Design method of vibration platform for large hydraulic vibration system and vibration platform thereof

Abstract

The invention discloses a design method of a vibration platform for a large hydraulic vibration system and the vibration platform, and the method comprises the steps: determining the size, bearing capacity and exciting force of the platform according to the use demands, building a three-dimensional finite element model, and carrying out the modal, stress and buckling analysis; and through multi-round optimization, it is ensured that the first-order inherent frequency is larger than the multiple maximum use frequency, the structural stress is lower than the allowable stress of materials, and the buckling stability meets the safety requirement. The finally designed platform is of a space rigid structure formed by welding the top plate, the parallel rib plates, the inclined rib plates, the surrounding plates and the sealing plates and has high rigidity, low mass and excellent multi-direction bearing capacity, 121 threaded holes are formed in the top plate so that a sample can be conveniently installed, weight reduction holes are formed in the second rib plates, the dynamic response efficiency and adaptability are effectively improved, and the stability of the platform is improved. The device is suitable for high-load and high-frequency hydraulic vibration test scenes.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of structural vibration testing and hydraulic servo control, and particularly relates to a design method of a vibration platform for a large hydraulic vibration system and the vibration platform. BACKGROUND

[0002] The vibration platform is an important component of the hydraulic vibration system, is the main bearing structure for installing the test sample, and is also the direct object of the excitation force of the actuator. During the vibration test, the vibration platform not only bears the static load, but also needs to bear the high-frequency and large-amplitude dynamic excitation, so the structural performance of the vibration platform has a decisive influence on the overall operation stability of the vibration system and the reliability of the test data.

[0003] The design of the vibration platform usually needs to consider multiple key parameters, including the natural frequency, the structural stiffness, and the overall mass. Among them, the natural frequency needs to be far away from the system excitation frequency to avoid resonance; the structural stiffness needs to ensure the overall stability and local deformation control of the platform under excitation conditions; and the structural weight directly affects the response efficiency and energy consumption of the vibration table, which is an optimization target that needs to be considered. Therefore, how to maintain high stiffness and high modal performance while realizing the mass control of the platform structure is a key technical problem in the design of the vibration table.

[0004] Some related technical solutions have been applied in engineering. For example, the patent application with the publication number CN217878260U discloses a horizontal hydraulic vibration table, which uses an excitation assembly to apply force from the center of the platform bottom and controls the guidance through a sliding assembly, realizes the transmission of vibration from the center to the periphery, improves the force uniformity and response consistency of the table surface, and thus improves the precision of the vibration test. CN102141110A discloses a hydraulic vibration active isolation platform, which combines two-degree-of-freedom and three-degree-of-freedom Hooke's joints and a pre-tightening gap elimination structure, realizes high-precision six-degree-of-freedom vibration isolation, and is mainly used for vibration environment control of shipborne or vehicle-mounted photoelectric systems.

[0005] Although the above-mentioned technologies have achieved certain results in the design of small and medium load vibration platforms, the load capacity of most current hydraulic vibration platforms is still concentrated in the tens of tons, and there are still few public technologies and documents for the design of vibration table platforms with load capacity exceeding one hundred tons. The vibration platform exceeding one hundred tons not only needs to bear large-amplitude excitation force and three-axis coupling working conditions, but also faces higher requirements for structural modal performance and weight optimization.

[0006] In view of the above problems, the present application is proposed. SUMMARY

[0007] The application discloses a design method of a vibration platform for a large hydraulic vibration system and the vibration platform thereof, and aims to solve the technical problems in the prior art.

[0008] In order to achieve the above-mentioned purpose, according to one aspect of the application, a design method of a vibration platform for a large hydraulic vibration system comprises the following steps:

[0009] According to the use requirement, the maximum size, the maximum carrying weight of the vibration platform and the maximum exciting force of the actuator are determined, and the structural design drawing is preliminarily set;

[0010] Based on the structural design drawing, a three-dimensional finite element analysis model is established, modal performance simulation is carried out, and mode shape information of the first three order natural frequencies of the vibration platform is obtained; the first order natural frequency is obtained according to the following formula:

[0011]

[0012] Wherein,

[0013] f1: the first order natural frequency;

[0014] E: the elastic modulus;

[0015] ρ: the material density;

[0016] v: the Poisson's ratio;

[0017] coefficient;

[0018] h: the height of the vibration platform;

[0019] If the first order natural frequency is greater than times the maximum use frequency, the safety margin requirement is met, and the next step is entered; if not, the structural design drawing is returned to adjust;

[0020] According to the design working condition, the maximum acceleration of the vibration platform output in X / Y / Z three directions is set, the connection position of the vibration platform and the actuator is selected as the maximum excitation point, a load is applied for finite element stress analysis, the maximum stress and the maximum displacement of the vibration platform are calculated, and the maximum stress and the maximum displacement are compared with the allowable stress of the vibration platform material: if the stress level meets the requirement, the next step is entered; if not, the structural design drawing is returned to adjust;

[0021] The maximum exciting force of a single actuator is used as the limit load, buckling analysis is carried out on X / Y / Z three directions respectively, the buckling load limit of the vibration platform structure is determined, and whether there is a local buckling risk under the use load is judged: if the buckling stability requirement is met, the next step is entered; if not, the structural design drawing is returned to adjust;

[0022] When the vibration platform passes through the first three natural frequencies, stress and buckling analysis, the final structure design scheme is determined.

[0023] As a preferred technical solution, the buckling load limit is obtained by using the following formula for calculation:

[0024]

[0025]

[0026] Wherein,

[0027] k: buckling coefficient;

[0028] E: elastic modulus;

[0029] ν: Poisson's ratio;

[0030] h: the height of the vibration platform;

[0031] D: bending stiffness;

[0032] b: the width of the vibration platform;

[0033] N cr : unit length critical buckling load.

[0034] As a preferred technical solution, the buckling stability requirement is that the total buckling force P cr The ratio of the input force P is greater than 2.

[0035] As a preferred technical solution, the total buckling force P cr It is obtained by calculating according to the following formula:

[0036] P cr =N cr ×b

[0037] Wherein,

[0038] N cr : unit length critical buckling load;

[0039] b: the width of the vibration platform.

[0040] As a preferred technical solution, when the vibration platform passes through the natural frequency, stress and buckling analysis, the vibration platform is also subjected to mass optimization design.

[0041] As a preferred technical solution, The maximum use frequency is 84.8Hz.

[0042] As another aspect of the present application, a vibration platform designed by the above design method is also provided, comprising a top plate, a plurality of first rib plates, a plurality of second rib plates, a plurality of surrounding plates and a sealing plate.

[0043] A plurality of threaded holes are formed in the top plate for mounting the sample;

[0044] A plurality of first rib plates are vertically arranged below the top plate and parallel to each other;

[0045] A plurality of second rib plates are arranged in a staggered manner to connect the plurality of first rib plates to form a spatially staggered rigid structure;

[0046] A plurality of surrounding plates are arranged vertically around the top plate;

[0047] The sealing plate is integrally formed with the top plate, the plurality of first rib plates, the plurality of second rib plates and the plurality of surrounding plates by welding.

[0048] As a preferred technical solution, the number of threaded holes is 121, evenly distributed in rows, and the diameter of the threaded holes is 20mm.

[0049] As a preferred technical solution, the plurality of second rib plates are connected to the plurality of first rib plates by welding.

[0050] As a preferred technical solution, the plurality of second rib plates are provided with weight-reducing holes.

[0051] The technical solution adopted by the present application can at least achieve one of the following beneficial effects:

[0052] 1. The present application uses a design method based on modal analysis to ensure that the first order natural frequency of the vibration platform is greater than √2 times the maximum use frequency, avoiding resonance phenomenon due to close working frequency to natural frequency, effectively improving the dynamic stability and safety margin of the platform under high frequency excitation working condition.

[0053] 2. The present application uses multi-directional finite element stress analysis and buckling analysis to ensure that the stress level of the platform under the action of the maximum excitation force is lower than the allowable stress of the material, and meets the buckling stability requirement (P cr / P>2), effectively preventing local buckling or overall instability, and ensuring long-term stable operation of the platform.

[0054] 3. The present application adopts spatially staggered rigid structure and rib plate welding integrated design, which improves the overall stiffness and carrying capacity, reduces the self-weight of the platform by setting weight-reducing holes, reduces energy consumption and cost. In addition, the 121 evenly arranged threaded holes on the top plate facilitate the quick installation and replacement of multiple types of samples, enhancing the versatility and adaptability of the platform.

[0055] 4. The vibration platform provided by the application forms a multi-directional force bearing integrated rigid frame structure through the space structure between the top plate, the first rib plate, the second rib plate, the surrounding plate and the sealing plate, has high overall rigidity and excellent bending resistance, can effectively bear the periodic excitation load of the large hydraulic vibration system in X / Y / Z three directions, and ensures that the platform maintains structural stability and response consistency under high load and high frequency vibration working conditions.

[0056] 5. The application connects the plurality of first rib plates through the plurality of second rib plates arranged in a diagonal staggered manner to form a spatial diagonal strengthening structure, further improves the modal performance of the platform, and realizes local lightweight design by providing weight reduction holes on the second rib plate, thereby effectively reducing the structural mass and improving the overall response efficiency and energy utilization rate of the vibration table under the premise that the natural frequency of the platform is higher than times the maximum use frequency. BRIEF DESCRIPTION OF DRAWINGS

[0057] In order to more clearly illustrate the technical solutions of the embodiments of the application, the drawings needed to be used in the embodiment description will be briefly introduced as follows, which constitutes a part of the application. The illustrative embodiments of the application and the description and explanation thereof do not constitute an improper limitation on the application. In the drawings:

[0058] Figure 1 It is a top plate structure schematic diagram of a vibration platform for a large hydraulic vibration system of the application;

[0059] Figure 2 It is an internal structure schematic diagram of a vibration platform for a large hydraulic vibration system of the application;

[0060] Figure 3 It is a sealing plate structure schematic diagram of a vibration platform for a large hydraulic vibration system of the application;

[0061] Figure 4 It is a flowchart schematic diagram of a design method of a vibration platform for a large hydraulic vibration system of the application;

[0062] Figure 5 It is a first-order vibration mode torsional mode schematic diagram of a vibration platform of the application;

[0063] Figure 6 It is a second-order vibration mode bending mode schematic diagram of a vibration platform of the application;

[0064] Figure 7 It is a second-order vibration mode bending mode schematic diagram of a vibration platform of the application.

[0065] Explanation of reference signs:

[0066] 1. top plate; 2. threaded hole; 3. first rib plate; 4. second rib plate; 5. surrounding plate; 6. sealing plate. DETAILED DESCRIPTION

[0067] In order to make the objects, technical solutions and advantages of the present application clearer, the technical solutions of the present application will be described below in connection with specific embodiments of the present application and corresponding drawings. In the description of the present application, it should be noted that the term "or" is generally used in the sense of including "and / or" unless the context clearly indicates otherwise.

[0068] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connecting" should be understood broadly, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be mechanical connection, or magnetic connection; it can be directly connected, or indirectly connected through an intermediate medium, or the internal communication of two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances. In addition, in the description of the present application, the terms "first", "second" and the like are only used to distinguish the description and cannot be understood as indicating or implying relative importance.

[0069] Obviously, the described embodiments are only a part of the embodiments of the present application, not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the present application.

[0070] First, in order to facilitate the understanding of the embodiments of the present application, the following will explain and describe some terms or nouns involved in the present application:

[0071] Actuator refers to an execution mechanism that converts input control signals (such as hydraulic pressure, electrical signals or pneumatic signals) into mechanical displacement or force output. In a hydraulic vibration system, the actuator is usually a hydraulic drive device for applying a periodic excitation force to a vibration platform to realize linear vibration or compound vibration in X, Y and Z directions;

[0072] Natural frequency is the natural vibration frequency exhibited when free vibration without external excitation, which is usually determined by its mass distribution and stiffness characteristics;

[0073] First-order natural frequency usually corresponds to the vertical vibration of the overall rigid body of the vibration platform or the lowest-order overall flexural mode;

[0074] Second-order natural frequency usually corresponds to the overall vibration in the horizontal direction or the local bending mode of the main rib plate;

[0075] The third natural frequency may correspond to in-plane shear vibration of the vibration platform or the coupled vibration mode of the stiffening rib and the top plate.

[0076] To address the problems existing in the prior art, embodiments of the present invention provide a vibration platform for large hydraulic vibration systems, such as... Figures 1-3 As shown, the system includes a top plate 1, a first stiffening plate 3, a second stiffening plate 4, a surrounding plate 5, and a sealing plate 6. The top plate 1 serves as the working surface of the vibration platform, bearing the specimens and connecting them to specimens of different sizes. It also bears and transmits the vertical and horizontal loads introduced by the specimens, acting as the load input surface and connection interface of the entire vibration platform. The first stiffening plate 3, as the platform's height-direction support component, is the main stiffening plate, vertically positioned below the top plate 1. It bears and transmits the main loads of the platform under vertical excitation conditions, forming the core framework for achieving vertical stiffness and bending strength. The second stiffening plate 4 serves as a reinforcing stiffening plate, used to reinforce the first stiffening plate. The plates 3 are interconnected to form a spatial oblique rigid structure, which enhances the overall shear stiffness and lateral stability of the vibration platform. The surrounding plate 5 is used to form a closed rigid frame around the platform, serving as the connection interface with the horizontal actuator and bearing and transmitting the horizontal excitation force. The sealing plate 6 is set at the bottom of the vibration platform and is welded to the first stiffening plate 3, the second stiffening plate 4 and the surrounding plate 5 to form an integral structure. It serves as the direct connection interface with the vertical actuator, bearing the weight of the vibration platform and the sample and the vertical excitation force, enhancing the compressive and buckling resistance of the bottom of the vibration platform, and is the main force-bearing surface for the vibration platform to achieve vertical stable force transmission.

[0077] like Figure 1 As shown, the top plate 1 is made of integrally machined steel plate to balance high rigidity with flexible sample connection arrangement, avoiding problems such as limited connection, uneven load, or stress concentration. Preferably, the top plate 1 is made of Q345B alloy steel. More preferably, the top plate 1 has dimensions of 3.5m × 6m. To increase the versatility of sample installation and the stability of rigid connections, the top plate 1 has multiple threaded holes 2. To meet diverse experimental needs while ensuring the overall continuity and rigidity of the working surface structure, preferably, the top plate 1 has 11 rows of threaded holes 2 with a diameter of 20mm each along both the length and width directions.

[0078] like Figure 2To avoid the problem that the vibration platform is prone to deflection and insufficient rigidity under vertical excitation, a plurality of first rib plates 3 are arranged below the top plate 1 of the platform, and the plurality of first rib plates 3 are arranged in parallel. The first rib plates 3 are arranged vertically and are fixedly connected to the top plate 1 by welding to form a framework of the platform in the height direction and play a role in bearing and conducting vertical load. This design effectively enhances the overall bending resistance of the platform under vertical excitation and improves the structural stability. Preferably, the number of first rib plates 3 is 3-5. To solve the problem of local weak area between the first rib plates 3 and the corresponding frequency of the vibration platform mode, the vibration platform further comprises a plurality of second rib plates 4 arranged in a diagonal staggered manner, and the second rib plates 4 are connected to the first rib plates 3 by welding to form a diagonal cross rigid support structure. To reduce the weight of the vibration platform and improve the modal performance, the second rib plates 4 are provided with weight reduction holes after structural optimization. This arrangement not only improves the overall structural rigidity and first-order modal frequency of the vibration platform, but also effectively reduces the platform quality, so as to meet the design requirement that the first-order natural frequency is higher than times the maximum use frequency to avoid excitation resonance instability. As shown in Figure 2 , the vibration platform further comprises a plurality of surrounding plates 5, and the plurality of surrounding plates 5 are arranged vertically on the periphery of the top plate 1 and are integrally formed with the top plate 1, the first rib plates 3 and the second rib plates 4 by welding. As shown in Figure 2 and Figure 3 , the surrounding plates 5 are used to connect the horizontal actuators and are key stress components for transmitting horizontal excitation force. After the structure is strengthened, the overall bending rigidity and thrust transmission efficiency of the platform in the horizontal direction can be significantly improved to avoid structural side shift, mismatch and other phenomena and ensure the stability of excitation response.

[0079] As shown in Figure 3 , the vibration platform further comprises a sealing plate 6 as a bottom plate of the vibration platform, and the sealing plate 6 is welded with the surrounding plates 5, the first rib plates 3 and the second rib plates 4 to form an overall structure to avoid unreasonable design and easy buckling or fracture. The sealing plate 6 provides a rigid connection interface for the vertical actuators, bears the dead weight and vertical excitation force, disperses the load concentration effect, effectively suppresses the deformation of the bottom structure and improves the overall buckling stability.

[0080] The embodiment of the application also provides a design method of the vibration platform.

[0081] Step S1: structural design;

[0082] According to the use requirement of the vibration platform, the maximum size, the maximum bearing weight and the maximum excitation force of the actuator of the vibration platform are determined, the geometric size and arrangement scheme of the top plate 1, the first rib plate 3, the second rib plate 4, the surrounding plate 5 and the sealing plate 6 are preliminarily set, and an overall structural design drawing is formed;

[0083] Step S2: frequency analysis;

[0084] Based on the above structural design diagram, a three-dimensional finite element analysis model is established to simulate the modal performance of the vibration platform to obtain the mode shape information of the first three orders of the natural frequency of the vibration platform; the first order natural frequency obtained by analysis is compared with times the maximum use frequency, wherein the maximum use frequency is 60Hz, i.e. times the maximum use frequency is 84.8Hz, and the safety margin requirement is that the first order natural frequency should be greater than times the maximum use frequency;

[0085] The first order natural frequency is calculated according to the following formula:

[0086]

[0087] wherein,

[0088] f1: the first order natural frequency;

[0089] E: elastic modulus;

[0090] p: material density;

[0091] v: Poisson's ratio;

[0092] a: coefficient;

[0093] h: the height of the vibration platform;

[0094] If the safety margin requirement is met, i.e. f1>84.8Hz, then the next step is entered, preferably the height of the vibration platform is 0.6m, E=210GPa=210x10 9 Pa, p=7850kg / m 3 , v=0.3, and the calculated f1 is 128.07Hz, which is greater than 84.8Hz, meeting the safety margin requirement, and the first three order modal shapes are as shown in Figures 5-7 ;

[0095] If not, return to the structure design stage for adjustment;

[0096] Step S3: stress analysis;

[0097] According to the design working condition of the vibration platform, the maximum acceleration of the vibration platform output in X / Y / Z three directions is set, the connection position of the vibration platform and the actuator is selected as the maximum excitation point, the load is applied for finite element stress analysis, the maximum stress and maximum displacement of the vibration platform are calculated, and compared with the allowable stress of the vibration platform material, if the stress level meets the requirement, then the next step is entered;

[0098] If not, return to the structure design stage to adjust the structure;

[0099] Step S4: buckling analysis;

[0100] The maximum exciting force of a single actuator is taken as the limit load, and the X / Y / Z three directions are subjected to buckling analysis respectively to determine the buckling load limit of the vibration platform structure, and to judge whether there is a local buckling risk under the use load. The safety factor P cr / P>2(P cr is the total buckling force, P is the input force), that is, it is considered that buckling will not occur, there is no buckling risk, and the buckling stability requirement is met;

[0101] The buckling load limit, that is, the critical buckling load per unit length, is calculated according to the following formula when the rectangular thin plate is compressed in the plane:

[0102]

[0103] P cr =N cr ×b

[0104] Wherein,

[0105] k: buckling coefficient;

[0106] E: elastic modulus;

[0107] v: Poisson's ratio;

[0108] h: vibration platform height;

[0109] D: bending stiffness;

[0110] b: vibration platform width;

[0111] N cr : critical buckling load per unit length;

[0112] P cr : total buckling force;

[0113] If the buckling stability requirement is met, the next step is entered, preferably, the input force P adopts 800kN, under the condition of one-way compression, k takes 4, and D is calculated to be about 4.15×10 9 Nm, N cr is about 13370kN / m, P cr is about 46795kN, the safety factor P cr / P is equal to 58.5, which is greater than 2, and the buckling stability requirement is met;

[0114] If not, return to the structure design stage to optimize the first rib plate 3, the second rib plate 4 or the sealing plate 6 structure;

[0115] Step S5: mass optimization;

[0116] Under the premise that the modal performance, strength and buckling safety all meet the use requirements, further quality optimization design is performed on the vibration platform structure, including the optimization of the shape, arrangement mode and wall thickness size of the weight-reducing holes of the second rib plate 4, so as to reduce the overall quality of the vibration platform while ensuring that the key performance indicators are not weakened;

[0117] Step S6: design finalization;

[0118] When the vibration platform is verified through frequency analysis, stress analysis and buckling analysis and the quality optimization is completed, the final structure scheme is determined as the design finalization result of the vibration platform.

[0119] The embodiments of the present application are described above in combination with the drawings, but the present application is not limited to the above specific embodiments, and the above specific embodiments are only illustrative but not restrictive, and those skilled in the art can make many forms under the inspiration of the present application without departing from the purpose of the present application and the scope protected by the claims, which all belong to the protection of the present application.

Claims

1. A design method for a vibration platform for a large hydraulic vibration system, characterized in that, Includes the following steps: Based on the usage requirements, determine the maximum size, maximum load capacity, and maximum excitation force of the actuator of the vibration platform, and initially set the structural design drawings; Based on the structural design drawing, a three-dimensional finite element analysis model is established, and modal performance simulation is performed to obtain the mode shape information of the first three natural frequencies of the vibration platform; the first natural frequency is obtained according to the following formula: in, f1: First natural frequency; E: Elastic modulus; ρ: Material density; v: Poisson's ratio; a: coefficient; h: Height of the vibration platform; If the first natural frequency is greater than the If the maximum operating frequency is doubled, the safety margin requirement is met, and proceed to the next step; otherwise, return to adjust the structural design drawing. Based on the design conditions, the maximum acceleration output by the vibration platform in the X / Y / Z directions is set simultaneously. The connection point between the vibration platform and the actuator is selected as the maximum excitation point. A load is applied and finite element stress analysis is performed to calculate the maximum stress and maximum displacement of the vibration platform. The results are then compared with the allowable stress of the vibration platform material. If the stress level meets the requirements, proceed to the next step; otherwise, return to adjust the structural design drawing. Using the maximum excitation force of a single actuator as the ultimate load, buckling analysis is performed in the X, Y, and Z directions to determine the buckling load limit of the vibration platform structure and to determine whether there is a risk of local buckling under the service load. If the buckling stability requirements are met, proceed to the next step; if not, return to adjust the structural design drawings. After the vibration platform has passed the first three natural frequencies, stress and buckling analyses, the final structural design scheme is determined.

2. The design method according to claim 1, characterized in that, The buckling load limit is calculated using the following formula: in, k: buckling coefficient; E: Elastic modulus; v: Poisson's ratio; h: Height of the vibration platform; D: Bending stiffness; b: Width of the vibration platform; N cr Critical buckling load per unit length.

3. The design method according to claim 1, characterized in that, The buckling stability requirement is the total buckling force P. cr The ratio of the input force P to the input force P is greater than 2.

4. The design method according to claim 3, characterized in that, The total buckling force P cr The following formula is used for calculation: P cr =N cr ×b in, N cr Critical buckling load per unit length; b: Width of the vibration platform.

5. The design method according to claim 1, characterized in that, After the vibration platform passes the natural frequency, stress, and buckling analysis, the process also includes a quality optimization design for the vibration platform.

6. The design method according to claim 1, characterized in that, The The maximum operating frequency is 84.8Hz.

7. A vibration platform designed based on the design method according to any one of claims 1 to 6, characterized in that, It includes a top slab, multiple first stiffening slabs, multiple second stiffening slabs, multiple surrounding slabs, and a sealing slab; The top plate has multiple threaded holes for sample installation; The plurality of first stiffening plates are vertically arranged below the top plate and are parallel to each other; The plurality of second stiffening plates are arranged obliquely and intersectingly to connect the plurality of first stiffening plates to form a spatial oblique rigid structure; The plurality of enclosure panels are arranged vertically around the periphery of the top plate; The sealing plate serves as the base plate of the vibration platform and is integrally formed by welding with the top plate, multiple first stiffening plates, multiple second stiffening plates, and multiple surrounding plates.

8. The vibration platform according to claim 7, characterized in that, The number of threaded holes is 121, which are evenly distributed in a row, and the diameter of the threaded holes is 20mm.

9. The vibration platform according to claim 7, characterized in that, The plurality of second stiffening plates are connected to the plurality of first stiffening plates by welding.

10. The vibration platform according to claim 7, characterized in that, The multiple second stiffeners are provided with weight-reducing holes.

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