Disc spring rubber composite large bearing low frequency vibration isolator and mounting method thereof

Abstract

This application discloses a disc spring rubber composite high-load-bearing low-frequency vibration isolator and its installation method, belonging to the field of low-frequency vibration isolation technology. The disc spring rubber composite high-load-bearing low-frequency vibration isolator includes an upper mounting mechanism, a lower mounting mechanism, a disc spring negative stiffness mechanism, a rubber vibration isolation mechanism, and a connecting rod. The rubber vibration isolation mechanism and the disc spring negative stiffness mechanism are arranged in parallel between the upper and lower mounting mechanisms; both ends of the connecting rod are connected to the upper mounting mechanism and the rubber vibration isolation mechanism, respectively; wherein, the disc spring negative stiffness mechanism includes a disc spring plate, the height-to-thickness ratio of the disc spring plate h0 / t > 0, so that the disc spring plate generates negative stiffness characteristics after the axial compression exceeds a threshold. The disc spring rubber composite high-load-bearing low-frequency vibration isolator of this application can achieve high load-bearing capacity and low stiffness characteristics, thereby reducing the natural frequency while maintaining high load-bearing performance and obtaining a lower initial isolation frequency.

Description

Technical Field

[0001] This application relates to the field of low-frequency vibration isolation technology, and in particular to a disc spring rubber composite high-load low-frequency vibration isolator and its installation method. Background Technology

[0002] Modern ships have increasingly higher requirements for navigation comfort and equipment reliability. The vibration excitation generated by the main and auxiliary engines and other power equipment during operation is transmitted to the hull structure through vibration isolators, bases, and other transmission paths. This not only affects the strength and service life of the hull structure and reduces the working efficiency of marine equipment, but also generates cabin noise and underwater radiated noise, impacting the living environment of the crew and the marine ecosystem. Therefore, marine vibration isolators, as the core device for vibration reduction and noise control in ships, directly determine the vibration isolation effect of ship equipment.

[0003] In related technologies, rubber vibration isolators are widely used for vibration isolation of power equipment such as main and auxiliary engines in ships due to their advantages such as simple structure, low cost, and certain damping characteristics. Rubber vibration isolators typically employ compression bearing, shear bearing, or a combination of compression and shear bearing, offering strong load-bearing capacity ranging from 10 kg to 12,000 kg. However, the natural frequency range of rubber vibration isolators is usually 5 Hz to 30 Hz, with a relatively high initial isolation frequency. This is not conducive to isolating low-frequency vibration energy below 10 Hz generated by equipment, making it difficult to meet the design requirements for low-frequency vibration and noise control in future quiet ships.

[0004] Furthermore, the vibration isolation system operates at an excitation frequency approximately higher than its natural frequency. Effective vibration isolation requires a frequency of approximately 1.41 times the normal frequency (i.e., 1.41 times the normal frequency). This means that for a vibration isolator with a natural frequency of 8Hz, its effective initial isolation frequency is approximately 11Hz, and low-frequency vibrations below 10Hz cannot be effectively isolated. In practical engineering, due to constraints on load-bearing capacity and stability requirements, rubber vibration isolators need to possess a certain stiffness to support equipment loads, thus their natural frequency cannot be further reduced. In the field of vibration isolation for marine equipment, vibration isolators generally suffer from the inability to simultaneously achieve both load-bearing capacity and natural frequency, failing to fully meet the vibration isolation requirements of low-frequency, high-load equipment such as ship propulsion systems and precision instruments. Summary of the Invention

[0005] This application provides a disc spring rubber composite high load-bearing low-frequency vibration isolator that can achieve high load-bearing capacity and low stiffness, thereby reducing the natural frequency while maintaining high load-bearing capacity and obtaining a lower initial vibration isolation frequency.

[0006] Another objective of this application is to provide an installation method for a disc spring rubber composite high-load low-frequency vibration isolator.

[0007] To achieve the above objectives, according to a first aspect of this application, a disc spring rubber composite high-load-bearing low-frequency vibration isolator is provided, comprising: An upper mounting mechanism is connected to the vibration-isolated equipment. Lower installation mechanism; A disc spring negative stiffness mechanism is disposed between the upper mounting mechanism and the lower mounting mechanism; A rubber vibration isolation mechanism is provided, wherein the rubber vibration isolation mechanism and the disc spring negative stiffness mechanism are arranged in parallel between the upper mounting mechanism and the lower mounting mechanism; A connecting rod, the two ends of which are respectively connected to the upper mounting mechanism and the rubber vibration isolation mechanism; The disc spring negative stiffness mechanism includes a disc spring plate, wherein the height-to-thickness ratio h0 / t of the disc spring plate is greater than 1. Where h0 is the free height of the disc spring and t is the thickness of the disc spring, so that the disc spring produces negative stiffness characteristics after the axial compression exceeds the threshold.

[0008] Optionally, the height-to-thickness ratio of the disc spring is h0 / t > .

[0009] Optionally, the disc spring negative stiffness mechanism further includes a disc spring base plate, the disc spring plate is located on the side of the disc spring base plate facing the upper mounting mechanism, the disc spring rubber composite high load-bearing low frequency vibration isolator further includes a support member, the lower mounting mechanism includes a lower mounting plate, and the disc spring base plate is connected to the lower mounting plate through the support member; The disc spring base plate, the support member, and the lower mounting plate are arranged independently of each other; or, At least two of the disc spring base plate, the support member, and the lower mounting plate are integrally formed.

[0010] Optionally, the distance between the disc spring negative stiffness mechanism and the upper mounting mechanism is adjustable so that the disc spring rubber composite high load-bearing low frequency vibration isolator produces negative stiffness characteristics under different axial compressions; Specifically, the negative stiffness mechanism of the disc spring is controlled to move closer to or further away from the upper mounting mechanism; and / or, The upper mounting mechanism is controlled to move closer to or further away from the disc spring negative stiffness mechanism.

[0011] Optionally, when the disc spring negative stiffness mechanism is controlled to move closer to or further away from the upper mounting mechanism, the distance between the disc spring negative stiffness mechanism and the upper mounting mechanism can be adjusted by adjusting the position of the disc spring base plate on the support member. Wherein, the disc spring base plate is threadedly connected to the support member; and / or, The disc spring negative stiffness mechanism further includes a first fastener, which is threadedly connected to the support member. The first fastener is provided on both sides of the disc spring base plate in the axial direction, and the support member is connected to the disc spring base plate through the first fastener.

[0012] Optionally, the upper mounting mechanism includes an upper mounting plate and an upper limit member, the upper limit member protruding from the side of the upper mounting plate facing the disc spring base plate, and the disc spring negative stiffness mechanism further includes a lower limit member, the lower limit member protruding from the side of the disc spring base plate facing the upper mounting plate, and the disc spring plate being located between the upper limit member and the lower limit member. Wherein, the upper limit positioner and the upper mounting plate are independently configured, or the upper limit positioner and the upper mounting plate are integrally formed; The lower limit member and the disc spring base plate are set independently of each other, or the lower limit member and the disc spring base plate are integrally formed.

[0013] Optionally, the disc spring is disposed between the upper limit member and the lower limit member in a forward or reverse mounting manner.

[0014] Optionally, the rubber vibration isolation mechanism includes a rubber top plate, a rubber body, and a rubber bottom plate. At least a portion of the rubber top plate is located on the side of the rubber body facing the upper mounting mechanism. The connecting rod is connected to the rubber top plate. At least a portion of the rubber bottom plate is located on the side of the rubber body facing the lower mounting plate. The rubber base plate and the lower mounting plate are provided independently of each other; or, The rubber base plate and the lower mounting plate are integrally formed.

[0015] Optionally, the rubber body is bonded to the rubber top plate and the rubber bottom plate respectively through a vulcanization process; and / or, The connecting rod is threadedly connected to the rubber top plate; and / or The rubber vibration isolation mechanism further includes a second fastener and a washer. The second fastener is threadedly connected to the connecting rod, and the washer is located between the second fastener and the rubber top plate to lock the connecting rod to the rubber top plate.

[0016] Optionally, the rubber top plate has an overall T-shaped structure, and the rubber top plate includes a first baffle and a second baffle. The second baffle is located on the side of the first baffle facing the rubber body, and at least a portion of the second baffle is embedded in the rubber body. The rubber base plate has an overall U-shaped structure. The rubber base plate includes a third baffle and two fourth baffles. The two fourth baffles are located on opposite sides of the third baffle, and part of the rubber body is located between the two fourth baffles. The rubber body has an arc-shaped groove on the side facing the third baffle, and a concave arc surface is formed on the side of the rubber body adjacent to the fourth baffle.

[0017] Optionally, the disc spring rubber composite high-load-bearing low-frequency vibration isolator further includes a guide bearing, which is mounted on the disc spring negative stiffness mechanism and sleeved on the outer periphery of the connecting rod; and / or, The connecting rod and the upper mounting mechanism are set independently of each other, or the connecting rod and the upper mounting mechanism are integrally formed.

[0018] Optionally, the number of disc springs can be one or more. When the number of disc springs is multiple, the multiple disc springs are combined to form a disc spring assembly. The disc spring assembly can be combined in any one of the following ways: paired combination, overlapping combination, or composite combination.

[0019] Optionally, when the disc spring assembly is used in a mating assembly, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =F, f i =i*f,H i =i*h0, where F, f, and h0 are the load, displacement, and free height of a single disc spring, respectively, and i is the number of disc springs; When the disc spring assembly is assembled in a stacked manner, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =n*F,f i =f,H i =h0+(n-1)*t, where F, f, and h0 are the load, displacement, and free height of a single disc spring, respectively, n is the number of disc springs, and t is the thickness of the disc spring; When the disc spring assembly adopts a composite assembly method, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =n*F,f i =i*f,H i =i*[h0+(n-1)*t], where F, f, and h0 are the load, displacement, and free height of a single disc spring, respectively, n is the number of stacked groups, i is the number of paired groups, and t is the thickness of the disc spring.

[0020] According to a second aspect of this application, a method for installing a disc spring rubber composite high-load-bearing low-frequency vibration isolator is provided, employing the disc spring rubber composite high-load-bearing low-frequency vibration isolator as described in any one of the above claims, the installation method comprising: Connect the upper mounting mechanism to the vibration-isolated equipment; Adjust the distance between the disc spring negative stiffness mechanism and the upper mounting mechanism; Connect the lower mounting mechanism to the mounting surface.

[0021] In the disc spring rubber composite high-load low-frequency vibration isolator of this application embodiment, a disc spring with a special high thickness ratio parameter (high thickness ratio h0 / t > 0) is designed. It can obtain the mechanical characteristic of negative stiffness under a certain deformation amount. When it is connected in parallel with the rubber vibration isolation mechanism, it can achieve the characteristics of increased load and decreased stiffness of the disc spring rubber composite high load low frequency vibration isolator under a specific deformation amount. This enables the disc spring rubber composite high load low frequency vibration isolator to have the characteristics of high load and low stiffness, thereby reducing the natural frequency of the disc spring rubber composite high load low frequency vibration isolator while maintaining high load performance, and obtaining a lower initial vibration isolation frequency.

[0022] The installation method of the disc spring rubber composite high load-bearing low frequency vibration isolator in this application embodiment uses the disc spring rubber composite high load-bearing low frequency vibration isolator. The installation method of the disc spring rubber composite high load-bearing low frequency vibration isolator has the beneficial effects produced by the disc spring rubber composite high load-bearing low frequency vibration isolator, which will not be described in detail here.

[0023] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0025] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0026] Figure 1 This is a three-dimensional structural schematic diagram of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in an exemplary embodiment of this application. Figure 2 This is a three-dimensional structural schematic diagram of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in an exemplary embodiment of this application from another perspective. Figure 3This is a schematic planar structure diagram of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in an exemplary embodiment of this application. Figure 4 This is a schematic diagram of the planar structure of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in an exemplary embodiment of this application from another perspective. Figure 5 It is along Figure 4 Schematic diagram of the cross section of line AA; Figure 6 It is along Figure 4 Schematic diagram of the cross section of the middle BB line; Figure 7 This is a three-dimensional structural diagram of the rubber top plate provided in an exemplary embodiment of this application; Figure 8 These are simulation results of the load and displacement of the disc spring provided in the exemplary embodiments of this application; Figure 9 These are simulation results of disc spring displacement and disc spring stiffness provided in the exemplary embodiments of this application; Figure 10 These are the mechanical performance test results of the rubber vibration isolation mechanism provided in the exemplary embodiment of this application when it bears a load of 450kg; Figure 11 The results of the transmission rate test of the rubber vibration isolation mechanism provided in the exemplary embodiment of this application when it bears a load of 450kg; Figure 12 These are the mechanical performance test results of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in the exemplary embodiment of this application when it bears a load of 450kg; Figure 13 This is the transmissivity test result of the disc spring rubber composite high load-bearing low frequency vibration isolator provided in the exemplary embodiment of this application when it bears 450kg. Figure 14 These are the mechanical performance test results of the rubber vibration isolation mechanism provided in the exemplary embodiment of this application when compressed by 8mm; Figure 15 This is the result of the transmittance test of the rubber vibration isolation mechanism provided in the exemplary embodiment of this application when compressed by 8mm; Figure 16 These are the mechanical performance test results of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in the exemplary embodiment of this application when compressed by 8mm; Figure 17 This is the transmissivity test result of the disc spring rubber composite high load-bearing low frequency vibration isolator provided in the exemplary embodiment of this application when compressed by 8mm; Figure 18 This is a flowchart of the installation method of the disc spring rubber composite high load-bearing low-frequency vibration isolator provided in an exemplary embodiment of this application.

[0027] Explanation of reference numerals in the attached figures: 1. Upper mounting mechanism; 11. Upper mounting plate; 12. Upper limit stop; 13. Transition plate; 2. Lower mounting mechanism; 21. Lower mounting plate; 3. Disc spring negative stiffness mechanism; 31. Disc spring leaf; 32. Disc spring base plate; 33. First fastener; 34. Lower limit stop; 4. Rubber vibration isolation mechanism; 41. Rubber top plate; 411. First baffle; 412. Second baffle; 413. Protrusion; 42. Rubber body; 421. Arc groove; 422. Concave arc surface; 43. Rubber base plate; 431. Third baffle; 432. Fourth baffle; 44. Second fastener; 45. Shim; 5. Connecting rod; 6. Support; 7. Guide bearing; X, First direction; Y, Second direction; Z, Third direction. Detailed Implementation

[0028] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application. In addition, it should be understood that the specific embodiments described herein are only for illustration and explanation of this application and are not intended to limit this application. In this application, unless otherwise stated, directional terms such as "up," "down," "left," and "right" generally refer to up, down, left, and right in the actual use or working state of the device, specifically the drawing directions in the accompanying drawings.

[0029] In this application, unless otherwise expressly specified and limited, the terms "connected," "linked," "stacked," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two elements or the interaction between two elements. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0030] This application provides a disc spring rubber composite high-load-bearing low-frequency vibration isolator and its installation method, which are described in detail below. It should be noted that the order of description of the following embodiments is not intended to limit the preferred order of the embodiments of this application. Furthermore, in the following embodiments, the descriptions of each embodiment have their own emphasis; parts not described in detail in a certain embodiment can be referred to in the relevant descriptions of other embodiments.

[0031] According to the first aspect of this application, referring to Figures 1 to 3One embodiment of this application provides a disc spring rubber composite high-load-bearing low-frequency vibration isolator, which can be applied to shipbuilding, aerospace, high-end manufacturing, and semiconductor industries. In this application, the application of the disc spring rubber composite high-load-bearing low-frequency vibration isolator in shipbuilding is used as an example. The disc spring rubber composite high-load-bearing low-frequency vibration isolator can have three intersecting directions: a first direction X, a second direction Y, and a third direction Z. The first direction X can be the length direction of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. The second direction Y can be the width direction of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. The third direction Z can be the height direction of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. The disc spring rubber composite high-load-bearing low-frequency vibration isolator can include: an upper mounting mechanism 1, a lower mounting mechanism 2, a disc spring negative stiffness mechanism 3, a rubber vibration isolation mechanism 4, and a connecting rod 5.

[0032] Specifically, refer to Figure 1 The upper mounting mechanism 1 can be connected to the vibration-isolated equipment (not shown) to bear and transmit the load and vibration of the vibration-isolated equipment. The vibration-isolated equipment may be, for example, various types of marine equipment such as the ship's main propulsion system, auxiliary power equipment, and precision instruments. The upper mounting mechanism 1 can be a plate structure, a rod structure, or a combination of plate and rod structures. The upper mounting mechanism 1 connects to the vibration-isolated equipment, achieving a stable connection between the disc spring rubber composite high-load-bearing low-frequency vibration isolator and the vibration-isolated equipment. This allows the load and vibration of the vibration-isolated equipment to be transmitted to the disc spring negative stiffness mechanism 3 and the rubber vibration isolation mechanism 4, which then transmit the load and vibration to the lower mounting mechanism 2. The connection between the upper mounting mechanism 1 and the vibration-isolated equipment can be achieved through pressing contact, bolt locking contact, or other connection methods.

[0033] The lower mounting mechanism 2 can be located below the upper mounting mechanism 1 in the third direction Z. The lower mounting mechanism 2 is used to bear the load and vibration transmission of the vibration-isolated equipment and is connected to a mounting surface (not shown), such as a ship hull base. The lower mounting mechanism 2 may have mounting holes to facilitate the connection between the lower mounting mechanism 2 and the mounting surface.

[0034] The disc spring negative stiffness mechanism 3 can be positioned between the upper mounting mechanism 1 and the lower mounting mechanism 2 to generate axial negative stiffness mechanical characteristics under a certain axial compression. For example, when the disc spring negative stiffness mechanism 3 is initially compressed, it exhibits positive stiffness, serving a load-bearing and supporting function. Once the disc spring negative stiffness mechanism 3 reaches a certain axial compression displacement, the greater the compression displacement, the smaller the resulting axial supporting force, thus exhibiting negative stiffness characteristics.

[0035] The rubber vibration isolation mechanism 4 can be connected in parallel with the disc spring negative stiffness mechanism 3 between the upper mounting mechanism 1 and the lower mounting mechanism 2. The rubber vibration isolation mechanism 4 is used to provide load-bearing capacity and support positive stiffness characteristics in the vertical direction (i.e., the third direction Z), and the damping characteristics are provided by the rubber material itself. The rubber vibration isolation mechanism 4 can be designed with compression, shear, or a combination of compression and shear load-bearing methods.

[0036] Reference Figure 3 The connecting rod 5 can extend along the third direction Z, meaning its axial direction can be parallel to the third direction Z. Both ends of the connecting rod 5 can be connected to the upper mounting mechanism 1 and the rubber vibration isolation mechanism 4, respectively. The connecting rod 5 is used to transmit the load and vibration borne by the upper mounting mechanism 1 to the rubber vibration isolation mechanism 4. The connecting rod 5 can be a cylindrical rod, made of high-strength metal materials such as stainless steel, and its surface can be hardened to improve wear resistance. In this embodiment, the rubber vibration isolation mechanism 4 can be located below the disc spring negative stiffness mechanism 3 in the third direction Z. The end of the connecting rod 5 away from the upper mounting mechanism 1 can pass through the disc spring negative stiffness mechanism 3 and connect to the rubber vibration isolation mechanism 4. The connecting rod 5 and the rubber vibration isolation mechanism 4 can be connected by threaded connection, welding, integral molding, or other methods.

[0037] The disc spring negative stiffness mechanism 3 may include a disc spring 31. The disc spring 31 can be sleeved on the connecting rod 5, which reduces radial displacement of the disc spring 31 during compression. The disc spring 31 may be a single, unsupported disc spring. The disc spring 31 may be made of high-performance spring steel, which has excellent fatigue life and mechanical stability, enabling reliable operation of the disc spring rubber composite high-load low-frequency vibration isolator under long-term alternating loads. The height-to-thickness ratio h0 / t of the disc spring 31 is greater than... Where h0 is the free height of disc spring 31 and t is the thickness of disc spring 31, so that disc spring 31 produces negative stiffness characteristics after the compression in the axial direction (i.e., the third direction Z) exceeds a threshold. This is achieved by designing the height-to-thickness ratio of disc spring 31 to be h0 / t > 0. This causes the axial support force of the disc spring 31 to decrease as the compression displacement increases after the axial compression exceeds a certain threshold, thus generating negative stiffness characteristics. By arranging this negative stiffness disc spring mechanism 3 with a rubber vibration isolation mechanism 4, which has positive stiffness characteristics, in parallel, and utilizing the principle of positive and negative stiffness superposition, the overall dynamic stiffness of the vibration isolator can be effectively reduced while maintaining a high load-bearing capacity. This reduces the natural frequency of the disc spring rubber composite high-load-bearing low-frequency vibration isolator, resulting in a lower initial isolation frequency.

[0038] In this application, a disc spring 31 with a special high-thickness ratio parameter (high-thickness ratio h0 / t>) is designed. The disc spring rubber composite high-load-bearing low-frequency vibration isolator can achieve negative stiffness mechanical properties under a certain deformation. This negative stiffness characteristic can be used to reduce the dynamic stiffness of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. By connecting it in parallel with the rubber vibration isolation mechanism 4, the disc spring rubber composite high-load-bearing low-frequency vibration isolator can achieve increased load and decreased stiffness under a specific deformation, thus possessing high load-bearing capacity and low stiffness. This reduces the natural frequency of the disc spring rubber composite high-load-bearing low-frequency vibration isolator while maintaining high load-bearing performance, resulting in a lower initial isolation frequency. For example, it can effectively isolate low-frequency vibration energy below 10Hz. Testing has verified that the dynamic stiffness of the disc spring rubber composite high-load-bearing low-frequency vibration isolator can be reduced to approximately 40% of that of a single rubber vibration isolator, and its natural frequency can be reduced to approximately 60% of that of a single rubber vibration isolator. A single rubber vibration isolator refers to a traditional rubber vibration isolator without the parallel disc spring negative stiffness mechanism 3. Disc spring rubber composite high load-bearing low-frequency vibration isolators can be widely used for vibration isolation of various ship equipment such as ship propulsion systems, auxiliary power equipment, and precision instruments. They reduce the transmission of vibrations generated by the operation of ship power machinery, reduce the impact of vibration on the hull structure, equipment life and crew comfort, and improve the operational stability of ship equipment in complex marine environments.

[0039] In some embodiments, the height-to-thickness ratio h0 / t of the disc spring 31 is greater than that of the disc spring 31. As an example, when the height-to-thickness ratio h0 / t of the disc spring 31 is in the range of 0 to 0.5, the disc spring 31 can exhibit linear stiffness, and its mechanical properties are similar to those of a cylindrical compression coil spring. When the height-to-thickness ratio h0 / t is approximately equal to... At this time, the disc spring 31 has a deformation region with zero stiffness. When the height-to-thickness ratio h0 / t When the height-to-thickness ratio h0 / t > 1, the disc spring 31 can exhibit negative stiffness characteristics. At this time, the disc spring 31 has a larger negative stiffness characteristic area. In this embodiment, when the height-to-thickness ratio h0 / t of the disc spring 31 is greater than 1, the disc spring 31 has a larger negative stiffness characteristic area. At the same time, the disc spring 31 has a larger negative stiffness characteristic range, that is, a larger range in unstable working conditions, and can provide negative stiffness characteristics in a larger range of compression displacement, which is beneficial to better match the different compression or load requirements of the disc spring rubber composite high load-bearing low frequency vibration isolator.

[0040] As an example, the thickness t of the disc spring 31 is 1mm, the inner diameter d of the disc spring 31 is 40mm, the outer diameter D of the disc spring 31 is 80mm, the height h0 of the disc spring 31 is 6mm, and the height-to-thickness ratio h0 / t of the disc spring 31 is 6, which is significantly greater than... This allows the disc spring 31 to produce significant negative stiffness characteristics under a specific compression, thereby reducing the dynamic stiffness of the disc spring rubber composite high-load low-frequency vibration isolator.

[0041] In some embodiments, refer to Figure 1 and Figure 3 The disc spring negative stiffness mechanism 3 may also include a disc spring base plate 32. The disc spring base plate 32 can be a plate-like structure, for example, the disc spring base plate 32 can be quadrilateral in shape. The disc spring base plate 32 can be made of high-strength metal materials, such as aluminum alloy or steel, to ensure sufficient stiffness and strength. The disc spring plate 31 can be located on the side of the disc spring base plate 32 facing the mounting mechanism 1, that is, the disc spring plate 31 is disposed on the upper surface of the disc spring base plate 32. The disc spring base plate 32 can provide a mounting reference and support surface for the disc spring plate 31.

[0042] The lower mounting mechanism 2 may include a lower mounting plate 21. The lower mounting plate 21 may be a plate-like structure, for example, the lower mounting plate 21 may be quadrilateral in shape. The lower mounting plate 21 may be made of high-strength metal materials, such as aluminum alloy or steel, to ensure sufficient rigidity and strength. The lower mounting plate 21 may be provided with mounting holes for easy fixing to the mounting surface using bolts or the like.

[0043] The disc spring rubber composite high-load-bearing low-frequency vibration isolator may also include a support member 6. The disc spring base plate 32 can be connected to the lower mounting plate 21 through the support member 6, that is, the support member 6 can support between the disc spring base plate 32 and the lower mounting plate 21 to achieve effective transmission of load and vibration. The number of support members 6 can be one or more. In this embodiment, the number of support members 6 is four, and four support members 6 can provide more stable support. The four support members 6 can be distributed circumferentially. For example, the four support members 6 can be respectively set near the corners of the disc spring base plate 32.

[0044] As an example, the central area of ​​the lower mounting plate 21 can be used to install the rubber vibration isolation mechanism 4, and the outer area of ​​the lower mounting plate 21 can be connected to the disc spring base plate 32 through the support member 6. The support member 6 can be detachably connected to the disc spring base plate 32 and the lower mounting plate 21 through threaded connection, fastener connection or other means, and the support member 6 can also be fixedly connected to the disc spring base plate 32 and the lower mounting plate 21 through welding, integral molding or other means.

[0045] The disc spring base plate 32, support member 6, and lower mounting plate 21 can be independently configured, which reduces the manufacturing difficulty of the parts and facilitates disassembly and maintenance. Alternatively, at least two of the disc spring base plate 32, support member 6, and lower mounting plate 21 can be integrally formed. It can be understood that the disc spring base plate 32 and support member 6 are integrally formed, or the support member 6 and lower mounting plate 21 are integrally formed, or all three are integrally formed. This reduces the number of parts, simplifies the assembly process, and improves the overall structural integrity. The different connection methods of the disc spring base plate 32, support member 6, and lower mounting plate 21 provide flexibility for different production and application scenarios.

[0046] In some embodiments, the distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 is adjustable, that is, the gap between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 in the third direction Z is adjustable, so that the disc spring rubber composite high load-bearing low-frequency vibration isolator produces negative stiffness characteristics under different axial compression amounts. In other words, the distance between the disc spring 31 and the upper mounting mechanism 1 is adjustable, so that the disc spring rubber composite high load-bearing low-frequency vibration isolator produces negative stiffness characteristics under different axial compression amounts.

[0047] The distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 can be adjusted by controlling the disc spring negative stiffness mechanism 3 to move closer to or further away from the upper mounting mechanism 1. Alternatively, the distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 can be adjusted by controlling the upper mounting mechanism 1 to move closer to or further away from the disc spring negative stiffness mechanism 3. Or, the distance between the upper mounting mechanism 1 and the disc spring negative stiffness mechanism 3 can also be adjusted by simultaneously controlling the upper mounting mechanism 1 and the disc spring negative stiffness mechanism 3 to move closer to or further away from each other.

[0048] In this application, the timing of the disc spring negative stiffness mechanism 3's intervention can be controlled by adjusting the distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1. When the disc spring rubber composite high-load-bearing low-frequency vibration isolator has not generated any compression, there can be no gap between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1. The upper mounting mechanism 1 can simultaneously transmit the load and vibration of the isolated equipment to both the disc spring negative stiffness mechanism 3 and the rubber vibration isolator 4, allowing both mechanisms to generate compression simultaneously. It is understood that when there is no installation gap between the disc spring base plate 32 and the upper mounting plate 11, the disc spring negative stiffness mechanism 3 begins to work from the initial compression of the disc spring rubber composite high-load-bearing low-frequency vibration isolator, and the compression of the disc spring negative stiffness mechanism 3 is the same as that of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. As an example, when there is no installation gap between the adjusting disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1, the maximum compression of the disc spring negative stiffness mechanism 3 is 3mm, and the maximum compression of the disc spring rubber composite high load-bearing low frequency vibration isolator is 3mm.

[0049] When the disc spring rubber composite high-load low-frequency vibration isolator is not under compression, the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 can be spaced apart. The disc spring negative stiffness mechanism 3 only starts working when the compression of the rubber vibration isolation mechanism 4 exceeds the distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1. The distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 can be adjusted as needed, thus achieving low-stiffness mechanical characteristics under different loads or compressions. This allows the mechanical characteristics of the disc spring negative stiffness mechanism 3 to be fully utilized under different load conditions, perfectly matching the different compression or load requirements of the disc spring rubber composite high-load low-frequency vibration isolator, rather than being limited to a specific compression or load, thereby expanding the applicability of the disc spring negative stiffness mechanism 3. For example, when the installation gap between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 is adjusted to 5mm, the maximum compression of the disc spring negative stiffness mechanism 3 is 3mm, and the maximum compression of the disc spring rubber composite high-load low-frequency vibration isolator is 8mm. The disc spring rubber composite high-load-bearing low-frequency vibration isolator is supported by the rubber vibration isolation mechanism 4 within the compression range of 0mm to 5mm. When the compression of the disc spring rubber composite high-load-bearing low-frequency vibration isolator exceeds 5mm, the disc spring negative stiffness mechanism 3 begins to work, superimposing with the positive stiffness of the rubber vibration isolation mechanism 4. Within the range of 5mm to 8mm, the stiffness of the disc spring rubber composite high-load-bearing low-frequency vibration isolator first increases and then decreases, so that the disc spring rubber composite high-load-bearing low-frequency vibration isolator can still maintain a low dynamic stiffness at a compression of 8mm.

[0050] In some embodiments, by controlling the disc spring negative stiffness mechanism 3 to move closer to or further away from the upper mounting mechanism 1, the distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1 can be adjusted by adjusting the position of the disc spring base plate 32 on the support member 6. It is understood that the disc spring base plate 32 can drive the disc spring 31 to move, thereby adjusting the distance between the disc spring 31 and the upper mounting mechanism 1. The end of the support member 6 away from the disc spring base plate 32 can be connected to the lower mounting plate 21 by means of threaded connection, welding, integral molding, etc. In this embodiment, the end of the support member 6 away from the disc spring base plate 32 can be threadedly connected to the lower mounting plate 21 and locked with a nut, so that the disc spring base plate 32 and the lower mounting plate 21 are in a rigid connection state. The support member 6 is, for example, a bolt or screw.

[0051] Among them, reference Figure 1 and Figure 3The disc spring base plate 32 and the support member 6 can be threadedly connected. The disc spring base plate 32 can be provided with mounting holes, which can be through holes or blind holes, etc. In this embodiment, the mounting hole can be a through hole, which can increase the adjustment range of the disc spring base plate 32. The through hole can be provided with internal threads, and the support member 6 can be provided with external threads, thereby realizing the threaded connection between the disc spring base plate 32 and the support member 6. As an example, the position of the disc spring base plate 32 on the support member 6 can be changed by rotating the support member 6 to move it along the third direction Z, thereby changing the height position of the disc spring base plate 32.

[0052] Reference Figure 1 and Figure 3 The disc spring negative stiffness mechanism 3 may further include a first fastener 33, which may be a nut or the like. The first fastener 33 may be threadedly connected to the support member 6. The disc spring base plate 32 may have first fasteners 33 on both sides in the axial direction (i.e., the third direction Z). The support member 6 can be connected to the disc spring base plate 32 through the first fasteners 33. By providing first fasteners 33 on both sides of the disc spring base plate 32 in the axial direction, the position of the disc spring base plate 32 can be precisely adjusted and reliably locked, preventing changes in the position of the disc spring base plate 32 during operation. In this case, the disc spring base plate 32 and the support member 6 may be threadedly connected, or they may not be threadedly connected. In this embodiment, the disc spring base plate 32 may not have internal threads, which facilitates adjustment of the relative position of the disc spring base plate 32 and the support member 6.

[0053] In some embodiments, refer to Figure 3 The upper mounting mechanism 1 may include an upper mounting plate 11 and an upper limit member 12. The upper mounting plate 11 may be a plate-like structure, for example, the upper mounting plate 11 may be quadrilateral. The upper mounting plate 11 may be made of a high-strength metal material, such as aluminum alloy or steel, to ensure sufficient rigidity and strength. The upper limit member 12 may protrude from the side of the upper mounting plate 11 facing the disc spring base plate 32, that is, at least a portion of the upper limit member 12 is located on the side of the upper mounting plate 11 facing the disc spring base plate 32. In this embodiment, the upper limit member 12 is disposed on the lower surface of the upper mounting plate 11. The disc spring negative stiffness mechanism 3 may further include a lower limit member 34. The lower limit member 34 may protrude from the side of the disc spring base plate 32 facing the upper mounting plate 11, that is, at least a portion of the lower limit member 34 is located on the side of the disc spring base plate 32 facing the upper mounting plate 11. In this embodiment, the lower limit member 34 is disposed on the upper surface of the disc spring base plate 32. The disc spring 31 can be located between the upper limit member 12 and the lower limit member 34. The upper limit member 12 and the lower limit member 34 can position and limit the disc spring 31 to prevent the disc spring 31 from shifting horizontally or sliding laterally during compression, thereby improving the uniform compression of the disc spring 31 along the axial direction.

[0054] The upper limit stop 12 and the upper mounting plate 11 can be independently installed, which reduces the manufacturing difficulty of the upper limit stop 12 and the upper mounting plate 11 and facilitates disassembly and maintenance. The upper limit stop 12 and the upper mounting plate 11 can be connected by bolts or other means. Alternatively, the upper limit stop 12 and the upper mounting plate 11 can be integrally formed, which reduces the number of parts, simplifies the assembly process, and improves the overall structural integrity. The different connection methods of the upper limit stop 12 and the upper mounting plate 11 provide flexibility for different production and application scenarios.

[0055] The lower limit component 34 and the disc spring base plate 32 can be independently installed, which reduces the manufacturing difficulty of the lower limit component 34 and the disc spring base plate 32, and also facilitates disassembly and maintenance. The lower limit component 34 and the disc spring base plate 32 can be connected by bolts or the like. Alternatively, the lower limit component 34 and the disc spring base plate 32 can be integrally molded, which reduces the number of parts, simplifies the assembly process, and improves the overall structural integrity. The different connection methods of the lower limit component 34 and the disc spring base plate 32 provide flexibility for different production and application scenarios.

[0056] The upper mounting mechanism 1 may also include a transition plate 13. The transition plate 13 can be a plate-like structure, for example, the transition plate 13 can be quadrilateral in shape. The transition plate 13 can be made of high-strength metal materials, such as aluminum alloy or steel, to ensure sufficient rigidity and strength. The transition plate 13 can be positioned on the side of the upper mounting plate 11 facing the vibration-isolated equipment. The transition plate 13 and the upper mounting plate 11 can be connected by bolts or the like. The transition plate 13 is used to connect the vibration-isolated equipment. By replacing the transition plate 13 with different specifications, the disc spring rubber composite high-load-bearing low-frequency vibration isolator can be connected to different vibration-isolated equipment, thereby improving the applicability of the disc spring rubber composite high-load-bearing low-frequency vibration isolator.

[0057] In some embodiments, the disc spring 31 is disposed between the upper limit member 12 and the lower limit member 34 in a forward or reverse mounting manner. Forward mounting means that the large end of the disc spring 31 faces downward and the small end faces upward, i.e., the concave surface of the disc spring 31 faces towards the disc spring base plate 32. Reverse mounting means that the small end of the disc spring 31 faces downward and the large end faces upward, i.e., the convex surface of the disc spring 31 faces towards the disc spring base plate 32. Depending on different load-bearing requirements and negative stiffness characteristics, forward or reverse mounting can be selected, or multiple disc springs 31 can be combined and installed in different directions to obtain the desired mechanical characteristic curve.

[0058] In some embodiments, refer to Figures 4 to 6The rubber vibration isolation mechanism 4 may include a rubber top plate 41, a rubber body 42, and a rubber bottom plate 43. At least a portion of the rubber top plate 41 may be located on the side of the rubber body 42 facing the upper mounting mechanism 1. A connecting rod 5 may be connected to the rubber top plate 41. At least a portion of the rubber bottom plate 43 may be located on the side of the rubber body 42 facing the lower mounting plate 21. The rubber vibration isolation mechanism 4 adopts a three-layer structure of rubber top plate 41, rubber body 42, and rubber bottom plate 43, which is simple in structure and has a strong load-bearing capacity. The rubber body 42 typically adopts a compression, shear, or a combination of compression and shear load-bearing methods, which can provide stable positive stiffness and damping characteristics.

[0059] The rubber base plate 43 and the lower mounting plate 21 can be installed independently, which reduces the manufacturing difficulty of the rubber base plate 43 and the lower mounting plate 21 and facilitates disassembly and maintenance. The rubber base plate 43 and the lower mounting plate 21 can be connected by bolts or other means. Alternatively, the rubber base plate 43 and the lower mounting plate 21 can be integrally molded, which reduces the number of parts, simplifies the assembly process, and improves the overall structural integrity. The different connection methods of the rubber base plate 43 and the lower mounting plate 21 provide flexibility for different production and application scenarios.

[0060] In some embodiments, the rubber body 42 can be bonded to the rubber top plate 41 and the rubber bottom plate 43 respectively through a vulcanization process. In this way, a strong chemical bond can be formed between the rubber body 42 and the top and bottom plates, preventing the rubber body 42 from peeling or slipping during use, and improving the long-term stability and reliability of the rubber vibration isolation mechanism 4.

[0061] The connecting rod 5 and the rubber top plate 41 can be threaded together for easy assembly and disassembly.

[0062] The rubber vibration isolation mechanism 4 may further include a second fastener 44 and a washer 45. The second fastener 44 can be threadedly connected to the connecting rod 5. The washer 45 can be located between the second fastener 44 and the rubber top plate 41 to lock the connecting rod 5 and the rubber top plate 41 together. This can improve the reliability of the rigid connection between the connecting rod 5 and the rubber top plate 41, and realize the effective transmission of load and vibration. At the same time, by setting the washer 45, the contact area between the second fastener 44 and the rubber top plate 41 can be increased, reducing local compressive stress and preventing damage to the surface of the rubber top plate 41.

[0063] In some embodiments, refer to Figure 5 and Figure 7The rubber top plate 41 can be T-shaped. The rubber top plate 41 may include a first baffle 411 and a second baffle 412. The first baffle 411 can be located on the side of the rubber body 42 facing the mounting mechanism 1, and the first baffle 411 can be connected to the connecting rod 5. The second baffle 412 can be located on the side of the first baffle 411 facing the rubber body 42, and at least a portion of the second baffle 412 is embedded within the rubber body 42. In this embodiment, the second baffle 412 can be located at the middle position of the first baffle 411 in the first direction X. This increases the bonding area between the rubber body 42 and the rubber top plate 41, thereby improving the bonding strength, while the embedded portion can restrict the displacement of the rubber body 42 in the horizontal direction.

[0064] The second baffle 412 may be provided with protrusions 413, which can increase the bonding area between the rubber body 42 and the second baffle 412, thereby improving the bonding strength. There may be one or more protrusions 413. In this embodiment, there are multiple protrusions 413, and both sides of the second baffle 412 in the first direction X may be provided with protrusions 413. In some other embodiments, the second baffle 412 may also be provided with recesses (not shown). The location and function of the recesses are similar to those of the protrusions 413, and will not be described again here.

[0065] The rubber base plate 43 can be U-shaped and may include a third baffle 431 and two fourth baffles 432. The two fourth baffles 432 can be located on opposite sides of the third baffle 431, and a portion of the rubber body 42 can be located between the two fourth baffles 432. In this embodiment, the two fourth baffles 432 are located on opposite sides of the third baffle 431 in the first direction X. The two fourth baffles 432 wrap around the rubber body 42 from both sides, restricting the deformation of the rubber body 42 in the horizontal direction, causing the rubber body 42 to mainly undergo compression or shear deformation in the axial direction, thereby improving the vertical load-bearing stability of the rubber vibration isolation mechanism 4.

[0066] An arc-shaped groove 421 can be provided on the side of the rubber body 42 facing the third baffle 431. The arc-shaped groove 421 can extend along the second direction Y, and its cross-section can be circular arc-shaped. A concave arc surface 422 can be formed on the side of the rubber body 42 adjacent to the fourth baffle 432. The concave arc surface 422 can be located on both sides of the rubber body 42 in the first direction X. The arc-shaped groove 421 and the concave arc surface 422 can adjust the stiffness characteristics of the rubber body 42 in different directions, optimize the mechanical performance of the vibration isolator, and make the rubber body 42 produce a uniform deformation distribution when under pressure, avoiding stress concentration, thereby improving the load-bearing capacity and fatigue life of the rubber body 42.

[0067] The rubber body 42 can be formulated from natural rubber and nitrile rubber, for example, in a weight ratio of 1:3. Natural rubber has good elasticity and mechanical properties, while nitrile rubber has excellent oil resistance and aging resistance. The combination of the two can balance elasticity and environmental resistance, making it suitable for the complex working conditions of ships. In other embodiments, the rubber body 42 can also be made of other rubber materials, such as neoprene rubber or silicone rubber, depending on the different application environments.

[0068] In some embodiments, refer to Figure 5 and Figure 6 The disc spring rubber composite high-load-bearing low-frequency vibration isolator may further include a guide bearing 7. The guide bearing 7 can be installed on the disc spring negative stiffness mechanism 3. In this embodiment, the guide bearing 7 can be installed on the disc spring base plate 32. The guide bearing 7 can be sleeved on the outer periphery of the connecting rod 5. The guide bearing 7 can provide guidance for the connecting rod 5, reducing horizontal offset during axial movement, thereby improving the motion stability and vibration isolation reliability of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. The guide bearing 7 can be a linear bearing or a sliding bearing, etc., with a smooth inner wall to reduce frictional resistance with the connecting rod 5.

[0069] The outer diameter of the connecting rod 5 is matched with the inner diameter of the guide bearing 7. It is understood that the outer diameter of the connecting rod 5 is the same as or substantially the same as the inner diameter of the guide bearing 7. In some embodiments, the outer diameter of the connecting rod 5 may be slightly smaller than the inner diameter of the guide bearing 7, i.e., a clearance fit is used between the connecting rod 5 and the guide bearing 7, with the clearance controlled between 0.01mm and 0.05mm. This allows the connecting rod 5 to slide smoothly within the guide bearing 7, reducing the likelihood of jamming or seizing between the connecting rod 5 and the guide bearing 7, while also preventing excessive clearance from causing horizontal wobbling, thus achieving axial guidance for the upper mounting mechanism 1.

[0070] The connecting rod 5 and the upper mounting mechanism 1 can be set independently, meaning the connecting rod 5 can be a separate part. This reduces the manufacturing difficulty of the connecting rod 5 and the upper mounting plate 11 of the upper mounting mechanism 1, and also facilitates disassembly and maintenance. The connecting rod 5 and the upper mounting plate 11 of the upper mounting mechanism 1 can be connected by threaded connection, welding, or riveting. Alternatively, the connecting rod 5 and the upper mounting mechanism 1 can be integrally formed, which reduces the number of parts, simplifies the assembly process, and improves the overall structural integrity. The different connection methods of the connecting rod 5 and the upper mounting mechanism 1 provide flexibility for different production and application scenarios.

[0071] In some embodiments, the number of disc springs 31 can be one or more. When there are multiple disc springs 31, the multiple disc springs 31 can be combined to form a disc spring assembly. The disc spring assembly can be combined in any of the following ways: paired assembly, overlapping assembly, or composite assembly.

[0072] By changing the number and combination of disc springs 31, the load-bearing capacity and deformation of the disc spring negative stiffness mechanism 3 can be adjusted to adapt to different application requirements. In engineering applications, the displacement and load-bearing capacity of a single disc spring 31 cannot meet the actual engineering requirements. Therefore, multiple disc springs 31 can be combined to form different disc spring assemblies. Different combination methods result in different mechanical properties of the disc spring assemblies, which can adapt to different load environments. A mating combination can increase the deformation without changing the load-bearing capacity. A stacked combination can increase the load-bearing capacity without changing the deformation. A composite combination can simultaneously increase both the load-bearing capacity and the deformation.

[0073] In some embodiments, when the disc spring assembly adopts a mating combination method, the installation directions of two adjacent disc spring plates 31 are opposite, that is, the large ends or small ends of two adjacent disc spring plates 31 are opposite each other. The deformation capacity of the disc spring assembly adopting the mating combination method is an integer multiple of the deformation capacity of a single disc spring plate 31, and its load-bearing capacity is the same as that of a single disc spring plate 31. When it is necessary to increase the working displacement range of the disc spring negative stiffness mechanism 3, a mating combination method can be adopted to arrange multiple disc spring plates 31 in a mating arrangement, thereby increasing the total displacement without increasing the load-bearing capacity.

[0074] As an example, when the disc spring assembly is assembled in a mating configuration, the load F of the disc spring assembly... i Total displacement f i Total free height H i They are: F i =F, f i =i*f,H i =i*h0, where F, f, and h0 are the load, displacement, and free height of a single disc spring 31, respectively, and i is the number of disc springs 31.

[0075] When the disc spring assembly adopts a stacked combination method, multiple disc spring plates 31 are stacked sequentially in the same installation direction, that is, the large ends of multiple disc spring plates 31 are all facing down or all facing up. The disc spring assembly using the stacked combination method can significantly increase the load-bearing capacity without increasing the deformation space. The more disc spring plates 31 are stacked, the greater the load-bearing capacity. When it is necessary to increase the load-bearing capacity of the disc spring negative stiffness mechanism 3, the stacked combination method can be used to stack and arrange multiple disc spring plates 31 to improve the load-bearing capacity without increasing the deformation space.

[0076] As an example, when the disc spring assembly is assembled in a stacked manner, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =n*F,f i =f,H i=h0+(n-1)*t, where F, f, and h0 are the load, displacement, and free height of a single disc spring 31, respectively, n is the number of disc springs 31, and t is the thickness of the disc spring 31.

[0077] When a disc spring assembly adopts a composite assembly method, multiple disc spring pieces 31 are first stacked to form a stacked group, and then the multiple stacked groups are aligned and stacked together. The load-bearing capacity of the disc spring assembly using the composite assembly method is the same as that of the disc spring assembly using the stacked assembly method, while its deformation capacity is the same as that of the disc spring assembly using the aligned assembly method. Each stacked disc spring group can be composed of disc spring pieces 31 of the same specification and number. When it is necessary to increase both load-bearing capacity and displacement simultaneously, the composite assembly method can be used, combining the advantages of both stacking and aligned assembly.

[0078] As an example, when the disc spring assembly adopts a composite combination method, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =n*F,f i =i*f,H i =i*[h0+(n-1)*t], where F, f, and h0 are the load, displacement, and free height of a single disc spring 31, respectively, n is the number of stacked groups, i is the number of paired groups, and t is the thickness of the disc spring 31.

[0079] As an example, the working principle and performance test of the disc spring rubber composite high load-bearing low-frequency vibration isolator according to the embodiments of this application are described below.

[0080] Figure 8 and Figure 9 The simulation results show the mechanical properties of the disc spring 31 in this embodiment. As a special elastic element, the disc spring 31 exhibits load-displacement characteristics different from ordinary helical springs. Under the action of an axial (i.e., third-direction Z) force F, the disc spring 31 deforms from its initial position along the third-direction Z. The relationship between the applied load and the displacement of the top of the disc spring 31 satisfies the following calculation formula: Equation (1).

[0081] Where F is the external load in N; f is the top displacement of the disc spring 31 (i.e., the compression of the disc spring 31) in m; D is the outer diameter of the disc spring 31 in m; t is the thickness of the disc spring 31 in m; h0 is the free height of the disc spring 31 in m; E and μ are the elastic modulus and Poisson's ratio of the disc spring 31 material, respectively. As an example, when the disc spring 31 is made of high-performance spring steel, the corresponding elastic modulus E = 2.06 × 10⁻⁶. 5MPa, Poisson's ratio μ=0.3. K1 and K4 are the calculation coefficients for disc spring 31. For thin disc springs without a support surface, K4=1, and K1 is expressed as: Equation (2).

[0082] Where C is the ratio of the outer diameter D to the inner diameter d of the disc spring 31, D / d.

[0083] By differentiating formula (1), the stiffness-displacement relationship of disc spring 31 can be obtained: Equation (3).

[0084] Equations (1), (2), and (3) demonstrate that the height-to-thickness ratio h0 / t of the disc spring 31 has a crucial influence on its mechanical characteristic curve. When h0 / t is in the range of 0 to 0.5, the disc spring 31 exhibits linear stiffness, and its mechanical characteristics are similar to those of a cylindrical compression helical spring. When h0 / t is approximately equal to... At this time, the disc spring 31 has a deformation region with zero stiffness, meaning that the load does not change with displacement within this deformation region. When h0 / t > When h0 / t > 31, the disc spring exhibits negative stiffness characteristics, meaning that the load decreases as the displacement increases within this deformation region. Under these conditions, the disc spring's operation is unstable, a condition that should be avoided in conventional design. However, this application utilizes this characteristic to achieve the negative stiffness effect. At this time, the disc spring 31 has a larger negative stiffness characteristic area, that is, a larger range of unstable working conditions.

[0085] As an example, the design parameters of disc spring 31 are: thickness t = 1mm; inner diameter d = 40mm; outer diameter D = 80mm; free height h0 = 6mm; height-to-thickness ratio h0 / t = 6, which is greater than... .from Figure 8 and Figure 9 It can be seen that the static finite element analysis results based on shell elements and solid elements are in good agreement with the theoretical analysis results. When the axial compression (displacement) gradually increases from 0, the load on the disc spring 31 first increases and then decreases. When the axial compression exceeds approximately 2 mm, the elastic force generated by the disc spring 31 begins to decrease, and the corresponding stiffness value begins to be less than zero, exhibiting negative stiffness characteristics. When the axial compression reaches approximately 3 mm, the negative stiffness value generated by the disc spring 31 is approximately -1500 N / mm. With continued axial compression, the absolute value of the negative stiffness generated by the disc spring 31 further increases, but due to limitations imposed by the free height h0 and the manufacturing process, the maximum compression of the disc spring 31 is approximately 4 mm. Beyond this value, the disc spring 31 is flattened, and the negative stiffness effect disappears.

[0086] Figure 10 These are the mechanical performance test results of the rubber vibration isolation mechanism 4 in this embodiment when it bears a load of 450kg. From... Figure 10 It can be seen that when only the rubber vibration isolation mechanism 4 is used, a load of 450kg will produce a displacement compression of about 6mm. The static stiffness of the rubber vibration isolation mechanism 4 is about 800N / mm, and it exhibits linear stiffness characteristics, that is, the load and displacement are basically linearly related.

[0087] Figure 11 This shows the transmissivity test results for the rubber vibration isolation mechanism 4 in this embodiment when it bears a load of 450kg. Transmissivity is an important indicator for evaluating the vibration isolation performance of disc spring rubber composite high-load low-frequency vibration isolators; the lower the transmissivity, the better the vibration isolation effect. From Figure 11 It can be seen that when only the rubber vibration isolation mechanism 4 is used, the natural frequency of a single rubber vibration isolator is 8Hz when bearing 450kg. The corresponding initial vibration isolation frequency (i.e., the frequency at which the transmissivity begins to be less than 1) is approximately 11Hz. Below 10Hz, the transmissivity is greater than 1, resulting in no vibration isolation effect. Generally, the dynamic stiffness of a rubber vibration isolator is approximately 1.2 to 1.5 times its static stiffness. In this embodiment, the formula for calculating the dynamic stiffness value of the rubber vibration isolation mechanism 4 is: k = mω², where m is 450kg, and when the natural frequency f of the rubber vibration isolation mechanism 4 is... n At 8Hz, ω = 2πf n =2π×8 Hz =16π rad / s. The calculated dynamic stiffness of the rubber vibration isolation mechanism 4 is approximately 1136000 N / m, which is approximately 1136 N / mm, and is 1.42 times the static stiffness.

[0088] Figure 12 This section presents the mechanical performance test results of the disc spring rubber composite high-load-bearing low-frequency vibration isolator in this embodiment when it bears a load of 450 kg. From... Figure 12 It can be seen that the disc spring rubber composite high-load-bearing low-frequency vibration isolator has a compression of only about 2.5 mm when bearing 450 kg, which is much smaller than the 6 mm compression of a single rubber vibration isolator. The overall force-displacement curve exhibits a nonlinear characteristic of gradually softening stiffness, that is, the stiffness gradually decreases as the load increases. The negative stiffness characteristic generated by the disc spring negative stiffness mechanism 3 can be superimposed with the positive stiffness of the rubber vibration isolation mechanism 4, which can reduce the overall stiffness of the disc spring rubber composite high-load-bearing low-frequency vibration isolator.

[0089] Figure 13 This is the transmissibility test result of the disc spring rubber composite high-load low-frequency vibration isolator in this embodiment when it bears a load of 450kg. From Figure 13It can be seen that the natural frequency of the disc spring rubber composite high-load low-frequency vibration isolator drops to about 5Hz when it bears 450kg, and it already has vibration isolation performance from 8Hz (transmissivity less than 1). Its natural frequency drops to about 60% of the natural frequency of a single rubber vibration isolator (8Hz). The dynamic stiffness of the disc spring rubber composite high-load low-frequency vibration isolator is about 400N / mm, which is about 40% of the dynamic stiffness of a single rubber vibration isolator (1136N / mm). This indicates that the disc spring negative stiffness mechanism 3 reduces the dynamic stiffness of the disc spring rubber composite high-load low-frequency vibration isolator, thereby lowering the natural frequency and achieving a lower initial vibration isolation frequency.

[0090] Figure 14 These are the mechanical performance test results of the rubber vibration isolation mechanism 4 in this embodiment when compressed by 8mm. From... Figure 14 It can be seen that the load capacity of the rubber vibration isolation mechanism when compressed by 8mm is approximately 600kg, and the static stiffness remains linear, approximately 800N / mm.

[0091] Figure 15 This is the transmissibility test result of the rubber vibration isolation mechanism 4 when compressed by 8mm in this embodiment. From... Figure 15 It can be seen that the natural frequency of the rubber vibration isolation mechanism 4 under a load of 600kg is about 7Hz, the initial vibration isolation frequency is about 10Hz, and there is no vibration isolation effect in the low frequency band below 10Hz.

[0092] Figure 16 The results show the mechanical performance test results of the disc spring rubber composite high-load-bearing low-frequency vibration isolator in this embodiment when compressed by 8mm. By adjusting the height of the disc spring base plate 32 on the support member 6, a gap difference of approximately 5mm can be created between the disc spring plate 31 and the upper mounting plate 11. Thus, within the compression range of 0mm to 5mm, the disc spring negative stiffness mechanism 3 has not yet engaged, and the disc spring rubber composite high-load-bearing low-frequency vibration isolator exhibits the linear stiffness characteristics of the rubber vibration isolation mechanism 4. When the compression exceeds 5mm, the disc spring negative stiffness mechanism 3 begins to engage, the disc spring plate 31 is compressed, and the stiffness of the disc spring rubber composite high-load-bearing low-frequency vibration isolator first increases and then decreases, exhibiting nonlinear characteristics. At a displacement compression of 8mm, the disc spring rubber composite high-load-bearing low-frequency vibration isolator can achieve a load-bearing capacity of approximately 900kg. Compared to the load-bearing capacity of approximately 600kg for a single rubber vibration isolator at 8mm compression, the load-bearing capacity of the disc spring rubber composite high-load-bearing low-frequency vibration isolator is increased by 1.5 times.

[0093] Figure 17 This is the transmissivity test result of the disc spring rubber composite high load-bearing low-frequency vibration isolator in this embodiment when compressed by 8mm. From Figure 17It can be seen that the natural frequency of the disc spring rubber composite high-load low-frequency vibration isolator is about 3.5Hz, and the initial isolation frequency is about 5Hz. Compared with the 7Hz natural frequency and 10Hz initial isolation frequency of the rubber vibration isolator, while keeping the vertical compression constant, the natural frequency of the disc spring rubber composite high-load low-frequency vibration isolator decreases by about 50%, the dynamic stiffness decreases by about 60%, and the isolation initiation frequency decreases to 5Hz.

[0094] Based on the above performance test results, the disc spring rubber composite high-load-bearing low-frequency vibration isolator of this application achieves the following technical effects by combining the negative stiffness characteristics of the high-thickness-ratio disc spring 31 with the positive stiffness characteristics of the rubber vibration isolation mechanism 4 in parallel: High load-bearing capacity: The rubber vibration isolation mechanism 4 bears the main static load, while the disc spring negative stiffness mechanism 3 provides additional load-bearing support in the later stages of compression. The load-bearing capacity of the disc spring rubber composite high-load-bearing low-frequency vibration isolator can be increased by approximately 50% compared to a single rubber vibration isolator. Low natural frequency: The negative stiffness generated by the disc spring negative stiffness mechanism 3 is superimposed with the positive stiffness of the rubber vibration isolation mechanism 4, significantly reducing the total dynamic stiffness of the disc spring rubber composite high-load-bearing low-frequency vibration isolator. The natural frequency can be reduced by 40% to 50% compared to a single rubber vibration isolator. Low initial isolation frequency: The reduction in natural frequency leads to a synchronous reduction in the initial isolation frequency. The disc spring rubber composite high-load-bearing low-frequency vibration isolator can begin to perform vibration isolation at a low frequency range of around 5Hz, effectively compensating for the insufficient vibration isolation capacity of a single rubber vibration isolator below 10Hz. With a wide range of applications, the compression gap of the disc spring negative stiffness mechanism 3 can be changed by adjusting the height of the disc spring base plate 32, thus enabling the disc spring rubber composite high-load-bearing low-frequency vibration isolator to adapt to different load conditions and vibration isolation requirements, exhibiting strong engineering adaptability. The disc spring negative stiffness mechanism 3 has a compact structure and can generate a negative stiffness value on the order of 10³ N / mm, which can effectively reduce the dynamic stiffness and natural frequency of the rubber vibration isolator. This achieves the characteristics of high load-bearing capacity and low natural frequency in the disc spring rubber composite high-load-bearing low-frequency vibration isolator, resolving the contradiction between the high load-bearing performance and low natural frequency of a single rubber vibration isolator, thereby obtaining a vibration isolation effect with a lower starting frequency and possessing vibration isolation performance in the low-frequency range of 5Hz to 10Hz.

[0095] According to the second aspect of this application, referring to Figure 18 One embodiment of this application provides an installation method for a disc spring rubber composite high-load-bearing low-frequency vibration isolator, using the disc spring rubber composite high-load-bearing low-frequency vibration isolator as described above. The installation method may include steps S1-S3.

[0096] Step S1: Connect the upper mounting mechanism to the vibration-isolated equipment.

[0097] Specifically, the transition plate 13 is connected to the vibration-isolated equipment, thereby realizing the connection between the disc spring rubber composite high-load low-frequency vibration isolator and the vibration-isolated equipment. The transition plate 13 has a pre-set through hole for docking with the installation interface of the vibration-isolated equipment. The transition plate 13 can be set according to the installation interface of different vibration-isolated equipment.

[0098] Step S2: Adjust the distance between the disc spring negative stiffness mechanism and the upper mounting mechanism.

[0099] Specifically, by adjusting the position of the disc spring base plate 32 on the support member 6, the height of the disc spring base plate 32 is changed, thereby adjusting the distance between the disc spring negative stiffness mechanism 3 and the upper mounting mechanism 1. When it is necessary to increase the installation height difference, the disc spring base plate 32 is moved downward along the support member 6. When it is necessary to decrease the installation height difference, the disc spring base plate 32 is moved upward along the support member 6. After adjustment, the first fastener 33 is used to lock the disc spring base plate 32 on both axial sides to prevent the position of the disc spring base plate 32 from changing during operation. The magnitude of the installation height difference can be determined according to the weight of the vibration-isolated equipment and the required vibration isolation performance, so that the disc spring negative stiffness mechanism 3 generates negative stiffness characteristics under appropriate axial compression, which is superimposed with the positive stiffness of the rubber vibration isolation mechanism 4.

[0100] Step S3: Connect the lower mounting mechanism to the mounting surface.

[0101] Specifically, the lower mounting plate 21 is connected to the hull base or other mounting surfaces using bolts to ensure a rigid connection between the lower mounting mechanism 2 and the mounting surface, thereby effectively transmitting loads and vibrations to the mounting surface. The lower mounting plate 21 should have corresponding mounting holes to accommodate different installation environments.

[0102] The installation method described in this application allows for precise adjustment of the working state of the disc spring negative stiffness mechanism 3, enabling the vibration isolator to achieve better negative stiffness matching under different load conditions. Adjusting the installation height difference allows the disc spring rubber composite high-load-bearing low-frequency vibration isolator to adapt to vibration-isolated equipment of varying weights, achieving performance matching without changing the model of the disc spring rubber composite high-load-bearing low-frequency vibration isolator, thereby improving its versatility and economy.

[0103] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0104] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0105] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0106] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A disc spring rubber composite high-load-bearing low-frequency vibration isolator, characterized in that, include: An upper mounting mechanism is connected to the vibration-isolated equipment. Lower installation mechanism; A disc spring negative stiffness mechanism is disposed between the upper mounting mechanism and the lower mounting mechanism; A rubber vibration isolation mechanism is provided, wherein the rubber vibration isolation mechanism and the disc spring negative stiffness mechanism are arranged in parallel between the upper mounting mechanism and the lower mounting mechanism; A connecting rod, the two ends of which are respectively connected to the upper mounting mechanism and the rubber vibration isolation mechanism; The disc spring negative stiffness mechanism includes a disc spring plate, wherein the height-to-thickness ratio h0 / t of the disc spring plate is greater than 1. Where h0 is the free height of the disc spring and t is the thickness of the disc spring, so that the disc spring produces negative stiffness characteristics after the axial compression exceeds the threshold.

2. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 1, characterized in that, The height-to-thickness ratio of the disc spring is h0 / t > .

3. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 1, characterized in that, The disc spring negative stiffness mechanism also includes a disc spring base plate, the disc spring plate is located on the side of the disc spring base plate facing the upper mounting mechanism, the disc spring rubber composite high load-bearing low frequency vibration isolator also includes a support member, the lower mounting mechanism includes a lower mounting plate, and the disc spring base plate is connected to the lower mounting plate through the support member; The disc spring base plate, the support member, and the lower mounting plate are arranged independently of each other; or, At least two of the disc spring base plate, the support member, and the lower mounting plate are integrally formed.

4. The disc spring rubber composite high load-bearing low-frequency vibration isolator according to claim 3, characterized in that, The distance between the disc spring negative stiffness mechanism and the upper mounting mechanism is adjustable so that the disc spring rubber composite high load-bearing low frequency vibration isolator produces negative stiffness characteristics under different axial compression. Specifically, the negative stiffness mechanism of the disc spring is controlled to move closer to or further away from the upper mounting mechanism; and / or, The upper mounting mechanism is controlled to move closer to or further away from the disc spring negative stiffness mechanism.

5. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 4, characterized in that, By controlling the disc spring negative stiffness mechanism to move closer to or further away from the upper mounting mechanism, the distance between the disc spring negative stiffness mechanism and the upper mounting mechanism can be adjusted by adjusting the position of the disc spring base plate on the support member. Wherein, the disc spring base plate is threadedly connected to the support member; and / or, The disc spring negative stiffness mechanism further includes a first fastener, which is threadedly connected to the support member. The first fastener is provided on both sides of the disc spring base plate in the axial direction, and the support member is connected to the disc spring base plate through the first fastener.

6. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 3, characterized in that, The upper mounting mechanism includes an upper mounting plate and an upper limit member. The upper limit member protrudes from the side of the upper mounting plate facing the disc spring base plate. The disc spring negative stiffness mechanism also includes a lower limit member. The lower limit member protrudes from the side of the disc spring base plate facing the upper mounting plate. The disc spring is located between the upper limit member and the lower limit member. Wherein, the upper limit positioner and the upper mounting plate are independently configured, or the upper limit positioner and the upper mounting plate are integrally formed; The lower limit member and the disc spring base plate are set independently of each other, or the lower limit member and the disc spring base plate are integrally formed.

7. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 6, characterized in that, The disc spring is disposed between the upper limit member and the lower limit member in a forward or reverse installation manner.

8. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 3, characterized in that, The rubber vibration isolation mechanism includes a rubber top plate, a rubber body, and a rubber bottom plate. At least a portion of the rubber top plate is located on the side of the rubber body facing the upper mounting mechanism. The connecting rod is connected to the rubber top plate. At least a portion of the rubber bottom plate is located on the side of the rubber body facing the lower mounting plate. The rubber base plate and the lower mounting plate are provided independently of each other; or, The rubber base plate and the lower mounting plate are integrally formed.

9. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 8, characterized in that, The rubber body is bonded to the rubber top plate and the rubber bottom plate respectively through a vulcanization process; and / or The connecting rod is threadedly connected to the rubber top plate; and / or The rubber vibration isolation mechanism further includes a second fastener and a washer. The second fastener is threadedly connected to the connecting rod, and the washer is located between the second fastener and the rubber top plate to lock the connecting rod to the rubber top plate.

10. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 8, characterized in that, The rubber top plate has an overall T-shaped structure. The rubber top plate includes a first baffle and a second baffle. The second baffle is located on the side of the first baffle facing the rubber body, and at least a portion of the second baffle is embedded in the rubber body. The rubber base plate has an overall U-shaped structure. The rubber base plate includes a third baffle and two fourth baffles. The two fourth baffles are located on opposite sides of the third baffle, and part of the rubber body is located between the two fourth baffles. The rubber body has an arc-shaped groove on the side facing the third baffle, and a concave arc surface is formed on the side of the rubber body adjacent to the fourth baffle.

11. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 1, characterized in that, The disc spring rubber composite high-load-bearing low-frequency vibration isolator also includes a guide bearing, which is installed on the disc spring negative stiffness mechanism and sleeved on the outer periphery of the connecting rod; and / or The connecting rod and the upper mounting mechanism are set independently of each other, or the connecting rod and the upper mounting mechanism are integrally formed.

12. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 1, characterized in that, The number of disc springs can be one or more. When the number of disc springs is multiple, the multiple disc springs are combined to form a disc spring assembly. The combination method of the disc spring assembly is any one of pairing combination, overlapping combination or composite combination.

13. The disc spring rubber composite high-load-bearing low-frequency vibration isolator according to claim 12, characterized in that, When the disc spring assembly is assembled in a mating configuration, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =F, f i =i*f,H i =i*h0, where F, f, and h0 are the load, displacement, and free height of a single disc spring, respectively, and i is the number of disc springs; When the disc spring assembly is assembled in a stacked manner, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =n*F,f i =f,H i =h0+(n-1)*t, where F, f, and h0 are the load, displacement, and free height of a single disc spring, respectively, n is the number of disc springs, and t is the thickness of the disc spring; When the disc spring assembly adopts a composite assembly method, the load F of the disc spring assembly is... i Total displacement f i Total free height H i They are: F i =n*F,f i =i*f,H i =i*[h0+(n-1)*t], where F, f, and h0 are the load, displacement, and free height of a single disc spring, respectively, n is the number of stacked groups, i is the number of paired groups, and t is the thickness of the disc spring.

14. A method for installing a disc spring rubber composite high-load-bearing low-frequency vibration isolator, characterized in that, The installation method of the disc spring rubber composite high load-bearing low-frequency vibration isolator as described in any one of claims 1 to 13 includes: Connect the upper mounting mechanism to the vibration-isolated equipment; Adjust the distance between the disc spring negative stiffness mechanism and the upper mounting mechanism; Connect the lower mounting mechanism to the mounting surface.

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