Quasi-zero stiffness vibration isolator and design method thereof

Abstract

The application provides a quasi-zero stiffness vibration isolator and a design method thereof. The quasi-zero stiffness vibration isolator comprises a base, a guide bin, a guide rail, a bearing assembly, a connecting rod assembly and a second spring. The guide bin is arranged on the base, and the axial direction of the guide bin is parallel to the up-down direction. A pressing rod is arranged in the guide bin, and a first spring is arranged between the bottom end of the pressing rod and the inner bottom wall of the guide bin. The guide rail is arranged on the base. The bearing assembly comprises a bearing plate, and the bearing plate is provided with a through hole for sliding cooperation with the guide bin, a connecting portion for fixed connection with the pressing rod, and a sliding portion for sliding cooperation with the guide rail. The connecting rod assembly comprises a first connecting rod and a second connecting rod which are rotationally connected through a rotating shaft. The second spring is connected between the guide rail and the rotating shaft. The quasi-zero stiffness vibration isolator and the design method thereof have better vibration isolation effect, can effectively avoid instability, and have higher safety factor compared with the traditional structure.

Description

Technical Field

[0001] This invention belongs to the field of vibration isolator technology, specifically relating to a quasi-zero stiffness vibration isolator and its design method. Background Technology

[0002] High-end manufacturing industries have stringent performance requirements for vibration isolation equipment, especially in fields such as aviation, aerospace, precision instruments, and special transportation. Vibration isolation equipment mainly consists of vibration isolators, which are elastic elements connecting equipment and foundations to reduce and eliminate vibrational forces transmitted from equipment to foundations and vibrations transmitted from foundations to equipment.

[0003] Traditional vibration isolators consist of a bistable negative stiffness structure connected in parallel with a linear spring. This structure inevitably uses a multistable structure during use, which poses a safety hazard in terms of the structural stability of the vibration isolator. Furthermore, under large amplitude conditions, the equilibrium point is prone to switching, resulting in structural instability (such as sudden buckling of beams and slabs), vibration isolation failure, or even amplification of amplitude, leading to safety accidents. Summary of the Invention

[0004] This invention provides a quasi-zero stiffness vibration isolator and its design method, aiming to solve the technical problem that traditional vibration isolator structures are prone to instability due to easy switching of equilibrium points, which poses safety hazards.

[0005] In a first aspect, embodiments of the present invention provide a quasi-zero stiffness vibration isolator, comprising:

[0006] Base;

[0007] A guide chamber is provided on the base. The axis of the guide chamber is parallel to the vertical direction. A pressure rod is provided inside the guide chamber. A first spring is provided between the bottom end of the pressure rod and the inner bottom wall of the guide chamber. The first spring has a preload force to make the pressure rod extend out of the top surface of the guide chamber.

[0008] A guide rail is provided on the base and extends in the vertical direction;

[0009] The support assembly includes a support plate, which has a through hole that slides with the guide chamber, a connecting part that is fixed to the pressure rod, and a sliding part that slides with the guide rail.

[0010] The linkage assembly includes a first connecting rod and a second connecting rod that are rotatably engaged by a rotating shaft. The rotating shaft is located within the vertical projection range of the support plate. The end of the first connecting rod opposite to the rotating shaft is rotatably engaged with the support plate, and the end of the second connecting rod opposite to the rotating shaft is rotatably engaged with the base.

[0011] A second spring is connected between the guide rail and the rotating shaft, and the second spring is horizontally positioned.

[0012] The solution shown in this application embodiment, compared with the prior art, involves mounting the object to be isolated on a support plate during use. Initially, the object's weight causes the support plate to shift slightly. During vertical vibration, the support plate drives the pressure rod to compress or stretch the first spring within the guide chamber. Furthermore, as the support plate moves up and down, the vertical height of the linkage assembly changes with the height of the support plate, causing horizontal displacement of the pivot between the first and second connecting rods. This horizontal displacement of the pivot pulls or compresses the second spring, achieving vibration isolation. In this quasi-zero stiffness vibration isolator, the linkage assembly connects the support plate and the base. During the up-and-down movement of the support plate, the pivot remains within the vertical projection range of the support plate. For example, when moving downwards, the pivot approaches the vertical line passing through the center of the support plate, resulting in a smaller overall volume and higher load-bearing capacity. Therefore, the vibration isolation effect is better, effectively preventing instability compared to traditional structures, and offering a higher safety factor.

[0013] In conjunction with the first aspect, in one possible implementation, the end of the rotating shaft is connected to the second spring via a mounting plate. The mounting plate has an elongated hole, one end of which engages with the end of the rotating shaft, and the other end of which is fitted with a rod. One end of the second spring is sleeved on the rod.

[0014] In conjunction with the first aspect, in one possible implementation, the bottom of the support plate is provided with a first connecting seat, and the top of the base is provided with a second connecting seat. Both the first connecting seat and the second connecting seat are provided with connecting lugs. The end of the first connecting rod facing away from the rotating shaft is rotatably engaged with the connecting lug on the first connecting seat, and the end of the second connecting rod facing away from the rotating shaft is rotatably engaged with the connecting lug on the second connecting seat.

[0015] In conjunction with the first aspect, in one possible implementation, the support plate is a circular plate, and the guide compartment and the guide rail are evenly distributed around the axial direction of the support plate.

[0016] In conjunction with the first aspect, in one possible implementation, the guide chamber is provided with a groove that runs radially through it and extends in the vertical direction;

[0017] The bearing plate is provided with a crossbar, the two ends of which are fixed to the inner wall of the through hole and are parallel to the radial direction of the through hole. The crossbar is fixed to the pressure rod and slides in cooperation with the sliding groove, and the crossbar forms the connecting part.

[0018] In conjunction with the first aspect, in one possible implementation, the load-bearing assembly further includes a flange bearing connected to the load-bearing plate, the flange bearing forming the sliding portion.

[0019] In conjunction with the first aspect, in one possible implementation, the outer peripheral surface of the support plate is spaced apart from the guide rail, and the support assembly further includes a base fixed to the support plate, with the flange bearing connected to the base and protruding from the outer periphery of the support plate.

[0020] In conjunction with the first aspect, in one possible implementation, the guide compartment further includes:

[0021] Warehouse body;

[0022] A storage base is located at the bottom of the storage body and is connected to the base;

[0023] A fixing plate is pressed onto the top of the first spring, and the fixing plate is fixedly connected to the bottom end of the pressure rod;

[0024] The first spring abuts between the fixed plate and the housing.

[0025] In conjunction with the first aspect, in one possible implementation, the support plate has a weight-reducing hole in the middle, and the support plate also has a cross arm located in the weight-reducing hole, the cross arm being fixedly connected to the inner wall of the weight-reducing hole to support the isolated object.

[0026] Secondly, embodiments of the present invention also provide a design method for a quasi-zero stiffness vibration isolator, used to verify the aforementioned quasi-zero stiffness vibration isolator, comprising the following steps:

[0027] S10: Fix the object to be isolated to the bearing plate, and calculate the offset Δ0 and the stiffness coefficient of the first spring.

[0028]

[0029] Where, P = 2l²sinθ - Δ0, l2 is any positive number that is not zero, l2 is the length of the second connecting rod, and θ is the angle between the second connecting rod and the base in the initial state.

[0030] S20: Substitute the Δ0 calculated in S10 into the following formula to calculate the actual stiffness coefficient k1 of the first spring and the actual stiffness coefficient k0 of the second spring.

[0031]

[0032]

[0033] Where, m a Let g be the mass of the isolated object, and g be the acceleration due to gravity.

[0034] S30: Replace k1 in step S20 with k1 in step S10. In step S20, k0 replaces k0 in step S10. And calculate according to the formula in step S10 to obtain like If k0 and k1 meet the requirements, the first and second springs of the corresponding specifications are selected based on the values ​​of k0 and k1. Attached Figure Description

[0035] Figure 1 This is a three-dimensional structural schematic diagram of a quasi-zero stiffness vibration isolator provided in an embodiment of the present invention;

[0036] Figure 2 This is a schematic cross-sectional view of the quasi-zero stiffness vibration isolator provided in an embodiment of the present invention.

[0037] Figure 3 This is a three-dimensional structural diagram of the support plate used in an embodiment of the present invention;

[0038] Figure 4 This is a three-dimensional schematic diagram of the guide compartment used in an embodiment of the present invention.

[0039] Explanation of reference numerals in the attached figures:

[0040] 10-Base;

[0041] 20-Guide chamber; 21-Pressure rod; 22-First spring; 23-Slide groove; 24-Bug body; 25-Bug base; 26-Fixing plate;

[0042] 30-Guide rail;

[0043] 40-Bearing component; 41-Bearing plate; 42-Through hole; 43-Cross bar; 44-Flange bearing; 45-Base; 46-Weight reduction hole; 47-Cross arm;

[0044] 50 - Linkage assembly; 51 - First connecting rod; 52 - Second connecting rod; 53 - Rotating shaft; 54 - First connecting seat; 55 - Second connecting seat; 56 - Connecting lug;

[0045] 60 - Second spring;

[0046] 70-Hanging plate; 71-Oblong hole; 72-Plug. Detailed Implementation

[0047] To make the technical problems to be solved, the technical solutions, and the beneficial effects of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and are not intended to limit the present invention.

[0048] Please refer to the following: Figures 1 to 4 The quasi-zero stiffness vibration isolator provided by the present invention will now be described. The quasi-zero stiffness vibration isolator includes a base 10, a guide chamber 20, a guide rail 30, a load-bearing assembly 40, a connecting rod assembly 50, and a second spring 60. The guide chamber 20 is disposed on the base 10, and its axial direction is parallel to the vertical direction. A pressure rod 21 is provided inside the guide chamber 20. A first spring 22 is provided between the bottom end of the pressure rod 21 and the inner bottom wall of the guide chamber 20. The first spring 22 has a preload force to cause the pressure rod 21 to extend beyond the top surface of the guide chamber 20. The guide rail 30 is disposed on the base 10 and extends vertically. The load-bearing assembly 40 includes a load-bearing plate 41, on which a... The system has a through hole 42 that slides with the guide chamber 20, a connecting part that is fixed to the pressure rod 21, and a sliding part that slides with the guide rail 30; the connecting rod assembly 50 includes a first connecting rod 51 and a second connecting rod 52 that are rotatably engaged with a rotating shaft 53. The rotating shaft 53 is located within the vertical projection range of the support plate 41. The end of the first connecting rod 51 that is away from the rotating shaft 53 is rotatably engaged with the support plate 41, and the end of the second connecting rod 52 that is away from the rotating shaft 53 is rotatably engaged with the base 10; a second spring 60 is connected between the guide rail 30 and the rotating shaft 53, and the second spring 60 is horizontally arranged.

[0049] Compared with the prior art, the quasi-zero stiffness vibration isolator provided in this embodiment, when in use, the object to be isolated is installed on the support plate 41. When the object is initially placed, the support plate 41 undergoes initial displacement due to its own weight. During the up and down amplitude process, the support plate 41 drives the pressure rod 21 to squeeze or stretch the first spring 22 in the guide chamber 20. As the support plate 41 moves up and down, the vertical height of the connecting rod assembly 50 changes with the height of the support plate 41. The rotating shaft 53 between the first connecting rod 51 and the second connecting rod 52 undergoes horizontal displacement. When the rotating shaft 53 is horizontally displaced, it pulls or squeezes the second spring 60, thereby achieving the vibration isolation effect. In the quasi-zero stiffness vibration isolator of the present invention, the connecting rod assembly 50 is connected between the bearing plate 41 and the base 10. During the up-and-down movement of the bearing plate 41, the rotating shaft 53 is always within the vertical projection range of the bearing plate 41. For example, when it changes downward, the rotating shaft 53 is close to the vertical line passing through the center of the bearing plate 41. At this time, the overall volume is reduced and the load-bearing capacity is higher, so the vibration isolation effect is better. Compared with the traditional structure, it can effectively avoid the occurrence of instability and has a higher safety factor.

[0050] In some embodiments, a specific connection method between the aforementioned rotating shaft 53 and the second spring 60 can be as follows: Figures 1 to 2 The structure shown. See also Figures 1 to 2The shaft 53 is connected to the second spring 60 via a mounting plate 70. The mounting plate 70 has an elongated hole 71, one end of which mates with the shaft 53, and the other end of which is fitted with a rod 72. One end of the second spring 60 is fitted onto the rod 72. Both ends of the shaft 53 are equipped with mounting plates 70. The mounting plates 70 can be first installed with the second spring 60, and then the elongated hole 71 of the mounting plate 70 can be directly fitted onto the outer circumference of the shaft 53. Subsequently, it can be fixed by engaging a limiting block or screwing a nut at the end of the shaft 53. This structure is convenient for installation and operation.

[0051] It is easy to understand that the insertion rod 72 passes through the elongated hole 71 on the two mounting plates 70, and the opposite ends of the insertion rod 72 can be connected to fastening nuts to achieve fixation.

[0052] In some embodiments, one installation method for the aforementioned linkage assembly 50 may be as follows: Figures 1 to 2 The structure shown. See also Figures 1 to 2 The bottom of the support plate 41 is provided with a first connecting seat 54, and the top of the base 10 is provided with a second connecting seat 55. Both the first connecting seat 54 and the second connecting seat 55 are provided with connecting ear plates 56. The end of the first connecting rod 51 facing away from the rotating shaft 53 is rotatably engaged with the connecting ear plate 56 on the first connecting seat 54, and the end of the second connecting rod 52 facing away from the rotating shaft 53 is rotatably engaged with the connecting ear plate 56 on the second connecting seat 55. The connecting ear plates 56 can be used to easily position the first connecting rod 51 and the second connecting rod 52. Both ends of the first connecting rod 51 and both ends of the second connecting rod 52 are provided with corresponding mounting holes. The mounting holes on the first connecting rod 51 or the second connecting rod 52 are aligned with the holes on the connecting ear plates 56, and can be connected by pins, bolts, etc. The operation is convenient, the structure is simple, and the use is reliable.

[0053] Specifically, the base 10 needs to be equipped with structures such as the second connecting seat 55, the guide rail 30, and the guide compartment 20. Corresponding holes can be pre-drilled on the base 10. When installing the second connecting seat 55, the guide rail 30, and the guide compartment 20, simply align them with the corresponding holes to achieve quick assembly.

[0054] In some embodiments, a specific implementation of the aforementioned carrier plate 41 may employ, as follows: Figure 1 and Figure 3 The structure shown. See also Figure 1 and Figure 3The bearing plate 41 is a circular plate, and the guide chamber 20 and guide rail 30 are evenly distributed around the axial direction of the bearing plate 41. Both the guide chamber 20 and the guide rail 30 can provide guidance during the up-and-down movement of the bearing plate 41. The even distribution of the guide chamber 20 and the guide rail 30 around the axial direction of the bearing plate 41 can improve the stability of the bearing plate 41 during up-and-down movement, prevent the plate surface of the bearing plate 41 from tilting, ensure the uniform distribution of force, and improve the vibration isolation effect.

[0055] For example, when there are four guide chambers 20 and four guide rails 30, the four guide chambers 20 and four guide rails 30 can be arranged alternately; when there are two guide chambers 20 and four guide rails 30, a guide chamber 20 is provided between every two guide rails 30. This distribution can make the force of the first spring 22 acting on the bottom of the bearing plate 41 evenly distributed, further improving the vibration isolation effect.

[0056] In some embodiments, a specific cooperation method between the guide chamber 20 and the support plate 41 can be as follows: Figure 1 , Figure 2 and Figure 4 The structure shown. See also Figure 1 , Figure 2 and Figure 4 The guide chamber 20 is provided with a radially penetrating groove 23 extending vertically. The support plate 41 is provided with a crossbar 43, both ends of which are fixed to the inner wall of the through hole 42 and parallel to the radial direction of the through hole 42. The crossbar 43 is fixed to the pressure rod 21 and slidably engages with the groove 23, forming a connecting part. The through hole 42 and the guide chamber 20 are in a mating relationship, and the crossbar 43 and the groove 23 are in a mating relationship. These two vertically slidingly engaging components further improve the stability of the vertical movement of the support plate 41. Furthermore, when installing the support plate 41, adjusting the crossbar 43 on the support plate 41 to correspond with the groove 23 can prevent mistaken identification and facilitate assembly and disassembly.

[0057] In some embodiments, an improved implementation of the above-described carrier component 40 may employ, as follows: Figure 1 and Figure 3 The structure shown. See also Figure 1 and Figure 3 The support assembly 40 also includes a flange bearing 44 connected to the support plate 41, and the flange bearing 44 forms a sliding part. The flange bearing 44 in the support assembly 40 cooperates with the guide rail 30. During the up and down movement of the support plate 41, the friction between the flange bearing 44 and the guide rail 30 is reduced, which reduces the wear on the guide rail 30, extends the service life of the guide rail 30, and reduces noise.

[0058] In some embodiments, a specific installation method for the flange bearing 44 described above can be as follows: Figure 1 The structure shown. See also Figure 1The outer periphery of the support plate 41 is spaced apart from the guide rail 30. The support assembly 40 also includes a base 45 fixed on the support plate 41, and a flange bearing 44 connected to the base 45 and protruding from the outer periphery of the support plate 41. When the surface of the support plate 41 is large enough, holes can be directly drilled in the support plate 41 for the guide rail 30 to pass through. However, in this embodiment, the support plate 41 is selected with a smaller surface area, which does not exceed the guide rail 30. Then, the base 45 is installed on the support plate 41, and the flange bearing 44 is installed on the base 45 (at this time, the flange bearing 44 is indirectly connected to the support plate 41). This embodiment can save the material of the support plate 41 and reduce the cost.

[0059] In some embodiments, a specific implementation of the guide chamber 20 described above may adopt the following approach: Figure 2 and Figure 4 The structure shown. See also Figure 2 and Figure 4 The guide chamber 20 also includes a chamber body 24, a chamber base 25, and a fixing plate 26. The chamber base 25 is located at the bottom of the chamber body 24 and is connected to the base 10. The fixing plate 26 is pressed against the top of the first spring 22 and is fixedly connected to the bottom end of the pressure rod 21. The first spring 22 abuts against the fixing plate 26 and the chamber base 25. The first spring 22 is located inside the chamber body 24, and the inner wall of the chamber body 24 can provide guidance for the compression and reset of the first spring 22 to prevent the first spring 22 from tilting. During the downward movement of the pressure rod 21, the pressure rod 21 drives the fixing plate 26 to squeeze the first spring 22, or the first spring 22 resets and lifts the fixing plate 26. The contact area between the fixing plate 26 and the top of the first spring 22 is large, which facilitates the compression of the first spring 22.

[0060] It should be noted that the lower end of the pressure rod 21 is screwed to the fixing plate 26, and the upper end of the pressure rod 21 is screwed to the crossbar 43 to achieve connection.

[0061] In some embodiments, an improved implementation of the aforementioned carrier plate 41 may employ, as follows: Figure 3 The structure shown. See also Figure 3 The bearing plate 41 has a weight-reducing hole 46 in the middle, and a cross arm 47 located inside the weight-reducing hole 46 is also provided on the bearing plate 41. The cross arm 47 is fixed to the inner wall of the weight-reducing hole 46 to support the object to be isolated. By supporting the object to be isolated through the cross arm 47, the space between the cross arms 47 can reduce the weight of the bearing plate 41 while ensuring the support strength, thereby reducing the self-weight of the overall quasi-zero stiffness vibration isolator, making it more convenient to use and easier to install in the required working conditions.

[0062] Based on the same inventive concept, this application also provides a design method for a quasi-zero stiffness vibration isolator, comprising the following steps:

[0063] S10: Fix the object to be isolated to the bearing plate 41, and calculate the offset Δ0 and the stiffness coefficient of the first spring.

[0064]

[0065] Where, P = 2l²sinθ - Δ0, l2 is any positive number that is not zero, l2 is the length of the second connecting rod 52, and θ is the angle between the second connecting rod 52 and the base 10 in the initial state.

[0066] S20: Substitute the Δ0 calculated in S10 into the following formula to calculate the actual stiffness coefficient k1 of the first spring 22 and the actual stiffness coefficient k0 of the second spring 60.

[0067]

[0068]

[0069] Where, m a Let g be the mass of the isolated object, and g be the acceleration due to gravity.

[0070] S30: Replace k1 in step S20 with k1 in step S10. In step S20, k0 replaces the k0 in step S10. And calculate according to the formula in step S10 to obtain like If k0 and k1 meet the requirements, the first and second springs of the corresponding specifications are selected based on the values ​​of k0 and k1.

[0071] It should be noted that, It does not mean that they are completely equal; they are equal within 4 decimal places.

[0072] The quasi-zero stiffness vibration isolator design method provided in this embodiment, compared with the prior art, has three unknowns in step S10 after the quasi-zero stiffness vibration isolator is assembled: △0 and Since the value of △0 is extremely small, when taking 4 decimal places, The change in will not cause a change in Δ0, but Changes will cause The change is such that, therefore, in step S10, one can be arbitrarily chosen. The values ​​of Δ0 and Δ0 are calculated. Then, it is stated that △0 is the correct value. Since the values ​​are incorrect, the Δ0 obtained in step S10 is substituted into the actual k1 and k0 to recalculate. Then, k1 and k0 are verified in step S30. If the verification meets the conditions, it indicates that k1 and k0 are accurate values, and a first spring 22 with a stiffness coefficient of k1 and a second spring 60 with a stiffness coefficient of k0 can be selected to complete the design process. This design process allows for accurate and convenient calculation of the stiffness coefficients of the first spring 22 and the second spring 60, facilitating their selection in processing and manufacturing. Verification ensures the vibration isolation effect of the quasi-zero stiffness isolator.

[0073] It should be noted that the top end of the second connecting rod 52 is connected to the bottom end of the second connecting seat 55, and the second connecting rod 52 needs to have two corresponding holes. In this case, l2 is the distance between the two holes on the second connecting rod 52. When the second connecting rod 52 is connected by other means of rotation (i.e., it does not have holes), then l2 is the length of the second connecting rod 52.

[0074] In some embodiments, the vertical displacement y of the bearing plate 41 and the lateral displacement x of the rotating shaft 53 need to satisfy the following relationship:

[0075]

[0076] Where l2 is the length of the second connecting rod 52, and θ is the angle between the second connecting rod 52 and the base 10 in the initial state.

[0077] In some embodiments, the vertical displacement y of the bearing plate 41 described above also needs to satisfy the following relationship:

[0078]

[0079]

[0080] Where l1 is the distance between the two diagonally opposite second connecting seats.

[0081] The elastic restoring force of a quasi-zero stiffness vibration isolator must satisfy the following formula:

[0082]

[0083] equivalent stiffness The following formula should be satisfied:

[0084]

[0085] By using the above formula to design a quasi-zero stiffness isolator, the quasi-zero stiffness isolator can obtain an ideal quasi-stiffness displacement range under any load.

[0086] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A quasi-zero stiffness vibration isolator, characterized in that, include: Base; A guide chamber is provided on the base. The axis of the guide chamber is parallel to the vertical direction. A pressure rod is provided inside the guide chamber. A first spring is provided between the bottom end of the pressure rod and the inner bottom wall of the guide chamber. The first spring has a preload force to make the pressure rod extend out of the top surface of the guide chamber. A guide rail is provided on the base and extends in the vertical direction; The support assembly includes a support plate, which has a through hole that slides with the guide chamber, a connecting part that is fixed to the pressure rod, and a sliding part that slides with the guide rail. The linkage assembly includes a first connecting rod and a second connecting rod that are rotatably engaged by a rotating shaft. The rotating shaft is located within the vertical projection range of the support plate. The end of the first connecting rod opposite to the rotating shaft is rotatably engaged with the support plate, and the end of the second connecting rod opposite to the rotating shaft is rotatably engaged with the base. A second spring is connected between the guide rail and the rotating shaft, and the second spring is horizontally positioned. The guide chamber is provided with a radially penetrating groove that extends vertically. The bearing plate is provided with a crossbar, the two ends of which are fixed to the inner wall of the through hole and are parallel to the radial direction of the through hole. The crossbar is fixed to the pressure rod and slides with the sliding groove, and the crossbar forms the connecting part. Among them, the elastic restoring force of the quasi-zero stiffness vibration isolator The following formula must be satisfied: in, Let x be the stiffness coefficient of the second spring, and x be the lateral displacement of the shaft. y is the angle between the second connecting rod and the base in the initial state, and y is the vertical displacement of the bearing plate. The length of the second connecting rod. is the stiffness coefficient of the first spring.

2. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The end of the rotating shaft is connected to the second spring via a mounting plate. The mounting plate has an elongated hole, one end of which engages with the end of the rotating shaft, and the other end of which is fitted with a rod. One end of the second spring is sleeved on the rod.

3. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The bottom of the support plate is provided with a first connecting seat, and the top of the base is provided with a second connecting seat. Both the first connecting seat and the second connecting seat are provided with connecting lugs. The end of the first connecting rod facing away from the rotating shaft is rotatably engaged with the connecting lug on the first connecting seat, and the end of the second connecting rod facing away from the rotating shaft is rotatably engaged with the connecting lug on the second connecting seat.

4. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The support plate is a circular plate, and the guide compartment and the guide rail are evenly distributed around the axial direction of the support plate.

5. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The load-bearing assembly further includes a flange bearing connected to the load-bearing plate, the flange bearing forming the sliding portion.

6. The quasi-zero stiffness vibration isolator as described in claim 5, characterized in that, The outer peripheral surface of the bearing plate is spaced apart from the guide rail. The bearing assembly also includes a base fixed on the bearing plate, and the flange bearing is connected to the base and protrudes from the outer periphery of the bearing plate.

7. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The guide compartment also includes: Warehouse body; A storage base is located at the bottom of the storage body and is connected to the base; A fixing plate is pressed onto the top of the first spring, and the fixing plate is fixedly connected to the bottom end of the pressure rod; The first spring abuts between the fixed plate and the housing.

8. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The bearing plate has a weight-reducing hole in the middle and a cross arm located in the weight-reducing hole. The cross arm is fixed to the inner wall of the weight-reducing hole to support the isolated object.

9. A design method for a quasi-zero stiffness vibration isolator, characterized in that, The design of a quasi-zero stiffness vibration isolator as described in any one of claims 1-8 includes the following steps: S10: Fix the object to be isolated to the bearing plate and calculate the offset. and the stiffness coefficient of the first spring : in, , , , Let be any positive number that is not zero. The length of the second connecting rod. The angle between the second connecting rod and the base in the initial state; S20: The result calculated in S10 Substitute the values ​​into the following formula to calculate the actual stiffness coefficient of the first spring. and the actual stiffness coefficient of the second spring in, Let g be the mass of the isolated object, and g be the acceleration due to gravity. S30: The steps in S20... Replace the S10 step In step S20 Replace the S10 step And calculate according to the formula in step S10 to obtain ,like but and Meets the requirements, and The values ​​are selected from the first and second springs of the corresponding specifications.

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