Large-stroke hydraulic vibration horizontal test bench

Abstract

The invention discloses a large-stroke hydraulic vibration horizontal test bed, which is used for solving the problems of interference, abrasion and easy fatigue fracture of a force transmission component caused by a centering error between a large-stroke hydraulic vibration exciter and a horizontal table board. The test bed comprises a base, a hydraulic vibration exciter, a horizontal table top and a spring plate assembly connecting the base and the hydraulic vibration exciter. A function decoupling design is adopted, wherein a guide rail compensation block with horizontal transverse elasticity is arranged in a guide mechanism between a horizontal table top and a base and is specially used for dynamically compensating centering errors in the horizontal direction; meanwhile, the spring plate assembly is constructed to be composed of multiple layers of stacked spring plates parallel to the horizontal table top, centering errors in the vertical direction are dynamically compensated through bending flexibility of the spring plates in the vertical plane, the working stress is greatly reduced through the multi-layer structure, and the fatigue life is prolonged. By means of the design, unification of high-rigidity excitation force transmission and multi-dimensional dynamic error compensation is achieved, the reliability and precision of equipment are remarkably improved, and the service life of the equipment is remarkably prolonged.

Description

Technical Field

[0001] This invention relates to the field of mechanical environment testing, and in particular to a hydraulic vibration test bench with large load capacity, large thrust, and large stroke. Background Technology

[0002] A hydraulic vibration level test bench is a reliability testing device that uses a hydraulic system as its power core to simulate various vibration environments in the horizontal direction. Its core function is to reproduce the horizontal vibrations and impacts encountered by products during actual transportation and operation, testing the product's structural strength, component stability, and vibration resistance reliability. It is mainly used to meet the testing needs of heavy-duty, high-load, and high-amplitude applications. The hydraulic vibration level test bench mainly consists of a hydraulic vibrator, a base, and a horizontal platform. The horizontal platform is set on the base, and a guide mechanism is installed between the horizontal platform and the base. The guide mechanism constrains the horizontal platform, ensuring that it moves back and forth along the vibration direction of the hydraulic vibrator. The guide mechanism is used to achieve coordinated movement between the hydraulic vibrator and the horizontal platform.

[0003] With the continuous development of technology, the complexity of test scenarios has significantly increased, placing higher demands on parameters such as the effective installation space, load-bearing capacity, and thrust stroke of test benches. For example, catapult arresting simulation testing of carrier-based aircraft components is a core component of carrier-based aircraft compatibility verification, directly impacting the safety of takeoff and landing and combat effectiveness. Its dynamic response and structural strength must undergo rigorous testing and verification. Carrier-based aircraft components are large, requiring a hydraulic vibration test bench with high load-bearing capacity, high thrust, and long stroke for catapult arresting simulation testing. Due to the influence of machining accuracy and assembly errors, mechanical interference can easily occur between the hydraulic vibrator and the platform surface during long-stroke movement, leading to a decrease in the transmission efficiency of the hydraulic vibrator and equipment wear. The platform surface and the hydraulic vibrator are connected via a connector, a key component for transmitting excitation force. This connector is directly connected to the platform surface, which can weigh up to 1 ton, and is rigidly connected to the slide rail. Traditional connectors typically use bolts for direct connection, which have lower strength and rigidity than other transmission components on the test bench. This causes the error between the horizontal platform and the hydraulic vibrator to be concentrated at the relatively weak connector, resulting in irreversible plastic deformation of the connector in the vertical direction. During operation, due to the huge excitation force, it may completely break, affecting work production and personal safety.

[0004] Therefore, in view of the shortcomings of the existing technology, it is necessary to design a large-stroke hydraulic vibration level test bench to solve the above problems.

[0005] It should be noted that the above introduction to the technical background is only for the purpose of providing a clear and complete explanation of the technical solution of the present invention and for the convenience of those skilled in the art to understand it. It should not be assumed that the above content is known to those skilled in the art simply because it has been described in the background of the present invention. Summary of the Invention

[0006] To overcome the shortcomings of the existing technology, this invention provides a large-stroke hydraulic vibration horizontal test bench. Through innovative system architecture and specialized component design, this test bench fundamentally decouples the horizontal and vertical alignment error compensation functions. This ensures high-precision guidance and efficient excitation force transmission while achieving dynamic and adaptive compensation for multi-dimensional alignment errors, significantly improving the equipment's operational reliability, testing accuracy, and service life.

[0007] This invention discloses a large-stroke hydraulic vibration horizontal test bench, including a base, a hydraulic exciter and a horizontal platform. The hydraulic exciter is mounted on the base, and the horizontal platform is slidably connected to the base along the vibration direction of the hydraulic exciter through a guide mechanism.

[0008] The guiding mechanism includes a slide rail arranged on the base along the vibration direction and a slider connected to the slide rail. The slider is connected to the horizontal platform surface through a guide rail compensation block. The guide rail compensation block is configured to provide horizontal elastic deformation perpendicular to the vibration direction to dynamically compensate for the horizontal alignment error between the hydraulic vibrator and the horizontal platform surface.

[0009] A spring plate assembly connects the horizontal platform surface to the output end of the hydraulic vibrator to transmit the excitation force. The spring plate assembly is composed of multiple layers of spring plates stacked along the vibration direction to disperse and reduce the overall working stress when subjected to bending moment. Each layer of spring plates is set parallel to the horizontal platform surface to dynamically compensate for the vertical alignment error between the hydraulic vibrator and the horizontal platform surface by utilizing the bending flexibility of each spring plate in the vertical direction.

[0010] A preferred technical solution: The guide rail compensation block is I-shaped in a cross-section perpendicular to the vibration direction, comprising an upper connecting part, a lower connecting part, and a middle web connecting the two; the dimension of the middle web in the cross-section perpendicular to the vibration direction is smaller than the dimensions of the upper and lower connecting parts in the same direction; the upper connecting part is connected to the horizontal platform surface, and the lower connecting part is connected to the slider. This structural design of the guide rail compensation block enables it to obtain controllable elasticity in a specific direction in the horizontal plane, used to dynamically compensate for the alignment error between the hydraulic vibrator and the horizontal platform surface in the horizontal direction.

[0011] Preferred technical solution: The front end of the spring plate assembly is rigidly connected to the output end of the hydraulic vibrator through a front adapter, and the rear end of the spring plate assembly is rigidly connected to the horizontal platform through a rear adapter.

[0012] Preferred technical solution: The front adapter is provided with a front connecting part, and the front connecting part and the spring plate assembly are connected by an insert-type nested fit; the rear adapter is provided with a rear connecting part, and the rear connecting part and the spring plate assembly are also connected by an insert-type nested fit.

[0013] Preferred technical solution: The multi-layer spring plates of the spring plate assembly are divided into two groups by the front connecting part and the rear connecting part. The front ends of the two groups of spring plates are respectively locked to the upper and lower sides of the front connecting part by fasteners; the rear ends of the two groups of spring plates are respectively locked to the upper and lower sides of the rear connecting part by fasteners.

[0014] Preferred technical solution: The number of spring plates stacked on the upper and lower sides of the front connecting part is the same, and the number of spring plates stacked on the upper and lower sides of the rear connecting part is also the same.

[0015] Preferred technical solution: The multi-layered stacked spring plates are bonded and fixed together with adhesive, and the fasteners are bolt fasteners.

[0016] Preferred technical solution: A pad is provided at the connection end face of the bolt fastener and the spring plate.

[0017] Preferred technical solution: The interface width between the front connecting part and the spring plate assembly is greater than the corresponding width of the interface connecting the output end of the hydraulic vibrator; the interface width between the rear connecting part and the spring plate assembly is greater than the corresponding width of the interface connecting the horizontal platform.

[0018] Preferred technical solution: The elastic modulus of the spring plate is in the range of 300GPa to 400GPa; the spring plate has a layered composite structure, and its plate body includes a central layer and at least one functional layer bonded to its surface in the thickness direction; the functional layer is made of a material with a damping loss factor higher than that of the central layer.

[0019] Due to the application of the above technical solutions, the beneficial effects of this invention compared with the prior art are as follows:

[0020] This invention innovatively assigns the horizontal alignment error compensation function to the elastic element (guide rail compensation block) in the guiding mechanism, while assigning the vertical alignment error compensation and core excitation force transmission function to the spring plate assembly. This "horizontal-vertical" error-separated system architecture design breaks the technical bias of traditional designs that load all compensation requirements onto a single force transmission component, fundamentally solving the functional contradiction and achieving accurate and reliable dynamic compensation.

[0021] This invention, based on the principles of materials mechanics, replaces the solid plate connector with a total thickness of H with a spring plate assembly consisting of n layers of spring plates, still with a total thickness of H, under the same bending moment. This reduces the maximum bending stress of each layer to 1 / n of the original, significantly dispersing and lowering the working stress. Since material fatigue life is inversely proportional to stress, the exponential reduction in working stress directly leads to an exponential increase in the fatigue life of the component, greatly enhancing the long-term reliability of the equipment. Furthermore, the low-stress state allows the spring plate assembly to fully utilize the bending flexibility of the spring plates in the vertical plane to achieve the required dynamic compensation, while maintaining high axial stiffness in the vibration direction and high lateral stiffness in the horizontal direction, perfectly balancing error compensation and precise force transmission.

[0022] The elastic design of the guide rail compensation block in this invention can adaptively absorb and compensate for horizontal lateral alignment errors caused by manufacturing, installation and long-term wear, as well as the fit clearance between the slider and the guide rail. It transforms harmful rigid impacts into tiny elastic deformations, ensuring smooth and low-noise motion, and protecting the accuracy and lifespan of the guide mechanism.

[0023] The spring plate assembly forms a symmetrical and stable "sandwich" structure by clamping and fixing the front and rear connecting parts with two sets of spring plates, resulting in balanced stress and high bending and torsional stiffness. The combination of inter-plate bonding and bolt tightening, along with a widened connection interface and the use of pads, ensures the reliability and fatigue life of the connection interface under large alternating loads. In particular, the use of high-strength adhesive to bond the multi-layered spring plates into a slip-free whole completely eliminates energy loss caused by interlayer micro-slippage, ensuring near-rigid connection efficiency and precision in the transmission of excitation force from the hydraulic vibrator to the horizontal platform.

[0024] This invention employs a layered composite spring plate assembly with a high-stiffness central layer and a high-damping functional layer. This ensures that the spring plate assembly maintains high axial force transmission stiffness and vertical bending flexibility while also possessing excellent additional vibration attenuation and noise suppression capabilities. Ultimately, this achieves high-stiffness, precise force transmission and multi-dimensional dynamic error compensation, improving the operational reliability, testing accuracy, and service life of the test bench. Attached Figure Description

[0025] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0026] Figure 1 This is a front view of a large-stroke hydraulic vibration horizontal test bench according to the present invention;

[0027] Figure 2 This is a top view of a large-stroke hydraulic vibration horizontal test bench according to the present invention;

[0028] Figure 3 This is a schematic diagram of the spring plate assembly in the non-bent state in the front view direction of the present invention;

[0029] Figure 4 This is a schematic diagram of the spring plate assembly in the bending state in the front view direction of the present invention;

[0030] Figure 5 This is a schematic diagram of the guide rail compensation block in the front view direction of the present invention;

[0031] Figure 6 This is a schematic diagram of the guide rail compensation block in the non-bent state in the side view direction of the present invention;

[0032] Figure 7 This is a schematic diagram of the guide rail compensation block in the present invention under a bent state in the side view direction.

[0033] In the above attached figures, 1 is the base; 2 is the hydraulic vibrator; 21 is the output end; 3 is the horizontal platform; 4 is the guide mechanism; 41 is the slide rail; 42 is the slider; 43 is the guide rail compensation block; 431 is the upper connecting part; 432 is the lower connecting part; 433 is the intermediate web part; 5 is the spring plate assembly; 51 is the spring plate; 6 is the front adapter seat; 61 is the front connecting part; 7 is the rear adapter seat; 71 is the rear connecting part; 8 is the fastener; and 9 is the pad. Detailed Implementation

[0034] The following specific embodiments illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification.

[0035] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be used interchangeably where appropriate for the description of embodiments of this application herein. Furthermore, the terms "comprising" and "having," and their synonyms, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0036] In this application, the terms "upper," "lower," "left," "right," "front," "rear," "top," "bottom," "inner," "outer," "middle," "vertical," "horizontal," "lateral," and "longitudinal" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for the purpose of better describing the invention and its embodiments, and are not intended to limit the indicated device, element, or component to having a specific orientation, or to be constructed and operated in a specific orientation.

[0037] Furthermore, in addition to indicating direction or positional relationship, some of the aforementioned terms may also have other meanings. For example, the term "above" may also be used in certain situations to indicate a dependency or connection. Those skilled in the art can understand the specific meaning of these terms in this invention based on the specific circumstances.

[0038] Furthermore, the terms "installation," "setting," "equipped with," "connection," "linking," "fitting," and "fitting" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Similarly, "fitting" can mean completely or partially fitted. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0039] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0040] Example:

[0041] like Figure 1 , Figure 2 and Figure 5 As shown, the present invention provides a large-stroke hydraulic vibration horizontal test bench, the main body of which includes a base 1, a hydraulic vibrator 2, a horizontal platform 3, a guide mechanism 4, and a spring plate assembly 5 connecting the horizontal platform 3 and the hydraulic vibrator 2.

[0042] The base 1 is a rigid welded or cast structure, providing a stable mounting foundation for the test bench.

[0043] The hydraulic vibrator 2 is mounted on the base 1 through its housing, and its output end 21 can perform a large-stroke reciprocating motion in the horizontal direction (i.e. the vibration direction).

[0044] The horizontal platform 3 is used to mount the test piece.

[0045] The guiding mechanism 4 includes two or more parallel slide rails 41 fixed to the base 1 along the vibration direction, and sliders 42 mounted on each slide rail 41. It should be noted that the number of sliders 42 mounted on each slide rail 41 is one or more. The horizontal platform 3 is slidably connected to the base 1 through the sliding pair formed by the slide rails 41 and sliders 42, and is restricted to moving only along the vibration direction of the hydraulic vibrator 2. It should also be noted that the guiding mechanism 4 includes other auxiliary guiding mechanisms, such as side plates, which do not interfere with the lateral compensation of the guide rail compensation block 43.

[0046] like Figure 1 , Figure 2 , Figure 5 , Figure 6 and Figure 7 As shown, the slider 42 is not directly rigidly connected to the horizontal platform 3, but rather transitions through a specially designed guide rail compensation block 43. This guide rail compensation block 43 is constructed to provide horizontal elastic deformation perpendicular to the vibration direction. The lower connecting portion 432 of the guide rail compensation block 43 is fixed to the slider 42 by bolts, and the upper connecting portion 431 is fixed to the bottom surface of the horizontal platform 3 by bolts. Its cross-section perpendicular to the output vibration direction of the hydraulic vibrator 2 is "I-shaped," including a relatively wide upper connecting portion 431, a lower connecting portion 432, and a middle web portion 433 whose dimensions decrease significantly along the direction perpendicular to the vibration direction. This structure allows the middle web portion 433 to provide horizontal elastic deformation perpendicular to the vibration direction (i.e., horizontal lateral elastic deformation).

[0047] When there is a movement gap between the slide rail 41 and the slider 42, or when there is a horizontal lateral alignment error between the hydraulic vibrator 2 and the platform surface 3 (i.e., there is a small horizontal lateral alignment error between the axis of the output end 21 and the installation positioning of the platform surface 3), the intermediate web portion 433 can adapt through its lateral (perpendicular to the vibration direction) elastic bending deformation, thereby releasing the constraint stress, ensuring that the slider 42 moves freely, and maintaining the stable support of the platform surface 3.

[0048] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, the horizontal platform 3 and the output end 21 of the hydraulic vibrator 2 are connected and the excitation force is transmitted via a spring plate assembly 5. This spring plate assembly 5 is composed of multiple layers of high-strength spring plates 51 stacked together (it should be noted that...). Figure 3 and Figure 4The gaps between the spring plates 51 are merely to indicate that it is a layered structure; in actual use, adjacent spring plates 51 are tightly fitted together. All spring plates 51 are set parallel to the horizontal platform surface 3 (Note: parallelism here mainly refers to horizontal parallelism; bending generally occurs along the vibration direction to compensate for alignment errors, and they are only parallel to the horizontal platform surface when not under stress), and their length extends along the vibration direction. The spring plates 53 are preferably made of spring steel with an elastic modulus in the range of 300-400 GPa to ensure good elasticity and fatigue strength.

[0049] The front end of the spring plate assembly 5 is rigidly connected to the output end (piston rod end) of the hydraulic vibrator 2 via a front adapter 6, and the rear end is rigidly connected to the horizontal platform surface 3 via a rear adapter 7. The front adapter 6 has a front connecting part 61, which is inserted into and nested with the front end of the spring plate assembly 5. The rear adapter 7 has a rear connecting part 71, which is inserted into and nested with the rear end of the spring plate assembly 5.

[0050] More specifically, the spring plate assembly 5 is not a single piece, but rather consists of two sets of parallel and spaced-apart spring plates 51, with the same number of spring plates in both sets. The front ends of the two sets of spring plates 51 are respectively locked to the upper and lower sides of the front connecting part 61 by bolts and fasteners 8. Specifically, the front ends of the bolts and fasteners pass through the spring plates 51 and the front connecting part 61 and are fitted with nuts to assemble the two together, reducing the gap between the stacked spring plates. Similarly, the rear ends of the two sets of spring plates 51 are respectively locked to the upper and lower sides of the rear connecting part 71 by bolts and fasteners. A pad 9 is installed between the bolt head or nut of the bolt fastener 8 and the outermost spring plate 51 to distribute the clamping force and prevent local crushing.

[0051] The stacked multilayer spring plates 51 are firmly bonded together using an adhesive (e.g., epoxy resin with a shear strength of not less than 30 MPa). This bonding effectively eliminates micro-slippage between the layers, ensuring that the entire spring plate assembly 5 functions as a single unit when transmitting high-frequency excitation forces, thus improving the stiffness and efficiency of force transmission. The combination of bolting and bonding provides double assurance against gaps between the spring plates 51.

[0052] Furthermore, the contact interface width W1 between the front connecting part 61 and the spring plate 51 is designed to be greater than the interface width W2 between the front adapter 6 and the hydraulic vibrator output end 21. Similarly, the interface width between the rear connecting part 71 and the spring plate 51 is also greater than the interface width between the rear adapter 7 and the horizontal platform surface 3. This "widened load-bearing surface" design reduces stress concentration at the connection points, further improving the reliability and fatigue life of critical connection points under long-term large alternating loads.

[0053] like Figures 1 to 7 As shown, during operation, the excitation force generated by the hydraulic vibrator 2 is input to the spring plate assembly 5 through the front adapter 6. Since all the spring plates 51 are arranged along the vibration direction (axial direction), their superimposed axial stiffness is extremely high, which can transmit the thrust to the horizontal platform 3 with almost no loss and no hysteresis, driving it to make precise large-stroke reciprocating motion.

[0054] When there is a vertical alignment error, the spring plate assembly 5 as a whole utilizes the bending flexibility of each spring plate 51 in the vertical plane to generate corresponding elastic deflection, dynamically absorbing this error and protecting the hydraulic vibrator 2 and the horizontal platform 3 from damage by additional bending moment.

[0055] When there is a horizontal alignment error or guide gap, it is compensated by the elastic bending deformation of the middle web portion 433 of the guide rail compensation block 43. At the same time, the change in the height of the horizontal platform surface 3 caused by the elastic bending deformation of the middle web portion 433 is still dynamically absorbed by the corresponding flexural deformation of the spring plate assembly 5.

[0056] Through the collaborative mechanism of elastic guidance compensation for horizontal error and flexible force transmission compensation for vertical error, this invention achieves a perfect unity of high stiffness force transmission and multi-dimensional dynamic error compensation, providing a high-precision and high-reliability solution for large-stroke hydraulic vibration testing.

[0057] To ensure that the spring plate assembly 5 has sufficient flexibility in the vertical direction to dynamically compensate for alignment errors, its design must meet a basic principle: the maximum allowable deflection ω of the spring plate assembly 5 in the vertical direction should be greater than or equal to the sum of the installation error Δh of the hydraulic vibrator 2 and the vibration displacement δ of the horizontal platform 3 in the vertical direction, i.e., ω ≥ Δh + δ. This principle guarantees that under any working condition, the elastic deformation capacity of the spring plate assembly 5 is sufficient to "absorb" the alignment deviation caused by both static installation deviation and dynamic motion deviation, without generating rigid interference or excessive additional stress.

[0058] To meet the above criteria, the deflection ω of the spring plate assembly 5 can be estimated using a simply supported beam model, and its calculation formula is as follows:

[0059] ω=(F 垂 ·L³) / (48·E·I)

[0060] in:

[0061] F 垂 =m·g,F 垂 denoted as , where is the vertical load that the spring plate assembly 5 needs to withstand, m is the overall mass of the horizontal platform surface 3, and g is the acceleration due to gravity.

[0062] L represents the effective span of the spring plate assembly 5, which is the distance between the inner sides of the plate-shaped structures on the front and rear adapter seats 6 and 7.

[0063] E is the equivalent elastic modulus of spring plate assembly 5.

[0064] I is the moment of inertia of the section of the spring plate assembly 5, calculated by the formula I = (b·D³) / 12. Where b is the equivalent width of the section of the spring plate assembly (in this embodiment, the area with the greatest deflection influence, i.e., the narrowest part of the section width of the spring plate assembly 5, is selected as the equivalent width), and D is the equivalent thickness of the section of the spring plate assembly.

[0065] In a preferred embodiment of the present invention, the spring plate 51 is made of a high-strength composite material (such as spring steel), and its equivalent elastic modulus E ranges from 300 to 400 GPa. The equivalent thickness D of the spring plate assembly is 5-8 mm, the number of stacked spring plate layers n is 3-5 layers, and the layers are bonded together by epoxy resin to form an adhesive layer 12.

[0066] Let's take a specific design parameter as an example for verification:

[0067] Assuming the total mass of the platform surface is m = 1000 kg, then F 垂 =1000kg × 9.8m / s² = 9800N

[0068] The effective span of the spring plate assembly is L = 150mm.

[0069] The equivalent elastic modulus of the selected spring plate material is E=350GPa.

[0070] The spring plate assembly is made up of stacked spring plates with an equivalent width b=50mm and an equivalent thickness D=6.4mm. The equivalent thickness D=6.4mm (the thickness of the adhesive layer is ignored here for the sake of simplifying the calculation).

[0071] Calculate the moment of inertia of the cross section: I = (50mm × (6.4mm)³) / 12 = 1.092 × 10 4 mm 4

[0072] Substitute the above parameters into the deflection formula:

[0073] ω=(9800N×(150mm)³) / (48×350×10³N / mm²×1.092×10 4 mm 4 )≈0.18mm

[0074] The calculation results show that when there is a static installation error of Δh = 0.1 mm and a dynamic vibration displacement of δ = 0.05 mm in the vertical direction of the platform, the total compensation required is 0.15 mm. The maximum allowable deflection of 0.18 mm for the spring plate assembly fully meets the requirement of ω ≥ Δh + δ, and can effectively absorb this deviation. That is, by controlling the parameters of the spring plate material, quantity, and size in the spring plate assembly, dynamic compensation can be achieved for the vertical alignment error between the hydraulic vibrator and the platform surface.

[0075] In some embodiments, the spring plate 51 can also be made of layered composite material. Its core layer is made of high-quality spring steel with an elastic modulus in the range of 300 GPa to 400 GPa, and high yield strength and good toughness are obtained through heat treatment. Functional layers are firmly bonded to the upper and lower surfaces of the core layer through a hot-pressing diffusion bonding process. The selection of the functional layer material is based on the principle that its damping loss factor is higher than that of the core layer. Generally, the functional layer uses a high-damping alloy, such as a manganese-copper alloy (containing 60%-80% manganese, 20%-40% copper, 1%-3% aluminum, 0.5%-5% iron, and 0.5-5% nickel) or an iron-manganese damping alloy (iron-based, containing 15%-30% manganese, 0.05%-0.25% carbon, and 0.5%-2% silicon), whose damping performance can be more than an order of magnitude higher than that of ordinary structural steel. The total thickness of the functional layer typically accounts for 10%-30% of the total thickness of a single-layer spring plate.

[0076] The resulting layered composite spring plate maintains high elastic modulus and high strength, while the surface functional layer endows the entire plate with excellent damping characteristics. By stacking and bonding several layers of such composite spring plates and assembling them with front and rear adapters, the resulting spring plate assembly 5 not only compensates for vertical errors and disperses stress through bending flexibility, but also effectively dissipates additional vibration energy outside the main vibration direction during operation. This reduces the transmission of harmful vibrations to the horizontal platform 3 through the spring plate assembly 5, making the movement of the horizontal platform 3 smoother and improving testing accuracy. It also reduces air noise and structural radiation noise during equipment operation.

[0077] Finally, it should be noted that the above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A large-stroke hydraulic vibration horizontal test bench, comprising a base, a hydraulic vibrator, and a horizontal platform, wherein the hydraulic vibrator is mounted on the base, and the horizontal platform is slidably connected to the base along the vibration direction of the hydraulic vibrator via a guide mechanism, characterized in that: The guiding mechanism includes a slide rail arranged on a base along the vibration direction and a slider connected to the slide rail. The slider is connected to the horizontal platform surface via a guide rail compensation block. The guide rail compensation block is configured to provide horizontal elastic deformation perpendicular to the vibration direction. The horizontal platform is connected to the output end of the hydraulic vibrator via a spring plate assembly; the spring plate assembly is composed of multiple layers of spring plates extending along the vibration direction, with each layer of spring plates arranged parallel to the horizontal platform.

2. The large-stroke hydraulic vibration horizontal test bench according to claim 1, characterized in that: The guide rail compensation block is I-shaped in a cross section perpendicular to the vibration direction, and includes an upper connecting part, a lower connecting part, and an intermediate web part connecting the two; the dimension of the intermediate web part in the cross section perpendicular to the vibration direction is smaller than the dimensions of the upper connecting part and the lower connecting part in the same direction; the upper connecting part is connected to the horizontal platform surface, and the lower connecting part is connected to the slider.

3. The large-stroke hydraulic vibration horizontal test bench according to claim 1, characterized in that: The front end of the spring plate assembly is rigidly connected to the output end of the hydraulic vibrator via a front adapter, and the rear end of the spring plate assembly is rigidly connected to the horizontal platform via a rear adapter.

4. The large-stroke hydraulic vibration level test bench according to claim 3, characterized in that: The front adapter is provided with a front connecting part, which is connected to the spring plate assembly by an insert-type nested fit; the rear adapter is provided with a rear connecting part, which is also connected to the spring plate assembly by an insert-type nested fit.

5. The large-stroke hydraulic vibration level test bench according to claim 4, characterized in that: The multi-layer spring plates of the spring plate assembly are divided into two groups by the front connecting part and the rear connecting part. The front ends of the two groups of spring plates are respectively locked to the upper and lower sides of the front connecting part by fasteners; the rear ends of the two groups of spring plates are respectively locked to the upper and lower sides of the rear connecting part by fasteners.

6. The large-stroke hydraulic vibration level test bench according to claim 5, characterized in that: The number of spring plates stacked on the upper and lower sides of the front connecting part is the same, and the number of spring plates stacked on the upper and lower sides of the rear connecting part is also the same.

7. A large-stroke hydraulic vibration level test bench according to claim 5 or 6, characterized in that: The multiple stacked spring plates are bonded and fixed together by adhesive, and the fasteners are bolt fasteners.

8. The large-stroke hydraulic vibration level test bench according to claim 7, characterized in that: A pad is provided at the connection end face of the bolt fastener and the spring plate.

9. A large-stroke hydraulic vibration level test bench according to claim 8, characterized in that: The interface width between the front connecting part and the spring plate assembly is greater than the corresponding width of the interface connecting the output end of the hydraulic vibrator; the interface width between the rear connecting part and the spring plate assembly is greater than the corresponding width of the interface connecting the horizontal platform surface.

10. A large-stroke hydraulic vibration level test bench according to claim 1, characterized in that: The elastic modulus of the spring plate is in the range of 300 GPa to 400 GPa; the spring plate has a layered composite structure, and its plate body includes a central layer and at least one functional layer bonded to its surface in the thickness direction; the functional layer is made of a material with a damping loss factor higher than that of the central layer.

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