Spring assembly with damping characteristic and vibration reduction and isolation device

Abstract

The invention relates to a spring assembly with a damping characteristic and a vibration reduction and isolation device. The spring assembly with the damping characteristic at least comprises a first spiral spring and a second spiral spring, and the first spiral spring and the second spiral spring are arranged in a parallel connection mode, a series connection mode or a series-parallel connection mixed mode. The yield strength of the material of the first spiral spring is larger than or equal to 800 MPa. The yield strength of the material of the second spiral spring is larger than or equal to 250 MPa, the loss factor of the material under the conditions of the room temperature and the 4 * 10 <-4 > strain amplitude is larger than 2.0%, and the maximum static loss factor of the second spiral spring is not smaller than 6.0%. The vibration reduction and isolation device is composed of a spring assembly with the damping characteristic, a top base assembly, a bottom base assembly, an adjusting bolt assembly and a limiting ring. The vibration reduction and isolation device at least has the vertical variable stiffness characteristic, and the maximum static loss factor of the vibration reduction and isolation device is not smaller than 1.5%. The vibration reduction and isolation device is applied to the fields of buildings, bridges, mechanical supports and the like, and the effects of energy dissipation, vibration reduction and vibration isolation are achieved.

Description

Technical Field

[0001] The invention belongs to the technical field of vibration control and relates to a spring component with damping characteristics and a vibration reduction and isolation device. Background Art

[0002] Coil springs are often used to isolate mechanical vibrations to reduce the impact of structural vibrations on supports or the impact of support vibrations on structures. Here, structure is a general term for buildings, bridges, motors, mechanical structures, etc.; support is a general term for the foundation on which the structure is placed (such as foundation, etc.). Both structure and support can be excitation vibration sources. When subjected to excitation vibration, the coil spring will undergo tensile / compressive elastic deformation, absorb the vibration energy and store it inside itself (forming elastic potential energy); when the vibration stops, the spring will rebound to its initial state and release the stored elastic potential energy. Therefore, in a strict sense, the coil spring is an element that stores and releases elastic potential energy, and it can only play a role in instantaneous vibration relief. However, since the vibration energy cannot be dissipated in time, the structure will continue to oscillate for a long period of time or the supporting foundation will be affected by structural vibration for a long time.

[0003] In order to control and suppress mechanical vibration and maintain the stability of the structure (reduce the vibration amplitude of the structure), it is usually necessary to use springs and dampers (or damping units) in coordination, using the damper to consume vibration energy, thereby suppressing the continuous oscillation caused by the rebound of the spring after absorbing vibration. The combination of springs and dampers constitutes a vibration reduction and isolation device. The commonly used damper at present is a viscous damper (also known as a damping cylinder), which hinders the propagation of vibration through the compression deformation of the damping medium (viscous damping fluid) inside the damper, and converts mechanical energy into heat energy to suppress vibration. However, viscous dampers have disadvantages such as the risk of damping fluid leakage, large installation space required, and high maintenance costs. Eddy current damper is another device that dissipates external vibration energy. It forms damping through the eddy currents generated by the relative movement of the conductor plate (copper plate) between two groups of permanent magnets. At the same time, the eddy currents are converted into heat energy due to the resistance in the conductor plate and dissipated. However, due to the high material cost of the conductor plate and the permanent magnet, the cost and maintenance cost of the eddy current damper itself are also correspondingly high. In addition, the above-mentioned viscous damper and eddy current damper themselves cannot provide stiffness, so the stiffness of the vibration reduction and isolation device formed by the spring and damper comes from the spring element (usually more springs are required to achieve the required stiffness). In addition, in many engineering application scenarios, the vibration excitation frequency range is wide. In order to give full play to the vibration isolation effect, the vibration reduction and isolation device is usually required to have a variable stiffness characteristic (stiffness changes with the vibration displacement amplitude). In comparison, ordinary cylindrical helical steel springs have a fixed stiffness (stiffness does not change with the vibration displacement amplitude). Here, stiffness usually refers to the vertical (or axial) stiffness of the spring.

[0004] In view of the above technical problems and practical application needs, it is urgent to develop a new vibration reduction and isolation device with the required stiffness and damping performance, which can simultaneously achieve the effect of isolating vibration and reducing the amplitude of structural vibration. The new vibration reduction and isolation device developed can effectively overcome the unfavorable properties of the combination of traditional springs and viscous dampers or springs and eddy current dampers, and can achieve variable and adjustable stiffness of the vibration reduction and isolation device (stiffness changes with the vibration displacement amplitude). The new vibration reduction and isolation device developed is used in the fields of buildings, bridges, mechanical supports, etc., and plays the role of energy dissipation, vibration reduction and vibration isolation. Summary of the invention

[0005] The present invention provides a novel spring vibration reduction and isolation device to solve the technical problems introduced in the above background technology: traditional springs can only play the role of instantaneous buffering of mechanical vibration and vibration isolation, but cannot reduce the energy of mechanical vibration; the combination of traditional springs and dampers requires a large installation space, has high cost and maintenance cost, and the viscous damper has the risk of damping fluid leakage and other unfavorable properties; the stiffness of traditional coil spring vibration isolation devices has a fixed value and cannot be changed.

[0006] The first aspect of the present invention provides a spring assembly with damping characteristics, the second aspect provides a vibration reduction and isolation device composed of the spring assembly with damping characteristics, and the third aspect provides an application of the vibration reduction and isolation device.

[0007] The purpose of the present invention can be achieved through the following technical solutions.

[0008] The present invention first provides a spring assembly with damping characteristics.

[0009] The spring assembly with damping characteristics is used in a vibration reduction and isolation device to isolate vibration and reduce the transmission of vibration energy. The characteristics are:

[0010] The spring assembly with damping characteristics comprises at least a first coil spring and a second coil spring, wherein the central axes of the first coil spring and the second coil spring are parallel to or coincide with each other;

[0011] The mechanical properties of the material of the first coil spring meet the following requirements: yield strength ≥ 800 MPa, tensile strength ≥ 1000 MPa, elongation after fracture ≥ 6%, and section shrinkage ≥ 20%;

[0012] The mechanical properties of the material of the second coil spring meet the following requirements: yield strength ≥ 250 MPa, tensile strength ≥ 350 MPa, elongation after fracture ≥ 14%, and cross-sectional shrinkage ≥ 20%; the damping properties of the material of the second coil spring meet the following requirements: -4 The loss factor under strain amplitude conditions is greater than 2.0%, and the loss factor increases with the increase of elastic strain amplitude;

[0013] The maximum static loss factor of the second coil spring is not less than 6.0%; the second coil spring has at least a vertical variable stiffness characteristic;

[0014] In the spring assembly with damping characteristics, the first coil spring and the second coil spring are arranged in parallel, in series, or in a combination of series and parallel;

[0015] The maximum static loss factor of the spring component with damping characteristics is not less than 1.5%, and the spring component with damping characteristics has at least a vertical variable stiffness characteristic.

[0016] The spring assembly with damping characteristics of the present invention comprises a first coil spring and a second coil spring. The two types of coil springs can be tension springs or compression springs; the cross-sectional shape of the wire used to make the coil springs can be circular, square, or the like.

[0017] Since the material of the first coil spring has high strength (yield strength ≥ 800MPa, tensile strength ≥ 1000MPa), the first coil spring plays the main role of bearing, providing rigidity and isolating vibration. The present invention stipulates that the elongation after fracture of the first coil spring material is ≥ 6% and the cross-sectional contraction rate is ≥ 20%, the purpose is to ensure that the wire with the above ductility can be smoothly wound into a coil spring and the first coil spring exhibits good fatigue resistance during use.

[0018] The material of the second coil spring has appropriate strength (yield strength ≥ 250MPa, tensile strength ≥ 350MPa). The second coil spring mainly provides rigidity and vibration isolation, and can also play a certain load-bearing role. The elongation after fracture of the second coil spring material is limited to ≥ 14% and the cross-sectional shrinkage rate is ≥ 20%, in order to ensure that the wire with the above ductility can be smoothly wound into a coil spring and that the second coil spring exhibits good fatigue resistance during use.

[0019] More importantly, the material of the second coil spring has good damping properties, which enables the spring assembly to exhibit damping effect. The present invention stipulates that the damping performance of the material of the second coil spring satisfies: -4 Under the strain amplitude condition, the loss factor is greater than 2.0%. In addition, the loss factor of the second coil spring material in the present invention increases with the increase of the elastic strain amplitude (ie, it is positively correlated), such as Figure 1 In other words, as the elastic strain amplitude increases, the second coil spring and the spring assembly including the second coil spring exhibit better damping characteristics, and the effect of dissipating vibration energy is more significant. It should be pointed out here that the loss factor of the second coil spring material is also closely related to the chemical composition of the second coil spring material.

[0020] The present invention further stipulates that: the maximum static loss factor of the second coil spring is not less than 6.0%; and the second coil spring has a variable stiffness characteristic. The maximum static loss factor of the second coil spring is stipulated to be not less than 6.0% in order to ensure that the spring assembly and the vibration isolation device have good damping characteristics. In addition, the second coil spring has a vertical variable stiffness characteristic, which is significantly effective in isolating excitation vibrations in a wide frequency range; relatively speaking, traditional coil springs with fixed stiffness are only effective in isolating excitation vibrations of a specific frequency. In actual application scenarios, excitation vibrations often have wide-frequency characteristics, so the variable stiffness spring and variable stiffness spring vibration isolation device of the present invention are more effective in isolating actual vibrations. The vertical variable stiffness characteristics of the second coil spring mentioned here are derived from the inherent characteristics of the material of the second coil spring (the damping characteristics of the material).

[0021] The present invention defines the loss factor of the spring material, the static loss factor of the spring, and the maximum static loss factor of the spring respectively. The loss factor of the spring material is an inherent property of the material, and it is an important parameter to measure the damping performance of the material; from the energy point of view, the material loss factor is defined as the ratio of the energy dissipated per cycle of the material under the action of the alternating force field to the maximum stored energy in one cycle, reflecting the energy loss of the material during the force-bearing process; the measurement of the material loss factor is carried out in accordance with national standards or international standards. In the present invention, the loss factor of the second coil spring material shows a positive correlation with the elastic vibration strain amplitude. The static loss factor of the spring is defined as the ratio of the energy lost by the spring during a loading-unloading cycle to the maximum stored energy; the static loss factor of the spring is closely related to the loss factor of the spring material and is also related to the geometric shape and size of the spring. In the present invention, since the loss factor of the second coil spring material shows a positive correlation with the vibration elastic strain, accordingly, the static loss factor of the second coil spring shows a positive correlation with the deformation displacement amplitude of the spring. It should be pointed out that in a vertical loading-unloading cycle of the spring, the starting point of loading should coincide with the end point of unloading. The static loss factor of the spring under the condition of the limit deformation displacement amplitude is the maximum static loss factor of the spring; when the deformation displacement applied to the spring exceeds the limit displacement amplitude, the spring cannot return to the starting point of loading after unloading (that is, the spring will retain permanent residual deformation). In the normal deformation working state of the spring, relative to the initial equilibrium position of the spring, the deformation displacement amplitude of the spring is between 0 and the limit deformation displacement amplitude. In comparison, the material of the first coil spring and the first coil spring in the present invention usually do not have damping characteristics or the damping characteristics can be ignored, so the static loss factor of the first coil spring can usually be considered to be 0.

[0022] Figure 2The figure shows a schematic diagram of the force-displacement curve (i.e., hysteresis curve) of the second coil spring with damping characteristics in a vertical loading-unloading cycle, wherein the arc segment OCA is the loading force-displacement curve in one cycle, the arc segment ADO is the unloading force-displacement curve, and the length of the line segment OB represents the displacement amplitude in one cycle. Since the spring material has damping characteristics, the loading arc segment OCA and the unloading arc segment ADO of the spring do not overlap. Figure 2 It can be seen that the area enclosed by the arc segments OCA and ADO (i.e., the envelope area of ​​the hysteresis curve) is the energy loss (ΔW) during a loading-unloading cycle, and the area of ​​the triangle OAB is the maximum stored energy (U). According to the definition, the static loss factor (η) of the spring is: η = ΔW / πU, where π is the pi constant (3.1415).

[0023] The present invention defines the vertical stiffness of a spring and the vertical average equivalent stiffness of a spring with damping characteristics, respectively. The vertical stiffness of a spring refers to the ratio of the load increment to the deformation displacement increment when the spring undergoes vertical elastic deformation, that is, the load required to produce a unit deformation displacement. In the present invention, the material of the first coil spring usually does not have damping characteristics or the damping characteristics can be ignored. In a vertical loading-unloading cycle of the first coil spring (when it is a cylindrical coil spring), the force-displacement relationship between the loading section and the unloading section is linear, and the loading section and the unloading section coincide. The slope of the force-displacement line is the vertical stiffness of the first coil spring (denoted as K), which is a fixed value, such as Figure 3 For example. The present invention does not exclude that the first coil spring also has a variable stiffness characteristic because the spring material has a damping characteristic. For the second coil spring (shaped like a cylindrical coil spring), Figure 2 As shown in the figure, due to the damping characteristics of the material, in a vertical loading-unloading cycle, the force-displacement of the loading segment and the unloading segment are not linearly related, and the arc line OCA of the loading segment does not coincide with the arc line ADO of the unloading segment, so the vertical stiffness of the second coil spring is variable; the slope of the straight line segment OA is defined as the vertical average equivalent stiffness of the spring in a loading-unloading cycle under the loading displacement amplitude (also called secant stiffness, denoted as ). Generally, the vertical average equivalent stiffness of the second coil spring varies with the spring deformation displacement amplitude.

[0024] Figure 4 The force-displacement curve of a second coil spring under different deformation displacement amplitudes in vertical loading-unloading cycles is exemplified (the coil spring is a cylindrical coil spring). The static loss factor and vertical average equivalent stiffness of the second coil spring under different deformation displacement amplitudes can be obtained from the cyclic force-displacement curve. Figure 4 The force-displacement curves of vertical loading-unloading cycles under three deformation-displacement amplitudes are given in Fig. Figure 5The figure shows the relationship between the static loss factor of the second coil spring and the deformation displacement amplitude. It can be seen from the figure that the static loss factor of the second coil spring increases with the increase of the deformation displacement amplitude, and the maximum loss factor of the second coil spring exceeds 6%. Figure 6 The figure shows the relationship between the vertical average equivalent stiffness of the second coil spring and the deformation displacement amplitude. It can be seen from the figure that the vertical average equivalent stiffness of the second coil spring changes (decreases) as the spring deformation displacement amplitude changes (increases). In the present invention, the vertical average equivalent stiffness of the second coil spring (the geometric shape of the spring is a cylindrical coil spring) usually decreases as the spring deformation displacement amplitude increases. Relative to the initial equilibrium position, when the deformation displacement amplitude approaches 0, the vertical average equivalent stiffness of the second coil spring has a maximum value; when the deformation displacement amplitude approaches the limit displacement amplitude, the vertical average equivalent stiffness of the second coil spring has a minimum value. Therefore, in the deformation working state, the vertical average equivalent stiffness of the second coil spring is variable and adjustable, and its size is between the minimum and maximum values ​​of the vertical average equivalent stiffness.

[0025] In the present invention, in the spring assembly with damping characteristics, the first coil spring and the second coil spring can be arranged in parallel, in series, or in a mixed manner of series and parallel.

[0026] The present invention defines that: when the first coil spring and the second coil spring are arranged in parallel, Figure 7 As shown, in the deformed working state, the product (nK) of the number of first coil springs n and their vertical stiffness K in the spring assembly is not greater than the number of second coil springs n d Its vertical average equivalent stiffness The product of 3 times of The purpose of the above limitation is to ensure that the maximum static loss factor of the spring assembly and the vibration reduction and isolation device composed of the spring assembly is not less than 1.5%. When the product of the number of roots n of the first coil spring and its vertical stiffness K is greater than the number of roots n of the second coil spring d Its vertical average equivalent stiffness The maximum static loss factor of the spring assembly consisting of the first coil spring and the second coil spring will be less than 1.5%. Here, the vertical average equivalent stiffness of the second coil spring is Related to the deformation displacement amplitude of the second coil spring.

[0027] When the first coil spring and the second coil spring are arranged in series, Figure 8As shown, the spring assembly has a two-layer or multi-layer structure, each layer only contains the same type of coil springs (i.e., the first coil spring or the second coil spring), and the vibration load is transmitted between the first coil spring layer and the second coil spring layer through the interlayer support transition plate. The present invention stipulates that in the deformed working state, in any two adjacent layers of the spring assembly, the product (nK) of the number of first coil springs n and their vertical stiffness K is not less than the number of second coil springs n d Its vertical average equivalent stiffness The product of 1 / 3 times of The purpose of the above limitation is to ensure that the maximum static loss factor of the spring assembly and the vibration reduction and isolation device composed of the spring assembly is not less than 1.5%. When the product of the number of roots n of the first coil spring and its vertical stiffness K is less than the number of roots n of the second coil spring d Its vertical average equivalent stiffness The maximum static loss factor of the spring assembly consisting of the first coil spring and the second coil spring will be less than 1.5%. Similarly, here, the vertical average equivalent stiffness of the second coil spring is Related to the deformation displacement amplitude of the second coil spring.

[0028] When the first coil spring and the second coil spring are arranged in a series-parallel hybrid manner, such as Fig. 9 As shown, the spring assembly has a two-layer or multi-layer structure, and the vibration load is transmitted between the layers through the interlayer support transition plate. Each layer structure can contain the first coil spring and the second coil spring at the same time. When one layer of the adjacent two-layer structure contains only the first coil spring and the other layer contains only the second coil spring, this type of structure degenerates into a series arrangement between the first coil spring and the second coil spring. In any adjacent two-layer structure, one layer contains n1 first coil springs and n d,1 The second coil springs, and the other layer contains n2 first coil springs and n d,2 The second coil spring; the vertical stiffness of the first coil spring is K, and the vertical average equivalent stiffness of the second coil spring is In the deformed working state, any two adjacent layers of the spring assembly arranged in a series-parallel hybrid manner must meet the following requirements:

[0029] in, When n1, n2 of any two adjacent layers of the spring assembly d,1 、n2、n d,2 and K, satisfy Then the maximum static loss factor of the spring assembly arranged in the hybrid manner will be less than 1.5%. Similarly, here, the vertical average equivalent stiffness of the second coil spring is Related to the deformation displacement amplitude of the second coil spring.

[0030] The present invention further specifies the microstructure and chemical composition of the two types of spiral spring materials.

[0031] In some embodiments of the present invention, the microstructure of the material of the first coil spring is mainly tempered martensite, and the remaining structures are one or more of carbide, bainite and retained austenite. The above microstructure helps the mechanical properties of the material of the first coil spring to meet the following requirements: yield strength ≥ 800MPa, tensile strength ≥ 1000MPa. In particular, when the material of the first coil spring also contains bainite or retained austenite, the material of the first coil spring has good elongation after fracture, cross-sectional shrinkage and fatigue failure resistance.

[0032] In order to make the material of the first coil spring have the above-mentioned microstructure and mechanical properties, it is further stipulated that the mass percentage of the chemical composition of the material of the first coil spring is: 0.4%≤C≤1.0%, Mn≤2.0%, 0.1%≤Si≤2.5%, Cr≤3.0%, V≤0.6%, Mo≤0.5%, Ni≤2.0%, Cu≤0.4%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest is Fe and inevitable impurity elements. Preferably, the mass percentage of the chemical composition of the material of the first coil spring can be limited to: 0.4%≤C≤0.7%, Mn≤1.6%, 0.8%≤Si≤2.2%, Cr≤1.5%, V≤0.3%, Mo≤0.3%, Ni≤1.0%, Cu≤0.25%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest is Fe and inevitable impurity elements. Based on the above preferred components, the material of the first coil spring can mainly contain tempered martensite and residual austenite, or mainly contain tempered martensite, residual austenite and bainite, so as to significantly improve the toughness and fatigue resistance of the first coil spring material. For the above preferred components, the mechanical properties of the first coil spring can reach: yield strength ≥1400MPa, tensile strength ≥1650MPa, elongation after fracture ≥8%, and cross-sectional shrinkage ≥25%. Under the premise of not changing the above microstructure, the material of the first coil spring can also contain a small amount of Al element. The present invention limits the mass percentage of Al element content to Al≤2.0%.

[0033] In addition, when the material of the first coil spring has the above chemical composition and microstructure characteristics, and the geometric shape of the spring is a cylindrical coil spring, the vertical stiffness of the first coil spring is usually a fixed value, that is, the vertical stiffness of the spring does not change with the change of the deformation displacement of the spring.

[0034] In some embodiments of the present invention, the microstructure of the material of the second coil spring is mainly ε martensite and austenite, and may also contain α′ martensite or carbide, wherein the volume proportion of ε martensite in the whole structure is not less than 75%. The above-mentioned microstructure helps the mechanical properties of the material of the second coil spring to meet the following requirements: yield strength ≥ 250MPa, tensile strength ≥ 350MPa, elongation after fracture ≥ 14%, and cross-sectional shrinkage ≥ 20%. There are stacking faults inside the ε martensite and austenite, and there is a phase interface between the two phases of ε martensite and austenite. Under the action of vibration elastic strain, the stacking faults and the phase interface move, thereby dissipating vibration energy and giving the spring material damping characteristics. A small volume content of ε martensite makes it difficult for the spring material to have good damping properties. The present invention stipulates that the damping properties of the material of the second coil spring meet the following requirements: at room temperature and 4×10 -4 The loss factor under strain amplitude condition is greater than 2.0%, and the loss factor increases with the increase of elastic strain amplitude.

[0035] In order to make the material of the second coil spring have the above-mentioned microstructure, mechanical properties and damping properties, the present invention further stipulates that the mass percentage of the chemical composition of the material of the second coil spring is: C≤0.2%, 15.0%≤Mn≤20.0%, Cr≤3.0%, Ti≤0.4%, Nb≤0.8%, V≤0.6%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest is Fe and inevitable impurity elements. Considering the two factors of material cost and performance, the mass percentage of the chemical composition of the material of the second coil spring is preferably: C≤0.1%, 16.5%≤Mn≤19.0%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest is Fe and inevitable impurity elements.

[0036] The material of the second coil spring has the above-mentioned chemical composition, microstructure characteristics and damping characteristics, which helps to make the maximum static loss factor of the second coil spring not less than 6.0%; and the second coil spring has a vertical variable stiffness characteristic, that is, relative to the initial equilibrium position, the vertical stiffness of the spring changes with the change of the spring deformation displacement amplitude. In the present invention, the inherent characteristics of the material of the second coil spring enable the second coil spring to have a vertical variable stiffness characteristic.

[0037] In the present invention, the elastic modulus of the material of the first coil spring of the spring assembly is usually greater than the elastic modulus of the material of the second coil spring. The above property of the material of the first coil spring, combined with its high yield strength characteristics, helps to significantly improve the load-bearing capacity of the first coil spring in the spring assembly.

[0038] In one embodiment of the present invention, all the coil springs in the spring assembly including the first coil spring and the second coil spring are coated in a polymer elastomer to form a coil spring-polymer elastomer composite spring assembly, such as Fig.10 As shown; or, a part of the coil springs in the spring assembly are coated in a polymer elastomer to form a partial composite spring assembly of the coil spring-polymer elastomer, such as Fig.11 As shown. In addition to the second coil spring, the polymer elastomer has damping properties, which enables the composite spring assembly or part of the composite spring assembly to have better damping properties and the ability to dissipate external vibration energy. However, the polymer elastomer cannot significantly improve the vertical stiffness of the composite spring assembly or part of the composite spring assembly. Fig.10 and Fig.11 In the example, the first coil spring and the second coil spring are arranged in parallel.

[0039] In the spring assembly of the present invention, the first coil spring mainly plays the role of bearing and providing stiffness; the second coil spring has good damping characteristics, mainly plays the role of dissipating vibration energy and providing stiffness, and the second coil spring also plays the role of appropriate bearing. Therefore, the spring assembly of the present invention can play a good role in bearing, providing stiffness and reducing vibration isolation. In addition, all the above technical solutions of the present invention are applicable to coil springs with different structural characteristics, including cylindrical coil springs and variable diameter coil springs (the cross-section of the spring changes along the axial direction). When the first coil spring is a cylindrical coil spring, the stiffness of the first coil spring is usually a fixed value; and when the first coil spring is a variable diameter coil spring, the first coil spring also has a variable stiffness characteristic. When the second coil spring is a cylindrical coil spring, the variable stiffness characteristic of the second coil spring only comes from the material itself; and when the second coil spring is a variable diameter coil spring, the variable stiffness characteristic of the second coil spring comes from both the material itself and the structural design.

[0040] In the present invention, the spring assembly is composed of two types of coil springs, a first coil spring and a second coil spring. The stiffness of the first coil spring is usually a fixed value, and the stiffness of the second coil spring shows a changing trend due to the damping characteristics of the spring material (the stiffness of the second coil spring decreases as the deformation displacement increases). The combined use of two types of coil springs can easily adjust the stiffness of the spring assembly, and the stiffness of the spring assembly does not fail to meet its required stiffness range (less than the required stiffness of the spring assembly) due to excessive changes (reductions) in the stiffness of the second coil spring. Therefore, a notable feature of the present invention's combined use of two types of coil springs is that, in addition to damping performance, the spring assembly not only has a variable stiffness characteristic, but also the stiffness of the spring assembly is easy to adjust and control within the required stiffness range. This feature is particularly effective for applications where the spring assembly and the vibration isolation device are placed in a limited space.

[0041] A second aspect of the present invention provides a vibration reduction and isolation device consisting of a spring assembly having damping characteristics.

[0042] The vibration reduction and isolation device is composed of four parts: a spring assembly with damping characteristics (or a composite spring assembly, or a partial composite spring assembly), a top seat and a base assembly, an adjusting bolt assembly, and a limit ring. The spring assembly with damping characteristics (or a composite spring assembly, or a partial composite spring assembly) is the core component of the vibration reduction and isolation device, which plays the role of bearing and providing stiffness, weakening (attenuating) and isolating vibration. Figure 7 The spring assembly shown, Figure 8 The adjacent two-layer structure of the spring assembly shown (or the spring assembly having a two-layer structure), Fig. 9 The adjacent two-layer structure of the spring assembly shown (or the spring assembly with a two-layer structure) respectively provides three arrangements of the first coil spring and the second coil spring in parallel, in series, and in series-parallel. Fig.12 and Fig.13 Taking the vibration reduction and isolation device as an example, the functions of the top and base components, the adjusting bolt components and the limiting ring components are introduced.

[0043] Fig.12 The figure shows a schematic diagram of a vibration reduction and isolation device consisting of a parallel spring assembly. Fig.13 The figure shows the structural disassembly diagram of the above-mentioned vibration reduction and isolation device. As can be seen from the figure, the top seat and base assembly includes a top seat and a base. The top seat is connected to the upper structure (such as a building, a bridge, a motor, a mechanical structure, etc.) and directly supports the weight of the upper structure; the base is connected to the supporting foundation. For active vibration isolation scenarios (the upper structure is the excitation vibration source), the top seat is used to transfer vibration loads and energy; while for passive vibration isolation scenarios (there is vibration in the supporting foundation), the base is used to transfer vibration loads and energy. The adjustment bolt assembly is used to adjust the initial equilibrium position (initial height) of the spring assembly when it is used. It mainly includes bolts, nuts and flat washers. The limit ring is used to establish the initial horizontal position of the first coil spring and the second coil spring and prevent the spring assembly from losing its stable state (or tilting excessively) during operation. The limit ring can be welded to the top seat and base assembly of the vibration reduction and isolation device, or it can be fixed to the top seat and base assembly with screws. The outer diameter of the limit ring should be slightly smaller than the inner diameter of the first coil spring and the second coil spring so that the limit ring can be smoothly placed in the inner diameter of the first coil spring and the second coil spring. The bolts in the adjusting bolt assembly pass through the limiting ring and the top seat and the base, and a gap is left between the bolt and the limiting ring (the outer diameter of the bolt is smaller than the inner diameter of the limiting ring), so that the top seat and the base of the vibration reduction and isolation device can move relative to each other in any direction in the horizontal plane, providing horizontal rigidity.

[0044] Fig.14 Shown is a schematic diagram of a vibration reduction and isolation device consisting of a series spring assembly. Fig.15The schematic diagram of the vibration reduction and isolation device composed of series-parallel spring components is shown. The vibration reduction and isolation device of the present invention has vertical and horizontal stiffness and plays a three-dimensional vibration isolation effect.

[0045] In the present invention, the damping and stiffness characteristics of the spring assembly enable the vibration reduction and isolation device to have a maximum static loss factor of not less than 1.5% and a variable stiffness characteristic.

[0046] The third aspect of the present invention provides the application of a vibration reduction and isolation device with damping characteristics. The vibration reduction and isolation device is used in the fields of buildings, bridges, mechanical supports, etc., and plays the role of energy dissipation, vibration reduction and vibration isolation.

[0047] Compared with the prior art, the present invention has the following beneficial effects:

[0048] 1) Compared with traditional springs and their isolators, the spring assembly and vibration reduction and isolation device of the present invention have damping and variable stiffness characteristics, which can simultaneously attenuate and isolate vibrations, and are particularly effective in isolating wide-band vibration excitations (vibration excitations in actual working scenarios usually have wide-band characteristics). Traditional springs can only instantaneously buffer mechanical vibrations and isolate vibrations, but cannot reduce mechanical vibration energy; and, they have the characteristics of fixed stiffness (when the coil spring is a cylindrical coil spring), and can only isolate vibration excitations of a certain frequency.

[0049] 2) Compared with the traditional combination of a spring and a viscous damper or a spring and an eddy current damper, the spring assembly and the vibration isolation device of the present invention have excellent properties such as high stiffness (the second coil spring can provide stiffness, while the viscous damper and the eddy current damper cannot provide stiffness), smaller installation space, lower own cost and maintenance cost, not easy to be damaged (the viscous damper has the risk of damping fluid leakage, and the magnetic steel sheet in the eddy current damper is easy to break), and variable stiffness.

[0050] 3) The spring assembly of the present invention uses a first coil spring and a second coil spring in combination, and the spring assembly not only has a variable stiffness characteristic, but also the stiffness of the spring assembly is easy to adjust and control within the required stiffness range. Compared with a spring assembly consisting only of a second coil spring, the second coil spring and its spring assembly may have an excessive change in stiffness (reduction) so that the stiffness of the spring assembly is not within the required use stiffness range (less than the required use stiffness of the spring assembly). In addition, the spring assembly of the present invention can have a greater load-bearing capacity than a spring assembly consisting only of a second coil spring.

[0051] 4) The spring assembly and spring vibration isolation device of the present invention meet the requirements of rapid installation and replacement on site. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] Figure 1 The relationship between the material loss factor of the second coil spring and the elastic strain amplitude at room temperature is illustrated.

[0053] Figure 2 The figure is a schematic diagram of the force-displacement curve of the second coil spring with damping characteristics in a vertical loading-unloading cycle. From the figure, the static loss factor and vertical average equivalent stiffness of the second coil spring under given deformation displacement amplitude can be calculated.

[0054] Figure 3 The force-displacement curve of the first coil spring in a vertical loading-unloading cycle in Example 1 (the coil spring is a cylindrical coil spring). The force-displacement of the first coil spring is linear, and the slope of the force-displacement line is the vertical stiffness of the first coil spring.

[0055] Figure 4 1 is the force-displacement curve of the vertical loading-unloading cycle of the second coil spring under different deformation displacement amplitude conditions in Example 2 (the coil spring is a cylindrical coil spring). The figure shows the force-displacement curve of the vertical loading-unloading cycle under three deformation displacement amplitude conditions.

[0056] Figure 5 for Figure 4 The relationship between the static loss factor of the second coil spring and the deformation displacement amplitude.

[0057] Figure 6 for Figure 4 The relationship between the vertical average equivalent stiffness of the second coil spring and the deformation displacement amplitude.

[0058] Figure 7 The diagram is a schematic diagram of a spring assembly in which a first coil spring and a second coil spring are arranged in parallel.

[0059] Figure 8 The diagram is a schematic diagram of a spring assembly having two adjacent layers, wherein the first coil spring and the second coil spring are arranged in series. When the spring assembly has only two layers, the diagram is a schematic diagram of a spring assembly having the first coil spring and the second coil spring arranged in series.

[0060] Fig. 9 The diagram is a schematic diagram of a spring assembly having two adjacent layers in which a first coil spring and a second coil spring are arranged in a mixed manner in series and parallel. When the spring assembly has only two layers, the diagram is a schematic diagram of a spring assembly having a first coil spring and a second coil spring arranged in a mixed manner in series and parallel.

[0061] Fig.10 Schematic diagram of a spring assembly of a composite body of a coil spring and a polymer elastomer, wherein the first coil spring and the second coil spring are arranged in parallel.

[0062] Fig.11The schematic diagram of the spring assembly of a partial composite of a coil spring and a polymer elastomer is shown in FIG. In the figure, the first coil spring and the second coil spring are arranged in parallel.

[0063] Fig.12 It is a schematic diagram of a vibration reduction and isolation device composed of a parallel spring assembly.

[0064] Fig.13 for Fig.12 The structural disassembly diagram of the vibration reduction and isolation device is shown.

[0065] Fig.14 It is a schematic diagram of a vibration reduction and isolation device composed of a series spring assembly.

[0066] Fig.15 It is a schematic diagram of a vibration reduction and isolation device composed of series-parallel spring assemblies.

[0067] Fig.16 This is the microstructure of the first coil spring material in Example 2.

[0068] Fig.17 This is the microstructure of the second coil spring material in Example 2.

[0069] Numbers in the figure: 1. first coil spring; 2. second coil spring; 3. parallel spring assembly; 4. interlayer support transition plate; 5. series spring assembly; 6. series-parallel spring assembly; 7. polymer elastomer; 8. composite spring assembly; 9. partial composite spring assembly; 10. first vibration reduction and isolation device; 11. top seat and base assembly; 111. top seat; 112. base; 12. adjusting bolt assembly; 121. bolt; 122. nut; 123. flat washer; 13. limiting ring; 14. second vibration reduction and isolation device; 15. third vibration reduction and isolation device. DETAILED DESCRIPTION

[0070] The present invention is described in detail below with reference to the accompanying drawings and specific embodiments.

[0071] Embodiment 1:

[0072] A vibration reduction and isolation device with damping characteristics, namely a first vibration reduction and isolation device 10, is composed of four parts: a parallel spring component 3 with damping characteristics, a top seat and a base component 11, an adjusting bolt component 12, and a limiting ring 13. Fig.12 shown. Fig.13The structure disassembly diagram of the vibration reduction and isolation device 10 is shown. The top and base assembly 11 includes a top 111 and a base 112. The top 111 is connected to the upper structure (such as a building, a bridge, a motor, a mechanical structure, etc.) and directly supports the weight of the upper structure; the base 112 is connected to the supporting foundation. For active vibration isolation scenarios (the upper structure is the excitation vibration source), the top 111 is used to transfer vibration loads and energy; while for passive vibration isolation scenarios (there is vibration in the supporting foundation), the base 112 is used to transfer vibration loads and energy. The adjusting bolt assembly 12 is used to adjust the initial equilibrium position (initial height) of the spring assembly when it is used. It mainly includes a bolt 121, a nut 122 and a flat washer 123. The limiting ring 13 is used to establish the initial horizontal position of the first coil spring 1 and the second coil spring 2 and prevent the spring assembly from losing its stable state (or excessive tilt) during operation. The limiting ring 13 can be welded to the top and base assembly of the vibration reduction and isolation device, or it can be fixed to the top and base assembly with screws. The outer diameter of the limiting ring 13 is slightly smaller than the inner diameter of the first coil spring 1 and the second coil spring 2, so that the limiting ring 13 can be smoothly placed in the inner diameter of the first coil spring 1 and the second coil spring 2. The bolt 121 in the adjusting bolt assembly 12 passes through the limiting ring 13 and the top seat 111 and the base 112, and a gap is left between the bolt 121 and the limiting ring 13 (the outer diameter of the bolt 121 is smaller than the inner diameter of the limiting ring 13), so that the top seat 111 and the base 112 of the vibration reduction and isolation device can move relative to each other in any direction on the horizontal plane to provide horizontal rigidity.

[0073] In this embodiment, the spring component with damping characteristics is a parallel spring component 3, such as Figure 7 As shown, the parallel spring assembly 3 is composed of 1 first coil spring and 4 second coil springs (the first coil spring 1 and the second coil spring 2 are both cylindrical coil springs); the first coil spring 1 and the second coil spring 2 have the same free height, the central axes of the first coil spring 1 and the second coil spring 2 are parallel to each other, and the two types of coil springs are arranged in parallel. The two types of coil springs have the same geometric shape, with a wire diameter of 12 mm, a middle diameter of 80 mm, a free height of 110 mm, and 5 effective turns.

[0074] The mass percentage of the chemical composition of the material of the first coil spring 1 is: 0.68% C, 0.72% Mn, 0.2% Si, 0.15% Cr, 0.02% P, 0.01% S, 0.01% N, and the rest is Fe and inevitable impurity elements. The mechanical properties of the material of the first coil spring 1 are: yield strength of 845MPa, tensile strength of 1120MPa, elongation after fracture of 10.5%, and cross-sectional reduction of 37%. The microstructure of the material of the first coil spring 1 is mainly tempered martensite structure, and also contains fine carbides.

[0075] The chemical composition of the material of the second coil spring 2 is as follows: 0.02% C, 18.5% Mn, 0.018% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the second coil spring 2 are as follows: yield strength is about 420MPa, tensile strength is about 645MPa, elongation after fracture is 34%, and cross-sectional shrinkage is 48%. The damping performance of the material of the second coil spring 2 is as follows: at room temperature and 4×10 -4 The loss factor under strain amplitude condition is about 2.8%, and the loss factor increases with the increase of elastic strain amplitude. The microstructure of the material of the second coil spring 2 is mainly ε martensite and austenite, which also contains a small amount of α′ martensite, and the volume proportion of ε martensite in the whole structure is about 83%.

[0076] The elastic modulus of the material of the first coil spring 1 (about 205 GPa) is greater than the elastic modulus of the material of the second coil spring 2 (usually less than 185 GPa).

[0077] Figure 3 The force-displacement curve of the first coil spring in a vertical loading-unloading cycle is shown in FIG. The force-displacement of the first coil spring is linear, and the slope of the force-displacement line is the vertical stiffness of the first coil spring, which is about 72 N / mm.

[0078] The second coil spring has at least a vertical variable stiffness characteristic. From the force-displacement curve of the vertical loading-unloading cycle, it is calculated that the maximum vertical average equivalent stiffness of the second coil spring is about 58 N / mm and the minimum vertical average equivalent stiffness is about 46 N / mm. The maximum static loss factor of the second coil spring is not less than 7.0%.

[0079] In the deformed working state, the product of the number of first coil springs n (n = 1) and its vertical stiffness K (K = 72N / mm) in the parallel spring assembly is less than the number of second coil springs n d (n d =4) and its vertical average equivalent stiffness ( 3 times the product of 58N / mm to 46N / mm, that is The maximum static loss factor of the spring assembly is measured to be no less than 5.0%, and the spring assembly exhibits vertically variable stiffness characteristics.

[0080] Accordingly, the vibration reduction and isolation device has a maximum static loss factor of not less than 5.0% and a vertical variable stiffness characteristic.

[0081] Embodiment 2:

[0082] A vibration reduction and isolation device with damping characteristics, namely a first vibration reduction and isolation device 10, is composed of four parts: a parallel spring assembly 3, a top seat and a base assembly 11, an adjusting bolt assembly 12, and a limiting ring 13. Fig.12 and Fig.13 shown.

[0083] The spring assembly with damping characteristics described in this embodiment is a parallel spring assembly 3, which is composed of 2 first coil springs 1 and 4 second coil springs 2 (the first coil springs 1 and the second coil springs 2 are both cylindrical coil springs); the first coil springs 1 and the second coil springs 2 have the same free height, the central axes of the first coil springs 1 and the second coil springs are parallel to each other, and the two types of coil springs are arranged in parallel. The geometric shape of the first coil spring 1: the wire diameter of the spring is 16mm, the middle diameter is 85mm, the free height is 160mm, and the effective number of turns is 6. The geometric shape of the second coil spring 2: the wire diameter of the spring is 14mm, the middle diameter is 60mm, the free height is 160mm, and the effective number of turns is 5.

[0084] The mass percentage of the chemical composition of the material of the first coil spring 1 is: 0.61% C, 0.9% Mn, 1.95% Si, 0.25% Cr, 0.025% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the first coil spring 1 are: yield strength of 1540MPa, tensile strength of 1720MPa, elongation after fracture of 11.0%, and cross-sectional reduction of 39%. The microstructure of the material of the first coil spring 1 is mainly tempered martensite structure, and also contains residual austenite accounting for about 10% by volume, such as Fig.16 shown.

[0085] The chemical composition of the material of the second coil spring 2 is as follows: 0.003% C, 17.8% Mn, 0.015% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the second coil spring 2 are: yield strength of about 460MPa, tensile strength of about 650MPa, elongation after fracture of 37%, and reduction of cross-sectional area of ​​52%. The loss factor of the material of the second coil spring 2 increases with the increase of elastic strain amplitude; at room temperature and 4×10 -4 The loss factor under the strain amplitude condition is about 3%. The microstructure of the material of the second coil spring 2 is mainly ε martensite and austenite, which also contains a small amount of α′ martensite, and the volume proportion of ε martensite in the whole structure is about 86%. Fig.17 shown.

[0086] The elastic modulus of the material of the first coil spring 1 is greater than the elastic modulus of the material of the second coil spring 2 .

[0087] From the force-displacement curve of the vertical loading-unloading cycle, it can be obtained that the vertical stiffness of the first coil spring 1 is about 185 N / mm.

[0088] Figure 4 The figure shows the force-displacement curve of the second coil spring 2 under different deformation displacement amplitudes in the vertical loading-unloading cycle. It can be seen from the figure that the second coil spring 2 has a vertical variable stiffness characteristic. From the force-displacement curve of the vertical loading-unloading cycle, the relationship between the static loss factor of the second coil spring 2 and the deformation displacement amplitude is calculated ( Figure 5 ) and the relationship between the vertical average equivalent stiffness and the deformation displacement amplitude ( Figure 6 ). The maximum static loss factor of the second coil spring 2 is not less than 8.0%. The maximum vertical average equivalent stiffness of the second coil spring 2 is about 220N / mm, and the minimum vertical average equivalent stiffness is about 160N / mm.

[0089] In the deformed working state, the product of the number n (n=2) of the first coil spring 1 in the parallel spring assembly 3 and its vertical stiffness K (K=185N / mm) is less than the number n of the second coil spring 2. d (n d =4) and its vertical average equivalent stiffness ( 3 times the product of (between 160N / mm and 220N / mm), that is, The maximum static loss factor of the spring assembly is measured to be no less than 5.0%, and the spring assembly exhibits vertically variable stiffness characteristics.

[0090] Accordingly, the vibration reduction and isolation device has a maximum static loss factor of not less than 5.0% and a vertical variable stiffness characteristic.

[0091] Embodiment 3:

[0092] The vibration reduction and isolation device with damping characteristics, i.e., the second vibration reduction and isolation device 14, is composed of four parts: a series spring assembly 5, a top seat and a base assembly 11, an adjusting bolt assembly 12, and a limiting ring 13. The vibration reduction and isolation device with damping characteristics is as follows: Fig.14 shown.

[0093] In this embodiment, the structures of the top and base assembly 11, the adjusting bolt assembly 12, and the limiting ring 13 refer to Example 1. The difference between this vibration reduction and isolation device and Example 1 is that the vibration reduction and isolation device of this embodiment adopts a series spring assembly 5.

[0094] like Figure 8As shown, the spring assembly with damping characteristics (series spring assembly 5) includes a two-layer structure, namely a first coil spring layer composed of four first coil springs 1 and a second coil spring layer composed of four second coil springs 2 (the first coil spring and the second coil spring are both cylindrical coil springs), and the vibration load is transmitted between the first coil spring layer and the second coil spring layer through an interlayer support transition plate 4. The central axes of the first coil spring 1 and the second coil spring 2 are parallel to each other, and the two types of coil springs are arranged in series.

[0095] The mass percentage of the chemical composition of the material of the first coil spring 1 is: 0.46% C, 0.8% Mn, 0.22% Si, 0.85% Cr, 0.15% Ni, 0.15% V, 0.012% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the first coil spring 1 are: yield strength of 1300MPa, tensile strength of 1480MPa, elongation after fracture of 11.5%, and cross-sectional reduction of 40%. The microstructure of the material of the first coil spring 1 is mainly tempered martensite structure, and also contains a small amount of carbide.

[0096] The second coil spring 2 is the same as the second coil spring in Example 2. The mass percentage of the chemical composition of the material of the second coil spring 2 is: 0.003% C, 17.8% Mn, 0.015% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the second coil spring 2 are: yield strength of about 460MPa, tensile strength of about 650MPa, elongation after fracture of 37%, and cross-sectional shrinkage of 52%. The loss factor of the material of the second coil spring 2 increases with the increase of elastic strain amplitude; at room temperature and 4×10 -4 The loss factor under the strain amplitude condition is about 3%. The microstructure of the material of the second coil spring is mainly ε martensite and austenite, which also contains a small amount of α′ martensite, and the volume proportion of ε martensite in the whole structure is about 86%.

[0097] The elastic modulus of the material of the first coil spring 1 is greater than the elastic modulus of the material of the second coil spring 2 .

[0098] The vertical stiffness of the first coil spring 1 is about 130N / mm. The static loss factor of the second coil spring 2 increases with the increase of the deformation displacement amplitude, and the maximum static loss factor is not less than 8.0%. The vertical average equivalent stiffness of the second coil spring 2 decreases with the increase of the deformation displacement amplitude, and its maximum vertical average equivalent stiffness is about 220N / mm and the minimum vertical average equivalent stiffness is about 160N / mm.

[0099] In the deformed working state, the product of the number n (n=4) of the first coil spring 1 in the series spring assembly 5 and its vertical stiffness K (K=130N / mm) is not less than the number n of the second coil spring 2. d (n d =4) and its vertical average equivalent stiffness ( 1 / 3 times the product of (between 160N / mm and 220N / mm), that is, The maximum static loss factor of the spring assembly is measured to be no less than 3.0%, and the spring assembly exhibits vertically variable stiffness characteristics.

[0100] Accordingly, the vibration reduction and isolation device has a maximum static loss factor of not less than 3.0% and a vertical variable stiffness characteristic.

[0101] Embodiment 4:

[0102] The vibration reduction and isolation device with damping characteristics, i.e., the third vibration reduction and isolation device 15, is composed of four parts: a spring assembly with damping characteristics (i.e., a series-parallel spring assembly 6), a top seat and a base assembly 11, an adjusting bolt assembly 12, and a limiting ring 13. Fig.15 shown.

[0103] In this embodiment, the structures of the top and base assembly 11, the adjusting bolt assembly 12, and the limiting ring 13 refer to Example 1. The difference between this vibration reduction and isolation device and Example 1 is that the vibration reduction and isolation device of this embodiment adopts a series-parallel spring assembly 6.

[0104] refer to Fig. 9 In the series-parallel spring assembly 6, the first coil spring 1 and the second coil spring 2 are arranged in a series-parallel hybrid manner, the central axes of the first coil spring 1 and the second coil spring 2 are parallel to each other (the first coil spring 1 and the second coil spring 2 are both cylindrical coil springs), and the first coil spring 1 and the second coil spring 2 have the same free height. The series-parallel spring assembly 6 has a two-layer structure, and the vibration load is transmitted between the layers through the interlayer support transition plate 4; a layer structure includes n1 first coil springs 1 and n d,1 The second coil springs 2, and the other layer contains n2 first coil springs 1 and n d,2 A second coil spring 2. Fig. 9 In the spring assembly shown, one layer of the structure includes four second coil springs 2, while the other layer includes four first coil springs 1 and two second coil springs 2.

[0105] In this embodiment, the mass percentage of the chemical composition of the material of the first coil spring 1 is: 0.62% C, 0.7% Mn, 1.7% Si, 1.1% Cr, 0.15% V, 0.01% P, 0.008% S, 0.006% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the first coil spring 1 are: yield strength of 1740MPa, tensile strength of 2060MPa, elongation after fracture of 11.0%, and cross-sectional reduction of 39%. The microstructure of the material of the first coil spring 1 is mainly tempered martensite, and also contains residual austenite, bainite and a small amount of carbide.

[0106] The chemical composition of the material of the second coil spring 2 is as follows: 0.09% C, 17.5% Mn, 0.35% Nb, 0.01% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the second coil spring 2 are: yield strength of about 520MPa, tensile strength of about 735MPa, elongation after fracture of 24%, and cross-sectional shrinkage of 40%. The loss factor of the material of the second coil spring 2 increases with the increase of elastic strain amplitude; at room temperature and 4×10 -4 The loss factor under strain amplitude condition is about 2.5%. The microstructure of the material of the second coil spring 2 is mainly ε martensite and austenite, which also contains a small amount of α′ martensite and carbide, wherein the volume proportion of ε martensite in the whole structure is about 85%.

[0107] The elastic modulus of the material of the first coil spring 1 is greater than the elastic modulus of the material of the second coil spring 2 .

[0108] From the force-displacement curve of the vertical loading-unloading cycle, it is found that the vertical stiffness of the first coil spring 1 is a fixed value, which is about 180 N / mm.

[0109] From the force-displacement curve of the vertical loading-unloading cycle of the second coil spring 2 under different deformation displacement amplitudes, it can be obtained that: the static loss factor of the second coil spring 2 increases with the increase of the deformation displacement amplitude, and the maximum static loss factor is not less than 6.5%; the vertical average equivalent stiffness of the second coil spring 2 decreases with the increase of the deformation displacement amplitude, and its maximum vertical average equivalent stiffness is about 145N / mm, and the minimum vertical average equivalent stiffness is about 115N / mm.

[0110] In the deformed working state, the number of first coil springs 1 and second coil springs 2 in each layer of the spring assembly is n1 (n1 = 0), n d,1 (n d,1 =4), n2(n2=4), n d,2 (n d,2=2) and the vertical stiffness K of the first coil spring 1 (K = 180 N / mm), the vertical average equivalent stiffness of the second coil spring 2 Calculate Further calculation Less than 0.8, satisfying This is a necessary condition. The maximum static loss factor of the spring assembly is measured to be not less than 3.5%, and the spring assembly shows a vertical variable stiffness characteristic.

[0111] Accordingly, the vibration reduction and isolation device has a maximum static loss factor of not less than 3.5% and a vertical variable stiffness characteristic.

[0112] Embodiment 5:

[0113] A vibration reduction and isolation device with damping characteristics, reference Fig.12 and Fig.13 It is composed of four parts: a parallel spring component 3 with damping characteristics, a top seat and base component 11, an adjusting bolt component 12, and a limiting ring 13. The structures of the top seat and base component 11, the adjusting bolt component 12, and the limiting ring 13 refer to Example 1.

[0114] The parallel spring assembly 3 with damping characteristics is composed of two first coil springs 1 and one second coil spring 2 (the first coil spring 1 and the second coil spring 2 are both cylindrical coil springs); the first coil spring 1 and the second coil spring 2 have the same free height, the central axes of the first coil spring 1 and the second coil spring 2 are parallel, and the two types of coil springs are arranged in parallel.

[0115] The mass percentage of the chemical composition of the material of the first coil spring 1 is: 0.87% C, 0.7% Mn, 0.21% Si, 0.15% Cr, 0.12% Ni, 0.08% Cu, 0.015% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the first coil spring 1 are: yield strength of 1050MPa, tensile strength of 1220MPa, elongation after fracture of 10.0%, and cross-sectional reduction of 36%. The microstructure of the material of the first coil spring 1 is mainly tempered martensite structure, and also contains a small amount of carbide.

[0116] The chemical composition of the material of the second coil spring 2 is as follows: 0.003% C, 17.8% Mn, 0.015% P, 0.01% S, 0.01% N, and the rest is Fe and unavoidable impurity elements. The mechanical properties of the material of the second coil spring 2 are: yield strength of about 460MPa, tensile strength of about 650MPa, elongation after fracture of 37%, and reduction of cross-sectional area of ​​52%. The loss factor of the material of the second coil spring 2 increases with the increase of elastic strain amplitude; at room temperature and 4×10 -4 The loss factor under the strain amplitude condition is about 3%. The microstructure of the material of the second coil spring 2 is mainly ε martensite and austenite, which also contains a small amount of α′ martensite, and the volume proportion of ε martensite in the whole structure is about 86%.

[0117] The elastic modulus of the material of the first coil spring 1 is greater than the elastic modulus of the material of the second coil spring 2 .

[0118] The vertical stiffness of the first coil spring 1 is about 145N / mm. The second coil spring 2 has a vertical variable stiffness characteristic. From the force-displacement curve in the vertical loading-unloading cycle, it is calculated that the maximum static loss factor of the second coil spring 2 is not less than 8.0%; the maximum vertical average equivalent stiffness of the second coil spring 2 is about 220N / mm, and the minimum vertical average equivalent stiffness is about 160N / mm.

[0119] In the deformed working state, the product of the number n (n=2) of the first coil spring 1 in the parallel spring assembly 3 and its vertical stiffness K (K=145N / mm) is less than the number n of the second coil spring 2. d (n d =1) and its vertical average equivalent stiffness ( 3 times the product of (between 160N / mm and 220N / mm), that is, The maximum static loss factor of the parallel spring assembly 3 is measured to be no less than 2.5%, and the spring assembly exhibits a vertical variable stiffness characteristic.

[0120] Accordingly, the vibration reduction and isolation device has a maximum static loss factor of not less than 2.5% and a vertical variable stiffness characteristic.

[0121] Example 6

[0122] Different from the first embodiment, in the present embodiment, all the coil springs including the first coil spring 1 and the second coil spring 2 in the spring assembly are coated in the polymer elastomer 7 to form a coil spring-polymer elastomer composite spring assembly 8, such as Fig.10 shown.

[0123] In addition to the second coil spring, the polymer elastomer has damping properties, which enables the composite spring assembly 8 to have better damping properties and the ability to dissipate external vibration energy. However, the polymer elastomer cannot significantly improve the vertical stiffness of the composite spring assembly 8.

[0124] Example 7

[0125] Different from the first embodiment, in the present embodiment, some of the coil springs in the spring assembly are coated in the polymer elastomer 7 to form a partial composite spring assembly 9 of the coil spring and the polymer elastomer, such as Fig.11 shown.

[0126] In addition to the second coil spring, the polymer elastomer has damping properties, which enables the partial composite spring assembly 9 to have better damping properties and the ability to dissipate external vibration energy. However, the polymer elastomer cannot significantly improve the vertical stiffness of the partial composite spring assembly 9.

[0127] The above description of the embodiments is to facilitate the understanding and use of the invention by those skilled in the art. It is obvious that those skilled in the art can easily make various modifications to these embodiments and apply the general principles described herein to other embodiments without creative work. Therefore, the present invention is not limited to the above embodiments, and improvements and modifications made by those skilled in the art based on the disclosure of the present invention without departing from the scope of the present invention should be within the scope of protection of the present invention.

Claims

1. A spring assembly with damping characteristics, used in a vibration reduction and isolation device, plays a role in isolating vibration and reducing vibration energy transmission, characterized in that: The spring assembly with damping characteristics comprises at least a first coil spring and a second coil spring, wherein the central axes of the first coil spring and the second coil spring are parallel to or coincide with each other; The mechanical properties of the material of the first coil spring meet the following requirements: yield strength ≥ 800 MPa, tensile strength ≥ 1000 MPa, elongation after fracture ≥ 6%, and section shrinkage ≥ 20%; The mechanical properties of the material of the second coil spring meet the following requirements: yield strength ≥ 250 MPa, tensile strength ≥ 350 MPa, elongation after fracture ≥ 14%, and cross-sectional shrinkage ≥ 20%; the damping properties of the material of the second coil spring meet the following requirements: -4 The loss factor under strain amplitude conditions is greater than 2.0%, and the loss factor increases with the increase of elastic strain amplitude; The maximum static loss factor of the second coil spring is not less than 6.0%; the second coil spring has at least a vertical variable stiffness characteristic; In the spring assembly with damping characteristics, the first coil spring and the second coil spring are arranged in parallel, in series, or in a combination of series and parallel; The maximum static loss factor of the spring assembly is not less than 1.5%, and the spring assembly has at least a vertical variable stiffness characteristic.

2. The spring assembly with damping characteristics according to claim 1, characterized in that: When the first coil spring and the second coil spring are arranged in parallel, in the deformed working state, the product of the number n of the first coil springs in the spring assembly and their vertical stiffness K is not greater than the number n of the second coil springs. d Its vertical average equivalent stiffness 3 times the product of When the first coil spring and the second coil spring are arranged in series only, the spring assembly has a two-layer or multi-layer structure including a first coil spring layer and a second coil spring layer, and the vibration load is transmitted between the first coil spring layer and the second coil spring layer through an interlayer support transition plate; in the deformed working state, in any two adjacent layers of the spring assembly, the product of the number n of the first coil springs and their vertical stiffness K is not less than the number n of the second coil springs d Its vertical average equivalent stiffness 1 / 3 times the product of When the first coil spring and the second coil spring are arranged in a series-parallel hybrid manner, the spring assembly has a two-layer or multi-layer structure, and the vibration load is transmitted between the layers through the interlayer support transition plate; in any two adjacent layers of the spring assembly, one layer includes n1 first coil springs and n d,1 The second coil springs, and the other layer contains n2 first coil springs and n d,2 The second coil spring has a vertical stiffness of K, and the vertical average equivalent stiffness of the second coil spring is Under deformation working state, n1, n d,1 、n2、n d,2 and K, Need to meet: in, 3. The spring assembly with damping characteristics according to any one of claims 1 to 2, characterized in that: The microstructure of the material of the first coil spring is mainly tempered martensite, and the remaining microstructures are one or more of carbide, bainite and retained austenite.

4. The spring assembly with damping characteristics according to any one of claims 1 to 2, characterized in that: The microstructure of the material of the second coil spring is mainly ε martensite and austenite, and may further include α′ martensite or carbide, wherein the volume proportion of ε martensite in the whole structure is not less than 75%.

5. The spring assembly with damping characteristics according to claim 3, characterized in that: The mass percentage of the chemical composition of the material of the first coil spring is: 0.4%≤C≤1.0%, Mn≤2.0%, 0.1%≤Si≤2.5%, Cr≤3.0%, V≤0.6%, Mo≤0.5%, Ni≤2.0%, Cu≤0.4%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest are Fe and unavoidable impurity elements.

6. The spring assembly with damping characteristics according to claim 3, characterized in that: The mass percentage of the chemical composition of the material of the first coil spring is: 0.4%≤C≤0.7%, Mn≤1.6%, 0.8%≤Si≤2.2%, Cr≤1.5%, V≤0.3%, Mo≤0.3%, Ni≤1.0%, Cu≤0.25%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest are Fe and unavoidable impurity elements.

7. The spring assembly with damping characteristics according to claim 4, characterized in that: The chemical composition of the material of the second coil spring is in percentage by mass as follows: C≤0.2%, 15.0%≤Mn≤20.0%, Cr≤3.0%, Ti≤0.4%, Nb≤0.8%, V≤0.6%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest are Fe and unavoidable impurity elements.

8. The spring assembly with damping characteristics according to claim 4, characterized in that: The chemical composition of the material of the second coil spring is as follows in percentage by mass: C≤0.1%, 16.5%≤Mn≤19.0%, P≤0.045%, S≤0.03%, N≤0.03%, and the rest are Fe and unavoidable impurity elements.

9. The spring assembly with damping characteristics according to any one of claims 1 to 8, characterized in that: Part or all of the first coil springs or the second coil springs are wrapped in a polymer elastomer to form a partial composite spring assembly or a composite spring assembly of a coil spring-polymer elastomer.

10. A vibration reduction and isolation device, characterized in that: The vibration reduction and isolation device is composed of a spring assembly with damping characteristics as described in any one of claims 1-9, as well as a top seat and base assembly, an adjusting bolt assembly, and a limiting ring; the vibration reduction and isolation device has at least a vertical variable stiffness characteristic, and its maximum static loss factor is not less than 1.5%.

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