and airbag pressure were then permuted and combined to generate a variety of design options. The peak sound absorption coefficient and total acceleration level drop for each combination were normalized to allow for performance comparison on a unified scale. This normalization yielded a comprehensive performance evaluation value, reflecting the overall effectiveness of the sound-absorbing and vibration-isolating base. Finally, based on this comprehensive performance evaluation, the combination with the highest score was selected as the optimal design parameter.

[0065] The design method of the sound-absorbing and vibration-isolating base provided by the present invention automatically adjusts the design parameters of the sound-absorbing and vibration-isolating base based on the coupling of multiple simulation software, and collaboratively characterizes the comprehensive performance of the sound absorption level and vibration isolation capability of the sound-absorbing and vibration-isolating base by normalizing the peak sound absorption coefficient and the total drop of the acceleration level. Based on this, the optimal design parameters of the sound-absorbing and vibration-isolating base are found, and the optimal design of the comprehensive performance of the sound absorption level and vibration isolation capability of the sound-absorbing and vibration-isolating base can be achieved.

[0066] In some embodiments, as Figure 3 As shown, the steps for determining the peak sound absorption coefficient include:

[0067] Step S301: Obtain the perforation diameter of the perforated plate and the thickness of the sound absorbing structure in the current combination.

[0068] Step S302: Determine a sound absorption coefficient curve.

[0069] Step S303: determining the peak sound absorption coefficient in the sound absorption coefficient curve.

[0070] Specifically, the overall sound absorption mechanism of the perforated plate sound absorption structure is resonance sound absorption, that is, during the propagation of sound waves, a pressure difference occurs inside and outside the sound absorption structure. Under the action of the pressure difference, the air column in the micropores rubs against the micropore wall to dissipate the sound wave energy. When the frequency of the incident sound wave is consistent with the structural resonance frequency, the system resonates, at which time the sound wave energy is consumed to the maximum, and the maximum sound absorption coefficient is obtained. Therefore, through COMSOL acoustics software, combined with the perforation diameter of the micro-perforated plate , thickness of sound-absorbing structure , the material properties of the perforated plate sound absorption structure and other characteristic parameters, the sound absorption coefficient curve of the perforated plate sound absorption structure can be calculated (such as Figure 4 As shown in Figure 2), the peak sound absorption coefficient G corresponding to the resonant sound absorption frequency can be obtained. Therefore, the larger the peak sound absorption coefficient G, the stronger the sound absorption performance of the sound-absorbing and vibration-isolating base.

[0071] In some embodiments, as Figure 5 As shown in FIG, the steps for determining the total acceleration level drop include:

[0072] Step S501: Obtain the vibration response of the middle base plate and the bottom rib plate in the current combination.

[0073] Step S502: determining the total drop in acceleration level of the vibration isolation structure based on the minimum and maximum values ​​of the calculated frequency range.

[0074] In this embodiment, referring to the traditional calculation method, the sound absorption and vibration isolation base 、 The total difference in acceleration levels between two points is defined as:

[0075]

[0076] in, 、 They are 、 Two points at a certain frequency The acceleration vibration response at 、 are the minimum and maximum values ​​of the calculated frequency range.

[0077] Secondly, the characteristics of the mechanical equipment supported by the sound-absorbing and vibration-isolating base are analyzed to determine its vibration frequency range as [ 、 ], the center point of the middle base plate (support surface) of the sound absorption and vibration isolation base is ,like Figure 6 As shown, the center point of the bottom rib (support surface) is .

[0078] Finally, the total drop in acceleration level used to characterize the vibration isolation capability of the sound-absorbing and vibration-isolating base is The calculation is as follows:

[0079]

[0080] in, 、 They are the center points of the middle substrate (support surface) of the sound absorption and vibration isolation base , center point of bottom rib (support surface) At a certain frequency The acceleration vibration response at 、 It is the minimum and maximum value of the vibration frequency range of the mechanical equipment supported by the sound-absorbing and vibration-isolating base.

[0081] Therefore, in the embodiment of the present invention, the peak sound absorption coefficient G of the sound absorption and vibration isolation base is used to represent the sound absorption level, and the total drop of the acceleration level is used to represent the total drop of the acceleration level. Characterizes the vibration isolation capability. The larger the peak sound absorption coefficient G of the sound-absorbing and vibration-isolating base, the better. The total drop of the acceleration level The bigger the better.

[0082] In a specific embodiment, the step of dividing the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag into multiple segments within the corresponding threshold range includes: the range of adjusting the perforation diameter e of the perforated plate is [ , ], the perforation diameter e of the perforated plate is divided into n+1 segments, which are , , ,…, ;Thickness of the sound-absorbing structure The threshold range of adjustment is [ , ]; the thickness of the sound absorbing structure Divided into n+1 segments, respectively , , ,…, ; Airbag pressure The threshold range of adjustment is [ , ], the pressure of the airbag Divided into n+1 segments, respectively , , ,…, .

[0083] For example, the design parameters of the sound absorption and vibration isolation base are mainly concentrated on the perforation diameter , thickness of sound-absorbing structure , airbag structure thickness , airbag pressure , perforation diameter The threshold range of adjustment is [ , ]; Thickness of sound absorbing structure The threshold range of adjustment is [ , ]; Airbag structure thickness The threshold range of adjustment is [ , ]; airbag pressure The threshold range of adjustment is [ , Due to the characteristics of the mechanical equipment it supports and the limitations of the cabin space size, the thickness of the sound-absorbing structure and the thickness of the airbag structure The sum should be a fixed value Therefore, the thickness of the sound absorbing structure After confirmation, the thickness of the airbag structure Automatically determined.

[0084] Divide the threshold range into n segments (n is a positive integer) and adjust the perforation diameter in steps , thickness of sound-absorbing structure , airbag pressure :

[0085] Perforation diameter e, including , , ,…, ;

[0086] Sound absorbing structure thickness a, including , , ,…, ;

[0087] Airbag pressure P, including , , ,…, .

[0088] Optional, in perforation diameter , thickness of sound-absorbing structure , airbag pressure Multiple candidate values ​​are selected within the value range of . The specific selection method can also use a geometric ratio to determine the candidate values, or randomly generate a certain number of candidate values ​​within the corresponding range. The specific selection method is not limited.

[0089] The above three design parameters can be combined arbitrarily, and each design parameter has There are a total of The above combination methods are stored in MATLAB software, and each combination of design parameters is transmitted to COMSOL software through the software interface based on OPC UA. The specific connection method is shown in Figure 7 Under each combination of design parameters, the basic conditions of the sound-absorbing and vibration-isolating base and the mechanical equipment it supports (such as the material properties of the sound-absorbing and vibration-isolating base, the vibration frequency range of the mechanical equipment it supports, etc.) are input, and the peak sound absorption coefficient G of the sound-absorbing and vibration-isolating base and the total drop in acceleration level are automatically calculated by COMSOL software. , and is transferred back to the MATLAB software through the software interface and stored. Design parameter combinations, corresponding to The total difference between the peak sound absorption coefficient G and the acceleration level .

[0090] It should be noted that OPC UA (Object Linking and Embedding for Process Control, Unified Architecture) is an industrial communication data interaction specification and architecture that provides a unified standard interface for different applications, devices, drivers, and software. It is independent of hardware manufacturers and software developers and can solve cross-platform, real-time, security, and integration issues of communication systems.

[0091] In some embodiments, the step of normalizing the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations to determine the comprehensive performance evaluation value of the sound absorbing and vibration isolation base includes: The peak sound absorption coefficient of each sound-absorbing structure is normalized to obtain the evaluation value of the sound absorption level ;right The total difference in acceleration level of the vibration isolation structure is normalized to obtain the evaluation value of the vibration isolation capability. ; Evaluation value based on sound absorption level and the estimated value of vibration isolation capability , determine the comprehensive performance evaluation value of the sound absorption and vibration isolation base .

[0092] Since the design of the sound absorption and vibration isolation base needs to consider the dual performance of sound absorption level and vibration isolation ability at the same time, the present invention calculates the peak sound absorption coefficient G and the total drop of acceleration level by Normalization processing is performed to collaboratively characterize the comprehensive performance of the sound absorption and vibration isolation base. The specific method is as follows:

[0093] First, for Design parameter combinations, corresponding to The total difference between the peak sound absorption coefficient G and the acceleration level For the sound-absorbing and vibration-isolating base, the larger the peak sound absorption coefficient G of the vibration-isolating base, the better. Bigger is better;

[0094] Then, respectively The total difference between the peak sound absorption coefficient G and the acceleration level Normalization is performed as follows:

[0095]

[0096]

[0097] in, , and They are The minimum and maximum values ​​of the peak sound absorption coefficient G, and They are Total difference in acceleration level The minimum and maximum values ​​of .

[0098] Finally, the comprehensive performance evaluation value of the sound absorption level and vibration isolation capability of the sound absorption and vibration isolation base It can be characterized as:

[0099]

[0100] in, ; ,and . It can be flexibly adjusted according to the specific requirements of the sound absorption and vibration isolation base for the sound absorption level and vibration isolation capacity design.

[0101] In MATLAB software, for The design parameter combinations are calculated respectively. The corresponding comprehensive performance evaluation value .Pick The maximum value of the design parameter combination is the optimal combination, which can achieve the optimal design of the comprehensive performance of the sound absorption level and vibration isolation capability of the sound absorption and vibration isolation base.

[0102] The embodiment of the present invention further provides a sound-absorbing and vibration-isolating base, which is manufactured using the above-mentioned design method. Figure 1 As shown, the sound-absorbing and vibration-isolating base includes a perforated plate 101, an intermediate base plate 20, a bottom rib plate 30, and an airbag arranged between the intermediate base plate 20 and the bottom rib plate 30, which are arranged in sequence from top to bottom; the perforated plate 101 and the intermediate base plate 20 cooperate to form a sound-absorbing structure 40, and the intermediate base plate 20, the airbag and the bottom rib plate 30 cooperate to form a vibration-isolating structure 50.

[0103] In this embodiment, the perforated plate 101 is located at the top layer and is provided with a plurality of perforations 101. These perforations 101 allow air circulation and help absorb sound. The material of the perforated plate 101 can be metal, plastic, or other lightweight, high-strength materials to meet specific application scenarios and durability requirements. The intermediate substrate 20 is located below the perforated plate 101 and together with the perforated plate 101 constitutes the sound-absorbing structure 40. The material of the intermediate substrate 20 can be similar to that of the perforated plate 101, or customized as needed to ensure good fit with the perforated plate 101 and the stability of the overall structure. The airbag is arranged between the intermediate substrate 20 and the bottom rib 30 as an important component of the vibration isolation structure 50. The airbag can be made of a flexible material such as rubber, plastic, or other elastic material to provide an effective vibration isolation effect. The shape and size of the airbag can be adjusted as needed to meet specific vibration isolation requirements. The exhaust hole is connected to the airbag to facilitate pressure adjustment. The bottom rib 30 is located at the bottom layer and provides support and stability for the entire base. The structure of the bottom rib 30 can be designed in the form of a reinforcement rib to increase its load-bearing capacity and anti-deformation ability.

[0104] When using this sound-absorbing and vibration-isolating base for sound absorption and vibration isolation, when sound waves reach the perforated plate 101, some of them pass through the perforations 101 and enter the space between the intermediate substrate 20 and the perforated plate 101. In this space, the sound waves undergo multiple reflections and interference, converting them into heat or other forms of energy and dissipating them, achieving a sound-absorbing effect. When the sound-absorbing and vibration-isolating base is subjected to vibration, the airbag absorbs and disperses this vibration energy. The flexibility and elasticity of the airbag effectively reduce vibration transmission, thereby minimizing interference with the surrounding environment and equipment.

[0105] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims

1. A design method for a sound-absorbing and vibration-isolating base, characterized in that: The sound absorption and vibration isolation base includes: a perforated plate, an intermediate base plate, a bottom rib plate, and an air bag arranged between the intermediate base plate and the bottom rib plate, which are arranged in sequence from top to bottom; the perforated plate and the intermediate base plate cooperate to form a sound absorption structure, and the intermediate base plate, the air bag, and the bottom rib plate cooperate to form a vibration isolation structure; The design method of the sound absorption and vibration isolation base includes: dividing the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag into multiple segments within corresponding threshold ranges; Combining the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag to determine the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations; Normalizing the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations to determine the comprehensive performance evaluation value of the sound absorbing and vibration isolation base; According to the comprehensive performance evaluation value, optimal design parameters are determined; the design parameters include the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag.

2. The design method of the sound absorption and vibration isolation base according to claim 1, characterized in that: The step of determining the peak sound absorption coefficient comprises: Obtaining the perforation diameter of the perforated plate and the thickness of the sound absorbing structure in the current combination; Determine the sound absorption coefficient curve; The peak sound absorption coefficient in the sound absorption coefficient curve is determined.

3. The design method of the sound absorption and vibration isolation base according to claim 1, characterized in that: The step of determining the total acceleration level drop comprises: Obtaining vibration responses of the intermediate base plate and the bottom rib plate in the current combination; The total drop in acceleration level of the vibration isolation structure is determined based on the minimum and maximum values ​​of the calculated frequency range.

4. The design method of the sound absorption and vibration isolation base according to claim 3 is characterized in that: The total drop in acceleration level is ; in, is the vibration response of the intermediate substrate, is the vibration response of the bottom rib, 、 It is the minimum and maximum value of the vibration frequency range of the mechanical equipment supported by the sound-absorbing and vibration-isolating base.

5. The design method of the sound absorption and vibration isolation base according to claim 1 is characterized in that: The step of dividing the perforation diameter of the perforated plate, the thickness of the sound absorbing structure, and the pressure of the airbag into multiple segments within corresponding threshold ranges includes: The range of adjustment of the perforation diameter e of the perforated plate is [ , ], the perforation diameter e of the perforated plate is divided into n+1 segments, which are , , ,…, ; The thickness of the sound absorbing structure The threshold range of adjustment is [ , ]; the thickness of the sound absorbing structure Divided into n+1 segments, respectively , , ,…, ; The pressure of the airbag The threshold range of adjustment is [ , ], the pressure of the airbag Divided into n+1 segments, respectively , , ,…, .

6. The design method of the sound absorption and vibration isolation base according to claim 5, characterized in that: The step of determining the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations includes: For sound absorption and vibration isolation base Design parameter combinations to generate The peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure.

7. The design method of the sound absorption and vibration isolation base according to claim 6, characterized in that: The steps of normalizing the peak sound absorption coefficient of the sound absorbing structure and the total drop of the acceleration level of the vibration isolation structure under different combinations to determine the comprehensive performance evaluation value of the sound absorbing and vibration isolation base include: right The peak sound absorption coefficient of the sound absorption structure is normalized to obtain the evaluation value of the sound absorption level. ; right The total difference in acceleration level of the vibration isolation structure is normalized to obtain the evaluation value of the vibration isolation capability. ; Evaluation value based on sound absorption level and the estimated value of vibration isolation capability , determine the comprehensive performance evaluation value of the sound absorption and vibration isolation base .

8. The design method of the sound absorption and vibration isolation base according to claim 7, characterized in that: ; ; in, , and They are The minimum and maximum values ​​of the peak sound absorption coefficient G, and They are Total difference in acceleration level The minimum and maximum values ​​of .

9. The design method of the sound absorption and vibration isolation base according to claim 8, characterized in that: ; in, ; ,and .

10. A sound-absorbing and vibration-isolating base, characterized in that: The sound-absorbing and vibration-isolating base is manufactured by the design method according to any one of claims 1 to 9.

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